DE102011080647A1 - Bearing assembly for ship propulsion system, comprises tensioning unit that is provided for applying tension to bearing outer rings of outer ring, where outer ring raceways of outer ring are concentric with respect to bearing axis - Google Patents

Abstract

The bearing assembly has outer ring (AR) and inner ring (IR) comprising outer ring raceways (1,2) and inner ring raceways (3,4) which are concentric with respect to bearing axis (X) respectively. The rolling elements (5,6) are formed as barrel between outer ring and inner ring, which are concentric to rolling axis (X5,X6). The spherical centers (Z1,Z2) are congruent to bearing axis, so that the inner ring is tilted about tilt center (K), which coincides with spherical centers. A tensioning unit (T) is provided for applying tension to bearing outer rings (AR1,AR2) of outer ring.

Description

Field of the invention

The invention relates to a bearing assembly, in particular for a marine propulsion system, with an outer ring device whose inner wall forms a first and a second concave and concentric to a bearing axis, as well as this facing outer ring raceway, an inner ring means whose outer wall a first and a second concave and the Bearing axis concentric, but the bearing axis facing away from the inner ring raceway, rolling elements are housed in a Wälzkörperbahnraum formed between the outer ring means and the inner ring means and form a first Wälzkörperlaufreihe and axially spaced therefrom second Wälzkörperlaufreihe, wherein the rolling elements are designed as tons and one to a Wälzkörperachse concentric barrel shell whose curvature in axial section substantially corresponds to the curvature of the outer ring track in axial section and wherein the first and the second outer ring running surface in each case forms a spherical ring surface, the spherical surface centers are substantially congruent on the bearing axis, so that the inner ring means is tiltable about a tilting center, which substantially coincides with the spherical surface centers.

Such, generally referred to as spherical roller bearings bearing arrangements are widely used for the storage of waves and allow tilting of the inner ring to a lying on the bearing axis tilting center, thereby avoiding static overdeterminations and allowed for the power transfer unimportant displacements of the gear members, concentricity errors and elastic component deformations, or can be compensated.

Out DE 10 2009 052 954 A1 a spherical roller bearing is known in which a one-piece bearing inner ring and a one-piece bearing outer ring are provided, wherein in the bearing outer ring designed as a ball ring surface Wälzkörperlauffläche is formed, the ball center is located on the bearing axis. In the bearing outer ring arranged in two rows of rows spherical rollers are added, which roll on two axially spaced inner raceways of the bearing inner ring.

Object of the invention

The invention has for its object to provide a bearing assembly by which the mechanical Betriebsveralten can be improved from previously formed with the inclusion of spherical roller bearings bearings.

Inventive solution

• – einer Außenringeinrichtung die eine erste und eine zweite jeweils im Axialschnittkonkave und zu einer Lagerachse konzentrische, sowie dieser zugewandte Außenringlauffläche bildet,
• – einer Innenringeinrichtung die eine erste und eine zweite wiederum im Axialschnittkonkave und zur Lagerachse konzentrische, jedoch der Lagerachse abgewandte Innenringlauffläche bildet,
• – Wälzkörpern die in einem zwischen der Außenringeinrichtung und der Innenringeinrichtung gebildeten Wälzkörperbahnraum aufgenommen sind und hierbei eine erste Wälzkörperlaufreihe und eine hiervon axial beabstandete zweite Wälzkörperlaufreihe bilden, wobei
• – die Wälzkörper als Tonnen ausgebildet sind und einen zu einer Wälzkörperachse konzentrischen Tonnenmantel aufweisen dessen Krümmung im Axialschnitt im wesentlichen der Krümmung der ersten bzw. der zweiten Außenringlauffläche im Axialschnitt entspricht,
• – die erste und die zweite Außenringlauffläche jeweils Kugelringflächen von Kugeln bilden, deren Kugelzentren auf der Lagerachse liegen und die Innenringeinrichtung um ein Kippzentrum kippbar ist, das im Bereich der Kugelzentren liegt,
• – die Außenringeinrichtung ein erstes Lageraußenringelement umfasst, dessen Innenumfangsfläche die erste Außenringlauffläche bildet,
• – die Außenringeinrichtung ein zweites Lageraußenringelement umfasst, dessen Innenumfangsfläche die zweite Außenringlauffläche bildet, und
• – eine Spanneinrichtung vorgesehen ist, zur Aufbringung einer die beiden Lageraußenringelemente auf einander zu drängenden Spannkraft.

The above object is achieved by a bearing assembly, with:

• - An outer ring means forming a first and a second concentric in each case in the Axialschnittkonkave and to a bearing axis, and this facing outer raceway surface,
• - An inner ring means which forms a first and a second in turn in the Axialschnittkonkave and the bearing axis concentric, but facing away from the bearing axis inner raceway surface,
• - Rolling bodies which are received in a Wälzkörperbahnraum formed between the outer ring means and the inner ring means and in this case form a first Wälzkörperlaufreihe and an axially spaced therefrom second Wälzkörperlaufreihe, wherein
• The rolling elements are designed as barrels and have a barrel shell concentric with a rolling body axis whose curvature in axial section substantially corresponds to the curvature of the first and the second outer ring rolling surface in axial section,
• - The first and the second outer ring raceway each form ball ring surfaces of balls whose ball centers are on the bearing axis and the inner ring means is tiltable about a tilting center, which is in the range of the ball centers,
• The outer ring device comprises a first bearing outer ring element whose inner circumferential surface forms the first outer ring raceway,
• - The outer ring means comprises a second bearing outer ring member whose inner peripheral surface forms the second outer raceway surface, and
• - A clamping device is provided for applying a the two bearing outer ring elements on each other to be urged clamping force.

This advantageously makes it possible to displace the first outer raceway surface and the second outer raceway surface axially relative to one another while defining the inner preload of the bearing assembly in a defined manner, wherein the preload increase can be achieved with such small adjustment travel in this way that even in the axially tensioned state still sufficiently correct geometrical Abwälzverhältnisse are given.

According to a particularly preferred embodiment of the invention, a restoring device is provided for applying an effective between the two bearing outer ring elements bearing restoring force. This restoring device can be designed in particular as a relatively stiff spring, which sits between the mutually facing inner end faces of the two bearing outer ring elements. This spring can in particular as Plate or wave spring be executed whose spring travel, for example, only about 5% of the bearing width.

Preferably, a stop device is provided for determining the maximum axial degree of compression of the outer ring device. This avoids that the rolling elements and the running surfaces are overloaded by applying excessive axial clamping forces. This stop device can be accomplished in an advantageous manner in interaction with the spring device. Thus, especially in the execution of the spring device as a plate or wave spring whose block length be tuned so that the spring reaches its maximum axial compression when reaching maximum bias and thus even as an axially highly rigid stop is effective without this being damaged.

According to a particular aspect of the present invention, the rolling elements of the two rows of runs are guided over a common cage. This cage can be designed in particular as a so-called. Double comb cage, or as a double-row window cage. The cage is preferably designed so that it leads the rolling elements with a high degree of enclosure. Preferably, the cage is also designed so that it is in the circumferential direction, as well as in the axial direction, i. developed between the Wälzkörperlaufreihen a high support effect.

As an alternative to the aforementioned variant, it is also possible to form the cage as an axially divided structure, so that the rolling elements of each row of rollers are guided in a separate cage section. Preferably, the two cage sections are in this case designed such that they form mutually facing end faces via which the two cage sections can contact and support axially.

The tensioning device is preferably designed according to a particular aspect of the present invention as an oil-hydraulic tensioning device. The clamping device can be recognized as an independent assembly axially to the outer ring device. Preferably, however, the clamping device is integrated into the bearing arrangement in such a way that the bearing arrangement can be handled as an assembly comprising the clamping device. The clamping device can be designed so that it comprises an annular piston, which is guided sealed in a Ringnutträger and axially disengageable under the pressure of a fluid. As an alternative to a design of the clamping device as a piston mechanism, it is also possible to manufacture these by at least partially elastically deformable elements, such as a thin-walled, tubular ring which is axially expandable under a prevailing oil pressure in its inner. The tensioning device can also be manufactured in interaction with structures which are provided by the outer ring elements.

The bearing assembly can also be designed such that upon reaching the maximum axial preload the ball centers of the two outer raceway surfaces lie on each other. This ensures that exist in a state of the bearing with the highest bias, or on elimination of the clearance and suppression of slip, ideal geometric Abwälzverhältnisse.

The solution according to the invention, it is possible to provide a bearing arrangement similar to a spherical roller bearings allows tilting of the La-gerinnenringes relative to the bearing outer ring and also allows dynamic biasing the now radially split spherical roller bearings outer rings. The bearing assembly according to the invention is particularly suitable for marine propulsion.

The invention enables a dynamic adjustment depending on the load direction and load case. The invention makes it possible to provide for the field of marine propulsion technology a spherical roller bearing in which can be apart from a measurement of the bearing clearance in the installed state of a ship's shaft. According to the invention, the hydraulic pressure acting on the hydraulic nut oil pressure is measured and regulated by means of a control system, so that prevails at the time of a load case occurring bias. Damage caused by slippage can be avoided with this defined preload. The hydraulic elements used to adjust the bearing clearance can be integrated into the bearing arrangement in an advantageous manner. The control of the bearing preload or the bearing clearance is done dynamically via a control unit. The outer ring means of the bearing assembly comprises two separate outer ring members forming common spherical raceways. Between these outer ring elements spring packs are added to generate the corresponding restoring forces. Furthermore, a control unit for the control pressure for axial clamping is provided. Instead of static prestressing, according to the invention, a spherical roller bearing of a marine propulsion system is dynamically prestressed by means of a control system in order in particular to be able to react to changing operating conditions. According to the invention, a spherical roller bearing outer ring is divided into two axially separated by springs single rings, with a separate or integrated into a single ring hydraulic nut can act against the spring force.

Brief description of the figures

Further details and features of the invention will become apparent from the following description taken in conjunction with the drawings. It shows:

1 a simplified axial section of a bearing assembly according to the invention, in particular for a ship propeller shaft;

2 a further Axialschnittdarstellung to illustrate the structure of a bearing assembly according to the invention in which the clamping device is realized in interaction with the outer ring means and also on the clamping device, a basic setting of the bearing device is ensured.

In 1 a bearing arrangement according to the invention is shown. This bearing arrangement comprises an outer ring device AR which has a first and a second concave, in axial section concave and concentric to a bearing axis, as well as this facing outer ring tread 1 . 2 forms. Furthermore, the bearing arrangement comprises an inner ring device IR which has a first and a second inner ring running surface, which in turn is concave in axial section and concentric with the bearing axis but faces away from the bearing axis 3 . 4 forms. The outer ring means AR and the inner ring means IR are by rolling elements 5 . 6 supported radially against each other. The rolling elements 5 . 6 are here received in a Wälzkörperbahnraum formed between the outer ring means AR and the inner ring means IR and in this case form a first Wälzkörperlaufreihe L5 and an axially spaced therefrom second Wälzkörperlaufreihe L6. The rolling elements 5 . 6 are designed as tons and have a concentric to a Wälzkörperachse X5, X6 barrel shell on the curvature in the axial section shown here substantially the curvature of the first and the second outer raceway surface 1 . 2 in axial section corresponds.

The first and second outer ring tread 1 . 2 each form ball ring surfaces whose spherical centers Z1, Z2 are on the bearing axis X. By means of this configuration, it is achieved that the inner ring device IR can be tilted about a tilting center K which lies in the region of the ball centers Z1, Z2.

The outer ring device AR comprises a first bearing outer ring element AR1, whose inner peripheral surface is the first outer ring raceway surface 1 forms. The outer ring device AR also comprises a second bearing outer ring element AR2, whose inner peripheral surface is the second outer raceway surface 2 forms.

The bearing assembly further comprises a tensioning device T, for applying one of the two bearing outer ring elements AR1, AR2 to be urged clamping force, and a restoring device R, for applying an effective between the two bearing outer ring elements AR1, AR2 bearing restoring force. The restoring device R here comprises two springs arranged in series 7 . 8th which sit between the mutually facing inner end faces of the two bearing outer ring elements AR1, AR2. Between these disc springs 7 . 8th seat an intermediate ring 9 , The feathers 7 . 8th and the intermediate ring 9 are designed so that they act as a stop in the maximum compressed state and prevent further axial approximation of the outer ring elements AR1, AR2. Alternatively to the design of the springs 7 . 8th as disc springs these can also be designed in particular as wave springs.

The rolling elements 5 . 6 The two rows L5, L6 are each about a cage 10 . 11 guided. The cage 10 . 11 are designed so that these are over faces 10a . 11a contact and support each other. The cage 10 . 11 are executed here as comb cages.

The tensioning device T is designed as an oil-hydraulic tensioning device and comprises an annular piston 12 in a support ring 13 is guided. In the support ring 13 is a circumferential groove 13a educated. This is filled with a fluid, especially oil or grease. This fluid can be acted upon by a pressure not shown here channel means. The ring piston 12 is about a sealing device 14 . 15 sealed and thus in the circumferential groove 13a guided in a sealing manner axially displaceable. In accordance with the in the circumferential groove 13a prevailing fluid pressure exerts the annular piston 12 on the outer ring member AR1 a corresponding axial force and thus urges this outer ring element AR1 against the restoring force of the return device R to the second outer ring element AR2. As a result, the running clearance of the rolling elements 5 . 6 the two rows L5, L6 reduced. By defined increase of the fluid pressure in the circumferential groove, the axial force of the annular piston 12 be further increased. Here, after removal of the bearing clearance, the pressure of the rolling elements 5 . 6 between the inner ring means IR and the outer ring means AR increases. This pressure is preferably increased to a level at which a required operating behavior of the bearing, in particular a largely slip-free rolling of the rolling elements 5 . 6 in the bearing assembly adjusts.

The bearing arrangement shown here is designed such that at a suitable for continuous operation axial bias the ball centers Z1, Z2 of the two outer raceway surfaces 1 . 2 lie relatively exactly on each other. This place of extensive congruence of the spherical centers then also provides the tilting center K, around which the bearing inner ring device IR can tilt at least slightly. Upon reduction of the axial pressure of the bearing outer ring elements AR1, AR2, the ball centers Z1, Z2 are slightly removed. The tilting center K is then located between these centers Z1, Z2. A tilting of the bearing inner ring device IR is also possible in this state, since the reduced pressure tolerates such geometrical conditions.

The bearing inner ring device IR is here designed as a one-piece bearing inner ring and forms the two concave inner ring raceways 3 . 4 , These inner raceways have the same curvature in the axial section shown here as the outer raceway surfaces 1 . 2 , the two inner raceway surfaces are aligned with each other "adjusted", so that the Wälzkörperachsen X5, X6 are inclined to each other. The angle of inclination is in particular the diameter of the orbits of the rolling elements 5 . 6 and the axial width of the bearing is adjusted and is preferably in the range of 140 ° to 160 °. The rolling elements 5 . 6 are executed as crowned tons whose mantle curvature of the curvature of the treads 1 . 2 in axial section and what those treads 1 . 2 each contact via line contact zones.

Between the two rows of runs, a center board M is formed on the bearing inner ring means IR which the rolling elements 5 . 6 axially leads. In addition, side walls S1, S2 are formed on the bearing inner ring device IR, through which also an axial guidance of the rolling bodies 5 . 6 is reached.

In 2 a second variant of a bearing assembly according to the invention is shown. This bearing arrangement, too, comprises an outer ring device AR, which has a first and a second concave, in axial section concave and concentric to a bearing axis, as well as this facing outer ring tread 1 . 2 forms. Furthermore, the bearing arrangement comprises an inner ring device IR which has a first and a second inner ring running surface, which in turn is concave in axial section and concentric with the bearing axis but faces away from the bearing axis 3 . 4 forms. The outer ring means AR and the inner ring means IR are by rolling elements 5 . 6 supported radially against each other. The rolling elements 5 . 6 are here received in a Wälzkörperbahnraum formed between the outer ring means AR and the inner ring means IR and in this case form a first Wälzkörperlaufreihe L5 and an axially spaced therefrom second Wälzkörperlaufreihe L6. The rolling elements 5 . 6 are designed as tons and have a concentric to a Wälzkörperachse X5, X6 barrel shell on the curvature in the axial section shown here substantially the curvature of the first and the second outer raceway surface 1 . 2 in axial section corresponds.

The first and second outer ring tread 1 . 2 each form ball ring surfaces whose spherical centers Z1, Z2 are on the bearing axis X. By this design, as in the embodiment according to 1 achieves that the inner ring device IR can be tilted about a tilting center K which lies in the area of the ball centers Z1, Z2.

The outer ring device AR comprises a first bearing outer ring element AR1, whose inner peripheral surface is the first outer ring raceway surface 1 forms. The outer ring device AR also comprises a second bearing outer ring element AR2, whose inner peripheral surface is the second outer raceway surface 2 forms.

The bearing assembly further comprises a tensioning device T, for applying one of the two bearing outer ring elements AR1, AR2 to be urged clamping force, and a restoring device R, for applying an effective between the two bearing outer ring elements AR1, AR2 bearing restoring force. The restoring device R here comprises a wave spring 7a which sits between the mutually facing inner end faces of the two bearing outer ring elements AR1, AR2. The wave spring 7a is designed so that it acts as a stop in the maximum compressed state and prevents further axial approximation of the outer ring elements AR1, AR2.

The tensioning device T comprises a bushing T. This bushing T1 forms an annular shoulder T2 which acts as an axial stop, as well as a cylinder bottom. The bushing T1 further forms an inner peripheral surface in which the first bearing outer ring element AR1 is guided axially displaceable. The socket T1 also continues to surround the second bearing outer ring element AR2 and is rigidly coupled thereto. This rigid coupling is achieved here by a threaded portion T3, which engages with a complementary threaded portion on the outer periphery of the second bearing outer ring element AR2. At the socket T1 a plurality of sealing ring grooves are formed in which each sealing, in particular O-rings O1, O2, O3, O4 sit. Through the sealing rings O3, O4 a pressure oil chamber C is sealed. This pressure oil chamber can via channel sections c1, 2c, c3, c4 with a pressure oil source 16 get connected. The pressure oil source 16 is via a control device 17 activated and causes the pressure oil source from a sump 20 To tap oil and feed under pressure into the channel section c4, or possibly oil in the sump 20 release until a required pressure exists.

Under the pressure of oil in pressure oil chamber C, the outer ring member AR1 is axially loaded and displaced in a direction toward the second outer ring member. This increases the radial pressure of the recorded between the outer ring means AR and the inner ring rolling elements 5 . 6 , The displacement is thus carried out against the reaction forces of the rolling elements 5 and the restoring force of the return R. The over the outer ring tread 1 on the rolling elements 5 applied pressure leads to a corresponding load on the inner ring means in turn to a radial load of the rolling elements 6 lead the second row L6. Overall, this also results in the outer ring tread 2 an increased Wälzkörperpressung. Since the bushing T is anchored to the outer ring element AR2, the same axial force acts on it as on the first outer ring element AR1.

About the bushing T, the outer ring means AR and thus the bearing assembly is combined to form a module. The bushing T is designed in such a way that it positions the two outer ring elements AR1, AR2 in a basic function position relative to one another in which a possibly small bearing pressure, which can be set via the bushing thread T3, prevails. This bearing pressure can then in accordance with the on the control device 17 controlled oil pressure can be further increased. The control device 17 is preferably incorporated in a closed loop which takes into account several relevant for the setting of the bearing pressure system sizes. In particular, it is possible to determine from an observation of Wälzkörper- or cage circulation whether slip occurs within the camp. If such slip is detected, the pressure is increased accordingly. The pressure prevailing in the bearing is preferably set to a level at which a mechanical operating behavior which is advantageous for the life of the bearing arrangement is established. If necessary, a presetting of the bearing clearance can also be made in the installed state via the bushing T. About the pressure chamber mechanics can then be carried out during operation a clearance adjustment.

The bearing assembly can via the bushing T in a receiving bore 18 inserted and therein via a circlip 19 be secured. The Axialpressung within the outer ring means can be varied, without causing the axial load on the locking ring 19 is increased. The clamping forces are guided completely in the module. In the embodiment shown here, the bearing outer ring element AR1 also acts as an annular piston which is axially movable on the bushing T under the action of the pressure prevailing in the chamber C oil pressure. The geometries of the components of the bearing arrangement are preferably coordinated so that the centers Z1, Z2 come into coincidence in a state of high radial pressure.

The bearing assembly according to the invention is particularly suitable for heavy duty applications, in particular for storage of ship shafts, rollers and drill heads.

The O-rings O1, O2 can be guided around the bushing T. Especially with large bearing diameters, it is also possible to mount the bearing in a defined circumferential position and to seal the seal of the pressure oil passages by a smaller sealing structure. Although not shown here, the displaceable bearing ring element AR1 is preferably secured against rotation in the circumferential direction. This can e.g. done by a feather key or other linear guide.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102009052954 A1 [0003]

Claims (10)

Bearing arrangement, comprising: - an outer ring device (AR) which has a first and a second respectively concave in axial section and a bearing axis (X) concentric, as well as this facing outer ring tread ( 1 ; 2 ), an inner ring device (IR) which has a first and a second, in axial section, a concave and to the bearing axis (X) concentric, but the bearing axis (X) facing away from the inner ring tread ( 3 ; 4 ), - Rolling elements ( 5 . 6 ) which are accommodated in a Wälzkörperbahnraum formed between the outer ring means (AR) and the inner ring means (IR) and in this case form a first Wälzkörperlaufreihe (L5) and an axially spaced therefrom second Wälzkörperlaufreihe (L6), wherein - the rolling elements ( 5 . 6 ) are designed as tons and have a rolling body axis (X5, X6) concentric barrel shell whose curvature in axial section substantially the curvature of the first and the second outer ring raceway ( 1 . 2 ) corresponds in axial section, - the first and the second outer raceway surface ( 1 . 2 ) each form ball ring surfaces of balls whose spherical centers (Z1, Z2) lie on the bearing axis (X) and the inner ring means (IR) is tiltable about a tilting center (K), which in the area of the largely covering spherical centers (Z1, Z2) the outer ring device (AR) comprises a first bearing outer ring element (AR1) whose inner peripheral surface is the first outer raceway surface (AR1) 1 ), - the outer ring means (AR) comprises a second bearing outer ring element (AR2) whose inner peripheral surface is the second outer raceway surface (AR2) 2 ), and - a tensioning device (T) is provided for applying a the two bearing outer ring elements (AR1, AR2) on each other to be urged clamping force. Bearing arrangement according to claim 1, characterized in that a restoring device (R) is provided for applying an effective between the two bearing outer ring elements (AR1, AR2) bearing restoring force. Bearing arrangement according to claim 2, characterized in that the restoring device (R) is designed as a spring which sits between the mutually facing inner end faces of the two bearing outer ring elements (AR1, AR2). Bearing arrangement according to claim 3, characterized in that the spring as a plate or wave spring ( 7 . 8th . 7a ) is executed. Bearing arrangement according to at least one of claims 1 to 4, characterized in that a stop device is provided for determining the maximum axial compression degree of the outer ring device (AR). Bearing arrangement according to at least one of claims 1 to 5, characterized in that the stop device in interaction with the spring device ( 7 . 8th . 7a ) is accomplished. Bearing arrangement according to at least one of claims 1 to 6, characterized in that the rolling bodies ( 5 . 6 ) of the two rows (L5, L6) via separate cages ( 10 . 11 ) are guided. Bearing arrangement according to at least one of claims 1 to 7, characterized in that the clamping device (T) is designed as an oil-hydraulic tensioning device. Bearing arrangement according to Claim 8, characterized in that the tensioning device (T) has an annular piston ( 12 ). Bearing arrangement according to at least one of claims 1 to 9, characterized in that the bearing arrangement is designed such that at a Wälzkörperschlupfunterdrückung sufficient axial preload, the ball centers (Z1, Z2) of the two outer raceway surfaces ( 1 . 2 ) lie on one another.

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