Plain bearing and method for operating a plain bearing

Abstract

The invention relates to a plain bearing (10) comprising at least one housing element (11), at least one bearing segment (12) and at least one vibration damper (13), wherein at least some sections of the bearing segment are connected to the vibration damper such that a vibration introduced into the bearing segment can be introduced into the vibration damper, and wherein at least some sections of the vibration damper are movably mounted on the housing element such that the bearing segment can be moved between an active position and a passive position (II) by an in particular linear movement of the vibration damper relative to the housing element, wherein a gap size of a lubrication gap between the bearing segment and a rotor element (15) supported in the plain bearing is smaller in the active position than in the passive position (II).

Description

[0001] Plain bearing and method for operating a plain bearing

[0002] Description

[0003] The invention relates to a plain bearing having the features of independent patent claim 1, a gear having the features of independent patent claim 14 and a method having the features of independent patent claim 15.

[0004] It is known from the prior art that rotor elements, in particular shafts, pass through critical speed ranges when accelerating from a standstill to an operating speed or during a reverse deceleration. These critical speed ranges are characterized by increased vibrations, which can lead to damage to the affected and / or adjacent components. Accordingly, it is common practice to dampen rotor elements, in particular shafts. This damping has the disadvantage that friction losses occur at the rotor element, thus reducing the energy efficiency of the respective system. Furthermore, since the damping is independent of the operating point (i.e., continuous), the energy efficiency of the respective system is reduced across the entire operating range.

[0005] It is therefore an object of the present invention to at least partially overcome at least one of the disadvantages described above. In particular, the object of the invention is to provide a plain bearing, a gear, and a method that enable demand-based damping of a rotor element mounted in the plain bearing, particularly when passing through critical speeds, while simultaneously allowing a reduction in the friction losses occurring at the plain bearing over a wide operating range.The above object is achieved by a plain bearing according to a first aspect of the present invention, in particular a plain bearing having the features of independent patent claim 1, by a transmission according to a second aspect of the present invention, in particular a transmission having the features of independent patent claim 14, and by a method according to a third aspect of the present invention, in particular a method having the features of independent patent claim 15. Further features and details of the invention emerge from the subclaims, the description and the drawings.Features and details that are described in connection with the plain bearing according to the invention naturally also apply in connection with the transmission according to the invention and / or in connection with the method according to the invention and vice versa, so that with regard to the disclosure of the individual aspects of the invention, reference is or can always be made mutually.

[0006] According to the invention, a, in particular hydrodynamic, plain bearing is provided, comprising at least one housing element, at least one bearing segment, and at least one vibration damper, wherein the bearing segment is connected, at least in sections, to the vibration damper, so that a vibration introduced into the bearing segment can be introduced into the vibration damper and wherein the vibration damper is mounted, at least in sections, movably on the housing element, so that by a, in particular linear, movement of the vibration damper relative to the housing element, the bearing segment can be moved at least between an active position and a passive position, wherein in the active position a gap dimension of a lubricating gap between the bearing segment and a rotor element mounted in the plain bearing is smaller than in the passive position.

[0007] In other words, a particularly hydrodynamic plain bearing is provided, which comprises at least one housing element, in particular exactly one housing element, at least one bearing segment, and at least one vibration damper. The bearing segment is connected to the vibration damper. The connection between the bearing segment and the vibration damper can preferably be designed such that a movement, in particular a translational movement, of the vibration damper can be or is transmitted, preferably uniformly, to the bearing segment. Through the connection between the bearing segment and the vibration damper, a vibration introduced into the bearing segment by the rotor element mounted in the plain bearing can be introduced into the vibration damper.Furthermore, the vibration damper is movably mounted on the housing element, at least in sections, such that the bearing segment can be moved between an active position and a passive position by a movement, in particular a linear movement, of the vibration damper relative to the housing element. It is provided that in the active position, a gap dimension of a lubricating gap between the bearing segment and a rotor element mounted in the plain bearing is smaller than in the passive position. In other words, in the active position, a distance between the bearing segment and a central axis of the plain bearing is smaller than in the passive position. Compared to the passive position, when the plain bearing is transferred to the active position, it is advanced in the direction of the central axis of the plain bearing or the rotor element mounted in the plain bearing.

[0008] In the active position, the bearing segment is arranged relatively close to the surface of the rotor element. The rotation of the rotor element in the plain bearing pumps a lubricant located in the plain bearing, particularly in a bearing chamber of the plain bearing, into the lubrication gap between the bearing segment and the rotor element. The small distance between the bearing segment and the rotor element and the constant pumping of the lubricant into the lubrication gap create a stable lubricating film with increased pressure in the lubrication gap, via which power is transmitted between the rotor element and the bearing segment. Vibration of the rotor element, particularly when traveling through critical speed ranges, can thus be transmitted to the bearing segment and accordingly to the vibration damper. Accordingly, damping of a rotor element mounted in the plain bearing can be provided in the active position.

[0009] By moving the vibration damper relative to the housing element, the bearing segment can be moved from the active position to the passive position or vice versa. During the move to the passive position, the distance between the bearing segment and the rotor element mounted in the plain bearing is increased. The gap size of the lubrication gap between the bearing segment and the rotor element is increased accordingly and the pressure in the lubrication gap is reduced. This also reduces or interrupts the transmission of force between the rotor element and the bearing segment. Damping of the rotor element is therefore reduced in the passive position compared to the damping in the active position. In particular, in the passive position there is no or essentially no damping of the rotor element by the bearing segment. However, the interrupted or interrupted damping of the rotor element.Reduced force transmission between the bearing segment and the rotor element in the passive position also reduces the friction losses occurring at the plain bearing compared to the active position, which ultimately enables more energy-efficient operation of the plain bearing.

[0010] Thus, a plain bearing according to the invention offers the advantage that damping of a rotor element can be provided as needed and depending on the operating point, but the associated friction losses in non-critical operating ranges can be reduced or completely or essentially completely eliminated by transferring one or more bearing segments from the active position to the passive position.

[0011] The features described in the context of the present invention with regard to a bearing segment and / or a vibration damper can be transferred completely or at least partially to further bearing segments or vibration dampers.

[0012] In this case, the active position is to be understood as a position in which the bearing segment is advanced towards a rotor element guided in the plain bearing in such a way that force is transmitted between the bearing segment in question and a rotor element guided in the plain bearing, and thus damping of the rotor element by the bearing segment or the vibration damper connected to it is possible. The passive position, on the other hand, is to be understood as a position in which the bearing segment is positioned away from the rotor element in such a way that no or essentially no force is transmitted between the rotor element and the bearing segment, and thus no or essentially no damping of the rotor element by the bearing segment or the vibration damper connected to it is possible.

[0013] Within the scope of the invention, it can be provided that the gap dimension of a lubrication gap between the bearing segment and a rotor element mounted in the plain bearing in the passive position is a multiple, in particular at least twice, preferably at least three times, particularly preferably at least four times, of the gap dimension in the active position. In particular, it is conceivable that the gap dimension of a lubrication gap between the bearing segment and a rotor element mounted in the plain bearing in the passive position is at least 2 mm or 2 mm, in particular at least 4 mm or 4 mm, preferably at least 6 mm or 6 mm.

[0014] Preferably, the housing element can form a bearing space, in particular a rotationally symmetrical or annular one, for supporting a rotor element. In particular, at least one bearing segment can be arranged at least partially within the bearing space. Additionally or alternatively, at least one bearing segment can be arranged at one end of a vibration damper, wherein this end of the vibration damper, in particular, faces the bearing space and / or a rotor element mounted in the plain bearing.

[0015] Preferably, at least one bearing segment can be designed as a tilting segment. For this purpose, it can be provided that the bearing segment is pivotally mounted on the vibration damper, at least in sections. In particular, the pivot axis can be oriented parallel or substantially parallel to a central axis of the plain bearing and / or the central axis of the rotor element mounted in the plain bearing. Designing a bearing segment as a tilting segment results in the advantage that, in the active position, upon rotation of a rotor element mounted in the plain bearing, a convergent or wedge-shaped lubricating gap forms between the bearing segment and the surface of the rotor element, which adapts to the respective current operating point, in particular the current speed of the rotor element, over a wide operating range.This ensures efficient and secure support of the rotor element in the active position of the bearing segment over a wide operating range. Additionally or alternatively, at least one bearing segment can be designed differently. In particular, the plain bearing can be designed as a circular bearing or a wedge bearing, in particular a two-wedge bearing, a three-wedge bearing, or a four-wedge bearing.

[0016] In particular, it can be provided that the plain bearing comprises a plurality of, in particular at least two or exactly two, preferably at least three or exactly three, particularly preferably at least four or exactly four, vibration dampers and / or bearing segments, wherein in particular each vibration damper is connected at least in section to at least one tilting segment. The vibration dampers can have an identical structure. Additionally or alternatively, the vibration dampers can each be mounted in a similar way on the housing element. Additionally or alternatively, it is conceivable that the vibration dampers and / or bearing segments are arranged distributed, in particular at equidistant intervals, over the circumference of the plain bearing, in particular of the housing element.

[0017] Within the scope of the invention, it may be advantageous for the vibration damper to comprise at least one damping element, wherein the damping element is designed to at least partially dissipate the kinetic energy introduced into the vibration damper. The damping element can preferably be designed as a spring element.

[0018] In particular, it can be provided that at least one damping element is designed as a friction spring. A friction spring offers the advantage that a comparatively large portion of the introduced vibration energy is dissipated. In other words, when a friction spring is relieved of load, only a small portion of the energy previously introduced during a load is released. The use of a friction spring as a damping element thus enables efficient damping of a rotor element mounted in the plain bearing.

[0019] At least one friction spring can preferably comprise a plurality of ring elements, in particular at least two ring elements, wherein each ring element is in contact, in particular surface contact, with at least one further ring element at least in sections. The ring elements can each comprise at least one wedge-shaped contact section, wherein the ring elements are arranged such that contact between two ring elements occurs via the wedge-shaped contact sections. This ensures the largest possible contact area between the ring elements and increased surface pressure when a force is introduced into the friction spring. Such a design can increase the friction losses arising when a force is applied to the friction spring and a resulting movement of the ring elements relative to one another, thus supporting effective damping.

[0020] Additionally or alternatively, it can be provided that at least one damping element is formed, at least in sections, from an elastic material, in particular an elastomer. At least one damping element can be designed as a sleeve, wherein the sleeve is formed, at least in sections, from an elastic material.

[0021] Additionally or alternatively, at least one damping element can be designed as a disc spring, in particular as a disc spring stack or a disc spring column. The use of a disc spring stack has also proven particularly advantageous within the scope of the present invention. When a disc spring stack compresses, friction occurs at the contact points between the individual disc springs, enabling efficient damping of a rotor element mounted in the plain bearing.

[0022] In particular, a disc spring stack can comprise a plurality of disc springs. The disc springs can preferably be arranged coaxially or substantially coaxially with respect to their central axis. In particular, at least two or all disc springs in the disc spring stack can be arranged serially or in a row. This can increase spring travel. Additionally or alternatively, at least two or all disc springs in the disc spring stack can be arranged in parallel. This allows the force required for compression to be dimensioned.

[0023] Within the scope of the invention, it is conceivable for the preload of the damping element in the active position to be between 25% and 35%, in particular between 28% and 32%, preferably 30%, of a maximum spring travel of the damping element and / or for the preload of the damping element in the passive position to be between 3% and 7%, in particular between 4% and 6%, preferably 5%, of a maximum spring travel of the damping element. A preload of the damping element in the above-mentioned order of magnitude has shown particularly advantageous behavior of the plain bearing both in the active position and in the passive position. In particular, a corresponding preload in the active position can achieve a high degree of damping of the damping element. The preload in the passive position can be regarded as a minimum preload to ensure reliable operation of the damping element.

[0024] Within the scope of the invention, it can be provided that at least one vibration damper comprises a first contact element and a second contact element, wherein the damping element is arranged between the first contact element and the second contact element in such a way that a movement of the first contact element in the direction of the second contact element or vice versa causes a force to be introduced into the damping element. In particular, a force introduction into the damping element can be understood here as the introduction of a compressive force into the damping element. In other words, it can be provided that at least one vibration damper comprises a first and a second contact element, wherein the damping element is arranged between the first and the second contact element and is supported at least in sections on both the first and the second contact element.Thus, a force can be introduced into one of the contact elements and a resulting movement of the contact elements relative to each other, resulting in a force being introduced into the damping element.

[0025] At least one contact element can preferably be provided or designed to connect the vibration damper to components and / or to support the vibration damper on an abutment. For example, it can be provided that the vibration damper is connected to at least one bearing segment via a contact element, in particular the first or second contact element, and is supported on a component of the plain bearing via a further contact element, in particular the first or second contact element. In other words, the component of the plain bearing thus serves as an abutment, so that kinetic energy introduced into the vibration damper can be absorbed and at least partially dissipated by the damping element. The support of a contact element on the plain bearing or abutment of the plain bearing can also occur indirectly, in particular via a link element, preferably connected to the contact element.

[0026] It is further conceivable for at least one contact element, in particular the first contact element, and the housing element to be connected in a form-fitting manner, at least in sections, wherein in particular the form-fitting arrangement is designed such that exclusively or substantially exclusively a linear movement of the first contact element relative to the housing element can be carried out, in particular at least in sections. It can preferably be provided that the linear movement is a radial or substantially radially oriented movement, in particular relative to a bearing element mounted in the plain bearing. A form-fitting arrangement between the contact element and the housing element results in the advantage of a guided and controlled movement of the vibration damper relative to the housing element.Furthermore, the positive locking results in a stable positioning of the vibration damper, which enables advantageous behavior with regard to the absorption of vibrations introduced into the bearing element.

[0027] For the formation of a positive connection between at least one vibration damper, in particular at least one contact element of a vibration damper, and the housing element, it can be provided that the housing element has at least one recess. The recess can penetrate the housing element and / or be oriented radially or substantially radially. The vibration damper, in particular at least one contact element of a vibration damper, can be designed at least partially complementary to the recess and / or at least partially arranged in the recess, so that between the

[0028] Vibration damper, in particular at least one contact element of the

[0029] vibration damper, and the housing element a said form fit is formed.

[0030] It is also conceivable for the first contact element and the second contact element to be connected in a form-fitting manner, at least in sections, wherein the form-fitting arrangement is in particular designed such that exclusively or substantially exclusively a linear movement of the first contact element relative to the second contact element or vice versa, in particular at least in sections, can be carried out. It can preferably be provided that the linear movement is a radial or substantially radially oriented movement, in particular relative to a bearing element mounted in the plain bearing. A form-fitting arrangement between the contact elements offers the advantage of a guided and controlled movement of the contact elements relative to one another. This enables particularly controlled force introduction into the damping element to be achieved.

[0031] To form a positive connection between the first contact element and the second contact element, at least one recess can be formed on one contact element, in particular on the first contact element. The other contact element, in particular the second contact element, can be formed at least partially complementary to the recess and / or arranged at least partially in the recess, so that a positive connection is formed between the contact elements.

[0032] Within the scope of the invention, it is optionally possible for at least one, in particular a first, sealing element to be arranged on at least one contact element, in particular on the first or the second contact element, wherein the sealing element seals a gap between the first contact element and the housing element. This results in the advantage that no lubricant can escape to the outside via the damping element or the gap between the damping element and the housing element. The sealing element can preferably be designed as a sealing ring, in particular an O-ring. In particular, the sealing element can be arranged in a groove formed on the, in particular first or second, contact element.

[0033] Additionally or alternatively, it can be provided that at least one, in particular a second, sealing element is arranged on at least one contact element, in particular on the first or the second contact element, wherein the sealing element seals a gap between the first contact element and the second contact element. This results in the advantage that no lubricant can escape through the gap between the first and second contact elements. The sealing element can preferably be designed as a sealing ring, in particular an O-ring. In particular, the sealing element can be arranged in a groove formed on the, in particular the first or second, contact element.

[0034] Additionally or alternatively, it can be provided that at least one sealing element is arranged between the bearing segment and the damping element with respect to a longitudinal extension of the vibration damper. This provides the advantage that no lubricant can escape via the damping element or the gap between the damping element and the housing element. Additionally or alternatively, it can be provided that at least one sealing element is arranged between the damping element and a preload element with respect to a longitudinal extension of the vibration damper.

[0035] Furthermore, it can be provided within the scope of the invention that at least one prestressing element is included, wherein at least one vibration damper is held in contact with at least one abutment of the plain bearing by the prestressing element. In particular, it can be provided that at least one prestressing element is designed as a spiral spring. Preferably, several, in particular at least two, at least three or at least four or exactly four, prestressing elements can also be included. Particularly preferably, at least as many or just as many prestressing elements can be included as vibration dampers. Preferably, it can be provided that each vibration damper is assigned at least one prestressing element. An assignment of the prestressing element to a vibration damper should be understood to mean that the vibration damper is held in contact with at least one abutment of the plain bearing by the prestressing element.In other words, at least one preload element can be included, wherein a preload force is transmitted from the preload element to the vibration damper both in the active position and in the passive position of the bearing segment or the vibration damper, in order to keep the latter in contact with at least one abutment of the plain bearing. An abutment of the plain bearing can be formed by various components of the plain bearing. In particular, an abutment with respect to at least one vibration damper can be formed by the housing element and / or an adjusting element.

[0036] Within the scope of the invention, it can be provided that at least one preload element is arranged, at least in part, in a recess of the housing element. Additionally or alternatively, it is conceivable that at least one preload element is supported, on the one hand, at least in part, on the housing element and, on the other hand, at least in part, on a vibration damper. This allows the housing element to be used as an abutment for the preload element in order to apply a force to the vibration damper and thus keep it in contact with at least one other abutment of the plain bearing.

[0037] At least one prestressing element can form a positive connection, at least in sections, with at least one contact element, in particular the first contact element, of a vibration damper. For this purpose, the prestressing element can form a recess, wherein the contact element is at least partially received in the recess. In other words, it can be provided that the prestressing element encloses the contact element at least in sections. Additionally or alternatively, it can be provided that a central axis of the contact element and a central axis of the prestressing element are arranged coaxially or essentially coaxially. This results in the advantage of a particularly compact arrangement. The positive connection can preferably be designed such that exclusively or essentially exclusively a linear, in particular radial, movement of the prestressing element relative to the contact element or vice versa can be carried out.This ensures a defined and guided introduction of force from the preload element into the vibration damper or the contact element.

[0038] With regard to the present invention, it is conceivable that at least one adjustment element is included, wherein by a movement, in particular rotation, of the adjustment element relative to the housing element, at least one bearing segment can be moved from the active position into the passive position and / or vice versa. In other words, it is conceivable that at least one adjustment element is included by the plain bearing. In particular, it can be provided that by a movement, in particular rotation, of the adjustment element relative to the housing element, a movement of at least one vibration damper can be carried out relative to the housing element, such that the bearing segment connected to the vibration damper can be moved from the active position into the passive position or vice versa.In particular, it can be provided that the adjusting element is mounted on the housing element so as to be movable, in particular rotatable, at least in sections and / or that a central axis of the adjusting element and the housing element are arranged coaxially or substantially coaxially.

[0039] Within the scope of the invention, it can be provided that the adjusting element is designed to be annular, at least in part or entirely, and / or surrounds the housing element at least in part, in particular completely. Additionally or alternatively, it can be provided that the adjusting element forms a housing element of the plain bearing that seals off the plain bearing to the outside.

[0040] Preferably, it can be provided that, by a movement, in particular rotation, of the adjusting element relative to the housing element, at least two, in particular all, bearing segments can be moved from the active position to the passive position or vice versa, in particular simultaneously. This results in improved operation of the plain bearing, since all bearing segments can be moved, in particular simultaneously, from the active position to the passive position or vice versa. The bearing segments therefore do not have to be moved one after the other, whereby the damping of a rotor element arranged in the bearing segment can be quickly activated or deactivated by the vibration dampers connected to the bearing segments.

[0041] Furthermore, it is conceivable for the adjusting element to comprise at least one guide slot, wherein at least one vibration damper comprises at least one guide slot element, wherein the guide slot element is at least partially received in the guide slot and is at least partially in contact with an edge of the guide slot, in particular one which delimits the guide slot radially or outwards, and wherein the edge of the guide slot is designed or contoured in such a way that a movement range of the vibration damper can be changed with respect to a movement, in particular a radial movement, relative to the housing element by a movement of the adjusting element relative to the housing element. In particular, it can be provided that the movement range of the vibration damper can be changed with respect to a movement, in particular a linear and / or radial movement, relative to the housing element.

[0042] It is conceivable within the scope of the invention for the adjusting element to comprise more than one guide slot, in particular at least two, at least three, at least four or exactly four guide slots. In particular, it can be provided that at least one guide slot is assigned to each vibration damper, i.e. in particular a guide slot element of a vibration damper is accommodated at least in section in each guide slot and is in contact at least in section with an edge of the respective guide slot. The edge of the respective guide slots can be designed or contoured in such a way that when the adjusting element moves relative to the housing element, a range of motion of the vibration dampers assigned to the respective guide slots can be changed with respect to a movement, in particular a linear and / or radial movement, relative to the housing element.

[0043] The edge of at least one slotted guide can preferably be contoured such that a radial dimension of the edge increases or decreases along an extension of the slotted guide along the circumferential direction. By decreasing or increasing the radial dimension of the edge along the extension of the slotted guide with respect to the circumferential direction, a movement of at least one vibration damper relative to the housing element can be realized upon rotation of the adjusting element relative to the housing element. Within the scope of the invention, it can be provided that the length of the edge of at least one slotted guide determines a maximum adjustment path of the adjusting element.Additionally or alternatively, the edge of at least one guide slot can be contoured in such a way that a movement of at least one vibration damper assigned to the guide slot, and thus of a bearing segment arranged on this vibration damper, from the active position to the passive position or vice versa is possible upon adjustment of the adjustment element by a portion, in particular a maximum of half or a maximum of one-third, of the maximum adjustment travel. This results in the advantage that, particularly upon movement of the bearing segment from the passive position to the active position, the remaining adjustment travel can be used to generate a preload force in the damping element.In other words, when the adjustment element is adjusted over the entire adjustment range, not only is the bearing segment moved from the active position to the passive position, but a preload force is also generated in the damping element by pressing the bearing segment against the rotor element arranged in the plain bearing.

[0044] Additionally or alternatively, at least one slotted guide can be formed as a recess in the adjusting element. Preferably, at least one slotted guide can extend in the circumferential direction and / or be intersected with an inner edge or an inner radius of the adjusting element.

[0045] In particular, it can be provided that the adjusting element forms an abutment for at least one vibration damper and / or that at least one vibration damper, in particular at least one guide element, is held in constant contact with the adjusting element by at least one preloading element. Thus, by appropriately contouring the edge of the guide element, a movement of the vibration damper can be realized by a movement of the adjusting element relative to the housing element.

[0046] Within the scope of the invention, it may be advantageous for the guide element to be rotatably mounted, so that the guide element is set in rotation when the adjustment element moves relative to the housing element. This results in a simplified movement of the adjustment element relative to the housing element, since the guide element is in contact with the adjustment element and, when the adjustment element moves, does not slide on the edge of the guide element, thereby producing comparatively high friction losses, but rather rolls onto it.

[0047] Within the scope of the invention, it is conceivable that at least one drive is included, wherein the drive is operatively connected to the adjusting element in such a way that the adjusting element can be moved, in particular rotated, at least in sections by the drive in order to move at least one bearing segment or at least one vibration damper from the active position to the passive position or vice versa. At least one drive can preferably be designed as an electric, hydraulic, or pneumatic drive. The use of an electric drive has proven particularly advantageous with regard to a simple and compact design of the plain bearing.

[0048] Within the scope of the invention, it can be provided that at least one temperature sensor is arranged on at least one bearing segment, wherein the temperature sensor can detect a material temperature of the bearing segment. By detecting the temperature of a bearing segment, safe and reliable operation of the plain bearing can be monitored or supported. In particular, unwanted heat development within the plain bearing can be detected early, and appropriate measures can be taken to prevent consequential damage. These measures can include, for example, braking the rotor element mounted in the plain bearing.

[0049] The above object is further achieved by a transmission according to the invention, in particular a turbo transmission, comprising at least one plain bearing according to one of the preceding claims. This results in the same advantages with respect to a transmission according to the invention as have already been described with respect to a plain bearing according to the invention.

[0050] The above object is further achieved by a method according to the invention for operating a plain bearing, wherein the plain bearing is preferably designed as a plain bearing according to the invention, in particular as a plain bearing according to one of claims 1 to 13, the method comprising at least one of the following:

[0051] Transferring at least one bearing segment from the active position to the passive position, in particular when a rotational speed of a rotor element mounted in the plain bearing reaches or exceeds a threshold value, Transferring at least one bearing segment from the passive position to the active position, in particular when a rotational speed of a rotor element mounted in the plain bearing reaches or falls below a threshold value.

[0052] This results in the same advantages with regard to a method according to the invention as have already been described with regard to a plain bearing according to the invention and / or a transmission according to the invention.

[0053] It may be provided that at least one of the following is also included:

[0054] Detecting the temperature of at least one bearing segment, in particular by a temperature sensor,

[0055] - Increasing the lubrication gap between the bearing segment and the rotor element mounted in the plain bearing by moving the bearing segment towards the passive position, in particular when the temperature of the bearing segment reaches or exceeds a threshold value.

[0056] If the bearing segment is pressed too tightly against the rotor element, high temperatures can arise in the bearing chamber of the plain bearing or on the bearing segment due to comparatively high friction losses. By enlarging the lubrication gap, friction can be reduced and the resulting heat can be reduced. This prevents any adverse effects on the plain bearing and the lubricant it contains due to excessive heat. The bearing segment can be moved from the active position to the passive position. Additionally or alternatively, the bearing segment can be moved to a position between the active position and the passive position, in particular continuously. In this way, heat development can be limited while at the same time a damping effect of the bearing segment with respect to the rotor element can be at least partially maintained.

[0057] Furthermore, within the scope of the invention, it can be provided that a plain bearing according to the invention, in particular a plain bearing according to one of claims 1 to 13, is used for supporting a rotor element, in particular a shaft.

[0058] Further advantages, features, and details of the invention will become apparent from the following description, which describes several embodiments of the invention in detail with reference to the drawings. The features mentioned in the claims and in the description may be essential to the invention individually or in any combination.

[0059] This shows

[0060] Fig. 1 is a sectional view of a plain bearing,

[0061] Fig. 2 is a sectional view of a vibration damper,

[0062] Fig. 3 a sectional view of a plain bearing,

[0063] Fig. 4 is a sectional view of a damping element,

[0064] Fig. 5 is a sectional view of a housing element,

[0065] Fig. 6 is a schematic view of a plain bearing,

[0066] Fig. 7 is a schematic view of a gearbox and

[0067] Fig. 8 is a schematic view of a process,

[0068] Fig. 9 is a schematic view of a plain bearing,

[0069] Fig. 10 is a schematic sectional view of a vibration damper,

[0070] Fig. 11 is a schematic view of a damping element and

[0071] Fig. 12 is a schematic view of a damping element.

[0072] In the figures, identical reference numerals are used for the same technical features, even for different embodiments.

[0073] Fig. 1 shows a sectional view of a plain bearing 10 comprising at least one housing element 11. The plain bearing 10 is a hydrodynamic plain bearing 10. The housing element 11 forms a bearing chamber 22. A lubricant (not shown in detail), in particular an oil, is provided in the bearing chamber 22 and is introduced into the bearing chamber 22 via the lubricant nozzles 23.

[0074] The plain bearing 10 further comprises at least one bearing segment 12 and at least one vibration damper 13. Such a vibration damper 13 in combination with a bearing segment 12 is shown in an enlarged view in Fig. 2.

[0075] It is apparent from Fig. 1 and 2 that the bearing segment 12 is at least partially connected to the vibration damper 13, so that a vibration of the rotor element 15 introduced into the bearing segment 12 can be introduced into the vibration damper 13 via the bearing segment 12.

[0076] Fig. 3 shows a further sectional view of the plain bearing 10. In particular, from the combination of Figs. 1 and 3, it is evident that the vibration damper 13 is mounted on the housing element 11 so as to be movable, at least in sections, such that a linear movement of the vibration damper 13 relative to the housing element 11 allows the bearing segment 12 to be moved at least between an active position I and a passive position II, wherein in the active position I, a gap dimension S of a lubricating gap 14 between the bearing segment 12 and a rotor element 15 mounted in the plain bearing 10 is smaller than in the passive position. The passive position II is shown in Fig. 1 and the active position I in Fig. 3.

[0077] It can be seen from Fig. 1 and 3 that the bearing segment 12 in the active position I is arranged comparatively close to the surface of the rotor element 15. Due to the rotation of the rotor element 15 in the plain bearing 10, a lubricant located in the bearing chamber 22 of the plain bearing 10 is conveyed into the lubricating gap 14 between the bearing segment 12 and the rotor element 15. Due to the small distance between the bearing segment 12 and the rotor element 15 and the constant conveyance of the lubricant into the lubricating gap 14, a stable lubricating film with increased pressure is created in the lubricating gap 14, via which a force transmission between the rotor element 15 and the bearing segment 12 is enabled. A vibration of the rotor element 15, in particular when passing through critical speed ranges, can thus be introduced into the bearing segment 12 and accordingly into the vibration damper 13.Accordingly, in the active position I, damping of a rotor element 15 mounted in the plain bearing 10 can be provided.

[0078] By moving the vibration damper 13 relative to the housing element 11, the bearing segment 12 can be moved from the active position I shown in Fig. 3 to the passive position II shown in Fig. 1, or vice versa. By moving it from the active position I to the passive position II, the distance between the bearing segment 12 and the rotor element 15 mounted in the plain bearing 10 is increased. The gap size S of the lubricating gap 14 between the bearing segment 12 and the rotor element 15 is thus increased accordingly, and the pressure in the lubricating gap 14 is reduced. As a result, no load-bearing lubricating film can form in the lubricating gap 14, and the force transmission between the rotor element 15 and the bearing segment 12 is reduced or interrupted. Damping of the rotor element 15 is therefore reduced in the passive position II compared to the damping in the active position I.In particular, in the passive position, there is essentially no or no damping. However, the interrupted or reduced force transmission between bearing segment 12 and rotor element 15 in the passive position II also reduces the friction losses occurring at the plain bearing 10 compared to the active position I, which ultimately enables more energy-efficient operation of the plain bearing 10.

[0079] Thus, a plain bearing 10 according to the invention offers the advantage that damping of a rotor element 15 can be provided as needed and depending on the operating point, but the associated friction losses in non-critical operating ranges can be reduced or completely or essentially completely eliminated by transferring one or more bearing segments 12 from the active position I to the passive position II.

[0080] The bearing segment 12 shown, for example, in Fig. 2 is designed as a tilting segment. For this purpose, the bearing segment 12 is pivotally mounted on the vibration damper 13, at least in sections, via a joint 24. Designing a bearing segment 12 as a tilting segment has the advantage that, in the active position I, upon rotation of a rotor element 15 mounted in the plain bearing 10, a convergent or wedge-shaped lubrication gap 14 forms between the bearing segment 12 and the surface of the rotor element 15, which optimally adapts to the current operating point, in particular the current speed of the rotor element 15, over a wide operating range. This ensures efficient and secure mounting of the rotor element 15 over a wide operating range.

[0081] Fig. 2 further shows that at least one temperature sensor 21 is arranged on the bearing segment 12, wherein the temperature sensor 21 can detect a material temperature of the bearing segment 12. By detecting the temperature of a bearing segment 12, safe and reliable operation of the plain bearing 10 can be monitored and supported. In particular, unwanted heat development within the plain bearing 10 can be detected early, and appropriate measures can be taken to prevent consequential damage.

[0082] Fig. 2 also shows that the vibration damper 13 comprises at least one damping element 13.3. The damping element 13.3 is designed to at least partially dissipate the kinetic energy introduced into the vibration damper 13. In this case, the damping element 13.3 is designed as a friction spring, which is shown in detail in Fig. 4.

[0083] A friction spring offers the advantage that a comparatively large portion of the introduced shrinkage energy is dissipated. In other words, when a friction spring is relieved of load, only a small portion of the energy previously introduced during a load is released again. The use of a friction spring as a damping element 13.3 consequently enables efficient damping of a rotor element 15 mounted in the plain bearing 10. As shown in Fig. 4, the friction spring comprises a plurality of ring elements 25, wherein each ring element 25 is in contact, in particular surface contact, with at least one other ring element 25, at least in sections.

[0084] The ring elements 25 each comprise at least one wedge-shaped contact section 26, wherein the ring elements 25 are arranged such that contact between two ring elements 25 occurs via the wedge-shaped contact sections 26. This ensures the largest possible contact area between the ring elements 25 and increases the surface pressure when a force is applied to the friction spring. Such a design can increase the friction losses that occur when a force is applied to the friction spring and the resulting movement of the ring elements 25 relative to one another, thus supporting effective damping by the damping element 13.3.

[0085] From Fig. 2 it is further apparent that the vibration damper 13 comprises a first contact element 13.1 and a second contact element 13.2, wherein the damping element 13.3 is arranged between the first contact element 13.1 and the second contact element 13.2 in such a way that a movement of the first contact element 13.1 in the direction of the second contact element 13.2 or vice versa causes a force to be introduced into the damping element 13.3.

[0086] From Fig. 1 and 2 it is further apparent that the vibration damper 13 is connected to the bearing segment 12 via the first contact element 13.1 and is supported on an abutment 18 via the second contact element 13.2, so that a kinetic energy introduced into the vibration damper 13 can be absorbed and at least partially dissipated by the damping element 13.3.

[0087] From Figs. 1 and 3, it is further apparent that the vibration damper 13 is at least partially connected to the housing element 11 in a form-fitting manner via the first contact element 13.1. The form-fitting connection is designed such that only or essentially only a linear movement of the first contact element 13.1 and thus of the vibration damper 13 relative to the housing element 11 can be carried out.

[0088] To form a positive connection between the first contact element 13.1 and the housing element 11, the housing element 11 has at least one recess 27. For this purpose, Fig. 5 shows a sectional view of a housing element 11, in which the recess 27 is shown without a vibration damper 13 arranged therein. The recess 27 penetrates the housing element 11 and is oriented radially or essentially radially. The first contact element 13.1 is formed at least in sections complementary to the recess 27 and is arranged at least in sections in the recess 27, so that a said positive connection is formed between the first contact element 13.1 of the vibration damper 13 and the housing element 11.

[0089] From Fig. 2 it is further apparent that the first contact element 13.1 and the second contact element 13.2 are connected in a form-fitting manner at least in sections, wherein the form-fitting arrangement is designed such that exclusively or substantially exclusively a linear movement of the first contact element 13.1 relative to the second contact element 13.2 or vice versa can be carried out at least in sections.

[0090] In other words, the positive connection between the first contact element 13.1 and the second contact element 13.2 is therefore not a complete positive connection, but a partial positive connection, so that exclusively or essentially exclusively a linear movement of the first contact element 13.1 relative to the second contact element 13.2 or vice versa can be carried out at least in sections.

[0091] To form the positive connection between the first contact element 13.1 and the second contact element 13.2, a recess 27, in particular a bore, is formed on the first contact element 13.1. The second contact element 13.2 is formed at least partially complementary to the recess 27, in particular a bore, and is arranged at least partially in the recess 27, in particular a bore, so that a positive connection is formed between the contact elements 13.1, 13.2.

[0092] From Fig. 1 to 3 it is further apparent that at least one sealing element 16 is arranged on the first contact element 13.1, wherein the sealing element 16 seals a gap between the first contact element 13.1 and the housing element 11. For this purpose, the sealing element 16 bears at least partially against a wall of the recess 27 of the housing element 11. The sealing element 16 can preferably be designed as a sealing ring, in particular an O-ring. It is further apparent that the sealing element 16 is arranged between the bearing segment 12 and the damping element 13.3 with respect to a longitudinal extent of the vibration damper 13. This allows the damping element 13.3 to be protected from contact with a lubricant located in the bearing space 22 of the plain bearing 10. This allows the longevity of the damping element 13.3 to be increased. Furthermore, the lubricant can be prevented from escaping from the housing element 11 of the plain bearing 10.

[0093] From Figs. 1 and 3, it is further apparent that at least one preloading element 17 is included, wherein the vibration damper 13 is held in contact with at least one abutment 18 of the plain bearing 10 by the preloading element 17. In this case, the preloading element 17 is designed as a spiral spring. The abutment 18 is formed by the adjusting element 19.

[0094] The preload element 17 is arranged at least partially in the recess 27 of the housing element 11 and is supported, on the one hand, at least partially on the housing element 11 and, on the other hand, at least partially on the vibration damper 13. As a result, the housing element 11 can be used, at least partially, as an abutment 18 for the preload element 17 in order to apply a force to the vibration damper 13 and thus keep it in contact with at least one further abutment 18 of the plain bearing 10.

[0095] 1 and 3 show that the preload element 17 forms a positive connection with the first contact element 13.1 of the vibration damper 13, at least in sections, by the preload element 17 at least partially enclosing the first contact element 13.1. The positive connection is designed such that only or essentially only a linear, in particular radial, movement of the preload element 17 relative to the first contact element 13.1 or vice versa can be carried out. This achieves a defined and guided introduction of force from the preload element 17 into the vibration damper 13 or the first contact element 13.1.

[0096] Furthermore, Figs. 1 and 3 show that at least one adjusting element 19 is included. The adjusting element 19 is annular, surrounds the housing element 11, and is rotatably mounted on the housing element 11. By rotating the adjusting element 19 relative to the housing element 11, at least one bearing segment 12 can be moved from the active position I to the passive position II and vice versa.

[0097] The adjustment element 19 comprises at least one guide 19.1. Furthermore, the vibration damper 13 comprises at least one guide element 13.4, wherein the guide element 13.4 is at least partially received in the guide 19.1 and at least partially in contact with an edge 19.2 of the guide 19.1. The edge 19.2 of the guide 19.1 is contoured such that a movement of the adjustment element 19 relative to the housing element 11 can change the range of motion of the vibration damper 13 with respect to a movement relative to the housing element 11. Since the vibration damper 13 is pressed against the adjusting element 19 or the edge 19.2 of the link 19.1 via the preloading element 17, the vibration damper 13 is displaced relative to the rotor element 15 mounted in the plain bearing 10 when the adjusting element 19 is rotated, in accordance with the predetermined contouring of the edge 19.2 of the link 19.1.

[0098] From Fig. 1 to 3 it is also apparent that the link element 13.4 is rotatably mounted, so that the link element 13.4 is set in rotation when the adjusting element 19 moves relative to the housing element 11.

[0099] From Fig. 1 and 3 it is further apparent that the length of the edge 19.2 of at least one link 19.1 defines a maximum adjustment path V of the adjustment element 19. Additionally or alternatively, the edge 19.2 of at least one link 19.1 can be contoured in such a way that a movement of at least one vibration damper 13 assigned to the link 19.1 and thus of a bearing segment 12 arranged on this vibration damper 13 from the active position I into the passive position II or vice versa can be carried out when the adjustment element 19 is adjusted by a part, in particular a maximum of half or a maximum of one third, of the maximum adjustment path V. This results in the advantage that, in particular when the bearing segment 12 moves from the passive position II to the active position I, the remaining adjustment path V can be used to generate a preload force in the damping element 13.3.In other words, when the adjustment element 19 is adjusted over the entire adjustment range V, the bearing segment 12 is moved from the passive position I to the active position II or vice versa, whereby the respective end positions of the bearing segment are already reached after a portion of the maximum adjustment range. Furthermore, when the adjustment element 19 is adjusted over the entire adjustment range V, in particular during a movement from the passive position II to the active position I, a preload force is generated in the damping element 13.3 by pressing the bearing segment 12 against the rotor element 15 arranged in the plain bearing 10.

[0100] Fig. 6 further shows a schematic view of a plain bearing 10. It can be seen that at least one drive 20 is included, wherein the drive 20 is operatively connected to the adjusting element 19 such that the adjusting element 19 can be moved, in particular rotated, at least in sections by the drive 20 in order to move at least one bearing segment 12 from the active position I to the passive position II or vice versa. It can be seen from Figs. 1 and 3 that the plain bearing 10 comprises four vibration dampers 13 and four bearing segments 12, wherein each vibration damper 13 is connected at least in sections to a respective bearing segment 12. The vibration dampers 13 have an identical structure and are mounted or arranged in an identical manner on the housing element 11. The vibration dampers 13 are distributed at equidistant intervals over the circumference of the housing element 11.By moving the adjusting element 19 relative to the housing element 11, all bearing segments 12 or vibration dampers 13 can be moved from the active position I to the passive position II or vice versa, whereby the movement can be carried out simultaneously.

[0101] Fig. 7 shows a schematic view of a transmission 50, wherein the transmission 50 comprises at least one plain bearing 10.

[0102] Fig. 8 shows a schematic view of a method 100 for operating a plain bearing 10, the method 100 comprising:

[0103] Transferring 110 at least one bearing segment 12 from the active position I to the passive position II when a rotational speed of a rotor element 15 mounted in the plain bearing 10 reaches or exceeds a threshold value S,

[0104] Transferring 120 at least one bearing segment 12 from the passive position II to the active position I when a rotational speed of a rotor element 15 mounted in the plain bearing 10 reaches or falls below a threshold value S.

[0105] Fig. 9 shows a schematic sectional view of a plain bearing 10. The plain bearing 10 basically has the same functionality as already described with reference to Figs. 1 to 6. The plain bearing 10 is shown in Fig. 9 in the active position I.

[0106] The vibration damper 13 of the plain bearing 10 shown in Fig. 9 has a different structure compared to Figs. 1-4. The vibration damper 13 is shown in an enlarged sectional view in Fig. 10. It can be seen from Fig. 10 that the vibration damper 13 comprises at least one damping element 13.3. The damping element 13.3 is designed to at least partially dissipate the kinetic energy introduced into the vibration damper 13. In the present case, the damping element 13.3 is designed as a disc spring stack, which is shown in detail in Fig. 11. From Fig. 9 and 10 it is further apparent that the vibration damper 13 is connected to the bearing segment 12 via the second contact element 13.2 and is supported on an abutment 18 via the first contact element 13.1, so that a kinetic energy introduced into the vibration damper 13 can be absorbed and at least partially dissipated by the damping element 13.3.

[0107] Fig. 11 shows that the disc spring stack 13.3 comprises a plurality of disc springs arranged coaxially with respect to their central axis. The disc springs are arranged serially or in series. Fig. 12 shows an alternative embodiment of a disc spring stack in which two disc springs are arranged in parallel and the stacks of parallel disc springs are again arranged serially. In principle, the structures described with reference to Figs. 11 and 12 can be combined as required.

[0108] Furthermore, it can be seen from Fig. 9 and 10 that a first sealing element 16 is provided to seal a gap between the first contact element 13.1 and the housing element 11 and that a second sealing element 16 is also provided to seal a gap between the first contact element 13.1 and the second contact element 13.2.

[0109] Bezuq szei chen li ste

[0110] 10 plain bearings

[0111] 11 Housing element

[0112] 12 bearing segment

[0113] 13 vibration dampers

[0114] 13.1 First contact element

[0115] 13.2 Second contact element

[0116] 13.3 Damping element / friction spring / disc spring stack

[0117] 13.4 Backdrop element

[0118] 14 Lubrication gap

[0119] 15 Rotor element

[0120] 16 Sealing element

[0121] 17 Preload element / coil spring

[0122] 18 abutments

[0123] 19 Adjustment element

[0124] 19.1 Scenery

[0125] 19.2 Edge

[0126] 20 drive

[0127] 21 Temperature sensor

[0128] 22 storage rooms

[0129] 23 Lubricant nozzle

[0130] 24 joint

[0131] 25 ring element

[0132] 26 Contact section

[0133] 27 recess

[0134] 50 gearboxes

[0135] 100 procedures

[0136] 110 Transfer

[0137] 120 Transfer

[0138] I Active position

[0139] II Passive position

[0140] S gap size

[0141] V adjustment range

Claims

Patent claims 1. A plain bearing (10), comprising at least one housing element (11), at least one bearing segment (12), and at least one vibration damper (13), wherein the bearing segment (12) is connected, at least in sections, to the vibration damper (13), such that a vibration introduced into the bearing segment (12) can be introduced into the vibration damper (13), and wherein the vibration damper (13) is movably mounted, at least in sections, on the housing element (11), such that the bearing segment (12) can be moved between an active position (I) and a passive position (II) by a movement, in particular a linear movement, of the vibration damper (13) relative to the housing element (11), wherein in the active position (I) a gap dimension (S) of a lubricating gap (14) between the bearing segment (12) and a rotor element (15) mounted in the plain bearing (10) is smaller than in the passive position (II).

2. Plain bearing (10) according to claim 1, characterized in that the vibration damper (13) comprises at least one damping element (13.3), wherein the damping element (13.3) is designed to at least partially dissipate kinetic energy introduced into the vibration damper (13), wherein in particular the damping element (13.3) is designed as a friction spring (13.3) or a disc spring stack (13.3).

3. Plain bearing (10) according to claim 2, characterized in that a preload of the damping element (13.3) in the active position (I) is between 25% and 35%, in particular between 28% and 32%, preferably 30%, of a maximum spring travel and / or that a preload of the damping element (13.3) in the passive position (II) is between 3% and 7%, in particular between 4% and 6%, preferably 5%, of a maximum spring travel.

4. Plain bearing (10) according to one of claims 2 or 3, characterized in that the vibration damper (13) comprises a first contact element (13.1) and a second contact element (13.2), wherein the damping element (13.3) is arranged between the first contact element (13.1) and the second contact element (13.2) in such a way that a movement of the first contact element (13.1) in the direction of the second contact element (13.2) causes a force to be introduced into the damping element (13.3).

5. Plain bearing (10) according to claim 4, characterized in that the first contact element (13.1) and the housing element (11) are connected in a form-fitting manner at least in sections, wherein in particular the form-fitting arrangement is designed such that exclusively or substantially exclusively a linear, in particular radial, movement of the first contact element (13.1) relative to the housing element (11) can be carried out at least in sections.

6. Plain bearing (10) according to one of claims 4 or 5, characterized in that the first contact element (13.1) and the second contact element (13.2) are connected in a form-fitting manner at least in sections, wherein in particular the form-fitting arrangement is designed such that exclusively or substantially exclusively a linear, in particular radial, movement of the first contact element (13.1) relative to the second contact element (13.2) can be carried out at least in sections.

7. Plain bearing (10) according to one of claims 4 to 6, characterized in that at least one sealing element (16) is arranged on at least one contact element (13.1, 13.2), wherein the sealing element (16) seals a gap between the first contact element (13.1) and the housing element (11).

8. Plain bearing (10) according to one of the preceding claims, characterized in that at least one prestressing element (17) is included, wherein the vibration damper (13) is held by the prestressing element (17) in contact with at least one abutment (18) of the plain bearing (10), wherein preferably the prestressing element (17) is designed as a spiral spring (17).

9. Plain bearing (10) according to one of the preceding claims, characterized in that at least one adjusting element (19) is included, wherein by a movement of the adjusting element (19) relative to the housing element (11) the bearing segment (12) can be moved from the active position (I) into the passive position (II) or vice versa.

10. Plain bearing (10) according to claim 9, characterized in that the adjusting element (19) comprises at least one slotted guide (19.1) and wherein the vibration damper (13) comprises at least one slotted guide element (13.4), wherein the slotted guide element (13.4) is at least partially received in the slotted guide (19.1) and is at least partially in contact with an edge (19.2) of the slotted guide (19.1) and wherein the edge (19.2) of the slotted guide (19.1) is contoured such that a movement range of the vibration damper (13) with respect to a movement, in particular a radial movement, relative to the housing element (11) can be changed by a movement of the adjusting element (19) relative to the housing element (11).

11. Plain bearing (10) according to claim 10, characterized in that the link element (13.4) is rotatably mounted, so that the link element (13.4) is set in rotation upon movement of the adjusting element (19) relative to the housing element (11).

12. Plain bearing (10) according to one of claims 9 to 11, characterized in that at least one drive (20) is included, wherein the drive (20) is operatively connected to the adjusting element (19) in such a way that the adjusting element (19) can be moved at least in sections by the drive (20) in order to transfer the bearing segment (12) from the active position (I) into the passive position (II) or vice versa.

13. Plain bearing (10) according to one of the preceding claims, characterized in that at least one temperature sensor (21) is arranged on the bearing segment (12), wherein a material temperature of the bearing segment (12) can be detected by the temperature sensor (21).

14. Transmission (50), in particular turbo transmission, comprising at least one plain bearing (10) according to one of the preceding claims.

15. Method (100) for operating a plain bearing (10), wherein the plain bearing (10) is designed according to one of claims 1 to 13, the method (100) comprising at least one of the following: Transferring (110) at least one bearing segment (12) from the active position (I) to the passive position (II) when a rotational speed of a rotor element (15) mounted in the plain bearing (10) reaches or exceeds a threshold value, Transferring (120) at least one bearing segment (12) from the passive position (II) to the active position (I) when a rotational speed of a rotor element (15) mounted in the plain bearing (10) reaches or falls below a threshold value.

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