Planetary gearbox, driveline, wind turbine and industrial applications with improved lubricant delivery

Abstract

A planetary gearbox (10) is provided, comprising a lubricant transfer device (50) between a first and a second planetary stage (20, 30), the lubricant transfer device (50) comprising a discharge member (52) arranged in co-rotation on a member (13) of the second planetary stage (30), the lubricant transfer device comprising a receiving member (54) for lubricant (55) arranged in co-rotation on a member (13) of the first planetary stage (20), and a lubricant conduit (58) in communication with the lubricant transfer device (50); wherein the lubricant conduit (56) extends radially inside the tooth interface system (29) of the sun gear (22) over the entire axial extent of the tooth interface region (56) of the sun gear (21) and at least one planetary gear (26) of the first planetary stage (21). Thereby an economic, improved lubricant supply is achieved.

Description

Technical Field

[0001] This invention relates to a planetary gearbox with improved lubricant delivery and a transmission system equipped with such a planetary gearbox. The invention also relates to a wind turbine having such a transmission system and an industrial application of the planetary gearbox according to the invention. Furthermore, the invention relates to a computer program product for simulating the operational behavior of such a planetary gearbox. Background Technology

[0002] Patent specification EP3001071B1 discloses a planetary gearbox comprising planetary gears supplied with lubricant. A lubricant distribution conduit is formed between a sliding bushing connected to the housing wall and the web of the planet carrier.

[0003] WO 2012 / 055832A1 and US10337602B2 each disclose a planetary gearbox with a lubricant conduit that passes through the rotating components of each planetary star, including a lubricant delivery device for a discharge component and a relatively rotatable receiving component disposed between two components that rotate relative to each other, wherein the lubricant conduit and the associated lubricant delivery device are formed in an axial region between the sun gears of the successive planetary stars.

[0004] Increasing demands are being placed on planetary gearboxes in terms of performance and compactness. Therefore, it is essential to reliably and with low loss deliver lubricant to the relevant components of the gearbox. Simultaneously, it is desirable to be able to easily manufacture such planetary gearboxes. The object upon which this invention is based is to provide a planetary gearbox with a lubricant supply, which provides improvements in at least one of the described aspects. Summary of the Invention

[0005] This objective is achieved by a planetary gearbox. Preferred configurations are specified in the dependent claims and the following description, which in each case may represent an aspect of the invention individually or in combination. If one feature is presented in combination with another feature, this is only for a simplified presentation of the invention and does not mean that the feature cannot be a development of the invention in the absence of the other features.

[0006] The planetary gearbox has a first planetary gear group and a second planetary gear group, which are connected to each other and arranged adjacent to each other in a torque-transmitting manner. Each of the first and second planetary gear groups has a ring gear, a planet carrier with rotatable planetary gears, and a sun gear as components. In each of the first and second planetary gear groups, at least one of these components is in the form of a rotating component that rotates during operation of the planetary gearbox. The planetary gearbox also includes a lubricant delivery device arranged between the first and second planetary gear groups. The lubricant delivery device is configured to deliver lubricant from the second planetary gear group to the first planetary gear group. For this purpose, the lubricant delivery device includes a discharge component through which lubricant can be conveyed to a receiving component. The discharge component and the receiving component are configured to be complementary to each other in this respect. The discharge component is arranged on a component of the second planetary gear group in a co-rotational manner. The discharge component is rotatably fixed to the rotating component of the second planetary gear group and thus follows the existing rotational motion during operation of the planetary gearbox. As a result, the discharge component can have a compact construction while simultaneously allowing low-leakage delivery of lubricant from the second planetary gear group to the first planetary gear group. Therefore, lubricant can be supplied from the second planetary gear set to the first planetary gear set, thus eliminating the need for holes in the housing wall for lubricant conduits. Specifically, there is no need for additional lubricant supply from the outside to the first planetary gear set and / or holes bypassing the rotating parts of the second planetary gear set. Furthermore, the planetary gearbox can be in the form of a sequential planetary gearbox or a planetary gearbox with power distribution between planetary gear sets.

[0007] Furthermore, the receiving component is arranged on the component of the first planetary gear group in a co-rotating manner. The receiving component is used to receive the lubricant discharged by the discharging component and is rotatably fixed to this component, which is a rotating component of the first planetary gear group. Therefore, the receiving device follows the rotational movement of the first planetary gear group. Moreover, during operation of the planetary gearbox, the receiving component and the discharging component can rotate relative to each other relative to the main axis of rotation of the planetary gearbox. The relative rotation between the discharging and receiving components is relatively small, allowing even simple seals to provide sufficient sealing for low-leakage operation. Therefore, a lubricant delivery device with tested and usable seals can be manufactured in a simple manner. Furthermore, the discharging and receiving components can have reduced dimensions, resulting in a space-saving configuration and cost-effective manufacturing.

[0008] The planetary gearbox also has a lubricant conduit communicating with a lubricant delivery device. It is specified here that the lubricant conduit extends radially within the meshing system of the sun gear and at least one planet gear of the first planetary gear stage, over the entire axial range of the sun gear's meshing area. Instead of a substantially radially extending lubricant conduit, this lubricant conduit has sub-conduits branching in different axial directions to corresponding components to be lubricated, particularly planetary gear pins and / or planetary gears disposed on the respective planetary gear pins. The lubricant conduit can extend substantially over most of the axial range of the first planetary gear stage. Here, the knowledge that in a multi-stage planetary gearbox, a corresponding subsequent planetary gear stage is assembled to a corresponding preceding planetary gear stage via axial relative movement, and can be partially inserted into the preceding planetary gear stage, for example by means of a long hub of the planet carrier of the subsequent planetary gear stage, which can form the sun axis of the preceding planetary gear stage, is utilized. Therefore, the relatively disc-shaped main region (particularly the web) of the corresponding planetary gear stage is located on the axial side away from the subsequent planetary gear stage, and the planetary gear stage typically has a large central opening on the axial side pointing towards the subsequent planetary gear stage, into which the subsequent planetary gear stage and suitable bearings can be more easily inserted during assembly. Because the lubricant conduits extend over the entire axial range of the engagement area of ​​the sun gear in the first planetary gear group, they can route from the disk-shaped main region of the planetary carrier in the subsequent planetary gear group to the disk-shaped main region of the planetary carrier in the preceding planetary gear group. Specifically, the lubricant conduits can connect several planetary gear groups in series, as the lubricant conduits can route from the disk-shaped main region of the planetary carrier in the subsequent planetary gear group via the hub of that planetary carrier to the disk-shaped main region of the planetary carrier in the preceding planetary gear group, and so on. Therefore, lubrication of all planetary gears in a planetary gearbox comprising multiple planetary gear groups can be achieved reliably and cost-effectively in terms of design, particularly based on the modular principle of various planetary gear groups. Preferably, lubricant delivery devices can be respectively located at the transition points of the lubricant conduits between the respective planetary gear groups, and the lubricant delivery devices between each pair of planetary gear groups preferably have the same and / or similar design, for example, in a proportionally larger or smaller form, and particularly preferably have the same design. Therefore, production costs can be further reduced.

[0009] Lubricant conduits can supply lubricant, for example, from pitch tubes, which are particularly inserted radially inward. The pitch tube, or the annular gap defined by it, is not considered part of the lubricant conduit. The lubricant conduit involves portions of material formed by machining (particularly by drilling) of the corresponding rotating components of the respective planetary gears, which are interconnected and introduced into the respective planetary gears; the lubricant delivery device also forms part of the lubricant conduit. The lubricant conduit is formed specifically only in the material of the load-dissipating rotating components of the respective planetary gears plus the lubricant delivery device. Therefore, the bridging of the axial distance of the planetary gears of the first planetary gear is achieved by the rotating components of the first or second planetary gear, particularly by load-dissipating rotating components, rather than by the normally fixed pitch tube. Therefore, the axial range of the pitch tube can be reduced and / or minimized.

[0010] Lubricant conduits can be formed in or on components of the second planetary gear group, which extend axially through the gear engagement region of the first planetary gear group. The gear engagement region is the axial portion of the first planetary gear group where the planetary gears mesh with the sun gear and / or ring gear of the first planetary gear group. The lubricant conduits can therefore extend axially through the gear engagement region. This allows for the utilization of mounting space in the radially inward region of the planetary gearbox, around the main axis of rotation. The thus free mounting space remains easily accessible as a clear space. No further radially inward arrangement of lubricant conduits or lubricant delivery devices is required. This, in turn, allows for an increase in the diameter of the planetary gears or a decrease in the diameter of the sun gear. This allows for greater design freedom in the diameter ratios within the corresponding planetary gear group, thus enabling a wider range of static gear ratios within the corresponding planetary gear group. Therefore, the claimed planetary gearbox can achieve an increased static gear ratio, for example, in the first planetary gear group. As a result, the second planetary gear group can have a smaller, more compact, and lighter design. Therefore, the claimed planetary gearbox provides a higher power density to mass. The lubricant conduits attached to the components of the second planetary gear group can be, for example, in the form of pipes or annular conduits. Pipes avoid the production of long holes, as the longer the hole, the more difficult it becomes to produce precisely.

[0011] Specifically, the lubricant conduit within the lubricant delivery device deflects in the flow direction between an axial flow direction and a radial flow direction, wherein the lubricant conduit leads axially to the discharge component and exits radially from the receiving component. This allows for cost-effective formation of deflection, particularly a substantially 90° deflection, either within the discharge component or within the receiving component or on the contact surfaces of the discharge and receiving components. The contact surfaces can move relative to each other and face each other. This avoids blocking the cross-hole on one side due to the deflection of the lubricant conduit. Instead, the end of the lubricant conduit's orifice can be replaced with the lubricant delivery device, saving the need for plugs that would otherwise have to be blocked. The lubricant conduit is preferably formed only by unblocked through-holes, blind holes, and at least one lubricant delivery device.

[0012] The sun gear is preferably mounted on the hub of the planetary carrier of the second planetary star in a relatively rotatable or rotatably fixed manner, wherein a lubricant conduit within the hub passes through the tooth engagement area of ​​the sun gear, and a lubricant delivery device is located downstream of the hub. Therefore, the lubricant conduit does not need to pass through the axially shorter sun gear. Instead, the lubricant conduit passes through the hub of the planetary carrier of the subsequent planetary star, which is significantly longer than the axial extent of the sun gear. The lubricant conduit can extend radially at a distance from the sun gear within the corresponding planetary carriers of the preceding (particularly the first) and subsequent (particularly the second) planetary stars. Since the hub of the planetary carrier of the second planetary star represents the rotating component of the second planetary star, it can also be inserted into the first planetary star within the rotating component of the first planetary star. The lubricant delivery device is specifically positioned downstream of the lubricant conduit, from which the lubricant flows from the second planetary star to the first planetary star. Therefore, the lubricant delivery device can be positioned in the middle of the preceding, particularly the first, planetary star in a space-saving manner.

[0013] However, the sun gear can also be rotate-fixed to the sun gear shaft of the first planetary star system, wherein the lubricant conduit within the sun gear shaft passes through the tooth engagement area of ​​the sun gear, and the lubricant delivery device is located upstream of the sun gear shaft. Therefore, the lubricant conduit does not need to pass through the shorter sun gear in the axial direction. Instead, the lubricant conduit passes through the sun gear shaft of the preceding planetary star system. This sun gear shaft is significantly longer than the axial range of the sun gear. The lubricant conduit can extend radially at a distance from the sun gear within the corresponding planetary carriers of the preceding (particularly the first) and subsequent (particularly the second) planetary star systems, and is connected to each other via the sun gear shaft. Since the sun gear shaft of the first planetary star system represents the rotating component of the first planetary star system (which can also be inserted into the second planetary star system within its rotating component), the lubricant delivery device is specifically positioned upstream of the lubricant in the lubricant conduit. The lubricant flows from the second planetary star system to the first planetary star system. Therefore, the lubricant delivery device can be positioned in the middle of the subsequent, particularly the second, planetary star system in a space-saving manner.

[0014] Particularly preferably, the lubricant conduit leads to the planetary gear pins of the first and second planetary gear groups, the first planetary gear pins being rotatably or rotatably fixedly inserted into the planet carrier, and the second planetary gear pins being rotatably or rotatably fixedly inserted into the planet carrier. Specifically, the lubricant conduit terminates at the planetary gear pin of the first planetary group at an axial distance from the planetary gear disposed on the first planetary gear pin, and / or terminates at the planetary gear pin of the second planetary group at an axial distance from the planetary gear disposed on the second planetary group. Lubricant conduits extending within the disc-shaped web of the respective planetary gear carrier can terminate axially at the respective planetary gear pin without requiring the lubricant conduit within the planet carrier to be deflected toward the planetary gear. The planetary gear pins can be received in the planet carrier with corresponding clearance, such that the elastic deformation of the planetary gear pins during continuous operation allows lubricant to be delivered from the lubricant conduit along the planetary gear pin to the planetary gear, which is particularly rotatably mounted on the planetary gear pin. In particular, the planetary gear pins have channels, grooves, etc. extending in the axial direction, so that lubricant leaving the lubricant conduit outside the planet carrier can be easily delivered along the planetary gear pins and delivered to the associated planetary gears with sufficient mass flow.

[0015] Furthermore, the lubricant delivery device can be arranged axially (i.e., along the main axis of rotation of the planetary gearbox) on the side of the first planetary gear group opposite to the second planetary gear group. As a result, lubricant can be delivered over an increased distance in the components of the second planetary gear group, which in turn ensures substantially leak-free delivery of the lubricant. The lubricant in the first planetary gear group must be delivered only over a reduced axial distance. This leads to a simplification of the structure of the first and second planetary gear groups. Moreover, this positioning of the lubricant delivery device facilitates easy access from the first planetary gear group, which in turn simplifies the assembly and maintenance of the planetary gearbox under protection.

[0016] Furthermore, the discharge device can be arranged at the end of the hub of the second planetary carrier facing the first planetary carrier. The sun gear of the first planetary carrier can be arranged on a hub also known as a long hub. In particular, the discharge device can be attached to the end face of the hub facing the first planetary carrier, thus improving the accessibility of the lubricant delivery device. This allows for easier assembly and maintenance. The discharge device can be hydraulically connected to a lubricant conduit, which is essentially in the form of a hole passing through the hub in the axial direction. This hole can be manufactured in a simple manner, for example by a separate drilling process or by casting the planetary carrier. Alternatively or supplemented, the lubricant conduit can also be in the form of a pipe. The lubricant conduit can be formed in the radially inner region of the hub, which experiences less mechanical stress during operation of the planetary gearbox than the radially outer region. Therefore, mounting space that is not usable in the case of gearbox classes according to the prior art can be used in a technical manner. This improves the utilization of existing mounting space, which in turn means that the claimed planetary gearbox can have a compact structure. In particular, the discharge device can be integrally formed with the hub of the second planetary carrier.

[0017] In another embodiment of the claimed planetary carrier, the receiving component may be arranged on the web of the first planetary carrier opposite to the second planetary carrier, i.e., in a designated area of ​​the web. In the area of ​​the web of the first planetary carrier (opposite to the second planetary carrier), there are also pin holes for planetary gear pins on which the first planetary gears are rotatably arranged. The web extends substantially radially relative to the main axis of rotation. Therefore, lubricant received by the receiving component can be guided radially through the web to one of the planetary gear pins via lubricant conduits. The radial lubricant conduits can be manufactured in a simple manner, for example, through a single hole or by casting the first planetary carrier. The designated web of the first planetary carrier is also easily accessible, which simplifies maintenance. In particular, the seals that create a sealing effect between the receiving and discharging components can be replaced with less work. This allows for an effective sealing effect in the lubricant delivery system to be ensured in a cost-effective manner throughout the entire service life of the planetary gearbox. Similarly, radial and axial misalignment between the first and second planetary carriers can be compensated for with minimal leakage. Furthermore, no heavy moving mass acts on the seals during assembly, preventing damage to them. Additionally, the discharge and receiving components can have a relatively compact and lightweight construction, allowing for precise manual assembly. The assembly forces are relatively low, thus avoiding damage to the seals during assembly. This, in turn, allows for the use of seals made from mechanically sensitive materials, such as PTFE. Similar to the ease of assembly, ease of maintenance is also increased, or in the first place, maintenance is made possible.

[0018] Furthermore, in the claimed planetary gearbox, the lubricant delivery device can be configured to compensate for radial, axial, and / or angular misalignment between the discharge and receiving components. The terms "axial" and "radial" in this context refer to the main axis of rotation of the planetary gearbox. Angular misalignment can be caused by the tilting of corresponding components. Specifically, if radial, axial, and / or angular misalignment occurs between components of the first and second planetary gear groups, leakage losses at the lubricant delivery device, where the receiving or discharge device is attached to the first or second planetary gear group, are avoided or reduced. Therefore, the claimed planetary gearbox allows, for example, the planet carriers of the first and / or second planetary gear groups to be mounted in a movable manner. This avoids constraint forces on the planet carriers and gear meshing system. Therefore, the claimed planetary gearbox is suitable for a wide range of applications, robust to adverse operating conditions, and provides reduced leakage losses.

[0019] In the case of the claimed planetary gearbox, the lubricant delivery device can have resilient contact seals, labyrinth seals, gap seals, bushings, and / or sealing rings. Resilient contact seals, such as shaft sealing rings or seals based on the piston sealing ring principle, provide good sealing during rotation and at rest, and are available in various sizes and shapes. Labyrinth seals provide a substantially non-contact seal, thus avoiding mechanical losses at the lubricant delivery device during operation. A bushing, for example, is made of bronze or other soft metals. Gap seals also provide good sealing. The compact design of the claimed planetary gearbox makes the use of gap seals possible. In particular, in the claimed planetary gearbox, leakage losses from gap seals are reduced to a feasible level. Bushings allow for a good sealing effect in the lubricant delivery device in a compact and cost-effective manner. By selecting suitable materials, bushings can achieve a sufficient service life. For example, sealing rings in the form of O-rings provide good sealing and can be replaced in a cost-effective manner. Combinations of different seals can also be arranged on the lubricant delivery device in the claimed planetary gearbox. Therefore, the seals can be easily adapted to current operating requirements, and the solution requiring protection can be transferred to planetary gearboxes of different sizes and with different design concepts.

[0020] In another embodiment of the claimed planetary gearbox, a gap can be formed between the discharge component and the receiving component. This gap allows relative rotation between the discharge and receiving components to be achieved without contact, i.e., without friction. Simultaneously, leakage losses through the gap can be precisely designed to remain within acceptable limits. Furthermore, the gap between the receiving and discharge components allows for smooth assembly.

[0021] As an alternative or supplement, a centrifugal seal can be arranged between the discharge and receiving components. The centrifugal seal can open in a contact manner while stationary and is configured to provide a sealing effect at contact speeds higher than the design speed. Since lubricant delivery is also interrupted when the planetary gearbox is stationary, opening can be easily permitted, i.e., a non-sealing centrifugal seal. Lubricant delivery also increases with the planetary gearbox speed. The higher the planetary gearbox speed, the higher the requirements for the centrifugal seal, and the more pronounced the sealing effect of the centrifugal seal. As a result, an automatically adjusting seal is achieved.

[0022] Furthermore, the claimed planetary gearbox may also have at least a third planetary stage, arranged downstream of the second planetary stage. Corresponding to the first and second planetary stages, a lubricant delivery device may also be arranged between the second and third planetary stages, by means of which lubricant can be delivered from the third planetary stage to the second planetary stage. The lubricant delivery device between the second and third planetary stages can be constructed according to at least one of the above embodiments. Additionally, the two lubricant delivery devices may have the same construction or implement different embodiments. Therefore, the claimed planetary gearbox has a simple and efficient lubricant supply. Overall, the length of the lubricant conduits present in the planetary gearbox is minimized. This reduces pressure loss in the lubricant, i.e., hydraulic loss. This allows for the use of simple lubricant supply devices, particularly lubricant pumps with relatively low delivery rates, to ensure lubricant supply to complex planetary gearboxes comprising three or more planetary stages. This, in turn, means that at least a three-stage planetary gearbox can be manufactured in a simple and economically feasible manner. Such a three-stage planetary gearbox is obtained, for example, from International Application WO 2020 / 001942 A1. The disclosure of WO2020 / 001942 A1 is incorporated herein by reference. Furthermore, in the claimed planetary gearbox, the sun axis of the third planetary star can have a reduced inner diameter. Consequently, the outer diameter of the third planetary star is also reduced.

[0023] The object of the present invention is also achieved by a drivetrain according to the invention, which is suitable for wind turbines. The drivetrain includes a rotor shaft connected to a gearbox in a torque-transmitting manner. The drivetrain also includes a generator connected to the gearbox in a torque-transmitting manner. According to the invention, the gearbox is in the form of a planetary gearbox according to one of the above embodiments. The planetary gearbox and the generator can also be configured to be integrated into each other, that is, in the form of a generator gearbox. The planetary gearbox according to the invention further simplifies and accelerates the assembly of the drivetrain according to the invention.

[0024] Similarly, the objective described at the beginning is achieved by a wind turbine according to the invention. The wind turbine includes a nacelle on which a multi-bladed rotor is rotatably arranged. The multi-bladed rotor is connected to a rotor shaft in a torque-transmitting manner, and the rotor shaft forms part of the wind turbine's drivetrain. According to the invention, the drivetrain is constructed according to one of the above embodiments.

[0025] The object of the invention can also be achieved through its industrial applications. These industrial applications include a drive unit, which can be, for example, an electric motor, a burner, or a hydraulic motor. The drive unit provides driving force, which is supplied to a gearbox. For this purpose, the drive unit is connected to the gearbox in a torque-transmitting manner. The gearbox is in turn connected to an output unit in a torque-transmitting manner, providing driving force to the output unit at a corrected rotational speed, taking mechanical losses into account. The output unit can be in the form of a mechanical application, such that the industrial application as a whole is, for example, a mill, vertical mill, sugar mill, cement mill, rock crusher, conveyor belt, pump, roller press, slat conveyor, tube mill, rotary kiln, rotary gear, mixing unit, lifting device, waste compactor, or scrap compactor. According to the invention, the gearbox is in the form of a planetary gearbox constructed according to one of the above embodiments.

[0026] Furthermore, the above objectives are achieved by a computer program product according to the invention, configured to simulate the operational behavior of a planetary gearbox arranged (i.e., substantially mounted) in a wind turbine. For this purpose, the computer program product may have a physical model in which an image of the planetary gearbox can be displayed. The physical model may have simulation routines through which the kinematics of the planetary gearbox and / or its components can be mapped. Similarly, the physical model may be adapted to replicate the hydrodynamic behavior of a working medium, such as a lubricant. Likewise, the physical model may be configured to simulate the thermal behavior of the planetary gearbox, its components, and the working medium individually or in interaction. Furthermore, the physical model may be adapted to simulate the oscillatory behavior of the components based on the structural dimensions of the planetary gearbox components and data regarding their respective materials. The computer program product may include a data interface for receiving data specifying the main operating conditions of the planetary gearbox. Similarly, the computer program product may have a data interface for outputting simulation results, which will be output to a user and / or forwarded to other simulation-oriented computer program products. The computer program product may be in the form of a digital twin. For example, such digital twins are described in more detail in the specification disclosed in US2017 / 286572A1. The disclosure of US2017 / 286572A1 is incorporated herein by reference. According to the present invention, the planetary gearbox configured according to one of the above embodiments can have its operation simulated by a computer program product. Therefore, the claimed planetary gearbox can be installed in a variety of wind turbines. In particular, the assembly or maintenance of the planetary gearbox can be simulated so that the technical advantages of the claimed planetary gearbox can be fully utilized in wind turbines. Attached Figure Description

[0027] The invention will now be explained in more detail with reference to the various embodiments shown in the accompanying drawings. These drawings should be read in a complementary manner, 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 drawings can be combined with the features described above. Specifically:

[0028] Figure 1 An embodiment of the claimed planetary gearbox is schematically shown in longitudinal section;

[0029] Figure 2 A cross-sectional perspective view of an embodiment of the claimed wind turbine is shown;

[0030] Figure 3 The construction of an embodiment of the claimed industrial application is illustrated schematically. Detailed Implementation

[0031] Figure 1 The claimed embodiment of the planetary gearbox 10 is schematically shown in longitudinal section. The planetary gearbox 10 includes a first planetary group 20, followed by a second planetary group 30 and a third planetary group 40. Planetary groups 20, 30, and 40 are interconnected by a housing component 11, which is releasably connected to the gear rings 22, 32, and 42 of the respective planetary groups 20, 30, and 40. The first, second, and third planetary groups 20, 30, and 40 each have planet carriers 24, 34, and 44, and in each case, a plurality of planetary gear pins 28, 38, and 48 are fixed to the planet carrier. Corresponding planetary gears 26, 36, and 46 are rotatably arranged on the planetary gear pins 28, 38, and 48. In each of the planetary groups 20, 30, and 40, the planetary gears 26 and 36 mesh with sun gears 21 and 31. In the third planetary gear set 40, planetary gear 46 meshes with sun shaft 41, which is equipped with a gearing system and therefore also functions as a sun gear. Sun gears 21, 31 or sun shaft 41, planetary gears 26, 36, 46, and planet carriers 24, 34, 44 belong to the rotating components 13 of the planetary gearbox 10. Planet carriers 24, 34, 44 and sun gears 21, 31, 41 rotate about the main rotation axis 15 of the planetary gearbox 10 during operation, thereby transmitting driving force 25 from the drive side 17 to the output side 19 through the conversion of torque and speed. Driving force 25 is provided via hub 23, which is integral with the planet carrier 24 of the first planetary gear set 20.

[0032] The planet carrier 34 of the second planetary star 30 has a hub 33 extending toward the first planetary star 20. The hub 33 is connected to the sun gear 21 of the first planetary star 20 via a shaft-hub connector 57 in a torque-transmitting manner. The discharge component 52 of the lubricant delivery device 50 is arranged at an end 39 of the hub 33, the end being opposite to the second planetary star 30 and... Figure 1 The left side is shown. The lubricant delivery device 50 also includes a receiving component 54 connected to the first planetary gear 20. The receiving component 54 is attached to the planet carrier 24 of the first planetary gear 20. The receiving component 54 is fastened in the region of the web 27 of the planet carrier 24, such that lubricant 55 can be delivered from the discharge component 52 to the receiving component 54. In this case, the lubricant 55 is delivered along the flow direction 53. Due to the fact that the discharge component 52 is fastened to the planet carrier 34 of the second planetary gear 30, it rotates together with the planet carrier 34 during operation. Similarly, the receiving component 54 rotates together with the planet carrier 24 of the first planetary gear 20. Due to the different rotational speeds of the planet carrier 24 and the sun gear 21 of the first planetary gear 20, there is also relative rotation 59 between the receiving component 54 and the discharge component 52. The lubricant delivery device 50 has a seal 51 in the form of a sealing ring, so that even in the presence of relative rotation 59, it is suitable for delivering lubricant 55 with minimal leakage loss. Lubricant 55 is delivered axially 45 via a lubricant conduit 58, which is essentially in the form of a bore passing through the hub 33 of the planetary carrier 34 of the second planetary group 30. The lubricant 55 is deflected by the discharge member 52 and the receiving member 54 and delivered via the lubricant conduit 58 in the planetary carrier 24 of the first planetary group 20 to the planetary gear pin 28 received therein. Thus, lubricant 55 can be supplied to the sliding bearing between the planetary gear pin 28 and the planetary gear 26 in the first planetary group 20. The lubricant conduit 58, hydraulically connected to the receiving member 54, is essentially in the form of a bore in the radial direction 49, which extends on the drive side 17 through the web 27 of the planetary carrier 24.

[0033] A lubricant conduit 58, formed in the hub 33 of the planetary carrier 34 of the second planetary star 30, extends axially 45 through a gear engagement region 56 where the gear meshing system 29 of the planetary gears 26 and the sun gear 21 of the first planetary star 20 engages. Within the gear engagement region 56, there is also an area where a shaft-hub connector 57 between the sun gears 21 of the first planetary star 20 connects to the planetary carrier 34 of the second planetary star 20. Due to the use of the lubricant delivery device 50, the planetary carrier 24 of the first planetary star 20 has an enlarged inner diameter 16, in which a pitch tube 18 is arranged. Therefore, the first planetary star 20 is easily accessible, simplifying assembly and maintenance. Furthermore, the lubricant delivery device 50 is adapted to compensate for axial, radial, and / or angular misalignment between the planetary carriers 24, 34 of the first and second planetary star 20. As a result, Figure 1The planetary gearbox 10 shown is robust to temporarily excessive stress and exhibits minimal lubricant 55 leakage loss at the lubricant delivery device 50. In general, the delivery of lubricant 55 from the second planetary carrier 30 to the first planetary carrier 20 is also simplified because the length of the lubricant conduits 58 in the first planetary carrier 24 and the second planetary carrier 34 is reduced. As a result, hydraulic losses in the lubricant lines 58 can be reduced, that is, primarily pressure losses, which in turn allows for the use of a simpler lubricant pump. Figure 1 It is not shown in more detail here.

[0034] Figure 1 The planetary gearbox 10 also has a third planetary gear group 40, which is provided with a discharge component 52 of a lubricant delivery device 50. A corresponding receiving component 54 is attached to the planet carrier 34 of the second planetary gear group 30 in a rotatable manner. The lubricant delivery device 50 between the second planetary gear group 30 and the third planetary gear group 40 is constructed and arranged in a manner corresponding to the lubricant delivery device 50 between the first planetary gear group 20 and the second planetary gear group 30. Therefore, the technical aspects outlined above also apply to the lubricant delivery device 50 between the second planetary gear group 30 and the third planetary gear group 40. The planetary gearbox 10 is also simulated in a computer program product 90, resulting in the computational adjustment of the operating behavior of the planetary gearbox 10.

[0035] exist Figure 2 A cross-sectional oblique view shows an embodiment of the claimed wind turbine 70 with the claimed drivetrain 60. The drivetrain 60 is arranged in the nacelle 71 of the wind turbine 70 and has a rotor shaft 62, which is torque-transmitted to a multi-bladed rotor 72. The rotation of the multi-bladed rotor 72, as a driving force 25, is transmitted via the rotor shaft 62 to a gearbox 64, which is in turn torque-transmitted to a generator 66, which also forms part of the drivetrain 60. According to the invention, the gearbox 64 is in the form of a planetary gearbox 10 according to one of the above embodiments. Furthermore, the operating behavior of the gearbox 64, i.e., the operating behavior of the planetary gearbox 10, can be simulated by a computer program product 90. For this purpose, the computer program product 90 includes an image of the planetary gearbox 10 and is particularly suitable for processing the rotation of the multi-bladed rotor 72 to replicate the operating conditions of the wind turbine 70.

[0036] Figure 3The configuration of an embodiment of the claimed industrial application 80 is schematically shown, comprising a drive unit 82 and an output unit 84. The drive unit 82 provides a driving force 25, which is transmitted to the output unit 84 via a gearbox 85. The drive unit 82 may be in the form of an electric motor, a burner, or a hydraulic motor. The output unit 84 may be in the form of a mechanical application, such as an industrial application 80 being a mill, vertical mill, sugar mill, cement mill, rock crusher, conveyor belt, pump, roller press, slat conveyor, tube mill, rotary kiln, rotary gear, mixing unit, lifting device, waste compactor, or scrap compactor. According to the invention, the gearbox 85 is in the form of a planetary gearbox 10 according to one of the above embodiments.

Claims

1. A planetary gearbox (10) comprising: A lubricant delivery device (50) between a first planetary gear group (20) and a second planetary gear group (30), wherein the lubricant delivery device (50) includes a discharge component (52) and a receiving component (54) for lubricant (55), the discharge component (52) being rotatably attached to a component of the second planetary gear group (30) and the receiving component being rotatably attached to a component of the first planetary gear group (20); and a lubricant conduit (58) communicating with the lubricant delivery device (50), wherein the lubricant conduit (58) extends radially inside the gear engagement system (29) of the sun gear (21) of the first planetary gear group (20) and at least one planetary gear (26) of the first planetary gear group (20) over the entire axial range of the gear engagement region (56) of the sun gear (21). The lubricant delivery device (50) is located on the axial side of the first planetary star opposite to the second planetary star, and the component of the second planetary star (30) is connected to the sun gear (21) of the first planetary star (20) in a torque-transmitting manner, having relative rotation between the receiving component (54) and the discharging component (52).

2. The planetary gearbox (10) of claim 1, characterized in that The lubricant conduit (58) within the lubricant delivery device (50) deflects between the axial flow direction and the radial flow direction in the flow direction (53).

3. The planetary gearbox (10) as described in claim 1 or 2. characterized in that The sun gear (21) is mounted on the hub (33) of the planet carrier (34) of the second planetary gear (30) in a relatively rotatable or rotatably fixed manner, wherein the lubricant conduit (58) within the hub (33) passes through the tooth engagement area (56) of the sun gear (21), and the lubricant delivery device (50) is located downstream of the hub (33).

4. The planetary gearbox (10) as described in claim 1 or 2. characterized in that The sun gear (21) is rotatably fixed to the sun gear shaft of the first planetary star, wherein the lubricant conduit (58) within the sun gear shaft passes through the tooth engagement area (56) of the sun gear (21), and the lubricant delivery device (50) is located upstream of the sun gear shaft.

5. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The lubricant conduit (58) is routed to the planetary gear pins (28) of the first planetary group (20) and the planetary gear pins (38) of the second planetary group (30), wherein the planetary gear pins (28) of the first planetary group (20) are inserted into the planet carrier (24) in a rotatable or rotationally fixed manner, and the planetary gear pins (38) of the second planetary group (30) are inserted into the planet carrier (34) in a rotatable or rotationally fixed manner.

6. The planetary gearbox (10) of claim 5, characterized in that The lubricant conduit (58) terminates at the planetary gear pin (28) of the first planetary group (20) at an axial distance from the planetary gear on the planetary gear pin (28) of the first planetary group (20), and / or the lubricant conduit (58) terminates at the planetary gear pin (38) of the second planetary group (30) at an axial distance from the planetary gear on the planetary gear pin (38) of the second planetary group (30).

7. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The receiving component (54) is disposed on the web (27) of the planet carrier (24) of the first planetary plane (20) opposite to the second planetary plane (30).

8. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The lubricant delivery device (50) is configured to compensate for radial, axial and / or angular offsets between the discharge component (52) and the receiving component (54).

9. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The lubricant delivery device (50) has a labyrinth seal, a bushing and / or a sealing ring (51).

10. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that A gap is formed between the discharge component (52) and the receiving component (54).

11. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The centrifugal seal is arranged between the discharge component (52) and the receiving component (54).

12. The planetary gearbox (10) as claimed in claim 1 or 2, characterized in that The planetary gearbox (10) also has a third planetary gear (40).

13. The planetary gearbox (10) of claim 2, characterized in that, The lubricant conduit (58) extends axially to the discharge component (52) and exits radially from the receiving component (54).

14. A drive train (60) for a wind turbine (70) comprising a rotor shaft (62) connected in torque transmitting manner to a gearbox (64) and a generator (66) connected in torque transmitting manner to the gearbox (64), characterized in that The gearbox (64) is in the form of a planetary gearbox (10) as described in any one of claims 1 to 13.

15. A wind turbine (70) including a nacelle (71) on which a multi-bladed rotor (72) is rotatably disposed, the multi-bladed rotor (72) being connected to a drive system (60) in a torque transmission manner. characterized in that The transmission system (60) is configured as described in claim 14.

16. An industrial application device comprising a drive unit (82) and an output unit (84) connected to each other via a gearbox (85) in a torque transmission manner. characterized in that The gearbox (85) is in the form of a planetary gearbox (10) as described in any one of claims 1 to 13.

17. A computer program product (90) for simulating an operational behavior of a planetary gearbox (10) arranged in a drive train (60) of a wind turbine (70), characterized in that, The planetary gearbox (10) is constructed as described in any one of claims 1 to 13.

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