Couplings, drive trains, wind turbines and industrial applications for wind turbine gearboxes

Abstract

This invention relates to a coupling (30) for connecting a gearbox (50) to a drive shaft (45), comprising: a circumferentially extending intermediate member (10) having an input-side flange (12) and an output-side flange (14), the output-side flange being axially rigidly connected to the input-side flange (12) via longitudinal webs (16), wherein the longitudinal webs (16) are integrally formed with the input-side flanges (12) and the output-side flanges (14), and wherein each longitudinal web (16) consists of one or two parts. The invention also relates to a drivetrain (60) having this type of coupling (30), a wind turbine (70), industrial applications (80), and computer program products (90). Due to the longitudinal webs (30), an increase in the torsional stiffness of the intermediate member (10) of the coupling (30) is achieved economically in a weight-saving manner.

Description

Technical Field

[0001] This invention relates to a coupling suitable for mechanically attached wind turbines, a transmission system applicable to wind farms, a wind farm having such a transmission system, and corresponding industrial applications. Background Technology

[0002] WO 2012 / 052022 A1 discloses a gearbox for wind power plants, which is connected to a generator. The gearbox is configured as a planetary gearbox and is connected to the rotor on the drive side via a main shaft. Couplings of different designs are provided for connecting the main shaft to the gearbox.

[0003] JP 2010065724 A discloses a rigid coupling between two shafts, in which the respective shafts are screwed via associated shaft flanges to a separately configured flange in each case, and the flange is in turn screwed to a separately configured intermediate member. The intermediate member has a radially outwardly opening partially tubular recess. A portion of the recess is closed on the axial end side to allow for a threaded connection between the intermediate member and the flange. The remaining recess is axially open to enable a threaded connection between the flange and the corresponding shaft flange.

[0004] DE102005047305 A1 has disclosed that in each case, two hubs are connected to an associated flange via a multi-disc assembly, the flanges being rotatedly connected to each other via a spline meshing system, so that they can move relative to each other in the axial direction.

[0005] DE29623369U1 discloses a tapered bolt connection for a multi-disc assembly coupling.

[0006] In various fields of mechanical engineering, there is a need for a coupling that enables the reliable transmission of torque between rotating parts, and allows for compensation of inaccuracies in positioning and / or orientation during the process. Simplicity of assembly, maintenance, and high cost-effectiveness are also desired. This is particularly suitable for wind power technology and industrial applications where high drive torque is frequently required. The present invention aims to provide a coupling that offers improvements in at least one aspect of the requirements outlined. Summary of the Invention

[0007] The proposed objective is achieved by a coupling. Preferred improvements are detailed in the dependent claims and the description below, and these preferred improvements may represent an aspect of the invention individually or in combination in each case. If one feature is shown in combination with another feature, this is only for a simplified overview of the invention and is not intended to suggest in any way that the feature could not be a development of the invention even without the other features.

[0008] The coupling is configured to connect a transmission to a drive shaft. The coupling includes a circumferential intermediate member, which in particular has a generally tubular body along its circumference. The intermediate member has a drive-side flange and an output-side flange, which are particularly capable of abutting the body of the intermediate member. In the installed state, drive torque is introduced into and discharged from the coupling via the drive-side flange and the output-side flange, respectively. The flanges can be releasably connected directly or indirectly to the drive shaft and the transmission.

[0009] The output-side flange is axially and kinematically fixed to the drive-side flange via longitudinal webs. The longitudinal webs prevent axial relative movement of the output-side flange relative to the drive-side flange. The longitudinal webs specifically comprise recesses constructed from intermediate members; preferably, longitudinal webs that follow each other circumferentially can define recesses constructed between these longitudinal webs tangentially or circumferentially. On their substantially tangential sides, corresponding longitudinal webs can, particularly preferably in each case, define one side of a different recess that follows each other circumferentially. The recesses can be defined radially by the body of the intermediate member. The body can particularly have a ring that closes tubularly in the circumferential direction and can form the bottom side of all the recesses. As a result, the spoke-like longitudinal webs and the tubular body, together with the flanges, can form multiple recesses arranged front-to-back circumferentially.

[0010] In particular, the flanges are substantially circumferentially constructed. The drive-side flange and / or the output-side flange may have a particularly constant outer diameter. That is, the outer diameter of the flange is substantially the same at each circumferential angle. The drive-side flange and / or the output-side flange are preferably constructed as a disc or annulus. In particular, the flange has a flat and / or planar construction on its axial side. The outer diameter of the flange is preferably a multiple of its material thickness in the axial direction along the main axis of rotation of the coupling.

[0011] The longitudinal web extends substantially axially. Here, the axial direction is parallel to the main axis of rotation of the coupling. The longitudinal web may also have a certain range in the radial direction, particularly to define recesses. The longitudinal web may have a material thickness in the tangential direction, which is less than the range of the longitudinal web in both the axial and radial directions. The longitudinal web may be oriented entirely in the axial direction, or it may have an inclined position in the form of a helical gear system, resulting in the fundamental radial range of the longitudinal web being inclined, particularly at an angle of several degrees relative to the radial and / or axial directions. The longitudinal web may be configured to be substantially radially outward.

[0012] Furthermore, the corresponding longitudinal web is integrally constructed with the drive-side flange and the output-side flange. The longitudinal web can be integrally constructed with the body of the intermediate component, particularly to construct a seamless transition between the longitudinal web and the bottom side of the body, which defines a recess in the radial direction. Therefore, the intermediate component can be produced, for example, as a casting, and thus can be produced in a cost-effective manner. In particular, satisfactory demolding capability can be achieved.

[0013] The corresponding longitudinal web is constructed as a single piece or two pieces. If the longitudinal web is constructed as a single piece, the drive-side flange, output-side flange, longitudinal web, and body (which may be positioned as the bottom side of the construction recess) can be inexpensively and integrally combined into a single one-piece intermediate component. If the longitudinal web is constructed as a two-piece component, the longitudinal web and body (which may be positioned as the bottom side of the construction recess) can be separated substantially centrally in the axial direction, and a central dividing plane can be provided for the intermediate component. The corresponding parts of the intermediate component constructed as two pieces can have a symmetrical, particularly mirror-reversed, and preferably identical construction relative to the other part. As a result, the corresponding parts of the intermediate component can be inexpensively constructed as castings, the demolding direction of which corresponds to the axial direction and the main axis of rotation in the installed state. As a result, the intermediate component can be manufactured particularly inexpensively and simply. The two parts of the intermediate component can be held together by suitable fastening devices and are axially immovable relative to each other.

[0014] The longitudinal web increases the torsional stiffness of the intermediate component by reducing weight. This weight reduction also facilitates the installation of the coupling according to the invention. The coupling is also suitable for arrangement between components other than the drive shaft and transmission. Therefore, the technical advantages of the coupling according to the invention can also be used in further applications.

[0015] Specifically, the longitudinal web or the drive-side portion of the longitudinal web is incorporated into the drive-side flange on the drive-side flange side pointing towards the output-side flange via a rounded transition portion extending circumferentially, and / or the longitudinal web or the output-side portion of the longitudinal web is incorporated into the output-side flange on the output-side flange side pointing towards the drive-side flange via a rounded transition portion extending circumferentially. The rounded transition portion facilitates load and force or torque distribution between the respective longitudinal web and the associated flange, resulting in improved stability and strength, and avoiding or at least reducing stress concentration effects. Simultaneously, the corresponding rounded transition portion facilitates demolding of the intermediate part after the casting process; preferably, the rounded transition portion is a continuation of the draft angle, which is provided on the integrally attached longitudinal web and / or flange. The rounded transition portion can in particular be incorporated into the draft angle in a continuously differentiable manner, with almost no steps and no edges.

[0016] The longitudinal web preferably merges radially into the drive-side flange and / or output-side flange with substantially no steps on the outer side. This avoids radial misalignment between the radial shell surface of the flange and the radially outward-pointing web surface. The radial shell surface of the flange and the radially outward-pointing web surface can be set on a common radius relative to the main axis of rotation. As a result, stability and strength are improved, and stress concentration effects are avoided or at least reduced.

[0017] In one embodiment of the claimed coupling, an open recess is formed by the circumferential body of the intermediate member, the drive-side flange, the output-side flange, and the longitudinal web. The open recess opens radially outward relative to the main axis of rotation of the coupling. The recess provides increased torsional stiffness while preventing material buildup in the radially outer regions. As a result, the moment of inertia of the coupling is reduced compared to a solid integral design. The recess also simplifies installation by preventing fasteners or tools from falling into the interior of the coupling. Therefore, the installation of the claimed coupling is also simplified. Alternatively, the recess may also have a radially inward opening configuration. The recess has, for example, a U-shaped or H-shaped cross-section. Due to the longitudinal webs following each other in the circumferential direction, the corresponding recess has a straight radial configuration in at least a partial region. This avoids a partially circular cross-section of the recess, resulting in the longitudinal webs not impairing the positioning of the bottom surface of the recess relative to the main axis of rotation in small radii, even with small circumferential spacing. Particularly high torsional stiffness can be achieved through a large number of longitudinal webs in the case of a low mass moment of inertia in the intermediate member.

[0018] Furthermore, the drive-side flange and / or output-side flange can be connected to a multi-disc assembly in each case. Using at least one multi-disc assembly in the coupling provides compensation capability to compensate for radial, axial, and / or angular misalignment, i.e., tilting, between the drive and output sides of the coupling. Specifically, increased compensation capability is achieved when one multi-disc assembly is used on each of the drive-side and output-side flanges. The compensation capability, i.e., the maximum compensable radial, axial, and / or angular misalignment, is essentially defined by the multi-disc assembly. Considering the torsional stiffness of the intermediate components, the latter is negligible in determining the compensation capability. Therefore, the claimed coupling can be used in applications requiring compensation behavior. Furthermore, the multi-disc coupling is subjected to essentially tangential tensile loads during operation, which also leads to an increased service life. Moreover, the multi-disc assembly can be removed without damage while the coupling is in its installed state, and therefore can be replaced cost-effectively and easily. Thus, the claimed coupling simplifies operation and maintenance in applications with high mechanical loads, such as in wind farms. Furthermore, multiple disks can be constructed as multiple disk segments, which can be assembled to form a circumferential multi-disk assembly. For example, this type of multiple disk segments is described in EP3719335 A1 (application number EP19166941.5). The disclosure of EP3719335 A1 is incorporated herein by reference.

[0019] Furthermore, the drive-side flange and output-side flange may have recesses opposite each other and be configured to receive releasable fastening devices. These releasable fastening devices, for example, allow the multi-disc assembly to be fastened to both the drive-side and output-side flanges in each case. This type of recess can be easily created by drilling with high precision. In particular, the dimensions of the recess allow the fastening device to be inserted therein and can be inserted into the drive-side and output-side flanges by axial movement. This further simplifies the installation and therefore maintenance of the coupling requiring protection. Furthermore, the drive-side flange and / or output-side flange can be constructed in the region of the recess in a manner that minimizes the axial distance between the multi-disc assembly and the drive-side and output-side flanges. For this purpose, for example, the flange can have an increased wall thickness in the region of the recess, resulting in a reduced free bending length of the fastening device by which the multi-disc assembly is fastened to the drive-side and output-side flanges, allowing for further utilization of the load-bearing capacity of the fastening device.

[0020] In another embodiment of the claimed coupling, the drive-side flange and / or output-side flange may have recesses that allow operation of a releasable fastening device directly connected to a connecting flange, which in each case is also included in the claimed coupling. Here, the connecting flange should be understood as a flange that is also connected to the multi-disc assembly. Therefore, when viewed circumferentially, the multi-disc assembly can be connected, for example, alternately to the intermediate member and the connecting flange via the releasable fastening device. Thus, the coupling may have drive-side and / or output-side connecting flanges. The drive-side connecting flange is directly connected to the rotor shaft in the installed state, and the output-side connecting flange is directly connected to the gearbox, i.e., its input shaft. Recesses in the drive-side and output-side flanges allow the releasable fastening device to be guided through, thereby allowing the corresponding connecting flange to be releasably connected to the respective multi-disc assembly. As a result, the installation of the claimed coupling is further simplified, and consequently, the installation of wind farms is accelerated in particular.

[0021] Furthermore, the intermediate component is connected to the multi-disc assembly via at least one releasable fastening device, which may include a bolt with at least a partially tapered configuration. The at least partially tapered shape defines a specific installation direction for the bolt and ensures stable positioning of the releasable fastening device. It also prevents the bolt from slipping through and falling into inaccessible areas. As a result, the installation operation is designed to be fail-safe, thus speeding up the installation process. A recess receives the at least partially tapered bolt, and the recess has a configuration corresponding to the bolt. Alternatively or supplementarily, the fastening device connecting the multi-disc assembly to the corresponding connecting flange may also include a bolt with at least a partially tapered configuration. Therefore, the connecting flange may in each case have a recess with a configuration corresponding to the at least partially tapered bolt.

[0022] Furthermore, the bolts, which are at least partially tapered and whose intermediate components are connected to the multi-disc assembly via them, can be configured to be installed in an axially outward direction. For this purpose, the at least partially tapered bolts can be inserted into recesses and can move in an axially outward direction. The axially outward direction should be understood as movement towards the drive side and towards the output side when viewed from the central region of the intermediate component. Alternatively or additionally, the at least partially tapered bolts (through which the connecting flange can be connected to the corresponding multi-disc assembly) can be configured to be installed in an axially inward direction. In each case, the connecting flange is arranged in the axial edge region of the claimed coupling and can be accessed axially from the outside. As a result, the installation of the claimed coupling is also simplified.

[0023] As already described, the coupling may also have a drive-side connecting flange and / or an output-side connecting flange. In each case, they can be torque-transmittedly connected to the intermediate component by connecting to a multi-disc assembly. The drive-side or output-side connecting flange may have a first wall thickness in the portion opposite to the releasable fastening device, through which the corresponding multi-disc assembly is connected to the intermediate component. Here, the first wall thickness is reduced compared to a second wall thickness in the adjacent portion, which receives the releasable fastening device that connects the corresponding connecting flange to the corresponding multi-disc assembly. As a result, a clear space is also provided in the area of ​​the first wall thickness, which simplifies the installation of fastening components such as nuts for bolts (especially bolts that are at least partially tapered) and ensures mobility there. The portions with the first and second wall thicknesses are arranged alternately in the circumferential direction. As a result, the maintainability of the claimed coupling is further improved.

[0024] In another embodiment of the claimed coupling, it can have a torsional stiffness of 1200 MNm / rad to 2200 MNm / rad, preferably 1500 MNm / rad to 1800 MNm / rad. According to prior art designs, couplings with this type of torsional stiffness are relatively heavy and complex to install, maintain, and disassemble. The claimed coupling is suitable for wind farms due to its torsional stiffness, for example, to connect a gearbox or generator gearbox to the rotor shaft of a wind farm. The claimed coupling is also particularly compact and has an outer diameter of 1300 mm to 2300 mm, preferably 1600 mm to 2000 mm.

[0025] The proposed basic objective is further achieved by a drivetrain according to the invention, configured for use in a wind farm. This drivetrain includes a rotor shaft, a generator, a gearbox, and a coupling through which the rotation of the multi-bladed rotor is transmitted. The rotor shaft is connected to the gearbox in a torque-transmitting manner via the coupling. The gearbox and generator can be configured as separate components or integrated within the generator gearbox. According to the invention, the coupling is constructed according to one of the above embodiments. Using the coupling according to the invention in the drivetrain facilitates the installation and maintenance of the drivetrain to a certain extent.

[0026] The proposed objective is also achieved through a wind power plant according to the invention. The wind power plant includes a nacelle on which a multi-bladed rotor is rotatably arranged, the multi-bladed rotor being connected to a rotor shaft via torque transmission. The rotor shaft is part of a drive system constructed according to one of the embodiments described above.

[0027] Furthermore, the objective described at the beginning is also achieved through an industrial application according to the invention. This industrial application includes a drive unit connected to an output unit via a coupling in a torque-transmitting manner. Driving force is introduced into the coupling and transmitted to the drive unit via the drive unit. The drive unit can be configured as, for example, an electric motor, an internal combustion engine, or a hydraulic motor. Driving force is provided via an output shaft through the drive unit and transmitted to the output unit. The drive unit can be configured as, for example, a mill, vertical mill, sugar mill, cement mill, crusher, conveyor belt, pump, roller press, slat conveyor, tube mill, rotary kiln, rotary gear, mixing unit, lifting device, compactor, or automotive crusher. For this purpose, the output unit has an input shaft connected to the output shaft of the drive unit via a coupling. According to the invention, the coupling is constructed according to one of the above embodiments.

[0028] The outlined objectives are also achieved by a computer program product according to the invention, configured to simulate the operational behavior of a coupling. Operational behavior is understood to refer, for example, to the compensating behavior of a multi-disc assembly, i.e., bending behavior. The computer program product can also be used to simulate the kinematic system and / or vibration characteristics of the coupling. As a result, the operational behavior of the coupling can be simulated in the installation state of a wind farm drive system. Therefore, the physical behavior of the coupling is modeled in the computer program product according to the invention, and the coupling can be provided with a data interface. Through this interface, a further simulation-guided computer program product can forward input values ​​to the computer program product according to the invention. This computer program product can also be provided with a data interface for forwarding output values ​​of the computer program product according to the invention to a further simulation-guided computer program product. This computer program product can be configured as a so-called digital twin. For example, this type of digital twin is disclosed in publication US2017 / 286572A1. The disclosure of US2017 / 286572A1 is incorporated herein by reference. According to the present invention, the coupling simulated by the claimed computer program product is constructed according to one of the embodiments outlined above. Attached Figure Description

[0029] The invention will be explained in more detail below based on various embodiments illustrated in the accompanying drawings. These drawings should be interpreted as complementary to each other, provided that the same reference numerals in different drawings have the same technical meaning. Features of the various embodiments can also be combined with each other. Furthermore, the embodiments shown in the figures can be combined with the features outlined above. The accompanying drawings are described in detail below:

[0030] Figure 1 An embodiment of the coupling for which protection is claimed is schematically shown in a perspective view.

[0031] Figure 2An embodiment of the coupling to be protected is shown in a first longitudinal section oblique view.

[0032] Figure 3 A first embodiment of the coupling to be protected is shown in a second longitudinal section oblique view.

[0033] Figure 4 The schematic diagram illustrates the construction of one embodiment of the claimed wind farm, and

[0034] Figure 5 The construction of one embodiment of the claimed industrial application is illustrated schematically. Detailed Implementation

[0035] Figure 1 An embodiment of the claimed coupling 30 is shown in oblique view. The coupling 30 includes two multi-disc assemblies 20, which are releasably fastened to an intermediate member 10 on both sides (i.e., on the drive side 31 and the output side 33). Connecting flanges 40 are arranged on the multi-disc assemblies 20 on both the drive side 31 and the output side 33 in each case. Driving force 25 is supplied about the main axis of rotation 15 of the coupling 30 via the drive-side connecting flange 42. Furthermore, driving force 25 is also discharged from the coupling 30 via the output-side connecting flange 44. The drive-side and output-side connecting flanges 42, 44 are also releasably connected to the multi-disc assemblies 20 in each case. The intermediate member 20 includes a circumferential body 19 of substantially tubular construction. The body 19 is integrally constructed with the drive-side flange 12 and the output-side flange 14, which are also circumferentially constructed in each case. In each case, the drive-side and output-side flanges 12, 14 of the intermediate component 10 have recesses 17 configured to receive releasable fastening devices 24. The drive-side and output-side flanges 12, 14 are releasably connected to the respective multi-disc assembly 20 via the fastening devices 24 in the recesses 17 of the drive-side and output-side flanges 12, 14.

[0036] The longitudinal webs 16, which are essentially ribbed in structure, are also integrally molded onto the circumferential body 19 of the intermediate member 10. The longitudinal webs 16 extend substantially parallel to the main axis of rotation 15 and, in each case, establish a load-transfer connection between the drive-side flange 12 and the output-side flange 14. Consequently, in each case, multiple recesses 18 are constructed between the two longitudinal webs 16, the drive-side flange 12, the output-side flange 14, and the circumferential body 19. Thus, the recesses 18 are arranged circumferentially on the intermediate member 10. The longitudinal webs 16 act as reinforcements against torsional loads on the intermediate member 10. Due to the recesses 18, the intermediate member 10 is relatively lightweight while simultaneously possessing the rigidity to resist torsional loads between the drive-side and output-side flanges 12, 14. Fastening devices 24, to be installed for releasable fastening to one of the multi-disc assemblies 20, can be inserted radially 37 into the recesses 18 and can be installed substantially by axial movement, i.e., along the main axis of rotation 15. This avoids falling into the hard-to-access interior of the intermediate member 10. This simplifies and speeds up the installation of the coupling 30. Furthermore, the drive-side flange 12 and the output-side flange 14 have a first wall thickness 41 in the areas without the fastening device 24, and a second wall thickness 43 in the areas with the releasable fastening device 24. Here, the first wall thickness 41 is smaller than the second wall thickness 43. Therefore, the second wall thickness 43 provides a rigid receiving device for the fastening device 24, which establishes a releasable connection between the intermediate member 10 and one of the multi-disc assemblies 20. The higher the second wall thickness 43, the greater the load-bearing capacity of the drive-side flange 12 and the output-side flange 14 in this area, to receive the load resulting from the fact that the driving force 25 acting on the intermediate member 10 is converted into tensile loads in the respective multi-disc assemblies 20. Due to the first wall thickness 41, the areas of the drive-side flange 12 and the output-side flange 14 without the releasable fastening device 24 are designed for weight reduction. Due to the alternating arrangement of the first and second wall thickness regions 41, 43 on the drive side and output side flanges 12, 14 of the intermediate member 10, the intermediate member 10 is constructed in a manner suitable for the load, which allows for higher material utilization.

[0037] Corresponding to the drive-side flange 12 and output-side flange 14 of the intermediate component 10, the drive-side connecting flange 42 and output-side connecting flange 44 are also constructed with alternating regions having a first wall thickness 41 and a second wall thickness 43. In each case, the drive-side and output-side connecting flanges 42 and 44 are each constructed with a recess 17 for receiving a releasable fastening device 24. The drive-side and output-side connecting flanges 42 and 44 are connected to one of the multi-disc assemblies 20 via the fastening devices 24 received in the drive-side and output-side connecting flanges 42 and 44. The releasable fastening devices 24 received in the connecting flanges 42 and 44 and the flanges 12 and 14 of the intermediate component 10 are arranged in a circumferentially alternating manner, resulting in a load distribution suitable for the loads of the multi-disc assembly 20. The circumferential direction is... Figure 1 As indicated by arrow 35. The regions of connecting flanges 42, 44 with a first wall thickness 41 are positioned opposite to the regions of flanges 12, 14 of intermediate member 10 with a second wall thickness 43. Correspondingly, the regions of connecting flanges 42, 44 with a second wall thickness 43 are positioned opposite to the regions of flanges 12, 14 of intermediate member 10 with a first wall thickness 41. In a similar manner relative to intermediate member 10, the releasable fastening device 24 is thus received stably in the regions of connecting flanges 42, 44 in the regions with a second wall thickness 43, and the regions therebetween are constructed in a weight-reducing manner by means of the first wall thickness 41. Furthermore, the first wall thickness 41 provides a clear space 21 on intermediate member 10 and, correspondingly, on drive-side and output-side flanges 42, 44, which is suitable for receiving installation tools (not shown). In addition to reducing weight, the first wall thickness 41 on the flanges 12, 14 of the intermediate part 10 and the drive-side and output-side connecting flanges 42, 44 provides a clear space 21, which further simplifies the installation of the coupling 30.

[0038] according to Figure 1 The embodiments in Figure 2 The longitudinal section is shown in the detailed view. Figure 2 In the diagram, coupling 30 is connected to rotor shaft 74, which serves as drive shaft 45. Drive force 35 can be supplied to coupling 30 on drive side 31 via drive shaft. On output side 33, coupling 30 is connected to hub 54, which belongs to transmission 50, particularly planetary transmission, and serves as input shaft 52 in transmission 50. Coupling 30 is constructed via multi-disc assembly 20 to compensate for angular offset 47 between drive side connecting flange 42 and output side connecting flange 44. Here, angular offset 47 should be understood as substantially along... Figure 2 The tilting motion of the curved double arrow 47 shown. Due to the multi-disc assembly 20, the coupling 30 is also suitable for compensating for axial misalignment 48 and / or radial misalignment 49. According to... Figure 2As can be seen in the longitudinal section, the releasable fastening device 24 that establishes a connection between the drive-side flange 12 and the output-side flange 14 of the intermediate member 10 and the corresponding multi-disc assembly 20 includes, in each case, a bolt 23 that is at least partially tapered. The at least partially tapered nature of the bolt 23 allows it to be installed only in the axially outward direction 34. The recess 17 that receives the bolt 23 is also at least partially tapered in a manner corresponding to the corresponding bolt 23. The axially outward direction 34 and the corresponding axially inward direction 36 substantially involve the central region of the longitudinal web 16 or recess 18 on the intermediate member 10. During the installation of the fastening device 24, particularly the bolt 24, the recess 18 prevents them from falling into the interior of the coupling 30. Furthermore, the recess 18 is configured to receive a tool (not shown in more detail) by which screws 26 can be tightened or loosened. The bolt 23 is hollow and configured to receive at least one screw 26 that can be connected to the mating member 27. The corresponding multi-disc assembly 20 can be clamped to the intermediate part 10, that is, its drive-side and output-side flanges 12, 14, by tightening the corresponding screws 26. Precise and load-bearing placement of the fastening device 24 is achieved by at least a partial taper of the corresponding bolts 23. Due to the fact that the first wall thickness 41 and the second wall thickness 43 are constructed alternately along the circumferential direction 35 on the connecting flanges 40, 42, 44, a net space 21 is constructed in each case through the area with the first wall thickness 41, as well as... Figure 1 As shown. Because a clear space 21 is provided in this way, the mating parts 27, which are considered part of the corresponding fastening device 24, can be installed in a simple manner. Furthermore, the coupling 30 is modeled in a computer program product 90, which is configured to simulate the operating behavior of the coupling 30. The operating behavior of the coupling 30 includes, in particular, the time distribution of the transmitted driving force 25 and / or the occurring angular offset 47, axial offset 48, and / or radial offset 49.

[0039] Figure 3 Shown in detail view in longitudinal section Figure 1 and Figure 2 The embodiment of the claimed coupling 30, here, Figure 3 and Figure 2 The difference lies in the location of the cutting plane that produces the longitudinal section. Figure 3The drive-side connecting flange 42 and the output-side connecting flange 44 are shown, in each case also via a recess 17, which is configured to receive a bolt 23 that is at least partially tapered. For this purpose, the recess has a corresponding configuration relative to the at least partially tapered bolt 23. The bolt 23 and the recess 17 in the drive-side and output-side connecting flanges 42, 44 are configured such that the fastening device 24 (particularly the corresponding bolt 23) can be installed axially inward in the inward direction 36. In the region where the fastening device 24 establishes a releasable connection between the drive-side and output-side connecting flanges 42, 44 and the corresponding multi-disc assembly 20, the corresponding drive-side flange 12 and output-side flange 14 of the intermediate member 10 have a first wall thickness 41 that is less than the second wall thickness 43. Therefore, a clear space 21 is constructed between the region with a first wall thickness 41 on the drive-side and output-side connecting flanges 42, 44 and the corresponding multi-disc assembly 20. This clear space 21 allows the mating piece 27 to be easily mounted onto the screw 26, which is screwed into the bolt 23 in an axially outward direction 34. A recess 17 serving as a through opening 28 is constructed on the intermediate piece 10 on the drive-side and output-side flanges 12, 14. The recess 17 is constructed in the region with a first wall thickness 41 on the drive-side and output-side flanges 12, 14. For mounting purposes, the screw 26 can be received in the recess 18 on the intermediate piece 10 in each case and can be guided through the recess 17 serving as the through opening 28 and can be received in the corresponding bolt 23. As a result, in each case, a mating piece 27 can be clamped against the corresponding bolt 23, so that the corresponding multi-disc assembly 20 can be fastened to the drive-side and output-side connecting flanges 42, 44 via the mating piece 27. As a result, simple and quick installation of coupling 30 is also ensured.

[0040] Figure 4 The structure of one embodiment of the claimed wind farm 70 is schematically illustrated. The wind farm 70 includes a nacelle 71 on which a multi-bladed rotor 72 is rotatably arranged. The multi-bladed rotor 72 is torque-transmittedly connected to a rotor shaft 74, which serves as an input shaft 45 for a coupling 30. The coupling 30 is, in turn, torque-transmittedly connected to a gearbox 50, which is configured as a planetary gearbox 76. The gearbox 50 is torque-transmittedly connected to a generator 75, and the gearbox 50 and generator 75 are integrally constructed and together form a generator gearbox 77. The generator gearbox 77, coupling 30, and rotor shaft 74 together form one embodiment of the claimed transmission system 60. The coupling 30 is constructed in the claimed wind farm 70 according to one of the above embodiments. The operational behavior of the coupling 30 can be simulated by an embodiment of the claimed computer program product 90, in which the coupling 30 is modeled.

[0041] Figure 5 The structure of one embodiment of the claimed industrial application 80 is schematically illustrated. The industrial application 80 includes a drive unit 82, through which a driving force 25 is provided via a drive shaft 45. The drive unit 82 is connected to an output unit 84 via a coupling 30 in a torque-transmitting manner, through which the mechanical application is realized. According to the invention, the coupling 30 is constructed according to one of the above embodiments. The operational behavior of the coupling 30 can also be simulated in the industrial application 80 by a computer program product 90, in which the coupling 30 is modeled.

Claims

1. A coupling (30) for attaching a transmission (50) to a drive shaft (45), comprising a circumferential intermediate member (10) having a drive-side flange (12) and an output-side flange (14), the output-side flange (14) being axially fixedly connected to the drive-side flange (12) in terms of movement. Its features are: The drive-side flange (12) is connected to the output-side flange (14) via a longitudinal web (16). The longitudinal web (16) is constructed as a single unit with the drive-side flange (12) and the output-side flange (14). The corresponding longitudinal web (16) is constructed as one or two pieces. The drive-side flange (12) and the output-side flange (14) have opposing recesses (17) for receiving releasable fastening devices (24), and at least one of the fastening devices (24) includes a bolt (23), which is at least partially tapered. The intermediate component (10) includes a circumferential body (19) of tubular construction, wherein the circumferential body (19), the drive-side flange (12), the output-side flange (14), and the longitudinal web (16) form a recess (18) opening in the radially outward direction (37), the recess (18) extending continuously from the drive-side flange (12) to the output-side flange (14) and communicating with the recess (17), and further extending continuously from one longitudinal web to an adjacent longitudinal web.

2. The coupling (30) as described in claim 1, characterized in that, The longitudinal web (16) or the drive-side portion of the longitudinal web (16) is incorporated into the drive-side flange (12) on the drive-side flange side pointing towards the output-side flange (14) via a rounded transition portion extending in the circumferential direction, and / or the longitudinal web (16) or the output-side portion of the longitudinal web (16) is incorporated into the output-side flange (14) on the output-side flange side pointing towards the drive-side flange (12) via a rounded transition portion extending in the circumferential direction.

3. The coupling (30) as described in claim 1 or 2, characterized in that, The longitudinal web (16) merges radially outward into the drive-side flange (12) and / or the output-side flange (14) with essentially no steps.

4. The coupling (30) as described in any one of claims 1 to 2, characterized in that, The drive-side flange (12) and / or the output-side flange (14) are connected to the multi-disc assembly (20) in each case.

5. The coupling (30) as described in any one of claims 1 to 2, characterized in that, The bolt (23), which is at least partially tapered, can be installed in an axially outward direction (34).

6. The coupling (30) as described in any one of claims 1 to 2, characterized in that, The coupling (30) has a drive-side and / or output-side connecting flange, which is connected to the intermediate component (10) in a torque transmission manner.

7. The coupling (30) as described in claim 6, characterized in that, The drive-side and / or output-side connecting flange has portions that alternate circumferentially with a first wall thickness (41) and a second wall thickness (43), wherein the first wall thickness (41) is smaller than the second wall thickness (43).

8. The coupling (30) as described in any one of claims 1 to 2, characterized in that, The coupling (30) has a torsional stiffness ranging from 1200 MNm / rad to 2200 MNm / rad.

9. The coupling (30) as described in claim 8, characterized in that, The coupling (30) has a torsional stiffness ranging from 1500 MNm / rad to 1800 MNm / rad.

10. A drive system (60) for a wind power plant (70), comprising a rotor shaft (74), a generator (75), a gearbox (50), and a coupling (30), wherein the rotor shaft (74) is connected to the gearbox (50) via the coupling in a torque transmission manner, characterized in that, The coupling (30) is configured as described in any one of claims 1 to 9.

11. A wind power plant (70) comprising a multi-bladed rotor (72) rotatably arranged on a nacelle (71) and connected to a rotor shaft (74) belonging to a drive system (60) in a torque-transmitting manner, characterized in that, The transmission system (60) is configured as described in claim 10.

12. An industrial application (80) comprising a drive unit (82) and an output unit (84), the drive unit (82) and the output unit (84) being connected to each other via a coupling (30) in a torque transmission manner, characterized in that, The coupling (30) is configured as described in any one of claims 1 to 9.

13. A computer program product (90) for simulating the operational behavior of a coupling (30) arranged in a drive system (60) of a wind farm (70) or in an industrial application (80), characterized in that, The coupling (30) is configured as described in any one of claims 1 to 9.

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