DRIVE TRAIN MOUNTING ASSEMBLY WITH A TORQUE SUPPORT, AND INDUSTRIAL TRANSMISSION EQUIPPED THEREWITH, AND METHOD FOR ADJUSTING A DRIVE TRAIN MOUNTING ASSEMBLY AND USE

Abstract

A drive train mounting assembly for an industrial transmission, in particular for a rotor with double mounting or momentum mounting of a wind power installation, includes a first housing, a shaft of a drive train, a mounting supported in the first housing and supporting the shaft, a second housing, a transmission component surrounded by the second housing and coupled to the shaft, and a torque support designed to counteract a gravity-induced torque which acts on the shaft by the transmission component. The torque support is fastened to the first housing and includes an adjustable unit.

Claims

1.-38. (canceled)

39. A wind power installation, comprising: an industrial transmission, in particular with a planetary gear stage in particular for a rotor with double mounting or momentum mounting of the wind power installation, the wind power installation comprising: a drive train mounting assembly including a first housing, a second housing, and a shaft of a drive train; a mounting supported in the first housing and supporting the shaft; a transmission component including the planetary gear stage which is surrounded by the second housing and coupled to the shaft; a generator supported on the second housing and forming with the transmission a transmission/generator combination which is disposed in such a way as to float freely in space on one side of the drive train; and a torque support designed as a mechanical/hydraulic bridge between the first and second housings to counteract a gravity-induced (tilting moment) torque which acts on the shaft by the transmission component, said torque support being fastened to the first housing and comprising an adjustable unit.

40. The wind power installation of claim 39, wherein the adjustable unit is designed in at least one of two ways, a first way in which the adjustable unit generates on at least one circumferential position pairing, in particular at 6 and 12 o'clock and/or at 3 and 9 o'clock, a first force pair which is substantially axially aligned about an axial center of the drive train, in particular a force pair that is directed counter to tilting and/or yawing moments, a second way in which the adjustable unit generates on at least one circumferential position pairing, in particular at 3 and 9 o'clock and/or at 6 and 12 o'clock, a second torque-generating force pair which is substantially radially/tangentially aligned and acts orthogonally in relation to the axial center of the drive train, in particular a force pair that is directed counter to torques.

41. The wind power installation of claim 39, wherein the adjustable unit is designed to ensure on at least two mutually opposite circumferential positions vibration damping or vibration decoupling between interacting coupling parts in at least one coupling portion, in particular by a pre-tensioning unit per circumferential position.

42. The wind power installation of claim 39, wherein the adjustable unit is designed to act on at least two mutually opposite predefined circumferential positions, in particular at least on the circumferential positions 6 o'clock and 12 o'clock and/or at 3 and 9 o'clock, in a resilient and/or damping manner between traction members or traction members/compression tappet of the first and second housings.

43. The wind power installation of claim 39, wherein the drive train mounting assembly comprises a plurality of adjustable units designed to provide reactive force pairs acting about all three momentum axes, or acting three-dimensionally about all three spatial directions, and optionally to also actively adjust the reactive force pairs.

44. The wind power installation of claim 39, wherein the torque support is supported exclusively on the first housing, independently of any connection to a machine support or similar base disposed below the drive train or below the drive train mounting assembly.

45. The wind power installation of claim 39, wherein the torque support is supported on the first housing in support points/regions disposed along an outer connection diameter between the first housing and the second housing, in particular in at least four circumferential portions or fully circumferentially, in particular in the case of a rotationally symmetrical distribution of the support points/regions across an entire circumference, and/or wherein at least one of the first housing and the second housing is designed to provide at least partially at least one coupling partner for a mutual support of the first and second housings on one another, in particular designed integrally in one piece on an external shell face of the respective one of the first and second housings.

46. The wind power installation of claim 39, wherein the adjustable unit is designed for adjustment in terms of force and/or direction of action and/or force-engagement point/region.

47. The wind power installation of claim 39, wherein the torque support, in particular the adjustable unit of the torque support, is provided in an upper region and/or in a lower region of an interface between the first and second housings and/or wherein the torque support, in particular the adjustable unit, is diagonally connected, in particular in such a manner that a hydraulic or mechanical compensation is relatively soft in an axial direction and relatively stiff in a tilting direction.

48. The wind power installation of claim 39, further comprising a radially projecting flange or force-engagement collar or segment, which is provided on the second housing and delimited or encompassed, in particular in an annular manner, on an axial position by the torque support, in particular by the adjustable unit.

49. The wind power installation of claim 39, wherein the torque support is disposed in such a manner that an erection force acting substantially axially and counter to a tilting moment is provided so as to engage on the second housing; and/or wherein the torque support is disposed in such a manner that a supporting force which acts substantially axially but symmetrically eccentrically so as to counteract a yawing moment is provided so as to engage on the second housing.

50. The wind power installation of claim 39, wherein the torque support comprises a support unit which acts on the first housing and is disposed in such a manner that a force that acts substantially vertically or in a circumferential direction is provided so as to engage on the second housing.

51. The wind power installation of claim 39, wherein the transmission component is disposed between the shaft and the generator which engages on the second housing or on the transmission component.

52. A method for adjusting a mounting of a drive train mounting assembly of an industrial transmission, in particular in a drive train having a rotor with double mounting or momentum mounting, of a wind power installation, the method comprising: supporting a shaft of the drive train via a mounting in a first housing; surrounding a transmission component by a second housing and coupling the transmission component to the shaft; mounting the mounting and the transmission component in relation to one another; supporting a second housing and the transmission component on the first housing by a torque support that counteracts a gravity-induced torque which acts on the shaft by the transmission component, in particular in a drive train having a generator which is supported on the second housing; and establishing an active force-controlled and/or path-controlled feedback-control of an erection force or supporting force exerted on the second housing and dissipated by way of the first housing by an adjustable unit that acts between the first housing and the second housing, in particular in the drive train mounting assembly or in the industrial transmission or in the wind power installation.

53. The method of claim 52, further comprising providing vibration damping or vibration decoupling on at least two mutually opposite circumferential positions in at least one coupling portion between interacting coupling parts by the adjustable unit, in particular by a pre-tensioning unit per circumferential position.

54. The method of claim 52, wherein the active force-controlled and/or path-controlled feedback-control of the erection force or supporting force is established by the adjustable unit based on momentary measured values of a force/path sensor and/or acceleration sensor installed in the drive train.

Description

BRIEF DESCRIPTION OF THE FIGURES

[0051] The invention will be described in yet more detail by way of example by means of preferred exemplary embodiments in the following figures of the drawing, whereby the features illustrated hereunder can represent an aspect of the invention individually as well as in combination, and wherein reference to reference signs which are not explicitly described in a respective figure of the drawing is made to the other figures of the drawing. In each case in a schematic illustration:

[0052] FIGS. 1A, 1B show a drive train having a support of the drive train according to the prior art in a lateral view and in a partially sectional lateral view;

[0053] FIG. 2 shows a drive train mounting assembly according to a first exemplary embodiment, in particular for a rotor of a wind power installation, in a partially sectional lateral view;

[0054] FIG. 3 shows a drive train mounting assembly according to a further exemplary embodiment, in particular for a rotor of a wind power installation, in a partially sectional lateral view;

[0055] FIGS. 4A, 4B show a drive train mounting assembly according to a further exemplary embodiment, in particular for a rotor of a wind power installation, in a lateral view and in a sectional frontal view; and

[0056] FIGS. 5A, 5B show a drive train mounting assembly according to a further exemplary embodiment, in particular for a rotor of a wind power installation, in a lateral view and in a sectional frontal view.

DETAILED DESCRIPTION OF THE FIGURES

[0057] First, the invention will be explained in general with reference to all reference signs and figures. Particularities or individual aspects of the invention, or aspects of the invention that are readily visible/visualizable in the respective figure, will be discussed individually in the context of the respective figure.

[0058] A drive train has the following components, for example: hub 1, shaft 2 (in particular rotor shaft of a wind power installation), rotor bearing housing 3, rotor bearing/rotor mounting 4 (in particular torque mounting or tapered roller mounting), coupling 5, transmission 6 in the transmission housing 7, torque support unit or weight support 8 with coupling to the base (machine support), and a generator 9. The structure of the drive train is heavily stressed in the context of high weights in the event of strong, also dynamic, forces, for example also generated by bending moments proceeding from a rotor of a wind power installation that is coupled to the shaft, even when the torque support unit, or weight support 8 is of a comparatively good design/size. Apart from the rotor shaft, the flanged connection to the planet carrier, the planet carrier bearings and the torque support, the machine support is also exposed to quite high stress in the process. In this context, it is a matter of interest to achieve an advantageous type of mounting of the drive train, which can positively receive and transmit stresses of this type.

[0059] Provided is a drive train mounting assembly 10, for example for an industrial transmission 20, having a shaft 2 which is supported in a rotor mounting 14 (here: double mounting, or torque mounting). The rotor mounting 14 is encased or surrounded by a rotor bearing housing 13 (first housing). A transmission component 16, in particular with a planetary gear stage, is disposed in a transmission housing 17 (second housing), and the shaft 2 interacts with this transmission component 16. A torque support 18 (torque and/or tilting moment support) is provided as a type of mechanical/hydraulic bridge between the two housings 13, 17, in particular on an connection (diameter) which lies radially outside as far as possible, wherein supporting takes place on the first housing 13, for example in the points P1, P2 illustrated. The support in the region P1 can advantageously also take place symmetrically but eccentrically, in particular also so as to ensure a supporting and/or damping function in the yawing direction (perpendicular to the tilting and axial direction, rotating movement about the tower axis).

[0060] The following components are in particular provided for the support on the first housing 13: traction member 13.5, tappet/cam 13.7.

[0061] The following components are in particular provided for the support on the second housing 17 (or the transmission of force from the second housing): radially projecting flange 17.1 or similar force-engagement collar or segment or tappet, individual force-engagement segment 17.3 (in particular lug or tab or web); traction member 17.5, tappet/cam 17.7.

[0062] The torque support 18 enables a force to be received and transmitted from the transmission housing 17 by way of the bearing housing 13 into a/the base 101. In the process, an erection force F1 which acts counter to the weight/gravity g on the transmission housing 17 is provided (in particular as a force pair about the central longitudinal axis, or shaft axis) in the manner of a restoring supporting moment M2 which acts counter to a/the tilting moment M1. Optionally, the torque support 18 can additionally also cause or provide or actively generate a supporting force F2 by means of which a/the torque M3 acting on the transmission component and transmitted to the transmission housing can be counteracted. The erection force F1 and the supporting force F2 can optionally also be actively feedback-controlled, for example based on momentary measured values of force/path sensors at the respective interface.

[0063] The torque support 18 preferably has at least one adjustable unit 18.1, in particular comprising: pre-tensioning unit 18.2 (in particular axial, in particular having at least one mechanical spring), support unit 18.3 (in particular annular or semi-/shell-shaped); diagonal connection 18.5, further support unit 18.6 (in particular annular or semi-/shell-shaped), further pre-tensioning unit 18.7, or at least one correspondingly installed decoupling element (in particular disposed in the radial plane and/or aligned in the circumferential direction).

[0064] The type of support can optionally be actively adjusted and also feedback-controlled. For this purpose, at least one force/path sensor 19 can optionally be provided, which can be connected to a control/feedback-control unit.

[0065] The drive train mounting assembly 1 described here offers the advantages described herein in a particularly noticeable manner in particular also in the case of a wind power installation 100, wherein a machine support or similar base 101 for the drive train is disposed on a tower 102.

[0066] The invention will yet be explained more specifically hereunder with reference to the individual figures.

[0067] Illustrated in FIG. 1 is a known drive train assembly with reference to a wind power installation. A generator 9 is fastened to the transmission housing 7. The transmission housing is supported toward the bottom on the machine support 101 by way of a support unit 8 (torque and weight support). The rotor bearing housing 3 is shown in the lateral view in FIG. 1A, and the rotor bearing housing 3 is shown in a sectional lateral view in FIG. 1B. The rotor shaft 2 is comparatively massive, or large in diameter, and the rotor bearing 4 is supported in a comparatively robust manner by way of a rather large longitudinal portion on the machine support 101.

[0068] The weight of the transmission, and optionally of a generator flanged to the transmission housing, herein stress the rotor shaft, the rotor bearings, the planet carrier and in particular a/the first transmission stage, the planet carrier bearing thereof and the flanged connections between the rotor shaft and the transmission. Rotating bending is created in the rotating elements as a result, which has to be disadvantageously taken into account when sizing said rotating elements.

[0069] A first exemplary embodiment of the drive train mounting assembly 10 is shown in FIG. 2. The force pair F1 generated on the flange 17.1 or corresponding radial appendages causes an erection force counter to a pitching/tilting moment M1. A predefined type of support or development of force, or else an active feedback-control can be selectively implemented by way of the adjustable unit 18.1, for example also based on momentary measured values of at least one force/path sensor 19 and/or of an acceleration sensor 21. The transmission of force and the support of the latter on the rotor bearing housing 13 can take place in particular in the regions or points P1. This support can advantageously also take place symmetrically but eccentrically, in particular so as to ensure a supporting and/or damping function also in the yawing direction (perpendicular to the tilting and axial direction, rotating movement about the tower axis), in particular in the case of at least one adjustable unit 18.1 being disposed therebetween, comprising at least one pre-tensioning unit 18.2 in at least one coupling portion between interacting coupling parts 17.1, 18.3. Active damping in the case of vibrations, for example about the pitching or yawing axis, can be generated in conjunction with data from at least one sensor (in particular data from the acceleration transducer 21), and/or said vibrations can be passively damped by elastic elements.

[0070] The rotating bending resulting from the weight of the transmission/generator combination can be significantly reduced by means of the assembly according to the invention for example for a wind power installation having a rotor shaft with double mounting, or torque mounting, and a transmission and generator linked thereto. According to the invention, the rotating bending stress can be significantly reduced, and at the same time tilting in the transmission, in particular in a/the first planetary gear stage, can be reduced; as a result, not least a better supporting behavior of the toothings can also be achieved as a result. Moreover, an improved force reflux with fewer negative effects resulting from a usually dissimilar deformation between the machine support and the drive train (transmission and the linkage of the latter to the rotor shaft unit) can be achieved by the transmission torque being supported by way of the rotor bearing housing, and also by a torque support of the transmission. The pitching moments, in particular resulting from wind loads (in wind power installations) to this extent do not have to be supported by way of the machine support and also do not lead to additional loads as a result. Thanks to the type of mounting/support according to the invention, oversizing of the affected machine elements (rotor shaft, rotor bearing, rotor shaft flange to the planet carrier, planet carrier, planet carrier bearing, transmission and generator housing flanges) can now also be dispensed with, as a result of which an advantage in terms of cost and weight can also be generated. To this extent, an additional support of the weight between the generator and the machine support is no longer required; a support structure for supporting the weight below the generator becomes dispensable; a pitching movement of the drive train can now be absorbed or damped by way of the bearing housing without unfavorable leverage forces or excessive loads which could affect the overall structure.

[0071] The bending moment which is induced on the transmission housing (torque support) by the mass of the transmission and optionally the mass of the generator can preferably be supported in relation to the rotor bearing housing by an adjustable unit, or by at least one adjustable element, which is/are preferably disposed at least in the upper region and/or the lower region of the interface between the transmission housing and the rotor bearing housing. In this way, the adjustable unit compensates the negative effect of the bending moment on the affected machine elements, and at the same time aligns the corresponding transmission components, for example a ring gear of a first planetary gear stage in relation to the planet carrier, and the process can also ensure a better supporting behavior in the toothings.

[0072] According to the invention, a force-fit can be established between the non-rotating housing parts of the transmission and of the rotor bearing housing. The weight bending moment created by the weight is compensated by an erection force, in particular by an erection force in the form of a force pair that engages on the transmission housing at the bottom and the top.

[0073] In a further function, an almost load-free axial movement along the rotor shaft axis can be generated or permitted in that the adjustable unit, or the at least one adjustable element thereof, is/are diagonally connected in such a way that the weight bending moment continues to be received by a force pair of identical size, without the axial movement being impeded. In the present context, in particular in the context with a hydraulic and/or mechanical (force or position) compensation, a diagonal connection can also be referred to as a comparatively soft support in the actual direction (depending on the inclination of the shaft at least approximately in the horizontal plane) and a comparatively stiff support in the vertical direction, or in the tilting direction. A direction of movement of the transmission relative to the shaft, or relative to the rotor bearing housing, which is caused by the force of gravity is to be understood in particular as the tilting direction herein; the tilting does not necessarily have to take place about an axis which is orthogonal to the shaft, but depending on the dynamic state may also be a multi-axis tilting/yawing movement.

[0074] The destressing in terms of the weight and thus of the rotating bending moment for the rotating parts that can be implemented by means of the assembly according to the invention, is preferably carried out in those regions of the drive train, for example of a wind power installation, that are anyway capable of or provided for receiving high loads and bending moments, for example resulting from wind loads. Any potential additional enhancement or reinforcement for ensuring the desired destressing in terms of weight and bending moment is therefore associated with a comparatively minor complexity and at best no disadvantages which potentially result from a dissimilar deformation behavior between the drive train on the machine support; however circumstances of this type are significantly less disadvantageous in the assembly according to the invention than in a known weight support below the generator.

[0075] A second exemplary embodiment of the drive train mounting assembly 10 is shown in FIG. 3, in which the torque support 18 also comprises a further support unit 18.6 which is supported on the first housing 13 in the regions or points P2 and by means of which a supporting force F2, which is aligned so as to be substantially vertical (radial/tangential), or in the circumferential direction and acts counter to a (drive) torque M3 can be exerted on the transmission housing (with the resultant supporting moment M2), in particular likewise provided by at least one force pair on at least approximately mutually opposite circumferential positions, in particular in the case of at least one adjustable unit disposed therebetween, comprising at least one pre-tensioning unit in at least one coupling portion between interacting coupling parts 17.3, 18.6. A predefined type of support or development of force, or else an active feedback-control can be selectively implemented by way of a/the corresponding adjustable unit 18.1, or by means of individual pre-tensioning or decoupling elements 18.7, for example also based on momentary measured values of at least one force/path sensor 19, can also be implemented in terms of this supporting force F2. The transmission of force takes place, for example, in each case between the rotor bearing housing and radially projecting flange portions 17.1 or similar force-engagement collars or segments or tappets on the transmission housing, or between the rotor bearing housing and individual force-engagement segments 17.3 on the transmission housing, in particular lugs or tabs or webs.

[0076] The at least one adjustable unit herein can ensure vibration damping at different circumferential positions for a/the force pair F1 which is aligned so as to be at least approximately axial (or parallel to the drive train axis or a rotation axis), as well as for a/the force pair F2 which is aligned so as to be at least approximately tangential/radial (thus orthogonal to the rotation axis), or a vibration damping implemented in the corresponding direction of action. The corresponding pre-tensioning and support units herein advantageously engage on circumferential positions at least approximately at 12 o'clock and 6 o'clock, as well as circumferential positions at least approximately at 3 o'clock and 9 o'clock (in particular diametrically opposite), or on four circumferential positions which are in each case offset by at least 90 in the circumferential direction, wherein the respective circumferential position can also be a circumferential segment or region of, for example, 10 to 15, depending on the design embodiment of the corresponding coupling portion. A plurality of adjustable units are preferably provided, which each have an individual direction of action and spring/damper characteristic and are optionally also individually adjustable, controllable and/or feedback-controllable. This facilitates a highly individual situation-dependent response to momentary dynamic and also drive train-specific stresses in a plurality of spatial directions or even in all spatial directions.

[0077] In other words: in addition to the support unit/elements for the erection force, a further advantage can be achieved by means of the torque support, in that at least two further support elements, which act in the vertical direction and are likewise supported on the rotor bearing housing, are also used so as to be combined by means of the torque support. As a result of the rotor shaft being guided by way of the rotor shaft bearings in the rotor bearing housing, this additional support which in functional terms is to be described as a torque support is imparted the same relative movements as a transmission of torque support, and no additional loads resulting from the pitching loads of the rotor blades of the installation being received are created in the process. To this extent, such a functional integration in the torque support, or such a dual function of the torque support, offers a particularly slim design which is particularly tolerant in terms of forces/torques/movements.

[0078] The machine support (base) illustrated in FIGS. 2 and 3 herein can also be designed to be significantly shorter, or be significantly shortened in comparison to the axial extent customary to date in particular in wind power installations (no additional support point below the second housing/transmission housing or the generator); this is because the connection to the base can advantageously take place in the region of the rotor bearing housing (first housing), optionally exclusively there. This additional advantage is only visualized by way of example by the region of the machine support that is illustrated in dotted lines here. The connection of the machine support to a tower or a similar bearer lying therebelow can accordingly also be embodied in a slimmer manner. Also to this extent, the possibilities in terms of material savings described here increase exponentially in favor of a slim design.

[0079] A height tolerance mounting portion z1 is also indicated in FIG. 3; depending on the desired degree of freedom of movement, the freedom of movement in the vertical direction can be structurally restricted and/or be limited by counterforces generated actively and/or passively by pre-tensioning units or the like. The person skilled in the art can optimize this freedom of movement z1 individually depending on the specific application, in particular also in combination with an integrated damping function.

[0080] With reference to the different axes of action of torque, two differently adjustable units 18.1 may also be referred to in the exemplary embodiment according to FIG. 3, which are implemented for generating at least two different counter torques.

[0081] A further exemplary embodiment of the drive train mounting assembly 10 is shown in FIG. 4, in which the torque support 18 likewise comprises a tilting moment support as well as a torque support. The transmission of force takes place, for example, in each case between tappets 13.5 on the rotor bearing (housing) and tappets transmission (housing), or between traction members/cams 13.7 on the rotor bearing (housing) and tappets/cams 17.7 on the transmission (housing). The mutual engagement of the two housings 13, 17 in this exemplary embodiment can also be referred to/described as a type of claw coupling in which the two housings provide in each case one of the coupling partners, in particular in that the coupling elements or claws, or the tappets and traction member described further above, are formed in one piece so as to be integral on the respective housing. This not least also offers a high robustness and can avoid unnecessary relative movements or the loosening of parts. The mutually engaging traction members/cams of the two transmission housings are shown in FIG. 4A, and the exemplary distribution of the individual force transmission locations in the circumferential direction is illustrated in FIG. 4B, wherein six interfaces for the two different types of support or torque/force are in each case provided here in particular, thus repeating after each 60 in terms of a circumferential angle. The traction members can in particular also be advantageously positioned symmetrically but eccentrically; a supporting and/or damping function in the yawing direction (perpendicular to the tilting and axial direction, thus in the sense of a rotating movement about the tower axis) can also be advantageously ensured as a result, so that the planet carrier bearings are in particular also destressed in the case of vibrations, for example in the yawing direction.

[0082] With reference to the different axes of action of torque, at least two different adjustable units 18.1 may also be referred to in the exemplary embodiment according to FIG. 4, which are implemented for generating at least two different counter torques.

[0083] A further exemplary embodiment of the drive train mounting assembly 10 is shown in FIG. 5, in which the scope of functions of the torque support not only comprises a tilting moment support but also a yawing moment support which is particularly effective in the implementation shown. This type of support enables the absorbing and damping of vibrations, for example about the tower axis (yawing axis), in a particularly effective manner. Likewise, the adjustable unit 18.1 in an effective arrangement in the 12 o'clock and 6 o'clock position, respectively, can be effectively utilized to absorb and to damp vibrations, for example about the pitching/tilting axis. The corresponding mutually engaging traction members/cams 13.7, 17.7 of the two housings are shown in FIG. 5A (comparable to the housing coupling parts already explained in the context of the previous exemplary embodiments), moreover the traction members 13.5, 17.5 and the lateral traction members/compression members 13.9, 17.9 are shown in two planes which are aligned so as to be at least approximately mutually orthogonal, cf. also FIG. 4B. An exemplary distribution of the individual force transmission locations in the circumferential direction is illustrated in FIG. 5B, wherein the multiple e functionality of the lateral traction members/compression members 13.9, 17.9, which are preferably eccentric to the maximum, is particularly shown here, specifically as respective force transmission locations in the circumferential direction as well as in the axial direction. In other words: in addition to the components of the at least one adjustable unit 18.1 which have been described further above, the assembly 10 can also comprise the following further components, in particular in each case as a constituent part of a/the respective adjustable unit 18.1: lateral traction members/compression members 13.9 of the rotor bearing housing, in particular in the region of 3 o'clock and 9 o'clock, lateral traction members/compression members 17.9 of the transmission housing, in particular in the region of 3 o'clock and 9 o'clock, a further pre-tensioning unit 18.9, or at least one correspondingly aligned decoupling element, in particular axially aligned. As a result, a yawing force F3 can be counteracted in a particularly effective manner. Side note: the force F3 according to the implementation shown is indeed a force which is aligned substantially in the axial direction, like the force F1, but is here nevertheless provided with another reference sign because the corresponding reactive force pair generates a counter torque about another axis than a/the reactive force pair according to the force-engagement points of the forces F1. In this sense, with reference to the different axes of action of torque, reference may also be made to at least three different adjustable units 18.1 which are implemented in the exemplary embodiment according to FIG. 5.

[0084] It is to be mentioned that a yawing moment support does not necessarily have to take place in the manner according to the exemplary embodiment of FIGS. 5, but can already be implemented when the traction members 13.5, 17.5 described in the context of FIG. 4 are disposed, for example, so as to be slightly eccentric, thus disposed laterally eccentrically in a horizontal plane, on both sides of the central vertical axis of the drive train, or of the shaft 2. However, the exemplary embodiment described in FIG. 5 offers, or enables, more effective damping in particular by virtue of the larger effective lever arm. To this extent, a circumferential position which deviates from the circumferential position illustrated in each case in the figures can also be implemented for the traction members 13.5, 17.5. The lateral traction members/compression members 13.9, 17.9 which are in each case eccentric as far as possible, are nevertheless provided with another reference sign here, because a transmission of torque should also be able to take place in the circumferential direction on these members, cf. the force arrows F2 in FIG. 5A.

LIST OF REFERENCE SIGNS

[0085] 1 Hub [0086] 2 Shaft, in particular rotor shaft of a wind power installation [0087] 3 Rotor bearing housing [0088] 4 Rotor bearing/rotor mounting, in particular torque mounting/tapered roller mounting [0089] 5 Coupling [0090] 6 Transmission, in particular industrial transmission [0091] 7 Transmission housing [0092] 8 Torque support unit, or weight support, with coupling to the base [0093] 9 Generator [0094] 10 Drive train mounting assembly [0095] 13 Rotor bearing housing (first housing) [0096] 13.5 Traction member rotor bearing (housing), in particular in the region of 6 o'clock and 12 o'clock [0097] 13.7 Tappet/cam rotor bearing (housing) [0098] 13.9 Lateral traction members/compression tappet rotor bearing (housing), in particular in the region of 3'clock and 9 o'clock [0099] 14 Rotor bearing/rotor mounting [0100] 16 Transmission component, in particular with planetary gear stage [0101] 17 Transmission housing (second housing) [0102] 17.1 Radially projecting flange or similar force-engagement collar or segment, or tappet [0103] 17.3 Individual force-engagement segment on transmission housing, in particular lug or tab or web [0104] 17.5 Traction member transmission (housing), in particular in the region of 6 o'clock and 12 o'clock [0105] 17.7 Tappet/cam transmission (housing) [0106] 17.9 Lateral traction members/compression members transmission (housing), in particular in the region of 3 o'clock and 9 o'clock [0107] 18 Torque support (torque and/or tilting moment support) [0108] 18.1 Adjustable unit [0109] 18.2 Pre-tensioning unit (in particular axial), in particular having at least one mechanical spring [0110] 18.3 Support unit, in particular annular or (semi-) shell shaped [0111] 18.5 Diagonal connection [0112] 18.6 Further support unit, in particular annular or (semi-) shell shaped [0113] 18.7 Further pre-tensioning unit (or decoupling element), in particular radially aligned [0114] 18.9 Further pre-tensioning unit (or decoupling element), in particular axially aligned [0115] 19 Force/path sensor [0116] 20 Industrial transmission [0117] 21 Acceleration sensor [0118] 100 Wind power installation [0119] 101 Machine support or similar base [0120] 102 Tower [0121] F1 Erecting force [0122] F2 Supporting force [0123] F3 Yawing force, or corresponding reactive force on the system [0124] g Weight [0125] M1 Tilting moment [0126] M2 Supporting moment [0127] M3 (Drive) torque [0128] P1 First support point/region on the rotor bearing housing [0129] P2 Second support point/region on the rotor bearing housing [0130] z1 Height tolerance mounting portion