DRIVETRAIN ARRANGEMENT WITH TRAIN-BASED TRAIN TORQUE SUPPORT AND TRAIN-BASED SUPPORT METHOD FOR DRIVETRAINS AND USE

Description

TECHNICAL AREA

[0001] The present invention relates to a drive train arrangement for industrial gearboxes, comprising: a first housing which surrounds a bearing for a shaft of the drive train, and a gearbox component which is coupled, in particular axially aligned, to the shaft and which is surrounded by a second housing; the invention provides a tensile torque support acting between these housings, comprising at least one tensile element coupled to the second housing. The present invention further relates to a corresponding tensile element-based support method. BACKGROUND OF THE INVENTION

[0002] In torque conversion via gearboxes, differential torques between the input and output torques must typically be supported relative to the surroundings. Particularly in planetary gearboxes for wind turbines, as well as in industrial applications in general, a torque arm or a flange connection is usually used to support the torque relative to the non-rotating and often stationary environment. However, such conventional torque arms (especially in their massive designs) significantly increase the gearbox's installation dimensions and weight. This leads to limitations and additional costs, particularly in logistics (especially transport), due to the larger installation space required. Furthermore, space constraints in certain applications can also result in other disadvantages, such as...Regarding accessibility in a wind turbine, or specifically with planetary gearboxes, also with regard to limitations in the planetary ring gear diameter. With a flange connection, direct coupling typically does not allow for simple vibration decoupling. To decouple the gearbox from its environment, elastomer elements have been used, for example, particularly to compensate for different deformations and to reduce vibration excitation from the gearbox. The prior art is represented by documents EP1885001 A1, which forms the basis of the two-part form of the independent claims, DE202012013022 U1, US2017 / 253466 A1, and DE102018219012 A1.

[0003] Based on this, there is a need for more advantageous measures for torque support in drive trains, especially under comparatively large loads or highly dynamic stresses. In particular, an alternative to the use of conventional elastomer elements should be developed. SUMMARY OF THE INVENTION

[0004] The object of the present invention is to demonstrate measures by which a particularly advantageous torque support, or moment support in general, can be ensured in drive trains. In particular, the object is also to design a torque support, or moment support, in general for drive trains in such a way that the forces, moments, and loads acting on the drive train in the area of ​​a transmission can be absorbed and transmitted as comprehensively as possible in a particularly elegant manner.

[0005] The problem is solved by a drivetrain arrangement with the features of claim 1, by a support method with the features of the dependent method claim, and by uses according to the features of the dependent use claim. Preferred embodiments are specified in the dependent claims and in the following description.

[0006] One aspect of the invention relates to an advantageous way of providing traction-based torque support in a drivetrain arrangement, particularly also in combination with the absorption of weight forces and / or tilting moments.

[0007] The invention provides a drivetrain arrangement for industrial gearboxes, in particular for connection to a rotor of a wind turbine, comprising: a first housing which surrounds a bearing for a shaft of the drivetrain, and a gearbox component which is coupled / connected, in particular axially aligned, to the shaft and which is surrounded by a second housing; according to the invention, it is proposed to also equip the drivetrain arrangement with a tensile torque support or tensile torque support, which comprises at least one tensile element coupled at least to the second housing, wherein the tensile torque support or tensile torque support counteracts a torque acting on the shaft or the gearbox component coupled thereto; wherein the tensile torque support or tensile torque support is supported at least on the first housing to transmit the reaction forces exerted on the at least one tensile element.On the one hand, this provides a very quiet and optionally damped (prestressed) arrangement, especially with optional complete decoupling from the machine carrier; on the other hand, force transmission can take place without pressure forces and without moments, so that very effective decoupling, e.g. with regard to vibrations or similar dynamic effects, is also achievable.

[0008] In other words, the invention provides a drivetrain arrangement for industrial gearboxes, in particular for connection to a rotor of a wind turbine, comprising: a first housing which surrounds a bearing for a shaft of the drivetrain, a gearbox component which is coupled / connected, in particular axially aligned, to the shaft and which is surrounded by a second housing, and a tensile torque support (or specifically a tensile torque support) comprising at least one tensile element coupling the first and second housings together, wherein the tensile torque support (or specifically the tensile torque support) counteracts a torque acting on the shaft or the gearbox component coupled thereto; wherein the tensile torque support (or specifically the tensile torque support) is supported on the first housing to transmit the reaction forces exerted on the at least one tensile element, in particular exclusively by means of a tensile element.

[0009] Unless otherwise described herein, the term "torque" refers to a moment acting about the main axial alignment of the drive train, i.e., a drive / output torque or a difference thereof.

[0010] According to the present disclosure, reference is made specifically to a tensile torque support, and more generally to a tensile torque support. Unless otherwise specified, the term "tensile torque support" here refers specifically to the support of a torque acting around the longitudinal extent of the drivetrain (optionally, solely to the support of the torque), while the more general term "tensile torque support" also includes the support of moments caused by gravity or tilting moments. However, the respective disclosure may refer to both types of support unless explicitly denied. In this respect as well, both terms are to be understood interchangeably, as is also emphasized by the "or" combinations in the present disclosure.

[0011] The invention can be implemented, for example, in wind turbine gearboxes, gearbox-generator combinations, drive trains for wind turbines, or similar industrial gearboxes in general. Particularly in conjunction with comparatively robust two-point drive train bearings, the inventive method of coupling the traction elements enables torque-dependent compensation of tilting moments and weight forces even without a righting axial load pair.

[0012] The inventive tensile torque support allows the torque to be advantageously supported close to the existing diameter of a transmission component (for example, the diameter of the ring gear of a planetary gear stage). The tensile torque support also does not require any detrimental increase in installation space (especially since the components transmitting the tensile force can be easily and flexibly arranged for this purpose and do not require any noticeable installation space), which proves to be very advantageous in connection with the transport and assembly of the components of a respective drive train. The tensile torque support can also pick up the supporting torque at several points distributed around the circumference of the transmission and transfer it to an axially overlapping support structure.Therefore, the design concept of the tensile torque support is also comparatively variable and easily scalable, both in terms of size and the torques to be transmitted. The connection to the axially overlapping support structure (the surrounding structure, at least partially enclosing the second housing) can be flexibly / variably implemented at various points or circumferential and axial positions and can also be designed in such a way that the resulting loads can be generated to positively influence the operating behavior of the gearbox. For example, by appropriately selecting the material for the tensile torque support and connecting it via vibration decouplers, the effect of any excitation potentially generated by the gearbox gearing into the axially overlapping support structure (surrounding structure) can be easily reduced.

[0013] In contrast, based on the solutions currently available according to the prior art, many bolted connections with high preload would be necessary, or alternatively, a very complex friction / positive locking combination would be required to transmit the torque to be supported by friction. These disadvantages can also be overcome by the present invention.

[0014] The tensile torque support according to the invention can transfer or dissipate the support torque of gearboxes by means of a belt-, band-, or rope-like coupling, which essentially absorbs and transmits tensile forces (i.e., no compressive forces or torques), into an axially overlapping support structure (surrounding structure). The tensile torque support is advantageously designed such that the support torque is tapped and dissipated at several points around the circumference and / or at several axial positions along the longitudinal axis of the gearbox and / or generator and / or at several points distributed around the diameter (i.e., in different radial positions). An advantageously selected wrap angle of the belt-, band-, or rope-like coupling, and preferably also in conjunction with an adapted coefficient of friction between the surfaces, further enhances the effectiveness of the support torque.The individual connection force can be further reduced by using materials from the gearbox and the tensile torque support. By designing and shaping the tensile-link-based coupling of the tensile torque support, e.g., using V-belts or toothed belts, the individual connection force is also reduced by the corresponding counter-force (reaction force) on the gearbox and applied in a circumferentially distributed manner, particularly with a suitably scaled number of tensile elements.

[0015] For example, in application on a planetary gearbox (or between the planetary gearbox and the bearing housing), the tensile torque support transfers the holding force close to the existing (connection) diameter of the ring gear (in particular without requiring any increase in installation space) and therefore does not generate any additional bending stress in the gearbox structure. Thanks to the tensile torque support according to the invention, no detrimental increase in installation space needs to be considered for the transport of the respective gearbox, so that transport can also be designed more advantageously and cost-effectively from a technical point of view; although this is only a marginal advantage (positive side effect), it can prove to be very advantageous, especially with very large, bulky drive trains that, for example, also have to be mounted at great heights (e.g., inside the nacelle of a wind turbine).

[0016] The tensile torque support according to the invention can absorb the support torque at several points distributed around the circumference of the gearbox and transmit it to the surrounding structure (in particular, an axially overlapping support structure). By advantageously designing the tensile torque support with tensile elements, e.g., in the form of belts (flat, V-belts, toothed belts), especially in conjunction with a sufficiently high coefficient of friction and wrap angle, or a correspondingly efficient force-fit and optionally also positive-locking connection between the tensile element and the corresponding drivetrain component, the connection force can be reduced and advantageously distributed around the circumference of the second housing. The connection to the surrounding structure (or...)The axially overlapping support structure can be flexibly positioned at various points and can be designed in such a way that the resulting loads have a positive influence on the gearbox's operating behavior. Likewise, application-specific adaptation to the surrounding structure is possible with a virtually identical gearbox design, thus reducing the engineering effort required for individual solutions.

[0017] Previous torque supports, especially those utilizing compressive loads and generating bending stress within the support, typically required a significant increase in the gearbox's installation dimensions. This led to limitations and increased costs during transport, and could also result in disadvantages and limitations in the application itself due to space constraints, for example, regarding the planetary gear ring diameter. Furthermore, the weight of the gearbox was also negatively increased with massive torque supports. In the case of flanged connections, direct coupling does not allow for simple vibration decoupling; in particular, numerous bolted connections were previously necessary to transmit the supported torque via friction or through a complex combination with positive-locking connections.

[0018] It has been shown that the arrangement according to the invention is particularly advantageous for three-point rotor bearings, for which support against the surrounding structure is also recommended. In this respect, the invention also enables torque-dependent compensation of tilting moments and weight forces.

[0019] An exemplary embodiment of an advantageous connection of the gearbox to the adjacent structure, such as the rotor bearing housing and / or a machine carrier, is also explained in more detail in the accompanying figures.

[0020] Personalized terms, unless explicitly formulated in the neuter form, may refer to all genders within the context of this disclosure. Any English terms or abbreviations used herein are industry-standard technical terms and are familiar to those skilled in the art. Any synonymous German terms may be indicated here in parentheses for the sake of completeness, or vice versa.

[0021] If, according to the present disclosure, reference is made to an axial direction with regard to the gearbox, this refers to the intended extension of the (input or output) shaft in the installed position, in particular in a horizontal orientation or slightly inclined downwards / backwards (e.g. in the case of a rotor of a wind turbine that is angled slightly relative to the vertical plane), in which the center lines or the axis of rotation of the respective gearbox component and the power shaft are aligned in an axial direction, in particular at least approximately orthogonal to the direction of gravity.

[0022] The aforementioned problem can also be solved by a tensile torque support described herein, which has the features of a tensile torque support described herein, and vice versa. In this respect, the support method according to the invention allows the focus to be selectively directed either towards a wrap around outer shell surfaces using tensile elements, thereby optionally absorbing a large proportion of weight forces or tilting moments (so-called tensile torque support), or the tensile elements are provided on mutually axially overlapping housing sections, in particular pins, whereby a preload unit for applying a substantially axially acting righting force can optionally also be provided (so-called tensile torque support). The concept according to the invention thus also provides a highly variable tensile element-based approach for optimized support in drive trains.

[0023] According to one embodiment, the transmission of the reaction forces exerted on the tensile torque support is exclusively tensile-based. This also facilitates the functional integration of vibration decoupling.

[0024] According to one embodiment, force is transmitted from the second to the first housing exclusively by means of the at least one tension element. This also allows for a high degree of variability and flexibility with regard to individualization and scaling.

[0025] According to one embodiment, the tensile torque support is supported by a support structure that is either indirectly connected to the second housing or integrally integrated into the second housing, for example, cast in place. The support structure can optionally be the primary or even the sole support structure between the first and second housings for the type of support and force transmission described here. Optionally, the support structure also includes at least one (additional) support component that is coupled to / can be coupled to the machine carrier (base). Optionally, the support structure is an integral part of the first housing and / or the second housing (particularly depending on which housing has the larger diameter or connection diameter, for example, exclusively a component of the first housing).

[0026] According to one embodiment, the tensile torque support comprises a plurality of tension elements, each of which is attached to both the second housing and at least indirectly (in particular via a support structure, optionally also directly) to the first housing, defining the force flow path from the second to the first housing. This also allows for the design of the coupling method based on the material, number, attachment points, and / or strength of the tension elements.

[0027] According to one embodiment, the tensile torque support comprises a plurality of tension elements which are coupled between the first and second housings in such a way that the tensile torque support is designed for torque-dependent compensation of tilting moments and weight forces without a righting axial load pair. This also expands the functional integration achievable by means of the tension elements into a comparatively simple and compact design.

[0028] According to one embodiment, the tensile torque support comprises a plurality of tensile elements extending from the second housing on both sides in opposite circumferential directions and acting in opposite circumferential directions between the second and first housings, in particular to apply both a first upward tensile force and a first downward tensile force. This also provides good adjustment options with regard to tensile preload, e.g., for compensating for tilting moments and / or weight forces.

[0029] According to one embodiment, the second housing defines attachment points to which the at least one or each traction element can be fixed, particularly in such a way that, when the drive train is in its intended angular position, the respective traction element is wrapped around the outer surface of the housing at a predefined / predefinable wrap / circumference angle, in particular with a wrap / circumference angle of at least 90°, preferably at least 125°. This also facilitates power transmission via friction, whereby the respective component of the drive train can also be supported by the respective traction element with respect to weight forces or tilting moments. The wrap / circumference angle can optionally also exceed 360°, i.e., more than a complete full wrap.

[0030] According to one embodiment, the at least one tensile element is arranged essentially in a single plane that extends orthogonally to the axial orientation of the shaft, i.e., essentially in a tensile element-specific radial plane. This also facilitates force transmission along a force flow path that is not, or at most marginally, oriented in the axial direction.

[0031] The respective traction element is advantageously placed around the drive train or the second housing with a predefined wrap angle, in particular such that the force in the traction element supports a clamping of the beginning and / or end of the traction element on the corresponding component (support structure or second housing or generator), e.g. based on a wedge effect in conjunction with a lever arm; optionally, the traction element can also be bonded to the corresponding fastening point, e.g. by gluing, or be positively fixed to the corresponding component with a body integrated in the traction element.

[0032] According to one embodiment, the tensile torque support is supported on the first housing independently of rotating components (in particular, independently of the shaft, independently of any coupling provided on the shaft, and independently of the at least one transmission component), i.e., on non-rotating components. Such support also facilitates a functional extension or integration with regard to weight force and / or tilting moment support.

[0033] According to one embodiment, the first housing has an axially overlapping support structure, particularly arranged radially outside the second housing, through which the force transmission from the tensile torque support takes place. This also allows for an advantageous connection of the respective traction element, especially in a radial plane that is at least approximately orthogonal to the axial extent of the drivetrain. The support structure can optionally also axially overlap the generator. Optionally, the support structure also includes at least one support component connected to the base, particularly when large weight forces are to be absorbed or when connecting flanges or couplings between the drivetrain components are to be relieved of stress.

[0034] According to one embodiment, at least one support structure is provided on the first housing, overlapping / crossing the second housing at least partially axially, particularly in a material-bonded manner or in an integral one-piece design, to which the at least one tension element is attached. This allows the force transmission via the first housing to occur in a comparatively robust and precisely predefined manner, especially with a precisely predetermined or pre-calculated force distribution, even in the support areas on the first housing.

[0035] According to one embodiment, at least one support structure is provided on the first housing, which at least partially overlaps / crosses the second housing axially and is supported on the first housing at at least three support points / areas, in particular comprising support points / areas arranged opposite each other laterally below and / or above the central longitudinal axis of the drive train. This allows, for example, a first reaction force acting laterally upwards on one side (on the second housing) and two second reaction forces acting laterally downwards on both sides (on the second housing), particularly in the case of opposing preload on the downwardly supported tension members; for example, one support point / area is arranged laterally above the central longitudinal axis, and two support points / areas are arranged opposite each other laterally below the central longitudinal axis.The number of support points / areas mentioned here as an example can be smaller or larger depending on the specific application and design of the components to be supported, e.g., two, four, or five support points / areas. Multiple traction elements can also be attached to the individual support points / areas; for example, if there is only one support point / area located above the central longitudinal axis of the drive train, at least two traction elements can be connected or coupled at different axial positions on the drive train between the first and second housing or generator.

[0036] The axially overlapping support structure is, for example, cast onto the first housing, i.e., integrally formed as a single piece. Alternatively, a screw connection or positive-locking pin connection can be used. The support structure preferably consists of a cast material. At the respective support points / areas, the support structure preferably exhibits comparable or homogeneous stiffness.

[0037] The respective tensioning element is advantageously attached at its end with a favorable minimum wrap angle, particularly to the support structure or a corresponding structural component, especially in such a way that the tensile force in the tensioning element assists in clamping the corresponding end of the tensioning element at the fastening point, e.g., by pressing it in with wedges and / or by using a lever arm to assist the clamping force. The respective tensioning element can optionally also be received in a clamping device without wrapping. Furthermore, the corresponding end of the respective tensioning element can also be bonded / glued to the corresponding fastening area and / or essentially positively locked to a body integrated in the tensioning element. A person skilled in the art can identify preferable fastening methods for a given application.

[0038] The axially overlapping support structure does not necessarily have to be provided exclusively by the first housing; however, this type of support has proven advantageous for many applications, for example, in the relatively robust rotor bearings of wind turbines. Alternatively, the axially overlapping support structure can also be indirectly connected to the first housing, so that the force flow occurs at least partially (but not necessarily exclusively) via the first housing. For example, a frame (especially a welded one) is also provided, to which at least one of the tension members can be at least partially supported, deflected, or otherwise attached.

[0039] The number of preferably at least two or three support points / areas can be optimized by the person skilled in the art for the specific application, in particular in such a way that a torque-dependent weight force relief upwards is ensured by means of the traction means. In Depending on the extent of axial overlap, the attachment points of the tensioning elements can also be determined in such a way that any flange connections between generator and gearbox or between individual gearbox stages are relieved of stress.

[0040] According to one embodiment, the tensile torque support comprises a plurality of tensile elements which are connected in different axial positions to the second housing and optionally also to a generator coupled to the second housing. These elements counteract at least one relative rotational movement of the second housing relative to the first housing by applying at least one upward and / or circumferentially directed tensile force. This also enables very effective support for drivetrain components, particularly the generator, that are arranged freely in space over a comparatively large length without downward support.

[0041] According to one embodiment, a space is provided below the second housing and optionally also below a generator coupled to the second housing. Above this space, the second housing and, if applicable, a generator coupled to it are freely arranged without supports above a machine carrier, particularly with freedom of movement at least downwards. This arrangement is also made possible by support solely by means of the tension members on the first housing, for example, when support on the machine carrier is not possible or would not be practical from a load-bearing perspective.

[0042] At least one of the traction elements is designed in the form of a belt, tape, or rope, for example, a V-belt or toothed belt. This facilitates a frictional / force-fit connection to an outer surface of the respective drive train component. Depending on the design of the outer surface, a person skilled in the art can select a suitable or, in the specific application, particularly appropriate pairing of traction element type and surface (optionally also a positive fit) and optionally provide a correspondingly advantageous shape on the corresponding outer surface. Particularly with high power density in a drive train, robust and high-strength traction element materials are advantageous, e.g., polymer fibers, especially in the form of multifibrillar (multi-fiber) polyacrylonitrile fibers; or traction elements consisting of or based on aramid can be used; or polyester composite belts or high-strength synthetic fiber composites made of polyethylene, such as...Synthetic chemical fibers based on polyethylene with very high molecular weight (so-called Dyneema or PE-UHMW). In this process, at least one tensile element is attached to at least one of the outer surfaces of at least the second housing, either by force / friction and optionally also by form-fitting. This flexibility also facilitates the optimization of elastic or prestressing properties, particularly depending on the individual length sections of the respective tensile element (free length, contact length).

[0043] According to one embodiment, vibration decoupling between the second housing (or / or the gear component) and the first housing (or / or the shaft bearing) is ensured by means of at least one tension element, in particular by making the at least one tension element from a well-damping material such as polyurethane, or a very flexible and elastic material such as polyamide, or from a high-strength and also comparatively elastic material, e.g., polyethylene-based. This also promotes a synergistic effect with regard to the potentially numerous functions of the tension elements described here, depending on the desired functional scope in the application.

[0044] Another aspect of the invention relates to a drive train arrangement for industrial gearboxes, in particular for connection to a rotor of a wind turbine, comprising: a first housing which surrounds a bearing for a shaft of the drive train, a gearbox component which is coupled, in particular axially aligned, to the shaft and which is surrounded by a second housing, and a tensile torque support comprising at least one tensile element coupling the first and second housings, wherein the tensile torque support counteracts a torque acting on the shaft or the gearbox component coupled thereto; wherein the tensile torque support is supported on the first housing to transmit the reaction forces exerted on the at least one tensile element, in particular exclusively by means of a tensile element. This also facilitates combined support of tilting moments.

[0045] According to the further aspect, the following features can also be advantageously implemented, especially on the front side in the area of ​​axially overlapping pins of the two housings.

[0046] The tensile torque support can comprise a plurality of tensile elements which are provided between pins or similarly projecting sections of the second housing or the transmission component and pins or similarly projecting sections of the first housing, in particular in a loop-like manner between pairwise corresponding pins of the first and second housing, in particular in each configuration as a completely circumferential endless tensile element, in particular in each in a single or multi-layered arrangement.

[0047] The traction torque support can comprise a plurality of traction elements, which extend both in a first traction element direction, in particular in the operating / energy generation direction (main direction) defined by the torque acting on the drive train at the input, and in a second traction element direction, in particular in the reversing / braking operating direction (secondary direction).

[0048] The tensile torque support can comprise a plurality of first tensile elements which extend in a first tensile force direction (main tensile force direction) opposite a first torque acting about the axial orientation of the drive train, and wherein the tensile torque support comprises a plurality of second tensile elements which extend in a second tensile force direction (counter-direction of tensile force, secondary tensile force direction) opposite a second torque acting about the axial orientation of the drive train, wherein the first torque is greater than the second torque when the drive train is used as intended, and wherein the first tensile elements are dimensioned accordingly (i.e., are larger, more robust, or stiffer than the second tensile elements).

[0049] The first and second housings can interlock in the manner of a claw coupling, in particular by means of axially overlapping pins or similar axially protruding sections on which the respective traction elements engage.

[0050] The transmission of the torques exerted on the tensile torque support around the shaft or around the axial direction and the resulting reaction forces is preferably exclusively tensile-based.

[0051] The tensile moment support can further comprise at least one prestressing unit set up and arranged to apply and transmit an uprighting force to the second housing, counteracting a gravity-induced tilting moment, in particular in an arrangement between an outer shell surface of the first and second housing.

[0052] The tensile torque support can include a preload unit which is functionally decoupled from the action of the at least one tensile element, in particular by the preload unit acting essentially in the axial direction between the housings and the tensile element(s) acting essentially only in the circumferential and / or radial direction between the housings for torque transmission.

[0053] The preload unit can preferably engage in an upper circumferential segment of the first and second housings and transmit an erection force. The preload unit can comprise at least one elastically preloadable preload element, in particular a mechanical spring, and / or at least one hydraulic or electrical actuator. The preload unit can comprise at least one elastically preloadable preload element which acts in conjunction with the elasticity of the tensioning elements (in particular due to initial elongation during assembly) and provides a torque-dependent preload force. Such a preload unit can optionally be provided and adjustable independently of or in conjunction with the tensioning elements (or at least a subset of the effective tensioning elements).

[0054] Below the second housing and optionally also below a generator coupled to the second housing, a free space can be provided above which the second housing and, if applicable, a generator coupled to it are arranged freely in space without supports above a machine carrier, in particular with a degree of freedom of movement at least downwards.

[0055] At least one of the traction elements is designed in the form of a belt, strap or rope, in particular as a flat belt.

[0056] At least one of the tensile elements can be engaged at least by friction and optionally also by positive locking on a / the lateral surface of pins or similar protruding sections of the first and second housing.

[0057] By means of at least one tensile element, vibration decoupling between the first and second housing (or / or between the gear component and the bearing component or shaft) can be ensured, in particular by making the at least one tensile element from a damping material such as polyurethane or from a comparatively flexible and elastic material such as polyamide or from a high-strength and comparatively elastic material such as aramid or polyester or polyethylene or polymer fibers, in particular in the form of multifibrillar (multi-fibered) polyacrylonitrile fibers.

[0058] A further aspect of the invention relates to an industrial gearbox that is installed in or comprises such a drivetrain arrangement, in particular with a generator attached to the second housing and arranged freely in space without downward support to the base. The aforementioned problem is also solved by an industrial gearbox with / in a drivetrain arrangement described above, in particular for supporting torques acting on a gearbox component exclusively by means of at least one traction element. This results in the aforementioned advantages, especially with regard to small footprint and high degree of customizability, even for very specific applications. The aforementioned problem is also solved by a wind turbine with such an industrial gearbox.

[0059] The aforementioned problem is also solved by a method according to the corresponding dependent claim, namely by a method for adjusting a torque support of a drive train arrangement of an industrial gearbox, in particular in a drive train leading from a rotor of a wind turbine, wherein a first housing surrounding a bearing of a shaft of the drive train is mounted against a second housing which surrounds a gearbox component coupled to the shaft, wherein by means of a tensile torque support or tensile torque support which counteracts a torque acting on the shaft or the gearbox component coupled thereto, a torque support of the second housing and thus of the gearbox component on the first housing is achieved by absorbing and transmitting exclusively tensile forces by means of at least one belt,The tensioning of the tensioning element, which is designed as a band or rope, occurs at least from the second housing into the first housing, particularly in a drive train with a generator supported on the second housing, especially in a drive train arrangement described above, or generally in an industrial gearbox or wind turbine, particularly also when / through the use of a tensioning element arrangement described above. This results in the aforementioned advantages, especially with regard to a highly variable adaptability of the support method depending on the operating conditions, e.g., through adapted pretensioning in the tensioning elements, also with regard to temporarily high tilting moments.

[0060] The aforementioned task can also be solved by such a method, in which a preload of at least one tension member and / or at least one axially acting preload unit (in particular to apply an axially oriented righting force acting against the weight force at the center of gravity) is set and optionally actively controlled. This also allows for even more precise adaptation to individual load conditions.

[0061] For example, at least one force / displacement sensor can be used to detect the instantaneous load state along the respective force flow path defined by the traction element(s), and the components of the tensile torque support or tensile torque support can be adjusted accordingly. This adjustment might include preload in the respective traction element or bilateral coordination of the action of opposing traction elements acting in opposite circumferential directions. This active adjustment of the reaction forces can be advantageously implemented, for example, when at least one of the traction elements is attached to a base and a constant support force is to be ensured even when the drive train performs a pitching motion, such as due to wind loads exerted on a very large-diameter rotor. Alternatively, for example...A displacement / distance sensor may also be provided for measuring the distance between the base and the gearbox or generator (i.e., in the vertical direction). This displacement measurement data is evaluated in such a way that, for example, the effective length of the traction element is shortened or lengthened via an actively controlled rotational movement of the support structure, thereby actively adjusting the preload or damping. The support structure can, for example, be rotatably mounted on the first housing around its own axis, in particular in such a way that the respective traction element attached to it could be preloaded by rotation or by changing the angular position of the support structure, in the sense of preloading or reloading by winding a traction element around the respective support structure.For example, force measurement in the force flow path of the traction element or at the attachment points to the support structure in conjunction with an active actuator enables targeted force adjustment, for example by means of a pressure-controlled hydraulic cylinder or an electric motor with ball screw drive, especially in conjunction with appropriately positioned accelerometers (sensors) in the pitch, yaw or torsion direction; in this way, torsional and / or bending vibrations in the drive train can also be positively influenced and lower component loads or lower noise emissions can be achieved.

[0062] According to one embodiment, tensile forces are absorbed and transmitted exclusively to at least the first housing by means of a plurality of tension elements, each of which is attached to both the second housing and at least indirectly to the first housing and defines the force flow path from the second to the first housing. The tension elements are preferably coupled between the first and second housings in such a way that torque-dependent compensation of tilting moments and weight forces is also achieved without a righting axial load pair. This facilitates functional integration for providing numerous support functions by means of the tension elements, particularly with additional support at a base of the arrangement.

[0063] The aforementioned problem is also solved by using a drivetrain arrangement described above in an industrial gearbox, particularly in a wind turbine, in an arrangement between the rotor of the wind turbine and the generator of the wind turbine, especially in a uniaxially aligned arrangement / alignment of the entire drivetrain, wherein, by means of a tensile torque support or tensile torque support of the drivetrain arrangement, tensile forces are transmitted exclusively from at least one gearbox housing of the drivetrain arrangement to at least one rotor bearing housing arranged around a shaft of the drivetrain by means of a tensile element, preferably by means of a plurality of tensile elements, wherein the gearbox housing and any further components flanged / coupled to it, such as, for example,A generator is preferably supported exclusively on the rotor bearing housing, preferably by means of a plurality of tension members, in particular in a previously described relative arrangement of the tension members to each other and on the first and second housings. This allows the aforementioned advantages to be realized, especially with regard to the additional absorption and transmission of tilting moments and weight forces while minimizing stress on the drivetrain and surrounding components. BRIEF DESCRIPTION OF THE FIGURES

[0064] The invention is described in more detail in the following drawings by way of exemplary preferred embodiments, whereby reference numerals not explicitly described in a particular drawing are made to the other drawings. The drawings show: Figure 1In a front view from the output side, a drive train arrangement with a tensile torque support according to an embodiment in an installation situation on a wind turbine; Figure 2 a drive train arrangement according to an exemplary embodiment shown in a partially cut-away side view; Figure 3 in an end-face view in axial direction in isolated representation an additional tensile-based torque support by means of tensile elements coupled to the base of the tensile torque support according to a further embodiment; Figure 4 in a side view a drive train arrangement according to a further embodiment; Figures 5A, 5B in a side view and in a top view a drive train arrangement according to a further embodiment; Figure 6 in a side view a drive train according to the state of the art; DETAILED DESCRIPTION OF THE FIGURES

[0065] The invention will first be explained with general reference to all reference numerals and figures. Specific features or individual aspects, or aspects of the present invention that are clearly visible / representable in the respective figure, will be addressed individually in connection with that figure.

[0066] A drive train assembly 10 is provided, which has a bearing 4 for a shaft 2 (in particular with a two-point, three-point or four-point bearing or moment bearing with, for example, spherical roller bearings or preloaded tapered roller bearings), for example, for a rotor shaft to which, for example, the hub 1 of a rotor of a wind turbine 100 is coupled. The bearing 4 is surrounded by a first housing 13 (rotor bearing housing). The drive train transitions, in particular, via a coupling 5 (in particular a flange connection, shrink-fit connection, positive-locking plug connection, or the like), into a gearbox component 16 (in particular comprising at least one planetary gear stage of an industrial gearbox 20), wherein the gearbox component 16 is arranged in a second housing 17 (gearbox housing). A generator 9 can also be provided adjacent to the gearbox component, in particular connected to or flanged to the gearbox housing.Particularly in an installation situation on a tower 102 of a wind turbine, not only large static but also large dynamic loads act on the drive train and also on the mechanical interfaces to the tower, not least due to comparatively large pitching moments caused by the rotor of the wind turbine.

[0067] The drivetrain is subjected to a potentially quite dynamic input torque. M 1 (for example, generated by the rotor of a wind turbine), and it can have an output torque M2The force can be absorbed, for example, by an axially aligned generator 9. The weight force g also acts on the individual components of the drive train and can generate a considerable bending moment, particularly in the area of ​​the gearbox component or the generator. Furthermore, noticeable tilting moments can occur, especially in wind turbines, due to the large rotor diameter. In this context, the present invention provides an advantageous measure for supporting the components connected to the shaft 2 on the output side.

[0068] The drivetrain assembly 10 according to the present invention has a traction-link-based traction torque support 18, which comprises a plurality of traction links 18.1, 18.n, in the example shown in the figures at least four traction links 18.1, 18.2, 18.3, 18.4. Optionally, at least one further traction link 18.n can also be provided, in particular for additional support / force transmission to a base 101 (in particular a wind turbine) (in particular support at at least one further support point / area P4). The individual traction links or a subset thereof are preferably attached to at least one axially overlapping support structure 13.1, which extends radially outside the gearbox housing in the axial direction and is supported on the bearing housing, in particular at first and second support points / areas P1, P2.

[0069] The individual traction elements can each be attached to a mounting point P3 on the second housing or on the generator, in particular such that the respective traction element can come into contact with the corresponding outer shell surface section 9.3, 17.3 via an advantageously large wrap / circumference angle α. Corresponding mounting points are also provided on the support structure 13.1 in advantageously corresponding axial positions, in particular such that the respective traction element is aligned in a traction element-specific radial plane Er (no axial force component). Advantageously, the drive train from the coupling 5 (or a corresponding interface to the shaft) is arranged to float freely in such a way that a free space, free volume V, can be realized below the drive train down to the base 101. Optionally, in individual cases, additional downward support towards the base can also be provided ( Fig. 3 ).

[0070] Load conditions can be detected via one or more force / displacement sensors 19 arranged on the respective force flow path, whereby optionally a preload or similar parameters of the traction elements can also be set depending on (instantaneous) loads.

[0071] In Fig. 1 is (in front view) A Figure 18 shows a tensile-torque support system 18 comprising four tensile elements 18.1, 18.2, 18.3, 18.4 supported in three support areas. The individual tensile elements are positioned at an angle α of approximately 120° to 150° against the respective outer surface. Two of the tensile elements 18.2, 18.3 are guided bilaterally downwards and transmit the force. F2(downward pulling force), and two further pulling means 18.1, 18.4 are guided unilaterally upwards and transmit the force F1 (upward pulling force), which essentially counteracts the (differential) torque.

[0072] Out of Fig. 1 It also shows that the connection of the support structure to the first housing (support points / areas) can be made at different locations and diameters and in different support directions (bottom / top / sideways) depending on the application, in particular in such a way that the resulting forces at least partially compensate each other or complement each other in such a way that unfavorable force components (e.g. adverse effects of the weight force) are eliminated.

[0073] In Fig. 2 is the respective axial position of the individual traction elements as well as their extension in the corresponding radial plane Er(shown especially orthogonally to the slightly tilted drivetrain); one of the traction elements 18.4 also rests against the outer surface of the generator 9.3. The support structure 13.1 extends axially both above and below the gearbox component and the generator and is supported in the two areas P1, P2 on the bearing housing 13 (especially by integral, one-piece forming on the housing 13). Thus, the drivetrain extends freely from the coupling 5 in the space above the free volume. V.

[0074] In Fig. 3 An optional additional support is shown; the traction-link-based tensile torque support 18 can therefore also comprise at least one traction element 18.n coupled to the base 101, in particular with a force flow path guided via at least one deflection point / roller 14 and at least one (further) support component 15. Fig. 3Reference is made to the gearbox component 17; the connection method shown can alternatively or additionally also be implemented for a generator. The in Fig. 3 The radially projecting flange elements 17.1 or the like, force application ring or segment or pin, shown can optionally also be used in the following: Fig. 1 , 2 The outer shell surfaces of the gearbox component and the generator shown are provided.

[0075] The in Fig. 3 The illustrated traction-based connection to the base (machine carrier) can, depending on the application and size / mass of the components, be considered an additional aspect in combination with the previously mentioned, particularly in connection with the Fig. 1 , 2 described traction-based connection to the first housing (bearing housing) can be combined, especially for drive trains on which large tilting moments and / or weight forces or weight forces with a particularly long lever arm act.

[0076] In the following figures, a further aspect of the present invention is described in more detail, first in general terms, then with specific reference to the respective figure.

[0077] A drive train assembly 10 is provided, which has a bearing 4 for a shaft 2 (in particular with a two-point, three-point or four-point bearing or moment bearing with, for example, spherical roller bearings or preloaded tapered roller bearings), for example, for a rotor shaft to which, for example, the hub 1 of a rotor of a wind turbine 100 is coupled. The bearing 4 is surrounded by a first housing 13 (rotor bearing housing). The drive train transitions from the first housing 13 into a gearbox component 16 (in particular comprising at least one planetary gear stage of an industrial gearbox 20), wherein the gearbox component 16 is arranged in a second housing 17 (gearbox housing). A generator 9 can also be provided adjacent to the gearbox component, in particular connected to or flanged to the gearbox housing.Particularly in an installation situation on a wind turbine tower (102), not only large static loads but also large dynamic loads act on the drivetrain and the mechanical interfaces to the tower, not least due to the comparatively large pitching moments caused by the wind turbine rotor. The latter can also become noticeable whenever comparatively large weight forces act on long lever arms of a drivetrain subjected to relatively high dynamic stress.

[0078] The drivetrain is subjected to a potentially quite dynamic input torque. M1 (for example, generated by the rotor of a wind turbine), and it can have an output torque M2The force can be absorbed, for example, by an axially aligned generator 9. The weight force g also acts on the individual components of the drive train and can generate a considerable bending moment, particularly in the area of ​​the gearbox component or the generator. Furthermore, noticeable tilting moments can occur, especially in wind turbines, due to the large rotor diameter. In this context, the present invention provides an advantageous measure for supporting the components connected to the shaft 2 on the output side.

[0079] The drivetrain assembly 10 according to the present invention has a tensile-related tensile torque support 18, which comprises a plurality of tensile elements 18.1, 18.2, here in the example of the figures at least two different types of tensile elements 18.1, 18.2 in different orientations, each in radial planes Er. The individual tensile elements or a subset thereof are preferably attached to at least one axially overlapping support structure (here in an embodiment as axially overlapping pins 13.7, 17.7 of the respective housing 13, 17), which are supported on the respective housing, in particular at first and second support points / areas P1, P2.

[0080] The individual tension elements can each be attached to a fastening section P3 on the respective pin 13.7, 17.7, in particular in a loop-like fashion with a wrap / circumference angle on the corresponding outer shell surface section in the range of, for example, 150° to 180°. Advantageously, the drive train is arranged to float freely from the interface between the first and second housings in such a way that a free space, free volume V, can be realized below the drive train up to the base 101, whereby the base 101 can be designed to be correspondingly short in the axial direction. Optionally, in individual cases, additional support can also be provided downwards towards the base, which, however, is not necessary, especially since the tensile torque support 18 described here can also include a preload unit 18.6 acting in the axial direction ( Fig. 4 ), by means of which a counteracting the tipping moment M3 effective righting force F3transferable between the first and second housings ( Fig. 5A ), in particular in combination with at least one preload element 18.7 (e.g. mechanical spring or spring-damper combination or hydraulic or electric actuator, each optionally actively adjustable), which can also act as a kind of pressure buffer.

[0081] In connection with the preferably radially far outwardly arranged preload unit 18.6, an optionally situation-dependent active adjustment of a force transmitted between the housings can be carried out, in particular depending on momentary load conditions on the drive train, especially based on momentary measured values ​​of the at least one sensor.

[0082] Load conditions can be detected via one or more force / displacement sensors 19 arranged on the respective force flow path, whereby optionally a preload or similar parameters of the traction elements and / or the preload unit can also be set depending on (instantaneous) loads.

[0083] In Fig. 4 A tensile torque support 18 is shown, in which the individual tension elements (types) bear against axially overlapping housing pins in the manner of loops, whereby a comparatively large (reaction) force F1 is applied by a first type of tension element (torque support), and a comparatively smaller (counter) force F2 is also applied by a second type of tension element. The gearbox and generator can remain in a freely suspended arrangement above the base 101 without downward support.

[0084] In Fig. 5A, 5BThe axial interlocking is illustrated in detail, and the fastening and function of the additional (optional, depending on prevailing weight forces and tilting moments) preload unit are explained by way of example. This unit is advantageously positioned radially far out at the top of the respective housing edge area.

[0085] The preload unit 18.6 is supported, for example, on / between radially upwardly projecting tabs at a further support point / area P5 on the gearbox housing and / or bearing housing, particularly in axial positions that slightly overlap / spanne the respective radial plane in which the tensioning elements are arranged. This type of support can also be provided at several points along the circumference, particularly for the purpose of vibration damping, e.g., at the level of the axis on both sides of the drivetrain, especially to form a force couple whose direction of action compensates for the vibration mode, e.g., around the yaw axis (vertical or nearly perpendicular to the drivetrain axis) or the tilt axis (horizontal perpendicular to the drivetrain axis).

[0086] In Fig. 6A previously known arrangement according to the state of the art is shown. The rotor bearing housing 3 and the gearbox housing 7 are each independently supported downwards at the base, with torques and, if applicable, tilting moments being transmitted to the base by means of a torque support unit or weight force support 8. However, this type of support has proven to be disadvantageous, particularly under very dynamic loads on the drivetrain and with large tilting moments, as explained above. Reference symbol list

[0087] 1 Hub 2 Shaft, in particular rotor shaft of a wind turbine 3 Rotor bearing housing according to the prior art 4 Rotor bearing / rotor shaft bearing, in particular with spherical or tapered roller bearing 5 Coupling 7 Gearbox housing according to the prior art 8 Torque support unit or weight force support according to the prior art 9 Generator 9.3 Outer shell surface section for arranging or receiving a traction element 10 Drive train arrangement 13 Rotor bearing housing (first housing) 13.1 Axially overlapping support structure, radially outside the gearbox housing 13.7 Pin / cam rotor bearing (housing) 14 Deflection point / roller 15 (Further) support component 16 Gearbox component, in particular with planetary gear stage 17 Gearbox housing (second housing) 17.1 Radially projecting flange or similar force application ring or segment or pin 17.3 Outer shell surface section for arranging or receiving a traction element 17.7 Pin / Cam Gearbox (housing) 18 Pull torque support orTension torque support (each tension-based) 18.1 (first) tension member or first type of tension member 18.2 further (second) tension member or second type of tension member 18.3 optional further (third) tension member 18.4 optional further (fourth) tension member 18.n further tension member especially for additional support / force transmission to the base 18.6 pretensioning unit 18.7 pretensioning element 19 force / displacement sensor 20 industrial gearbox 100 wind turbine 101 machine carrier or similar base 102 tower . A Front view, viewing direction towards the figure, in axial direction Er traction-specific radial plane F1 (first) tensile force directed especially upwards or in the first circumferential direction F2 (second) tensile force directed especially downwards or in a second circumferential direction F3 (third) tensile force directed especially axially against a tilting moment g Weight force M 1 Input torque M2 Output torque M3Tilting moment, weight moment P1 first support point / area on the rotor bearing housing (first housing) P2 second support point / area on the rotor bearing housing (first housing) P3 Attachment point for traction device on the second housing or generator P4 further support point / area, especially at a base P5 Additional support point / area on the gearbox housing (second housing) V Free space, free volume α wrapping / circumference angle

Claims

1. Drivetrain arrangement (10) for industrial gearboxes, in particular for attachment to a rotor of a wind turbine, having: - a first housing (13) which surrounds a bearing arrangement (4) for a shaft (2) of the drivetrain, - a gearbox component (16) which is coupled to the shaft (2) in particular in an axially aligned manner and is surrounded by a second housing (17), - a traction-moment support or traction-torque support (18) which comprises at least one traction means (18.1) coupled at least to the second housing, wherein the traction-moment support or traction-torque support counteracts a torque (M1, M2) that acts on the shaft (2) or on the gearbox component coupled thereto; wherein the traction-moment support or traction-torque support (18), for transmitting the reaction forces (F1, F2) exerted on the at least one traction means (18.1), is supported at least against the first housing (13), characterized in that the at least one traction means (18.1, 18.n) is of belt-like, band-like or rope-like design.

2. Drivetrain arrangement (10) according to Claim 1, characterized in that the transmission of the reaction forces exerted on the traction-moment support or traction-torque support (18) is exclusively traction-means-based; or wherein a transmission of force from the second housing to the first housing takes place exclusively by means of the at least one traction means (18.1); or wherein the traction-moment support or traction-torque support (18) is supported via a supporting structure (13.1) which is connected indirectly to the second housing (17) or is provided integrally in one piece, for example cast, on the second housing.

3. Drivetrain arrangement (10) according to Claim 1 or 2, characterized in that the traction-moment support or traction-torque support (18) comprises a plurality of traction means (18.1) which are each fastened both to the second housing (17) and, at least indirectly, to the first housing (13) and which define the force-flow path from the second housing to the first housing; or wherein the traction-moment support or traction-torque support (18) comprises a plurality of traction means (18.1) which proceed from the second housing (17) on either side in opposite circumferential directions and which act oppositely between the second and first housings in opposite circumferential directions, in particular for applying both a first upwardly directed traction force (F1) and a first downwardly directed traction force (F2).

4. Drivetrain arrangement (10) according to one of Claims 1 to 3, characterized in that the second housing (17) defines fastening points (P3) to which the at least one or respective traction means (18.1, 18.n) is fixable, in particular in such an arrangement that the respective traction means (18.1), with the angular position of the drivetrain as intended, is placed around an / the outer shell surface of the housing over a predefinable circumferential angle (α), in particular with a circumferential angle of at least 90°, preferably at least 125°; or wherein the first and second housings interengage in the manner of a claw coupling, in particular by means of axially overlapping pins or similar axially protruding portions on which the respective traction means engage.

5. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that the traction-moment support or traction-torque support (18) is supported against the first housing (13) independently of rotating components.

6. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that the first housing (13) has a supporting structure (13.1) of axially overlapping form, in particular in an arrangement radially outside the second housing (17), via which the transmission of force by the traction-torque support (18) takes place; or wherein provision is made on the first housing (13), in particular fastened in a materially bonded manner or configured integrally in one piece, of at least one supporting structure (13.1) which at least partially axially overlaps the second housing (17) and to which the at least one traction means (18.1, 18.n) is fastened; or wherein provision is made on the first housing of at least one supporting structure (13.1) which at least partially axially overlaps the second housing (17) and which is supported against the first housing at at least three supporting points or regions (P1, P2).

7. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that traction-moment support or traction-torque support (18) comprises a plurality of traction means (18.1, 18.n) which are attached at different axial positions to the second housing (17) and selectively also to a / the generator (9), which is coupled to the second housing, and counteract at least a relative rotational movement of the second housing (17) relative to the first housing (13) by application of at least an upwardly and / or circumferentially directed traction force (F1).

8. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that provision is made below the second housing (17) and selectively also below a / the generator (9) coupled to the second housing of a clearance (V) above which the second housing and possibly also a / the generator (9) coupled thereto are freely arrangeable spatially above a / the machine support without support, in particular with a degree of freedom of movement at least downwards.

9. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that the at least one traction means (18.1, 18.n) is in the form of a V-belt or toothed belt; wherein the at least one traction means comes into abutment against a / the outer shell surface (17.3) at least of the second housing (17) at least in a force-fitting / frictionally engaging manner and selectively also in a form-fitting manner.

10. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that the traction-moment support (18) comprises a plurality of traction means which extend both in a first traction-means direction, in particular in the energy-generation direction defined by the torque acting on the drivetrain at the input side, and in a second traction-means direction, in particular in a braking-operation direction; or wherein the traction-moment support (18) comprises a plurality of first traction means which extend in a first traction-force direction counter to a first torque acting about the axial orientation of the drivetrain, and wherein the traction-moment support (18) comprises a plurality of second traction means which extend in a second traction-force direction counter to a second torque acting about the axial orientation of the drivetrain, wherein the first torque is greater than the second torque with the drivetrain used as intended, and wherein the first traction means are dimensioned accordingly.

11. Drivetrain arrangement (10) according to one of the preceding claims, characterized in that the traction-moment support further has at least one preload unit set up and arranged for application and transmission of a restoring force, which counteracts a tilting moment induced by gravitational force, to the second housing, in particular in an arrangement between the outer shell surfaces of the first and second housings; and / or wherein the traction-moment support has a / the preload unit, which is functionally decoupled from the action of the at least one traction means, in particular by the preload unit acting substantially axially between the housings and the traction means, for torque transmission, acting substantially only circumferentially and / or radially between the housings.

12. Industrial gearbox (10) having a drivetrain arrangement (10) according to one of the preceding claims for supporting torques acting by way of a gearbox component (16) exclusively by means of at least one traction means (18.1, 18.n), in particular in an arrangement in a wind turbine.

13. Method for setting torque support of a drivetrain arrangement (10) of an industrial gearbox, wherein a first housing (13) surrounding a bearing arrangement (4) for a shaft (2) of the drivetrain has been / is mounted against a second housing (17) surrounding a gearbox component (16) which is coupled to the shaft (2), wherein, by means of a traction-moment support or traction-torque support (18), which counteracts a torque (M1, M2) acting on the shaft (2) or on the gearbox component coupled thereto, torque support or the torque support of the second housing (17) and thus of the gearbox component against the first housing (13) takes place by way of accommodation of exclusively traction forces and transmission thereof at least from the second housing at least into the first housing, characterized in that the accommodation and transmission of exclusively traction forces takes place by means of at least one traction means (18.1, 18.n) of belt-like, band-like or rope-like design, in particular in a drivetrain with a generator (9) supported against the second housing (17), in a drivetrain arrangement (10) according to one of Claims 1 to 11 or in an industrial gearbox (20).

14. Method according to the preceding method claim, wherein the accommodation of exclusively traction forces and transmission thereof into at least the first housing (13) takes place by means of a plurality of traction means (18.1, 18.n) which are each fastened both to the second housing (17) and, at least indirectly, to the first housing (13) and which define the force-flow path from the second housing to the first housing.

15. Use of a drivetrain arrangement (10) according to one of Claims 1 to 11 in an industrial gearbox (20), in particular in a wind turbine (100) in an arrangement between a / the rotor of the wind turbine (100) and a / the generator (9) of the wind turbine, in particular in an arrangement of the entire drivetrain of single-axis alignment, wherein, by means of a / the traction-moment support or traction-torque support (18) of the drivetrain arrangement (10), exclusively traction forces are transmitted on the basis of traction means at least from a / the gearbox housing (17) of the drivetrain arrangement (10) to at least a / the rotor-bearing housing (13), which is arranged around a / the shaft of the drivetrain, by means of at least one traction means of belt-like, band-like or rope-like design, preferably by means of a plurality of traction means, wherein the gearbox housing (17) and any further components coupled thereto, such as for example a generator (9), is / are supported preferably exclusively against the rotor-bearing housing (13), preferably by means of the plurality of traction means.