Drive train mounting assembly with torque support and industrial drive equipped with the drive train mounting assembly, and method and use for adjusting a drive train mounting assembly

Abstract

The invention relates to a drivetrain mounting assembly for industrial drivetrains, in particular for a double-mounted or torque-mounted rotor of a wind power plant, comprising a mounting for a shaft of the drivetrain, which is supported or supportable in a first housing, and a drivetrain component, which is enclosed by a second housing and is coupled to the shaft, and a torque support, which counteracts at least one gravity-induced torque acting on the shaft by means of the drivetrain component; wherein the torque support is supported or fastened on the (first) housing of the mounting of the shaft. The invention also relates to related methods or mounting types and uses.

Description

Technical Field

[0001] This invention relates to a drivetrain mounting assembly having a mounting member for a shaft of the drivetrain, supported in a first housing; a transmission component, surrounded by a second housing and coupled to the shaft; and a torque support member, wherein the torque support member counteracts torque caused by at least one gravitational force acting on the shaft by means of the transmission component. Furthermore, this invention relates to a drivetrain and an industrial transmission device having this type of mounting assembly. Background Technology

[0002] In drive systems where relatively large masses and large components are interconnected, gravity already exerts a significant force, which can also act in a highly dynamic manner on the drive system and corresponding bearing components. Depending on the dynamics and load range, it may be necessary to support individual components relative to gravity and / or fix them relative to excessively dynamic load peaks. For example, dynamic forces and torques are particularly pronounced in wind power equipment due to unpredictable operating and weather conditions, and especially in the case of offshore installations, they impose considerable stress on components designed for long service lives. To this extent, it is desirable to improve the conditions and possibilities that have existed to date for minimizing the forces and torques applied to structural loads.

[0003] In some applications, particular attention must also be paid to so-called rotational bending moments: if the drivetrain is subjected to a large mass of static stress with a large leverage effect on one side (e.g., in addition to dynamic wind events), this results in dynamic loads or cyclic stresses on rotating components (e.g., rotor shafts, particularly the planetary carrier in the first gear stage and / or, for example, rotating connecting elements in flanged embodiments) caused by the rotor of the wind turbine, which is very large in diameter and potentially also rotates at a rather unfavorable frequency / rotational rate. This can lead to very strong effects on the structure and machine supports, as well as the entire assembly including bearings and any couplings. Therefore, minimizing this type of rotational bending moment is of great interest, especially with increased equipment power and component weight.

[0004] To date, the main issue has been the excessive size of the corresponding cost-intensive and material-intensive components, particularly based on relatively high safety factors. Currently, particularly heavy or large-weight components or particularly cantilevered components of the transmission system are typically supported in the direction of the machine support (base), especially in the area of ​​the generator, which is located behind the transmission components, i.e., further away from the rotor (torque support unit, or weight support connected to the base).

[0005] US2016 / 061191 A1 describes a claw-type connector for a drivetrain of a wind power generation device, wherein the claw is supported relative to a base at the interface between the end side of a planetary gear ring and a shaft flange, wherein a damper is provided on the side of the claw.

[0006] Therefore, there is a need for optimization measures to support the torque or weight of drivetrain components (such as gear stages and / or generators), especially in drivetrains used in wind power generation equipment. Summary of the Invention

[0007] The purpose of this invention is to demonstrate measures that can improve torque or gravity support for relatively large mass heavy drivetrain components, particularly gear stages and / or generator torque or weight support, especially in the drivetrain of wind power generation equipment.

[0008] This objective is achieved by a drivetrain mounting assembly having the features of claim 1, by an industrial drive system, by a wind power generation device having the features of the corresponding parallel claims, by a method according to the features of the parallel method claims, and by an application according to the features of the parallel use claims. Preferred design embodiments are set forth in the dependent claims and the following description, which in each case may represent an aspect of the invention individually or in combination with each other. Where one feature is shown in combination with another, this is merely for the purpose of simply visualizing the invention and in no way implies that the feature cannot be an improvement of the invention in the absence of the other features.

[0009] One aspect of the invention relates to a drivetrain mounting component in a transmission system subjected to dynamic and relatively high torque, particularly tilting torque. To this end, a drivetrain mounting assembly with dual or momentum mounts for an industrial transmission, particularly for a rotor in a wind power generator, is provided. This assembly comprises: a mounting component for the shaft of the transmission system (particularly having two axially offset support points), which is supported / can be supported in a first housing; and a transmission component (particularly having a planetary gear stage), which is surrounded by a second housing and coupled to the shaft. According to the invention, a torque support is provided to counteract the (tilting torque) torque (particularly the torque or rotational bending generated by a transmission-generator combination) caused by gravity acting on the shaft by means of the transmission component; wherein the torque support is fastened to the (first) housing of the shaft mounting component. This allows for a considerable reduction in static and dynamic loads applied to the transmission system or commonly rotated components (shaft, transmission, potential coupling). For example, in wind power generation equipment with a rotor shaft having dual mountings, or so-called momentum mountings, and the transmission and generator connected thereto, rotational bending caused by the weight of the generator-transmission combination can be significantly reduced. Structurally, advantages are also gained, particularly regarding the requirements for stiffness and dimensions of the machine supports.

[0010] The weight of the transmission and the generator, which may be flanged to the transmission housing, typically exerts stress on the rotor shaft, rotor bearings, transmission components (especially the planetary carrier and its bearings in the first gear stage), and the potential flange connection between the transmission and the generator. During this process, so-called rotational bending occurs in the rotating elements, which must be taken into account when determining dimensions or designing the overall structure. In this context, the present invention enables a significant reduction in rotational bending stress and simultaneously reduces tilting in the transmission, particularly in the first planetary gear stage. Therefore, better support performance of the transmission teeth can also be achieved. To this extent, the reduction in structural stress achievable according to the invention can also be associated with reduced wear.

[0011] This invention also achieves optimized force return, with relatively small negative impacts from the different deformations in / on the machine supports and in / on the transmission, particularly by means of the transmission torque and the lever weight supported by the torque supports through the rotor bearing housing. For example, in wind power equipment, when the orientation of the shaft and other potential components of the transmission system is at least slightly altered, for example by a slightly tilted rotor, the pitching effect caused by wind loads acting on the rotor and rotor shaft can also be absorbed in an optimized manner; in particular, these pitching effects no longer need to be dissipated through the machine supports as previously required, thus eliminating the need to receive additional loads in the support structure. Instead, depending on the type of support on the first housing, the invention also achieves at least small motion tolerances to this extent. The invention can be advantageously implemented in different types of transmission systems, particularly in cases of relatively large pitching effects. By way of example only, transmission systems with insert planetary gears, particularly in roller presses, can be mentioned as a further potential application.

[0012] In conventional transmission systems, the support is typically downward in the direction of the base / machine support. Previously, the resulting rotational bending moment and pitching effects were often absorbed by the excessive size of the affected machine components (particularly the rotor shaft, rotor bearings, including, for example, the gear stages of the planetary carrier, planetary carrier bearings, and the transmission and generator housing flanges). However, this approach incurs considerable disadvantages in terms of cost and weight, and the weight disadvantage can also have very adverse effects on other equipment components, such as the tower of a wind turbine, which must be designed for a correspondingly higher load-bearing capacity. To better meet these requirements, weight supports have also been used between the generator and the machine support to date. However, one advantage here is that the support structure under the generator is typically not designed for this purpose and can generate additional excessive loads during rapid pitching movements of the transmission; more importantly, the flange connection between the transmission and the generator is thus subjected to additional stress.

[0013] However, according to the present invention, the concept that force flux can also be absorbed and dissipated through the rotor bearing housing is utilized; the gear stage with the generator can also optionally be set in a "floating" manner, i.e., as the free end of the transmission system (especially floating freely in space on one side), which is given a certain degree of motion tolerance, and thus can also perform a predetermined maximum pitch motion in conjunction with the rotor or shaft; therefore, depending on the application of the transmission system and the desired or required stiffness of the transmission system, a considerable degree of motion freedom can optionally be ensured in multiple spatial directions; depending on the stiffness required herein, the supports on the rotor bearing housing can also be designed individually according to individual motion directions, for example according to motion tolerance values, according to pretension, damping (especially by means of elastomeric mountings), etc. Vibration decoupling can also occur here, especially at the interface between the first and second housings. The present invention also achieves a very sustainable and materially efficient mounting, which is also suitable for slender types of structures optimized for gravity, especially in the case of highly dynamic external influences, such as in wind power generation equipment (wind / weather; similar changes in rotor blade adjustment or system / operating conditions).

[0014] The torque support here may have, for example, one or more supports distributed circumferentially on the rotor bearing housing, particularly on the various circumferential portions. In specific cases, the type of support that is particularly advantageous can be selected by those skilled in the art based on other components of the corresponding transmission system, and particularly also on this disclosure.

[0015] The term "axial" as used below should be understood to refer specifically to the orientation according to the extent of the shaft, or according to the orientation of another component of the drivetrain connected to the shaft for axial common orientation. The "axial" orientation can also be at least approximately horizontal, depending on the inclination of the drivetrain, particularly within the range between a rotor or hub on one side and a transmission component or generator on the other. According to one design embodiment, the drivetrain described herein is defined on one side by a rotor and on the other side by a transmission component and / or generator (optionally directly connected to the drive unit).

[0016] When referring to "rotor mounts," other shaft mounts can also be used synonymously; the term "rotor mount" is chosen in this article to visualize the mount as a part of the shaft in which the forces and torques exerted on the shaft by the rotor are supported. Rotor mounts are designed to be relatively robust, strong, and large in size for wind power equipment, for example, especially because rotors can have diameters of many meters (even greater than 100m or even 200m), and therefore due to very high stress / torque.

[0017] Unless used in a neutral tone, anthropomorphic terms may refer to all genders in the context of this disclosure. Any English terms or abbreviations used herein are conventional technical terms in each case and are well known to those skilled in the art who are proficient in English. For completeness, any German terms that are used synonymously or can be used synonymously may be stated (in parentheses) and vice versa.

[0018] If the vertical or gravitational direction is used according to this disclosure, the direction (depending on the tilt of the shaft or / or rotor) is at an angle of at least about 90° relative to the axial direction of the transmission system or the latter's predetermined mounting position (the centerline or axis of rotation of the corresponding transmission component or output shaft, which is horizontal or slightly tilted relative to the latter).

[0019] If planetary gears are mentioned in this disclosure, this generally refers to both planetary gear stages and planetary spur gears.

[0020] The tilting moment, as defined in this disclosure, refers to the moment generated at the interface between the transmission and the rotor shaft by multiplying the weight of the transmission and potentially also the weight of the generator by the weight of the generator, multiplied by the weight of the generator, on the bearing / rotation point of the planetary carrier bearing.

[0021] It has been shown that the present invention is particularly useful in conjunction with the mounted planetary gears or planetary gear stages, especially when the generator is also mounted so as to be oriented in the same axis as the transmission. However, the advantages described herein can also be applied to transmissions with other or additional transmission types / stages.

[0022] According to an exemplary embodiment, at least one adjustable unit generates a first force pair F1 at at least one circumferential position pair, particularly at the 6 o'clock and 12 o'clock and / or the 3 o'clock and 9 o'clock positions, the first force pair F1 being substantially axially oriented about the axial center of the transmission system, particularly pointing towards the force pair F1 opposite to the tilting torque and / or yaw torque.

[0023] According to an exemplary embodiment, at least one adjustable unit generates a second torque-generating force pair F2 at at least one circumferential position pair, particularly at points 3 and 9 and / or 6 and 12. This second torque-generating force pair F2 is substantially radially / tangentially oriented and acts orthogonally relative to the axial center of the transmission system, particularly acting as a force pair F2 opposite to the torque around the shaft. In other words, the at least one adjustable unit is positioned at at least one circumferential position pair to generate counteracting torques around the corresponding spatial axes.

[0024] According to an exemplary embodiment, at least one adjustable unit ensures vibration damping or vibration decoupling in at least one connecting portion between interacting connecting parts at at least two mutually opposing circumferential positions, particularly by means of at least one pre-tensioning unit at each circumferential position.

[0025] According to an exemplary embodiment, at least one adjustable unit is mounted at at least two predetermined circumferential positions opposite each other, particularly at least at circumferential positions 6 and 12 and / or 3 and 9, so as to act in an elastic and / or damped manner between the respective traction member or traction member / compression tappet of the transmission housing and the rotor bearing housing in each case. The respective mutually opposing circumferential positions described herein can also be selected according to the primary load condition and scaled, for example, in terms of number and size.

[0026] According to one exemplary embodiment, the drivetrain mounting assembly includes a plurality of adjustable units that provide pairs of reaction forces acting about all three momentum axes or acting in three dimensions about all three spatial directions, and optionally are also actively adjustable. This also provides particularly effective damping.

[0027] According to one exemplary embodiment, the torque support is supported solely on a first housing or the housing of a shaft mount, independent of any connection to a machine support or similar base disposed below the drivetrain or drivetrain mounting assembly. This also achieves motion tolerance without having to provide machine support over a relatively large axial length and / or in a relatively robust design.

[0028] According to an exemplary embodiment, a torque support member is supported on the (first) housing of the shaft mounting member in support points / regions arranged along the outer connection diameter between the first and second housings, particularly supported on the first housing in at least four circumferential portions or throughout the entire circumference, especially when the support points / regions are rotationally symmetrically distributed over the entire circumference. This particularly enables optimization of force and torque transmission in a manner substantially independent of the direction of force and torque application.

[0029] According to an exemplary embodiment, the first and / or second housings provide / at least partially provide at least one coupling partner (pawl, cam, tappet, web, or similar attachment, particularly also in the radial and / or tangential directions, or in the circumferential direction) for supporting the housings on each other, particularly integrally at the outer surface of the respective housings in the integral design embodiment. This also provides particularly good robustness. With the coupling partners (elements) uniformly distributed along the circumferential direction, support can also be ensured largely independently of any instantaneous direction of force / torque application.

[0030] The torque support has at least one adjustable unit, particularly adjustable in terms of force (value) and / or direction of action and / or force engagement point / area. This also particularly facilitates customization in terms of the type of support, taking into account, for example, feedback control based on operating conditions.

[0031] The adjustable unit can be adjustable, for example, in terms of pretension (particularly spring force or hydraulic pressure) and / or in terms of active control force (reaction force) in response to instantaneous force and torque detected by sensors. The corresponding sensor system is, for example, located in the region of the corresponding interface on the end side and / or radial contact surface. To this extent, the invention also provides a concept for actively applying force, particularly in response to instantaneous forces / torques acting on the transmission system, such as in the case of offshore wind power generation equipment, depending on the instantaneous prevailing wind / meteorological conditions.

[0032] According to an exemplary embodiment, a torque support, particularly one or at least one adjustable unit of the torque support, is disposed in the upper and / or lower region of the interface between the housings. This type of arrangement also provides the advantage that, in each case, vertical and / or supporting forces can be applied in a targeted manner to a specific circumferential portion. With regard to the vertical force described herein, due to the associated advantageous lever arm, the force engagement point is disposed at the bottom and top of the corresponding connecting diameter on the housing, or even more radially outside the lug or tappet or similar lever element specifically designed for this purpose.

[0033] For example, the required vertical force is transmitted in combination with the potentially desired support force or possibly only a very localized support force, within a circumferential angle range of at least twice the range of at least 30° (substantially horizontal) and / or within a circumferential angle range of at least four times the range of 20° (substantially vertical). Depending on the number and design of the force transmission sections, shorter or narrower elements may be sufficient, for example, in a circumferential section spanning only 10° of angle.

[0034] According to an exemplary embodiment, the torque support, particularly at least one adjustable unit, is diagonally connected in such a manner that the hydraulic or mechanical compensation is relatively soft in the axial direction and relatively stiff in the tilting direction. This also particularly facilitates a positive trade-off between effective support and potentially desired positional tolerance compensation, especially in combination with manufacturing tolerances, rotor bearing clearance, or the axial elasticity of the rotor bearing.

[0035] The at least one adjustable unit or at least one adjustable element thereof can be diagonally connected in such a way that the hydraulic or mechanical compensation is relatively soft in the axial direction of the rotation axis and relatively stiff in the tilting direction, in particular in such a way that the hydraulic or mechanical compensation in the tilting direction is performed in a soft (softer) or stiffer (harder) manner, or has higher or lower vibration damping depending on the direction. This also provides advantageous operating behavior.

[0036] Torque support members can be hydraulically and / or mechanically supported within a circumferential angle range of at least twice that of at least 30°, and / or within a circumferential angle range of at least four times that of 20°, such that the hydraulic or mechanical compensation is relatively soft in the axial direction of the axis of rotation and relatively stiff in the circumferential direction, particularly in such a way that the hydraulic or mechanical compensation in the circumferential direction is performed in a soft or stiff manner, or has higher or lower vibration damping depending on the direction.

[0037] This invention implements multiple measures that can be combined with each other, relating not only to tilting moment support but also to torque support. The latter acts in the circumferential direction and can be required or adjusted / controlled based on the output. The tilting moment support counteracts weight in the tilting direction and can therefore also be described as a reaction force or restoring force with a vertical force component.

[0038] According to an exemplary embodiment, a radially extending flange or similar force-engaging collar or segment is provided on the (second) housing of the transmission component. This flange or similar force-engaging collar or segment is defined or surrounded at least in one axial position (particularly so as to be opposite each other on two axial sides) by a torque support, particularly by at least one adjustable unit, for example, in an annular manner as a C-shaped annular housing or multiple (half) housing elements. Therefore, a very robust assembly with angular tolerances and, for example, integrated damping functions can be advantageously provided.

[0039] For example, the corresponding force engagement points / areas can also be provided integrally on the corresponding housing components, for example, in the case of a cast metal housing, they are integrally cast, thus already taken into account in the context of construction and basic design. Alternatively (e.g., if a cast metal housing is not used) or additionally, reversible form-fit / force-fit type connections, such as threaded connections, can also be optionally provided. This is useful, for example, in existing transmissions or in the case of modifications or retrofitting options on an already installed transmission system, thereby also enabling integral material fastening.

[0040] According to an exemplary embodiment, the torque support is configured to provide a vertical force acting axially opposite to the tilting torque, so as to engage with the second housing, particularly in the radially external force engagement region located at the maximum outer position on the housing of the transmission component. For example, by providing a vertical force in a pair of opposing forces acting radially outwards in the engagement region, even small motion tolerances can be ideally and precisely compensated for with good leverage, and optionally damping. The term "axial" as used herein should also be understood to mean the axial range of the transmission system.

[0041] According to one exemplary embodiment, the torque support includes an additional support unit that acts on the first housing of the shaft mount and is arranged such that a substantially vertical (radial / tangential) or circumferential force is provided to engage with a second housing. This makes it particularly possible to achieve even greater functional integration in the torque support, especially with respect to torques acting around the shaft or drivetrain, and taking into account any possible positional tolerances or damping effects.

[0042] To this extent, the invention also provides torque supports (in the form of internal supports) in the radial plane along the tangential or circumferential direction and inclined supports (in the form of external supports) outside the radial plane, in each case being supports on a large-mass rotor bearing housing, wherein the machine support located below can be designed to be smaller or more slender. Force compensation here can be, for example, performed hydraulically.

[0043] According to one exemplary embodiment, the second housing is disposed separately from and axially spaced from the first housing. The housings are directly connected to each other, for example, only by the torque support described herein, and also indirectly connected only by corresponding mounting members and shafts disposed in the respective housings.

[0044] According to an exemplary embodiment, a transmission component is disposed between a shaft and a generator, the generator being engaged on a second housing or on the transmission component (or on the weight of the latter). This type of series connection in the transmission system has proven advantageous for various applications, and according to the invention, a support can also be advantageously implemented with an additional generator flange connected to the transmission system, particularly by means of support only on the first housing, thus without any further support in the direction of the machine support. This allows for relatively short / slender machine supports, especially in the case of generators arranged in series, and in this way also allows for advantageous distribution / concentration of forces at the interface with the bearing housing.

[0045] Furthermore, one aspect of the invention relates to an industrial transmission device having such a transmission system mounting assembly, particularly in components of wind power generation equipment.

[0046] To this extent, the aforementioned objectives are also achieved by industrial transmissions having transmission system mounting assemblies as further described above, particularly industrial transmissions with planetary gear stages. To this extent, the aforementioned objectives are also achieved by wind power generation equipment having industrial transmissions as described above or having such transmission system mounting assemblies. Therefore, the previously mentioned advantages are obtained, particularly considering the functional modes of the corresponding transmissions under significantly reduced external stress and significantly reduced wear.

[0047] Furthermore, one aspect of the invention relates to a method for adjusting or adapting the mounting members of a drivetrain mounting assembly of this type. To this extent, the aforementioned objective is also achieved by the method in the corresponding parallel method claims, specifically by a method for adjusting the mounting members of a drivetrain mounting assembly for an industrial transmission, particularly in the drivetrain of a wind power generator with a rotor having dual mounting members or momentum mounting members, wherein the mounting members of the drivetrain shaft supported in a first housing and the transmission components (particularly planetary transmission stages) surrounded by a second housing and connected to the shaft are mounted relative to each other, wherein the second housing and thus the transmission components are supported on the first housing, and thus on the housing of the shaft mounting members, by means of torque supports that counteract the torque caused by gravity acting on the shaft through the transmission components, particularly in drivetrains with generators, particularly in the drivetrain mounting assemblies further described above, or in industrial transmissions, or in wind power generators, wherein the generator is supported on a shaft, the generator is supported in the second housing, and correspondingly also on the first housing. Combining the advantages mentioned above, this also enables more sustainable operating modes for dynamic high-stress equipment and industrial transmission devices (such as in wind power generation equipment).

[0048] By means of at least one adjustable unit acting between the first and second housings, and particularly based on instantaneous measurements from at least one force / path sensor and / or acceleration sensor mounted in the drivetrain, feedback control of the main force and / or path control applied to the second housing and dispersed through the first housing, for example by hydraulic actuation, is achieved. This also facilitates sustainable operating modes, particularly by adapting the support type to instantaneous operating conditions.

[0049] According to an exemplary embodiment, vibration damping or vibration decoupling is performed at at least two mutually opposing circumferential positions in at least one connecting portion between interacting connecting parts by means of at least one adjustable unit, particularly by means of at least one pretensioning unit at each circumferential position. Depending on the specific application, multiple adjustable units may be implemented here, by means of which reaction force pairs acting around at least two or all three torque axes or acting in a three-dimensional manner around all three spatial directions may be provided, and can also be optionally actively adjustable.

[0050] The aforementioned objectives are further achieved in industrial transmission systems, particularly in wind power equipment, in the arrangement between the rotor and generator of the wind power equipment, especially in a single-shaft co-alignment arrangement / orientation, using the transmission mounting assembly further described above. This is achieved by utilizing the torque support of the transmission mounting assembly, where tilting torque and torque are transmitted from the transmission housing of the transmission mounting assembly to the rotor bearing housing arranged on the shaft of the transmission. The transmission housing and possibly other flanged components, such as the generator, are supported solely on the rotor bearing housing. As a result, the advantages further mentioned above can be achieved. Attached Figure Description

[0051] The invention will be described in more detail by way of example with reference to preferred exemplary embodiments shown in the following figures, wherein features shown below may individually or in combination represent an aspect of the invention, and wherein reference numerals not explicitly described in the respective figures refer to other figures in the figures. Each case is illustrated in the schematic diagrams as follows:

[0052] Figure 1A , 1B The transmission system of the support member with a transmission system according to the prior art is shown in side view and partial cross-sectional side view;

[0053] Figure 2 A partial cross-sectional side view shows a drivetrain mounting assembly according to a first exemplary embodiment, particularly a rotor for a wind power generation device;

[0054] Figure 3 A drivetrain mounting assembly according to another exemplary embodiment is shown in a partial cross-sectional side view, particularly for a rotor of a wind power generation device;

[0055] Figure 4A , 4B A drivetrain mounting assembly, particularly for a rotor of a wind power generator, is shown in a side view and a cross-sectional front view, according to another exemplary embodiment; and

[0056] Figure 5A , 5BA drivetrain mounting assembly, particularly for a rotor of a wind power generation device, is shown in a side view and a cross-sectional front view, according to another exemplary embodiment. Detailed Implementation

[0057] First, the invention will be generally explained with reference to all reference numerals and figures. The uniqueness or individual aspects of the invention, or aspects of the invention readily visible / visible in the respective figures, will be discussed separately in the context of the corresponding figures.

[0058] The drivetrain comprises components such as: a hub 1, a shaft 2 (particularly the rotor shaft of a wind turbine), a rotor bearing housing 3, a rotor bearing / rotor mount 4 (particularly a torque mount or tapered roller mount), a coupling 5, a transmission 6 within a drivetrain housing 7, a torque support unit or gravity support 8 connected to a base (machine support), and a generator 9. Even when the torque support unit or gravity support 8 has a relatively good design / size, the drivetrain structure is subjected to significant stress under high weight under strong, dynamic forces, for example, also generated by the bending moment from the rotor of the wind turbine connected to the shaft. In addition to the rotor shaft, the flange connection to the planetary carrier, the planetary carrier bearings, and the torque support, the machine support is also subjected to considerably high stress during this process. In this case, it is of interest to implement a drivetrain with an advantageous type of mount that can actively receive and transmit this type of stress.

[0059] A drivetrain mounting assembly 10 is provided, for example for an industrial drivetrain 20. The drivetrain mounting assembly 10 has a shaft 2 supported in a rotor mounting member 14 (here: a double mounting member or torque mounting member). The rotor mounting member 14 is surrounded or enclosed by a rotor bearing housing 13 (first housing). A transmission component 16, particularly having a planetary gear stage, is disposed in a drivetrain 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 mechanical / hydraulic bridge between the two housings 13, 17, particularly at the connection (diameter) as radially outward as possible, wherein the support occurs on the first housing 13, for example at points P1, P2 shown. Advantageously, the support in region P1 can also occur symmetrically but eccentrically, particularly also to ensure support and / or damping in the yaw direction (perpendicular to the tilt and axial directions, rotational movement about the tower axis).

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

[0061] Specifically, the following components are provided for support on the second housing 17 (or for transmitting forces from the second housing):

[0062] Radially extending flange 17.1 or similar force-engaging collar or segment or tappet; individual force-engaging segment 17.3 (especially lug or tab or web); traction element 17.5; tappet / cam 17.7.

[0063] The torque support 18 allows force to be received from the transmission housing 17 via the bearing housing 13 and transmitted to the base 101. In this process, a vertical force F1 (particularly as a force pair around a central longitudinal axis or shaft) acting on the transmission housing 17 in opposition to weight / gravity g is provided as a restoring support torque M2 acting in opposition to the tilting torque M1. Optionally, the torque support 18 can also additionally induce, provide, or actively generate a support force F2, by means of which the torque M3 acting on the transmission components and transmitted to the transmission housing can be counteracted. Optionally, the vertical force F1 and the support force F2 can also be actively controlled, for example, based on instantaneous measurements from force / path sensors at the respective interfaces.

[0064] The torque support 18 preferably has at least one adjustable unit 18.1, and in particular includes: a pretensioning unit 18.2 (particularly axial, especially having at least one mechanical spring), a support unit 18.3 (particularly annular or semi / shell-shaped); a diagonal connector 18.5, an additional support unit 18.6 (particularly annular or semi / shell-shaped), an additional pretensioning unit 18.7, or at least one correspondingly mounted separation element (particularly arranged in the radial plane and / or oriented in the circumferential direction).

[0065] This support can optionally be actively adjusted and also controlled by feedback. For this purpose, at least one force / path sensor 19 can optionally be provided, which can be connected to the control / feedback control unit.

[0066] The drivetrain mounting assembly 10 described herein provides the advantages described herein in a particularly significant manner, especially in the case of wind power generation equipment 100, wherein a machine support or similar base 101 for the drivetrain is mounted on a tower 102.

[0067] The invention will now be explained in more detail with reference to the accompanying drawings.

[0068] Figure 1 shows a known transmission system assembly of a reference wind power generation device. The generator 9 is fastened to the transmission housing 7. The transmission housing is supported towards the bottom on the machine support 101 by support units 8 (torque and weight supports). Figure 1A The rotor bearing housing 3 is shown in the side view. Figure 1BThe rotor bearing housing 3 is shown in a cross-sectional side view. The rotor shaft 2 has a relatively large mass or diameter, and the rotor bearing 4 is supported in a relatively robust manner on the machine support 101 by a fairly large longitudinal section.

[0069] The weight of the transmission and, optionally, the weight of the generator mounted to the transmission housing via flanges, exerts stress on the rotor shaft, rotor bearings, planetary carrier (particularly the first transmission stage), its planetary carrier bearings, and the flange connection between the rotor shaft and the transmission. As a result, rotational bending occurs in the rotating elements, which must be disadvantageously considered when determining the dimensions of said rotating elements.

[0070] Figure 2 A first exemplary embodiment of the drivetrain mounting assembly 10 is shown. The force generated on flange 17.1 or the corresponding radial attachment causes a vertical force opposite to the pitch / tilt moment M1 on F1. For example, the development of a predetermined type of support or force, or active feedback control, can also be selectively achieved by adjustable unit 18.1 based on instantaneous measurements from at least one force / path sensor 19 and / or acceleration sensor 21. The transmission of force and its support on rotor bearing housing 13 can occur particularly in area or point P1. This support can also be advantageously symmetrical but eccentric, particularly to ensure support and / or damping in the yaw direction (rotational movement about the tower axis perpendicular to the tilt and axial directions), especially when at least one adjustable unit 18.1 is disposed therebetween, the adjustable unit 18.1 including at least one pretensioning unit 18.2 in at least one connecting portion between at least one of the interacting connecting parts 17.1, 18.3. By combining data from at least one sensor (particularly from acceleration sensor 21), active damping, for example, about the pitch or yaw axis, can be generated in the event of vibration, and / or the vibration can be passively damped by an elastic element.

[0071] By means of components according to the invention, such as those for a wind turbine with a rotor shaft having dual mountings or torque mounts and a transmission and generator connected thereto, rotational bending caused by the weight of the transmission-generator assembly can be significantly reduced. According to the invention, rotational bending stress can be significantly reduced, while tilting in the transmission, particularly in the first planetary gear stage, can be reduced; thus, at least better tooth support behavior can be achieved. Furthermore, by supporting the transmission torque via the rotor bearing housing and also via torque supports of the transmission, improved force return can be achieved, reducing the negative impacts caused by typically dissimilar deformations between the machine supports and the transmission system (the transmission and its connection to the rotor shaft unit). Pitch moments, particularly those generated by wind loads (in wind turbines), do not need to be supported by machine supports to this extent, and do not result in additional loads. Because of this mounting / support according to the invention, the excessive size of the affected machine components (rotor shaft, rotor bearing, rotor shaft flange relative to the planetary carrier, planetary carrier, planetary carrier bearing, transmission, and generator housing flange) can now be omitted, resulting in advantages in both cost and weight. To this extent, additional support for the weight between the generator and the machine support is no longer needed; the support structure for supporting the weight below the generator can be omitted; and the pitching motion of the transmission system can now be absorbed or damped by the bearing housing without unfavorable leverage or excessive loads that could affect the overall structure.

[0072] The bending moment induced on the transmission housing (torque support) by the mass of the transmission unit and, optionally, the mass of the generator, can preferably be supported relative to the rotor bearing housing by an adjustable unit or at least one adjustable element, which is preferably arranged at least in the upper and / or lower region of the interface between the transmission housing and the rotor bearing housing. In this way, the adjustable unit compensates for the negative impact of the bending moment on the affected machine components and simultaneously aligns the corresponding transmission components, such as the ring gear of the first planetary gear stage, relative to the planet carrier, and this process also ensures better support performance in the gear teeth.

[0073] According to the present invention, a force fit can be established between the non-rotating housing component of the transmission device and the non-rotating housing component of the rotor bearing housing. The weight-induced bending moment is compensated by a vertical force, particularly by a vertical force in the form of a force pair engaged at the bottom and top of the transmission device housing.

[0074] In another function, nearly unloaded axial movement along the rotor shaft axis can be generated or permitted because the adjustable unit or at least one of its adjustable elements is diagonally connected in such a way that the weight bending moment continues to be received by a force pair of equal magnitude, while axial movement is unimpeded. In this context, particularly in the context of hydraulic and / or mechanical (force or position) compensation, the diagonal connection can also be described as a relatively soft support in the actual direction (depending on the inclination of the shaft being at least approximately in the horizontal plane) and a relatively stiff support in the vertical or inclined direction. The direction of motion of the transmission relative to the shaft or relative to the rotor bearing housing caused by gravity should be understood in this context specifically as the inclination direction; inclination does not necessarily have to occur around an axis orthogonal to the shaft, but depending on the dynamic state, it can also be a multi-axis tilt / yaw motion.

[0075] The reduction in weight and therefore rotational moment of the rotating components, achievable by means of the components according to the invention, is preferably carried out in areas such as the drivetrain of a wind turbine, which are, in any case, capable of or configured to receive high loads and moments, for example, generated by wind loads. Therefore, any potential additional enhancements or reinforcements to ensure the desired reduction in weight and moment are associated with relatively low complexity and, at best, no disadvantages that could arise from dissimilar deformation behavior between drivetrains on machine supports; however, in the components according to the invention, this type of situation is far less disadvantageous than in known weight supports beneath a generator.

[0076] Figure 3A second exemplary embodiment of the drivetrain mounting assembly 10 is shown, wherein the torque support 18 further includes another support unit 18.6, which is supported on the first housing 13 in region or point P2, and by means of the other support unit 18.6, a support force F2 can be applied to the drivetrain housing (resulting in a support torque M2). The support force F2 is substantially vertical or oriented in the circumferential direction (radial / tangential) and acts in opposition to the (drive) torque M3, particularly when at least one adjustable unit is arranged between at least one force pair. The support force F2 is also provided by at least one force pair, especially in at least a generally mutually opposing circumferential position. The at least one adjustable unit includes at least one pretensioning unit in at least one connecting portion between interacting connecting parts 17.3, 18.6. The development of a predetermined type of support or force can be selectively implemented by the corresponding adjustable unit 18.1 or by means of a separate pretensioning or separation element 18.7, or by active feedback control, for example, also based on the instantaneous measurement of at least one force / path sensor 19. For example, in each case, the transmission of force occurs between the rotor bearing housing and the radially extending flange portion 17.1 or the drive housing, or between similar force-engaging collars, segments, or tappets, or between separate force-engaging segments 17.3, particularly lugs, tabs, or webs, on the rotor bearing housing and the drive housing.

[0077] In this document, the at least one adjustable unit ensures damping of force pairs F1 oriented at least approximately axially (or parallel to the drivetrain axis or rotation axis) and force pairs F2 oriented at least approximately tangentially / radially (and therefore orthogonal to the rotation axis) at different circumferential positions, or damping in the respective directions of action. Here, the corresponding pretensioning and support units advantageously engage at at least approximately 12 o'clock and 6 o'clock circumferential positions and at least approximately 3 o'clock and 9 o'clock circumferential positions (particularly diametrically opposed), or in each case at four circumferential positions offset at least 90° in the circumferential direction, wherein the corresponding circumferential positions can also be, for example, circumferential segments or regions of 10° to 15°, depending on the design of the corresponding connection parts. Preferably, multiple adjustable units are provided, each with a separate direction of action and spring / damper characteristics, and optionally also individually adjustable, controllable, and / or feedback-controllable. This facilitates a highly individualized response to instantaneous dynamics and drivetrain-specific stresses in multiple spatial directions or even in all spatial directions.

[0078] In other words, in addition to the support unit / element for vertical forces, another advantage can be achieved by means of the torque support, because at least two additional support elements are used, acting vertically and also supported on the rotor bearing housing, in order to combine with the torque support. Since the rotor shaft is guided by the rotor shaft bearing in the rotor bearing housing, the additional support, which will be described functionally as the torque support, is given the same relative motion as the torque support drive, and in this process, no additional load is generated due to the pitch load of the received equipment rotor blades. To this extent, this functional integration or dual function of the torque support provides a particularly slender design with exceptional tolerance to force / torque / motion.

[0079] In this article, Figure 2 and Figure 3 The machine support (base) shown can also be designed to be significantly shorter or significantly reduced in axial length compared to what is typically seen in wind power equipment (where there are no additional support points below the second housing / transmission housing or generator); this is because the connection to the base can advantageously occur in the region of the rotor bearing housing (first housing), and optionally only there. This additional advantage is visualized only by way of example, shown here in dashed lines, of the region of the machine support. Therefore, the connection between the machine support and the tower or similar support located below it can also be achieved in a more slender manner. Also to this extent, the possibilities for material savings described herein increase exponentially, favoring slender designs.

[0080] exist Figure 3 The diagram also shows the height-tolerant mounting portion z1; depending on the required degree of freedom of motion, the vertical degree of freedom of motion can be structurally restricted and / or restricted by active and / or passive reaction forces such as pre-tensioning units. Those skilled in the art can individually optimize this degree of freedom z1 according to specific applications, and in particular, it can be optimized in combination with integrated damping functions.

[0081] The reference torque acts on different axes, according to Figure 3 In an exemplary embodiment, reference may also be made to two different adjustable units 18.1, which are implemented to generate at least two different counter torques.

[0082] Figure 4 shows another exemplary embodiment of the drivetrain mounting assembly 10, wherein the torque support 18 also includes a tilting torque support and a torque support. Force transmission occurs, for example, in each case, between the tappet 13.5 on the rotor bearing (housing) and the tappet 17.5 on the drivetrain (housing), or between the traction element / cam 13.7 on the rotor bearing (housing) and the tappet / cam 17.7 on the drivetrain (housing). In this exemplary embodiment, the mutual engagement of the two housings 13, 17 can also be referred to / described as a claw-type connection, wherein the two housings in each case provide one of the engagement partners, particularly because the engagement element or claw, or the traction element and tappet further described above, are formed as a single component so that they are integral on the respective housings. This also provides high robustness and avoids unwanted relative movement or loosening of parts. Figure 4A The diagram shows the interlocking traction element / cam of two transmission housings, and... Figure 4B The diagram illustrates an exemplary distribution of the various force transmission locations in the circumferential direction, wherein in each case, six interfaces are provided here, specifically for two different types of support or torque / force, thus repeating every 60° in terms of circumferential angle. The traction element can also advantageously be positioned symmetrically but eccentrically; thus, it can also advantageously ensure support and / or damping in the yaw direction (perpendicular to the tilt and axial directions, and therefore in the sense of rotational movement about the tower axis), so that the planetary carrier bearings are also relieved of pressure, especially in the yaw direction, in the event of vibration.

[0083] The reference torque can also refer to at least two different adjustable units 18.1, which are implemented to generate at least two different counter torques, in the exemplary embodiment according to FIG4.

[0084] Figure 5 illustrates another exemplary embodiment of the drivetrain mounting assembly 10, wherein the torque support's functional scope includes not only the tilt moment support but also the yaw moment support, which is particularly effective in the illustrated embodiment. This type of support is capable of absorbing and damping vibrations, for example, around the tower axis (yaw axis), in a particularly effective manner. Similarly, the adjustable unit 18.1, effectively arranged at the 12 o'clock and 6 o'clock positions respectively, can be effectively used to absorb and dampe vibrations, for example, around the pitch / tilt axis. Figure 5A The diagram shows corresponding interlocking traction elements / cams 13.7, 17.7 of the two housings (equivalent to housing connection components already explained in the context of the foregoing exemplary embodiments). Furthermore, traction elements 13.5, 17.5 and lateral traction / compression elements 13.9, 17.9 are shown in two planes oriented at least approximately orthogonally to each other. See also... Figure 4B .exist Figure 5BAn exemplary distribution of the various force transmission positions along the circumferential direction is shown, wherein the functions of the lateral traction / compression members 13.9 and 17.9, which are preferably the most eccentric, are specifically illustrated here, specifically as corresponding force transmission positions along the circumferential and axial directions. In other words, in addition to the components of at least one adjustable unit 18.1 already further described above, assembly 10 may also include the following additional components, particularly as part of the corresponding adjustable unit 18.1 in each case: the lateral traction / compression member 13.9 of the rotor bearing housing, particularly in the 3 o'clock and 9 o'clock regions; the lateral traction / compression member 17.9 of the transmission housing, particularly in the 3 o'clock and 9 o'clock regions; an additional pretensioning unit 18.9; or at least one separation element of a corresponding orientation, particularly an axially oriented separation element. Thus, the yaw force F3 can be counteracted in a particularly effective manner. Side note: The force F3 according to the illustrated embodiment is actually a force oriented substantially in the axial direction, similar to force F1, but still referred to by another reference numeral here because the corresponding reaction force pair generates a reaction torque about another axis relative to the reaction force pair at the force engagement point according to force F1. In this sense, the different axes of action of the reference torque can also be referenced to at least three different adjustable units 18.1 implemented in the exemplary embodiment according to FIG. 5.

[0085] It should be noted that yaw moment support does not necessarily have to be implemented in the manner of the exemplary embodiment according to FIG. 5. Rather, yaw moment support can already be achieved when the traction members 13.5, 17.5 described in the context of FIG. 4 are arranged, for example, slightly eccentrically, such that they are laterally eccentrically arranged on both sides of the central vertical axis of the drivetrain or shaft 2 in the horizontal plane. However, the exemplary embodiment described in FIG. 5 provides or implements more effective damping, particularly by means of a larger effective lever arm. To this extent, circumferential positions deviating from the circumferential positions shown in the figures can also be achieved for the traction members 13.5, 17.5. However, the laterally eccentric traction / compression members 13.9, 17.9 in each case are provided with another reference numeral here because torque transmission should also be able to occur circumferentially on these members, see [reference needed]. Figure 5A The force arrow F2 in the diagram.

[0086] List of reference numerals

[0087] 1 wheel hub

[0088] 2 shafts, especially the rotor shafts of wind power generation equipment

[0089] 3 Rotor bearing housing

[0090] 4. Rotor bearings / rotor mounts, especially torque mounts / tapered roller mounts

[0091] 5 couplings

[0092] 6. Transmission devices, especially industrial transmission devices

[0093] 7 Transmission device housing

[0094] 8 torque support units or gravity support components, with couplings connected to the base.

[0095] 9 generators

[0096] 10. Drivetrain Mounting Components

[0097] 13. Rotor bearing housing (first housing)

[0098] 13.5 Traction component rotor bearing (housing), especially in the 6 o'clock and 12 o'clock areas.

[0099] 13.7 Tappet / Cam Rotor Bearing (Housing)

[0100] 13.9 Lateral traction element / compression tappet rotor bearing (housing), especially in the 3 o'clock and 9 o'clock areas.

[0101] 14 Rotor bearings / rotor mounting components

[0102] 16 transmission components, especially those with planetary gear stages

[0103] 17. Transmission device housing (second housing)

[0104] 17.1 Radially extending flanges or similar force-engaging collars or segments, or push rods

[0105] 17.3 Individual force-engaging sections on the transmission housing, particularly lugs, tabs, or webs.

[0106] 17.5 Traction drive unit (housing), especially in the 6 o'clock and 12 o'clock areas.

[0107] 17.7 Tappet / Cam Drive (Housing)

[0108] 17.9 Lateral traction / compression drive (housing), particularly in the 3 o'clock and 9 o'clock areas.

[0109] 18 Torque Supports (Torque and / or Tilt Moment Supports)

[0110] 18.1 Adjustable unit

[0111] 18.2 Pretensioning unit (particularly axial), especially having at least one mechanical spring

[0112] 18.3 Supporting elements, especially annular or (semi-)shell-shaped

[0113] 18.5 Diagonal Connection

[0114] 18.6 Additional support units, particularly annular or (semi-)shell-shaped units.

[0115] 18.7 Additional pretensioning units (or separation elements), particularly radially oriented ones.

[0116] 18.9 Additional pretensioning units (or separation elements), particularly those axially oriented.

[0117] 19 Force / Path Sensors

[0118] 20 Industrial Transmission Devices

[0119] 21 accelerometers

[0120] 100 wind power generation equipment

[0121] 101 Machine support or similar base

[0122] 102 towers

[0123] F1 Vertical force

[0124] F2 support force

[0125] F3 yaw force, or the corresponding reaction force on the system.

[0126] g weight

[0127] M1 tilting moment

[0128] M2 Support Torque

[0129] M3 (Drive) Torque

[0130] First support point / area on P1 rotor bearing housing

[0131] Second support point / area on P2 rotor bearing housing

[0132] z1 Height Tolerance Installation Part

Claims

1. A wind power plant (100) with an industrial transmission (20), the wind power plant having: - a mounting (14) for a shaft (2) of a drive train, the mounting (14) being supported in a first housing (13); - a transmission component (16) with a planetary gear stage, which is enclosed by a second housing (17) and is coupled to the shaft (2); - a generator (9), which is supported to the second housing (17), while the transmission and generator combination is arranged to float freely in space on one side of the drive train; and - a torque support (18), which is provided as a mechanical or hydraulic bridge between the two housings, which counteracts a tilting moment or torque (Ml) acting on the shaft by means of the transmission component (16) caused by gravity; wherein the torque support (18) is fastened to the first housing (13), wherein the torque support (18) has at least one adjustable unit (18.1) for mechanical or hydraulic compensation. The at least one adjustable unit generates a first force pair on at least one circumferential position pair, which is essentially axially oriented around an axial center of the drive train; and / or the at least one adjustable unit generates a second torque-generating force pair on at least one circumferential position pair, which is essentially radially or tangentially oriented and acts orthogonally with respect to the axial center of the drive train.

2. A wind power plant (100) according to claim 1, characterised in that The at least one adjustable unit ensures vibration damping or vibration decoupling in at least one coupling section between interacting coupling components associated with the first housing and the second housing in at least two mutually opposite circumferential positions.

3. A wind power plant (100) according to claim 1 or 2, characterised in that, The at least one adjustable unit (18.1) acts in each case in an elastic and / or damped manner between traction or compression tappets of the second housing and the first housing in at least two mutually opposite predefined circumferential positions.

4. A wind power plant (100) according to claim 1 or 2, characterised in that, The drive train comprises a plurality of adjustable units, by means of which a counterforce pair is provided which acts three-dimensionally around all three spatial directions.

5. A wind power plant (100) according to claim 1 or 2, characterised in that, The torque support (18) is supported only on the first housing (13) independently of any connection to a machine support provided below the drive train.

6. A wind power plant (100) according to claim 1 or 2, characterised in that, The torque support (18) is supported on the first housing (13) in support points or regions provided along an outer connection diameter between the first housing and the second housing; and / or wherein the first housing (13) and / or the second housing (17) at least partially provide at least one coupling fit for the housings to support each other.

7. A wind power plant (100) according to claim 1 or 2, characterised in that, The at least one adjustable unit (18.1) is an adjustable unit in terms of force and / or direction of action and / or force engagement point or region.

8. A wind power plant (100) according to claim 1 or 2, characterised in that, The torque support (18) is provided in an upper region and / or a lower region of an interface between the first housing and the second housing.

9. A wind power plant (100) according to claim 1 or 2, characterised in that, A radially projecting force engagement section (17.1) is provided on the second housing (17), which is defined by the torque support (18) in at least one axial position.

10. A wind power plant (100) according to claim 1 or 2, characterised in that, ​ 11. A wind power plant (100) according to claim 1 or 2, characterised in that, The torque support (18) is arranged in such a way that a vertical force is provided which acts substantially axially and counter to the tilting moment to engage on the second housing (17); and / or wherein the torque support (18) is arranged in such a way that a support force is provided which acts substantially axially but symmetrically eccentrically to counteract the yaw moment to engage on the second housing (17).

12. A wind power plant (100) according to claim 1 or 2, characterised in that, The torque support (18) comprises a support unit (18.3) which acts on the first housing (13) and is arranged in such a way that a force is provided which acts substantially vertically or in a circumferential direction to engage on the second housing (17).

13. A wind power plant (100) according to claim 1 or 2, characterised in that, The transmission component (16) is arranged between the shaft (2) and a generator (9) which engages on the second housing (17) or on the transmission component (16).

14. A wind power plant (100) according to claim 1, characterised in that, The industrial transmission (20) has a planetary gear stage.

15. A wind power plant (100) according to claim 14, characterised in that, The planetary gear stage is a rotor with double mounting for the wind power installation.

16. A wind power plant (100) according to claim 2, characterised in that The at least one adjustable unit generates a first force pair at 6 o'clock and 12 o'clock and / or 3 o'clock and 9 o'clock in at least one circumferential position pair.

17. A wind power plant (100) according to claim 16, characterised in that, The first force pair is a force pair directed against the tilting and / or yaw moment.

18. A wind power plant (100) according to claim 2, characterised in that, The at least one adjustable unit generates a second torque-generating force pair at 3 o'clock and 9 o'clock and / or 6 o'clock and 12 o'clock in at least one circumferential position pair.

19. A wind power plant (100) according to claim 18, characterised in that, The second torque-generating force pair is a force pair directed against the torque.

20. A wind power plant (100) according to claim 3, characterised in that, The at least one adjustable unit ensures vibration damping or vibration decoupling in at least one coupling section between interacting coupling components associated with the first housing and the second housing in at least two mutually opposite circumferential positions by means of at least one pretensioning unit per circumferential position.

21. A wind power plant (100) according to claim 4, characterised in that, The at least one adjustable unit (18.1) acts in each case in an elastic and / or damping manner between traction or compression tappets of the second housing and the first housing at least at the circumferential positions 6 o'clock and 12 o'clock position and / or 3 o'clock and 9 o'clock position in at least two mutually opposite predefined circumferential positions.

22. A wind power plant (100) according to claim 7, characterised in that, The torque support (18) is supported on the first housing (13) in at least four circumferential sections or over the entire circumference in a support point or area arranged along the outer connection diameter between the first housing and the second housing.

23. A wind power plant (100) according to claim 7, characterised in that, The torque support (18) is supported on the first housing (13) in the case of a rotational symmetrical distribution of the support point or area over the entire circumference.

24. A wind power plant (100) according to claim 7, characterised in that, The at least one coupling partner is integrated in the overall design on the outer shell surface of the respective housing.

25. A wind power plant (100) according to claim 9, characterised in that, The at least one adjustable unit (18.1) of the torque support is arranged in an upper region and / or a lower region of the interface between the first housing (13) and the second housing (17).

26. A wind power plant (100) according to claim 25, characterised in that, The at least one adjustable unit (18.1) is connected diagonally.

27. A wind power plant (100) according to claim 26, characterised in that, The at least one adjustable unit (18.1) is connected diagonally in such a way that the hydraulic or mechanical compensation is softer in the axial direction and harder in the tilting direction. The at least one adjustable unit (18.1) is connected diagonally in such a way that the hydraulic or mechanical compensation is softer in the axial direction and harder in the tilting direction.

28. A wind power plant (100) according to claim 10, characterised in that, The radially protruding force engagement section (17.1) is ring-shaped defined by the torque support (18) in at least one axial position.

29. A wind power plant (100) according to claim 28, characterised in that, The radially protruding force engagement section (17.1) is ring-shaped defined by the adjustable unit (18.1) in at least one axial position.

30. A wind power plant (100) according to claim 5, characterised in that, The reactive force pair is actively adjusted.

31. A wind power plant (100) according to claim 9, characterised in that, The torque support (18) is connected diagonally.

32. A method for adjusting a mounting of a drive train mounting assembly (10) of an industrial drive, wherein The mounting (14) of the shaft (2) of the drive train supported in the first housing (13) and the transmission component (16) surrounded by the second housing (17) and coupled to the shaft (2) are mounted relative to each other, wherein the second housing (17) and thus the transmission component are supported on the first housing (13) by means of a torque support (18) which counteracts the torque (M1) caused by gravity acting on the shaft (2) through the transmission component (16), wherein in the wind power installation according to any one of claims 1 to 31, or in the industrial transmission (20), a feedback control of the active force control and / or path control of the vertical force or support force exerted to the second housing (17) and dissipated through the first housing (13) is carried out by means of at least one adjustable unit (18.1) acting between the first housing and the second housing.

33. The method of claim 32, wherein, By means of the at least one adjustable unit, vibration damping or vibration decoupling is carried out in at least two mutually opposite circumferential positions in at least one coupling section between the interacting coupling components associated with the first housing and the second housing, respectively.

34. The method of claim 32 or 33, wherein, The feedback control of the active force control and / or path control of the vertical force or support force is carried out by means of the at least one adjustable unit (18.1) based on the instantaneous measurement values of at least one force sensor or path sensor (19) and / or acceleration sensor (21) mounted in the drive train.

35. The method of claim 32, wherein, The adjustment takes place in a drive train of a wind power installation (100) having a rotor with double mounting.

36. The method of claim 32, wherein, In a drive train having a generator (9) supported on the second housing (17), the second housing (17) and thus the transmission component are supported on the first housing (13) by means of a torque support (18).

37. The method of claim 33, wherein, By means of at least one pre-tensioning unit per circumferential position, vibration damping or vibration decoupling is carried out in at least two mutually opposite circumferential positions in at least one coupling section between the interacting coupling components associated with the first housing and the second housing, respectively.

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