ARRANGEMENT WITH A GEARBOX AND A WORK MACHINE, METHOD FOR SIMULATION

Description

[0001] The invention relates to an arrangement comprising a drive-side transmission with an output shaft of the transmission extending along an axis, and comprising a working machine with a drive shaft connected to the output shaft in a torsionally rigid manner.

[0002] In addition, the invention also includes a computer-implemented method for simulating an arrangement and a corresponding computer program product for carrying out this method by means of at least one computer.

[0003] Such arrangements are often space-consuming and tend to quickly become overloaded due to higher loads while simultaneously requiring compactness.

[0004] One possible application for a generic arrangement is shown in EP 2 989 351 A1.

[0005] From US 2018 / 0251353 A1, a drive shaft of a motor designed as a hollow shaft is known, which is non-rotatably coupled radially on the inside via an internal toothing to a short toothing provided radially on the outside of an output shaft of a gearbox supported by a torque arm.

[0006] CN 203 594 733 U discloses a gearbox for an extruder in which drive power is transmitted via spur gear stages to a planetary gearbox supported by a torque arm. The planetary gearbox's two-part output shaft protrudes on different sides of the gearbox to drive the respective extruder screws. The two-part output shaft, connected to a planet carrier of the planetary gearbox, has two hollow shafts connected in a rotationally fixed manner via short gearing, to which the corresponding extruder screw can be attached via gearing or a flange connection.

[0007] EP 3 702 647 A1 discloses a gearbox for a wind turbine in which drive power is transferred to a generator via a spur gear stage from a planetary gear supported by a torque arm. The spur gear stage is rotationally fixedly coupled to a sun shaft configured as a hollow shaft via short gearing. The spur gear stage has an output shaft configured as a solid shaft that protrudes from the gearbox housing.

[0008] From US 2007 / 2950509 A1 a gearbox for a wind turbine is known in which a drive power is introduced via a planetary carrier of a planetary gear supported by a torque arm and is output to a generator via a sun shaft, wherein the sun shaft is designed as a solid shaft.

[0009] Based on the problems described above, the object of the invention is to create a reliable arrangement of the type defined at the outset which can withstand the high loads incurred while requiring moderate space.

[0010] To achieve the object, the invention proposes an arrangement of the type defined at the outset, in which the transmission on the working machine is supported by means of the connection of the output shaft to the drive shaft and by means of a torque support to at least 90% of the forces generated during operation, wherein the connection of the output shaft to the drive shaft is designed to be rigid in order to support transverse forces, wherein the axial end of the drive shaft is designed as a hollow shaft, wherein the axial end of the output shaft has a stub which is at least partially arranged in the hollow shaft of the drive shaft.

[0011] The drive shaft has a recess in the region of the hollow shaft design, with a retaining element being fastened by means of fastening means to the stub-shaped axial end of the output shaft in such a way that the recess is clamped in the region between the retaining element and an axial contact surface of the rest of the output shaft. The retaining element is preferably made of metal. In this way, the flange can be attached to the output shaft by means of the retaining element, and the flange can then be fastened to the drive shaft. In a particularly expedient manner for ease of assembly as well as for strength and smooth running, the retaining element in the arrangement of the invention, which can particularly advantageously be annular, i.e. designed as a retaining ring, can be designed as a one-piece piece.Particularly preferably, the arrangement according to the invention enables free axial accessibility to the mounting position of the holding element, in particular without an axially extending continuation of a shaft requiring a divisible - at least 2-part - design of the holding element.

[0012] The arrangement according to the invention preferably comprises a planetary gear as a gear and is preferably a component of a roller press or a mill, e.g. a sugar mill, preferably with an individual drive or various other applications in the industrial sector.

[0013] The arrangement according to the invention can be described as "shaft-riding" with regard to the transmission. This means that the output shaft of the transmission or planetary transmission is attached to the drive shaft of the driven machine in such a way that the output shaft and the transmission are supported there against transverse forces. The torque at the transmission or transmission housing is dissipated by means of a torque arm, e.g., indirectly or directly introduced into a foundation. The torque can also be dissipated via adjacent machine elements, e.g., via the driven machine to which the torque arm is attached. The torque arm is attached to the transmission in such a way that the transmission is prevented from axial rotation (relative to the output shaft). Other degrees of freedom of movement are preferably not restricted by the torque arm.

[0014] The drive shaft of the driven machine is in particular rigidly coupled to the output shaft of the transmission, so that radial offset and / or tiltability between the drive shaft of the driven machine and the output shaft of the transmission is preferably eliminated. In particular, the axes of rotation of the drive shaft of the driven machine and the output shaft of the transmission are aligned coaxially with one another, so that the axes of rotation of the drive shaft of the driven machine and the output shaft of the transmission can coincide. Preferably, in the assembled state, an axial relative movement of the drive shaft of the driven machine relative to the output shaft of the transmission is also blocked. The drive shaft of the driven machine and the output shaft of the transmission can be centered relative to one another. Torques occurring in the arrangement can thus be supported almost completely, in particular by at least 90%, via the torque arm.A torque to be supported introduced into the gearbox via the drive shaft by the driven machine is therefore not supported at the connection point between the drive shaft of the driven machine and the output shaft of the gearbox, but is diverted via the output shaft of the gearbox and only supported via the torque arm at a distance from the drive shaft of the driven machine. The torque to be supported introduced by the driven machine can thus be passed on via the individual gearings of the gearbox until it can be supported via the torque arm. The gearbox is designed in particular as at least a single-stage, preferably multi-stage, planetary gear, of which a toothed gear component, for example a fixed ring gear, is fixedly connected to a gearbox housing, to which the torque arm can in turn be connected.The torque introduced by the working machine to be supported is thus guided and supported via the individual gear teeth of the gearbox to the gearbox housing and the torque support, so that a low installation space requirement is achieved with good stability.

[0015] The drive shaft of the driven machine is in particular designed as a hollow shaft essentially only in an axial region in which the drive shaft engages radially outwardly around the output shaft of the gearbox, and is otherwise designed as a solid shaft. The region of the drive shaft forming the hollow shaft is designed, for example, as a cylindrical recess which is introduced on an axial end face, for example by turning, coaxial with the axis of rotation of the drive shaft. The output shaft of the gearbox is preferably designed as a solid shaft. A cylindrical opening running coaxially to the axis of rotation in the axial direction can be avoided in the output shaft, so that the output shaft can transmit the loads occurring without significant deflection even with a smaller nominal diameter than the drive shaft of the driven machine.

[0016] The output shaft represents, in particular, the last shaft attributable to the transmission in the torque direction, which in particular protrudes from a transmission housing of the transmission or is connected to the input shaft protruding into the transmission housing of the transmission. The output shaft can represent a power output of the transmission. The input shaft represents, in particular, the first shaft attributable to the driven machine in the torque direction, which in particular protrudes from a housing of the driven machine or is connected to the output shaft protruding into the housing of the driven machine. The output shaft can represent a power input of the driven machine.

[0017] The rigid connection between the drive shaft of the driven machine and the output shaft of the gearbox prevents deflection transverse to the axis of rotation. Instead, the resulting transverse forces can be transferred via the gearbox to the torque arm and supported at a location offset from the connection point between the drive shaft of the driven machine and the output shaft of the gearbox. This eliminates the need for additional support in the area of ​​the connection point between the drive shaft of the driven machine and the output shaft of the gearbox.

[0018] In particular, the drive shaft is supported on the output shaft via a radial support to absorb transverse forces. The radial support is formed, for example, by a step or shoulder against which the drive shaft can preferably rest flat against the output shaft. The radial support is, in particular, part of a centering of the drive shaft on the output shaft. For the rigid connection, the radial support acting transversely to the axis of rotation of the drive shaft of the driven machine and / or the output shaft of the gearbox, i.e., in particular, essentially in the radial direction, can therefore be provided between the drive shaft of the driven machine and / or the output shaft of the gearbox, via which transverse forces occurring in the radial direction can be supported and diverted via the gearbox to the rotary support.

[0019] The drive shaft is preferably supported on the output shaft via an axial support for dissipating longitudinal forces. The axial support is formed, for example, by a step or a shoulder against which the drive shaft can preferably rest flatly on the output shaft. The axial support is in particular part of a centering of the drive shaft on the output shaft. For the rigid connection, the axial support acting longitudinally to the axis of rotation of the drive shaft of the driven machine and / or the output shaft of the gearbox, i.e. in particular substantially in the axial direction, can therefore be provided between the drive shaft of the driven machine and / or the output shaft of the gearbox, via which longitudinal forces occurring in the axial direction can be supported and diverted via the gearbox to the rotary support.

[0020] Preferably, the arrangement is designed such that the transmission on the working machine is completely supported against the forces arising during operation by means of the connection of the output shaft to the drive shaft and by means of the torque support.

[0021] A characteristic of this arrangement is that the element connecting the driven machine shaft and the transmission shaft must transmit not only the drive torque but also the weight loads of the transmission and other components (engine, clutch, etc.). This creates high alternating bending loads at the connection.

[0022] According to the invention, it is possible to provide the short gearing, which is critical for dimensioning, on the maximum possible diameter of the output shaft or stub. It is particularly expedient if the outer diameter of the output shaft short gearing is between 85 and 100% of the outer diameter of the area of ​​the output shaft adjacent to the stub. For the purposes of the invention, the term "stub" refers only to an end-side shaft section, which in particular does not have to have a different diameter than the rest of the shaft or be otherwise necessarily designed differently. This is because this connection transmits not only the drive torque but also transverse forces.

[0023] An advantageous development of the invention provides that the drive shaft has a modular design, such that the axial end of the drive shaft, as a first axial section, is designed as a flange that is axially attached to a second axial section of the drive shaft, wherein the flange forms the end-side axial shaft section, which is designed as a hollow shaft. In particular, this modular design enables the use of the arrangement according to the invention with adjacent standard components. As standard, a flange can be used to connect the transmission shaft and the driven machine shaft. The flange is preferably screwed to the drive shaft or driven machine shaft.

[0024] The flange can be designed as a cast component, particularly made of metal, in a particularly cost-effective and practical manner. With a conventional arrangement of the type defined above, the correspondingly high loads make it only possible to manufacture the flange from a higher-strength material. The invention also opens up the possibility of a cast component. A forged part is significantly more expensive than a comparable cast version.

[0025] In order for the arrangement according to the invention to be radially aligned as well as possible, at least one first radial drive shaft centering device can be provided at an axial end of the drive shaft, wherein at least one radial output shaft centering device is provided at an axial end of the output shaft to which the drive shaft is connected, wherein the two centering devices are in radially centering contact with each other.

[0026] A particularly advantageous possibility for producing this flexural rigidity consists in that a second radial drive shaft centering device is provided at the axial end of the drive shaft, which is axially spaced from the first radial drive shaft centering device, wherein a second radial output shaft centering device is provided at the axial end of the output shaft, which is axially spaced from the first radial output shaft centering device, wherein the output shaft centering devices and drive shaft centering devices are assigned to one another in pairs to form two axially spaced centering pairs and are each in radially centering contact with one another.

[0027] On the gearbox side, the flange is preferably inserted into the output shaft during assembly, which is particularly preferably designed as a hollow shaft with internal short gearing and two centering seats. Bending loads are thus transmitted via the centering seats, and torques via the short gearing. Axial displacement of the components relative to one another is prevented by the retaining element, preferably designed as a retaining ring. This can be designed to be undivided in the circumferential direction.

[0028] The dimensioning criterion for the flange is the maximum possible inner diameter of the gearbox output shaft. This is linked to the outer diameter of the shaft via a minimum thickness ratio. As the torque density increases, the outer diameter of the gearbox output shaft becomes smaller, which also reduces the possible inner diameter. This also leads to a smaller journal on the flange, which makes the occurring alternating bending loads the dimensioning criterion. This is where the inventive solution reveals its strengths.

[0029] The preferred application of the invention is in the field of gears such as those used in mills, e.g., sugar mills. These gears are preferably designed as planetary gears.

[0030] Advantages and embodiments of the invention, which can be used individually or in combination with one another, are the subject of the dependent claims.

[0031] An unclaimed embodiment also relates to a computer-implemented method for simulating an arrangement according to at least one combination of features defined by the claims, in which, in particular, the individual components of the arrangement are virtually mapped in a simulation environment as computer-simulated parts, and their physical interactions are fully or partially analyzed in the simulation environment. Accordingly, the embodiment comprises, on the one hand, the physical structure with the features according to the invention and, on the other hand, also a digital twin, as used, for example, for the purpose of simulating the arrangement or the operation of the arrangement using at least one computer. In addition, the embodiment also relates to an unclaimed corresponding computer program product.The computer program product comprises instructions which, when the computer program product is executed by a computer, cause the computer to virtually represent the individual components of the arrangement according to the invention in a simulation environment as computer-simulated parts and to fully or partially analyze their physical interactions in the simulation environment in order to carry out the computer-implemented method.

[0032] One aspect further relates to an unclaimed data agglomerate with data packets combined in a common file or distributed across different files for mapping the three-dimensional shape and / or the interactions of all components provided in the arrangement, which can be designed and further developed as described above, wherein the data packets are adapted, when processed by a data processing device, to carry out an additive production of the components of the arrangement, which can be designed and further developed as described above, in particular by 3D printing, and / or a simulation of the functioning of the arrangement, which can be designed and further developed as described above.The data agglomerate can represent a virtual embodiment of the arrangement according to the invention in the form of a so-called "digital twin," which enables a virtual investigation in the form of a simulation or a real objectification using an additive manufacturing process. In particular, each data packet can represent a separately implemented component of the arrangement according to the invention, so that the individual components can be easily assembled, both physically and / or virtually, in terms of their relative position and / or relative mobility in order to realize the interactions essential to the invention. This enables cost-effective production of prototypes and / or computer-based simulations to study the functionality of the arrangement according to the invention, identify problems in the specific application, and find improvements.Preferably, individual and / or all data packets of the data agglomerate can be loaded into the simulation environment of the computer-implemented method and / or the computer program product, for example as part of a database or library, and uploaded for virtual representation as computer-simulated parts and / or their physical interactions.

[0033] Further features, characteristics, and advantages of the present invention will become apparent from the following description with reference to the figures, which schematically show: Figure 1 shows a simplified, two-dimensional longitudinal sectional view of an arrangement according to the invention, Figure 2 shows a schematic representation of a simulation of an arrangement according to the invention running on a computer, computer program product.

[0034] In the exemplary embodiments and figures, identical or similarly functioning elements may be provided with the same reference numerals. The illustrated elements and their relative sizes are generally not to be considered to scale; rather, individual elements may be shown larger in proportion for clarity and / or clarity.

[0035] Figure 1shows a simplified, two-dimensional longitudinal sectional view of an arrangement ARG according to the invention with an output shaft SHB of a gearbox GER, which extends along an axis X. The gearbox GER is designed as a planetary gear EPG. The output shaft SHB is connected to an input shaft SHN in a torsionally and flexurally rigid manner. The input shaft SHN is in a torque-transmitting connection with a driven machine, in particular a mill MLL. The gearbox GER is supported on the driven machine WMS by means of the connection of the output shaft SHB to the input shaft SHN and by means of a torque arm TSP for at least 90% - preferably completely - of the forces generated during operation. Forces BTQ (in particular bending loads, transverse forces) from the drive of the gearbox GER (not shown) are introduced into the input shaft SHN and the torque arm TSP (here in particular forces from a differential torque due to the gearbox GER).The torque on the gearbox GER or gearbox housing is diverted by means of the torque support TSP, e.g. indirectly or directly introduced into a foundation FDG.

[0036] The output shaft SHB is connected to one axial end of the input shaft SHN. A torque TRQ at a speed RVL is transmitted from the output shaft SHB to an input shaft short spline STN of the input shaft SHN by means of an output shaft short spline STB.

[0037] The axial end of the drive shaft SHN, which is connected to the output shaft SHB, is designed as a hollow shaft HLW. The axial end of the output shaft SHB has a stub STP, which is at least partially arranged in the hollow shaft HLW of the drive shaft SHN.

[0038] The drive shaft SHN has a modular design such that the axial end of the drive shaft SHN is formed as a first axial section AX1 as a flange FLG, which is axially attached to a second axial section AX2 of the drive shaft SHN. The flange FLG forms the end-side axial shaft section, which is designed as a hollow shaft HLW. The flange FLG is attached to the second axial section AX2 by means of screws SCR and is designed as a cast component, in particular made of metal.

[0039] The drive shaft SHN has, in the area of ​​the hollow shaft HLW design, a radially inwardly projecting formation PTR, wherein a holding element AFE is fastened to the axial end of the output shaft SHB designed as a stub STP by means of axially acting fastening means FXE screws SCR, such that the formation PTR is clamped in the area between the holding element AFE and an axial contact surface of the other output shaft SHB.

[0040] The AFE holding element is ring-shaped and formed as a single piece in the circumferential direction.

[0041] At the axial end of the drive shaft SHN, a first radial drive shaft centering RN1 is provided and at the axial end of the output shaft SHB, to which the drive shaft SHN is connected, a radial output shaft centering RB1 is provided, wherein the two centerings are in radially centering contact with each other.

[0042] The connection of the output shaft SHB to the drive shaft SHN is designed to be rigid, in that a second radial drive shaft centering RN2 is provided at the axial end of the drive shaft SHN, which is axially spaced from the first radial drive shaft centering RN1, wherein a second radial output shaft centering RB2 is provided at the axial end of the output shaft SHB, which is axially spaced from the first radial output shaft centering RB1, wherein the output shaft centerings RB1, RB2 and drive shaft centerings RN1, RN2 are assigned to one another in pairs to form two axially spaced centering pairs and are each in radial centering contact with one another.

[0043] Figure 2shows a schematic representation of a simulation SIM of an arrangement ARG according to the invention running on a computer CMP—here on several CMP computers of a network WWB comprising a cloud CLD. The software installed on the CMP computers is a computer program product CPP that, when executed on at least one CMP computer, allows the user to influence or configure the system and gain insights based on the executed simulation SIM via screen and keyboard interfaces, so that, in particular, technical design decisions can be supported and verified using the simulation.

[0044] Although the invention has been illustrated and described in detail by the preferred embodiment, the invention is not limited to the disclosed examples. Variations may be derived by those skilled in the art without departing from the scope of the invention as defined by the following claims.

Claims

1. Arrangement (ARG) comprising a drive-side transmission (GER) with an output shaft (SHB) of the transmission (GER), which extends along an axis (X), and comprising a work machine (WMS) with a drive shaft (SHN) connected in a rotationally fixed manner to the output shaft (SHB), wherein the transmission (GER) on the work machine (WMS), by means of the connection between the output shaft (SHB) and the drive shaft (SHN) and by means of a torque arm (TSP), is supported to the extent of at least 90% of the forces arising during operation, wherein the connection between the output shaft (SHB) and the drive shaft (SHN) is configured to be flexurally stiff to support transverse forces, wherein the axial end of the drive shaft (SHN) is embodied as a hollow shaft (HLW), wherein the axial end of the output shaft (SHB) has a stub (STP) which is at least partially disposed in the hollow shaft (HLW) of the drive shaft (SHN), characterized in that the drive shaft (SHN) in the region of the configuration as a hollow shaft (HLW) has a moulding (PTR), wherein a holding element (AFE) by means of fastening means (FXE) is fastened to the axial end of the output shaft (SHB) configured as a stub (STP) in such a manner that the moulding (PTR) is jammed in the region between the holding element (AFE) and an axial contact surface of the remaining part of the output shaft (SHB).

2. Arrangement (ARG) according to Claim 1, wherein the drive shaft (SHN) is supported on the output shaft (SHB) via a radial support for dissipating transverse forces.

3. Arrangement (ARG) according to Claim 1 or 2, wherein the drive shaft (SHN) is supported on the output shaft (SHB) via an axial support for dissipating longitudinal forces.

4. Arrangement (ARG) according to one of the preceding claims, wherein the drive shaft (SHN) is constructed in a modular manner such that the axial end of the drive shaft (SHN) as a first axial portion (AX1) is configured as a flange (FLG) which is attached axially to a second axial section (AX2) of the drive shaft (SHN), wherein the flange (FLG) forms the end-side axial shaft section which is configured as a hollow shaft (HLW).

5. Arrangement (ARG) according to Claim 4, wherein the holding element (AFE) is of a round or ring-shaped configuration.

6. Arrangement (ARG) according to Claim 4 or 5, wherein the flange (FLG) is configured as a casting.

7. Arrangement (ARG) according to one of the preceding claims, wherein an output shaft short spline (STB) is provided on an axial end of the output shaft (SHB) to which the drive shaft (SHN) is connected, wherein a drive shaft short spline (STN) is provided on an axial end of the drive shaft (SHN) to which the output shaft (SHB) is connected.

8. Arrangement (ARG) according to one of the preceding claims, wherein the transmission (GER) on the work machine (WMS) by means of the connection between the output shaft (SHB) and the drive shaft (SHN) and by means of the torque arm (TSP) is supported completely against the forces arising during operation.

9. Arrangement (ARG) according to at least one of the preceding claims, wherein at least one first radial drive shaft centring feature (RN1) is provided on an axial end of the drive shaft (SHN), wherein at least one radial output shaft centring feature (RB1) is provided on an axial end of the output shaft (SHB) to which the drive shaft (SHN) is connected, wherein the two centring features are in mutual contact in a radially centring manner.

10. Arrangement (ARG) according to Claim 9, wherein a second radial drive shaft centring feature (RN2) which is axially spaced apart from the first radial drive shaft centring feature (RN1) is provided on the axial end of the drive shaft (SHN), wherein a second radial output shaft centring feature (RB2) which is axially spaced apart from the first radial output shaft centring feature (RB1) is provided on the axial end of the output shaft (SHB), wherein the output shaft centring features (RB1, RB2) and drive shaft centring features (RN1, RN2) are assigned in pairs to one another to form two axially spaced-apart centring feature pairs and are in each case in mutual contact in a radially centring manner.

11. Arrangement (ARG) according to at least one of the preceding claims, wherein the output shaft (SHB) and / or the drive shaft (SHN) and / or the torque arm (TSP) are composed of metal.

12. Arrangement (ARG) according to Claim 4, wherein the flange (FLG) is composed of metal.