Planetary gearbox for a wind turbine, in particular a multi-planetary gearbox

Abstract

The invention relates to a planetary gearbox (26) comprising a planet carrier (44) having a first support flange (40) and a second support flange (42); planet gears (30) rotatably mounted on the first support flange (40) and the second support flange (42) in each case via bearing pins (38); an annular gear (36) meshing with the planet gears (30), an assembly clearance being formed between on the one hand the outer flange diameter (D) of the first support flange (40) and the second support flange (42) and on the other hand the inner diameter of the annular gear (36); at least one planet carrier web (68) positioning the first support flange (40) and the second support flange (42) at a defined distance from one another, wherein the radially outward-facing outer side (74) of the planet carrier web (68) is spaced more radially inwards from the radially inner addendum circle radius of the inner teeth (34) of the annular gear (36) than the first support flange (40) and the second support flange (42) and is arranged radially outside the inner diameter of the planet gears (30). This makes it possible to obtain a planetary gearbox (26) having a high power density while requiring a small installation space.

Description

Technical Field

[0001] The present invention relates to a planetary gearbox by means of which torque and rotational speed can be converted. Background Art

[0002] EP 1 985 850 A1 has disclosed a planetary gearbox for a wind turbine, in which two opposite planet carrier cheeks of the planet carrier are interconnected via axially extending planet carrier spokes. The radially outwardly directed cylindrical shell surface of the planet carrier spoke has a configuration radially inwardly offset relative to the radially outer edge of the planet carrier cheek and merges into the planet carrier cheek in a sharp-edged manner. The cylindrical shell surface of the planet carrier spoke is arranged at a radius relative to the axis of rotation of the planet carrier, and an antifriction bearing is also provided on the planet carrier, which is located between a bearing pin connected to the planet carrier cheek and a planet gear mounted on the bearing pin. The antifriction bearing is inserted into the inner diameter of the planet gear.

[0003] There has always been a requirement to achieve a high power density in a planetary gearbox with small installation space requirements. Summary of the Invention

[0004] The object of the present invention is to specify measures that make it possible for a planetary gearbox to have a high power density and small installation space requirements.

[0005] This object is achieved by the planetary gearbox. Preferred refinements of the present invention are specified in the dependent claims and the following description, and these preferred refinements can each individually or in combination represent an aspect of the present invention.

[0006] According to the present invention, a planetary gearbox for a wind power installation, in particular a multi-planetary gearbox, is provided with a planet carrier having a first planet carrier cheek and a second planet carrier cheek; planet gears rotatably mounted on the first planet carrier cheek and the second planet carrier cheek respectively via a bearing pin; an internal gear meshing with the planet gears; an assembly gap is provided between the outer diameter of the cheeks of the first planet carrier cheek and the second planet carrier cheek on the one hand and the inner diameter of the internal gear on the other hand; and at least one planet carrier spoke positioning the first planet carrier cheek and the second planet carrier cheek relative to each other at a defined spacing, the radially outwardly directed outer side of the planet carrier spoke being spaced more radially inwardly from the radially inner addendum circle radius of the internal tooth system of the internal gear than the first planet carrier cheek and the second planet carrier cheek and being arranged radially outside relative to the inner diameter of the planet gears.

[0007] In order to increase the power density in the drive train of a wind power installation and to achieve a satisfactory efficiency for the power to be transmitted, multiple multi-planetary gearboxes can be connected in series. Compared to a conventional planetary gearbox with three planet gears, a multi-planetary gearbox has four, five or more planet gears and can have a relatively low static gear ratio. For example, for a planetary gearbox, especially designed as a multi-planetary gearbox, a static gear ratio i0 of 1.0 < │i0│ ≤ 3.0, especially 1.1 ≤ │i0│ ≤ 2.5, preferably 1.2 ≤ │i0│ ≤ 2.0, and particularly preferably 1.3 ≤ │i0│ ≤ 1.5 is configured. In the case of such a small gear ratio of this type, a particularly high efficiency is achieved and thus a high power density is achieved. However, this results in high requirements for the geometry of the planetary gearbox and the installation space. In the case of such a low static gear ratio of this type, the planet gears have a smaller diameter compared to the sun gear meshing with the planet gears, so that the radial spacing between the tip circle diameter of the external tooth system of the sun gear and the tip circle diameter of the internal tooth system of the internal gear is very narrow. In addition, the planet gears should be axially supported on the planet carrier cheek plates, and as a result, the planet carrier cheek plates must have a large outer cheek plate diameter. Here, the outer cheek plate diameter should be chosen so large that the planet carrier cheek plates can only move axially in the radial inner direction past the internal tooth system of the internal gear during the assembly process. As a result, a rather small clearance is configured between the outer cheek plate diameter of the planet carrier cheek plates and the tip circle diameter of the internal tooth system of the internal gear.

[0008] However, during the operation of the planetary gearbox, it must be ensured that the planet carrier does not come into contact with the internal tooth system, which cannot be guaranteed with sufficient safety in the case where the clearance between the planet carrier web and the internal gear is rather small. Therefore, a spacing is provided between the outer side of the planet carrier web and the tip circle radius of the internal tooth system of the internal gear that exceeds the assembly clearance between the planet carrier cheek plates and the internal tooth system. Since the planet carrier cheek plates are axially offset relative to the internal tooth system of the internal gear, a very small radial spacing of the outer cheek plate diameter from the internal diameter of the internal gear can be provided, while the outer side of the planet carrier web is radially inwardly offset slightly relative to the outer cheek plate diameter of the planet carrier cheek plates in order to reliably avoid contact with the internal tooth system of the internal gear, even taking into account manufacturing and production tolerances and possible thermal expansion effects and / or centrifugal force effects.

[0009] In addition, for the spacing a between the rotational axes of two planet gears following one another in the circumferential direction, the tip circle diameter d a corresponding to the outer diameter of the planet gears, the spacing a can in particular be only 1.0 ≤ a / d a ≤ 2.0, preferably 1.1 ≤ a / d a ≤ 1.5, particularly preferably 1.2 ≤ a / d a≤ 1.3. A substantially triangular meshing intermediate region is generated between the planetary gears following one another in the circumferential direction and between the tip circle radius of the internal teeth and the narrowest point between the planetary gears following one another. The planet carrier web can be arranged in this meshing intermediate region. Here, the planet carrier web is positioned as close as possible to the internal gear, but does not contact the internal tooth system of the internal gear. Here, the radially outwardly directed outer side of the planet carrier web can be arranged slightly radially inside the tip circle radius of the internal tooth system of the internal gear in the common axial region with the internal tooth system of the internal gear, wherein in particular the outer side of the planet carrier web extends at a substantially constant spacing from the tip circle radius of the internal tooth system of the internal gear at least in a part of the circumferential angle region occupied by the outer side. Here, the outer side of the planet carrier web is arranged at least radially outside the inner diameter of the adjacent planetary gears, whereby the planetary gears are mounted on bearing pins which are connected to the planet carrier cheek plates. The inner diameter of the planetary gear defines a radius with respect to the rotational axis of the gearbox (i.e., the rotational axes of the sun gear, internal gear and planetary gear) at the point located at the maximum distance radially outside, and the outer side of the planet carrier web is arranged outside this radius.

[0010] As a result, the planet carrier web can be arranged in the installation space between the sun gear and the internal gear, wherein sufficient installation space can be configured in the circumferential direction between the planetary gears for a sufficiently large cross-section of the planet carrier web in order to support the planet carrier cheek plates in a reliable and stable manner in a stacked manner and / or to interconnect the planet carrier cheek plates. At the same time, the cross-section of the planet carrier web can be positioned far enough away from the external tooth system of the planetary gears and the internal tooth system of the internal gear to reliably avoid contact and not affect sufficient lubrication. Alternatively, the outer side of the planet carrier web can even retain the lubricant dripping from the internal tooth system of the internal gear and / or can discharge it in the circumferential direction towards the planetary gears, so that the lubrication of the planetary gearbox is improved even with a reduced lubricant requirement. For this purpose, in particular, the outer side of the planet carrier web can cover a part of the corresponding planetary gear when observed radially, so that the lubricant detached from the internal tooth system of the internal gear does not flow between the planetary gears in the circumferential direction, but is collected by the outer side of the planet carrier web and discharged to the planetary gears. In addition, the meshing intermediate region in which the planet carrier web is arranged allows the planet carrier web to form a relatively sharp shape at those ends pointing tangentially on the outer side and allows the release of lubricant drops from the planet carrier web, in particular the lubricant drops are not guided away from the adjacent planetary gears by the adhesion effect on the lower side pointing away from the outer side of the planet carrier web. The improved lubrication achieved thereby can further increase the efficiency and power density of the planetary gearbox. By arranging the planet carrier web in the meshing intermediate region directly below the internal gear, stable support of the planet carrier cheek plates and improved lubrication can be achieved in the case of limited installation space, so that a planetary gearbox with high performance density can be realized with only a small installation space.

[0011] The planetary gearbox can have a sun gear that meshes with the planetary gears and is arranged coaxially radially inside relative to the internal gear. The torque flow transmitted by the planetary gearbox can in principle be introduced via the sun gear or the planet carrier or the internal gear and can be output via the sun gear or the planet carrier or the internal gear if the component has not been provided for introducing torque. It is possible here that the sun gear, the planet carrier and the internal gear are rotatably mounted; alternatively, one of the components of the sun gear, the planet carrier or the internal gear is permanently or temporarily braked and / or fixedly coupled for co-rotation and / or fixedly held so as not to be movable. For example, the internal gear can be part of the stationary gearbox housing. The bearing pin can be connected to the first planet carrier cheek plate and the second planet carrier cheek plate and can in particular be clamped axially between the first planet carrier cheek plate and the second planet carrier cheek plate. The bearing pin is preferably immovably fixed to the planet carrier cheek plate and the respective planetary gear is mounted on the bearing pin such that the planetary gear can rotate relative to the bearing pin. The planetary gearbox can be arranged in a gearbox housing that protects the planetary gearbox from environmental influences and / or contamination. Here, the gearbox housing can be configured to be immovably fixed or to rotate together with the internal gear. For example, the gearbox housing has an oil sump for receiving a lubricant, in particular lubricating oil.

[0012] In particular, the radially outwardly directed outer side of the planet carrier web is arranged at least for most of the circumference of the planetary gear radially outside the root circle radius of the external tooth system of the planetary gear, wherein, in particular, the circumferential angle region Δα of the planetary gear at the root circle radius of the external tooth system extends 270° ≤ Δα ≤ 360°, preferably 300° ≤ Δα ≤ 345°, particularly preferably 315° ≤ Δα ≤ 330° radially inside relative to the maximum radially external region of the said outer side of the planet carrier web configured in the axial region common with the internal tooth system of the internal gear.

[0013] In a common axial region, the internal tooth system of the internal gear covers the outer side of the planet carrier web when observed in the radial direction. The outer side of the planet carrier web has a maximum radially outer point that defines a radius relative to the axis of rotation of the planetary gearbox (i.e., the axis of rotation of the sun gear, internal gear, and planet carrier). This imaginary radius passes through the planetary gears such that most of the planetary gears are radially arranged within this radius, and only a part of the outer tooth system of the planetary gears extends beyond this radius in order to be able to mesh with the internal tooth system of the internal gear. Here, this radius can be completely outside the root circle radius of the outer tooth system of the planetary gears, or it can extend radially in the form of an intersecting secant line within the root circle radius of the outer tooth system of the planetary gears in only a small part of the circumference of the planetary gears. As a result, the planet carrier web can reach particularly far relative to the radial outside, which leads to a corresponding increase in the stability and strength of the planet carrier, and the lubrication of the planetary gears can be further improved by the lubricant dripping from the internal gear. At the same time, just enough clearance can be provided between the planet carrier web and the internal tooth system of the internal gear.

[0014] Preferably, the planet carrier web has a first part web and a second part web, where the first part web is configured integrally with the first planet carrier cheek plate, and the second part web is configured integrally with the second planet carrier cheek plate. The first part web and the second part web support each other particularly in the axial direction. As a result, the planet carrier can have a substantially double-shell construction, where, in particular, on the one hand, the first planet carrier cheek plate can have a configuration substantially the same as that of the first part web, and on the other hand, the second planet carrier cheek plate can have a configuration substantially the same as that of the second part web, so that the production cost can be reduced.

[0015] Particularly preferably, the first part web and / or the second part web merge into the first planet carrier cheek plate and / or the second planet carrier cheek plate substantially at the outer diameter of the cheek plate in a manner axially spaced apart from the internal gear; the outer side of the planet carrier web provided in the common axial region of the internal space merges into the first planet carrier cheek plate and / or the second planet carrier cheek plate particularly via a curved and / or radius-shaped transition region. Here, the following finding is utilized: By providing an axial intermediate space between the respective planet carrier cheek plate and the internal gear, the planet carrier web can radially extend beyond the internal gear to the outside to such an extent that the outer side of the planet carrier web can reach the outer diameter of the respective planet carrier cheek plate. As a result, a radial step and a sharp-edge transition between the outer diameter of the planet carrier cheek plate and the outer side of the planet carrier web can be avoided. Therefore, the stress concentration effect in the transition region between the part web and the respective associated planet carrier cheek plate can be avoided or at least reduced, thereby increasing the strength and stiffness of the planet carrier.

[0016] In particular, the first part web and / or the second part web merge into the first planet carrier cheek plate and / or the second planet carrier cheek plate at an angle forming a transition edge. Due to the fact that the part web does not merge into the planet carrier cheek plate without a shoulder, for example via an asymptote, the radial offset between the outer diameter of the planet carrier cheek plate and the region radially arranged inside the internal tooth system of the internal gear on the outer side of the planet carrier web can be achieved via a relatively small axial intermediate space between the planet carrier cheek plate and the internal tooth system of the internal gear, so that the axial installation space requirement can be kept at a low level.

[0017] In a further embodiment, the first planet carrier cheek plate and the second planet carrier cheek plate have a tapered diameter section of the radius to the radially outwardly directed outer side of the planet carrier web in a circumferential region common with the planet carrier web, and the tapered diameter section merges into the outer diameter of the cheek plate of the first planet carrier cheek plate and / or the second planet carrier cheek plate in particular via a curved and / or radius-shaped path and / or at an angle forming a transition edge. The following finding is utilized here: No planet gear can be arranged in the region of the planet carrier web, so that it is not necessary at all for the planet carrier cheek plate to extend beyond the addendum circle radius of the internal tooth system of the internal gear in order to configure an axially extending region for the planet gear in this circumferential region. In order to avoid stress concentration effects, the planet carrier cheek plate can have a correspondingly suitable outer contour between the outer diameter and the diameter of the tapered diameter section.

[0018] Preferably, the planet carrier web extends radially inwards at least as far as the inner diameter of the planet gear, in particular at least as far as the axis of rotation of the planet gear. Therefore, the cross-section of the planet carrier web can have a correspondingly large size so as to sufficiently strengthen the planet carrier even when the torque to be transmitted is very large. As a result, the meshing intermediate region inside the internal gear can be largely occupied by the planet carrier web.

[0019] Particularly preferably, a spacing a is arranged in an axial region common with the internal tooth system of the internal gear between the internal tooth system of the internal gear and the radially outwardly directed outer side of the planet carrier web: 3.0 mm ≤ a ≤ 8.0 mm, in particular 4.0 mm ≤ a ≤ 7.0 mm, preferably 5.0 mm ≤ a ≤ 6.5 mm and particularly preferably 5.5 mm ≤ a ≤ 6.0 mm. In the case of this type of spacing, contact between the internal gear and the planet carrier web can be reliably avoided within the allowable manufacturing and assembly tolerances. At the same time, the spacing is large enough to avoid or at least make the flow resistance between the components rotating relative to each other negligibly small.

[0020] In particular, a gap with a substantially constant gap width s is arranged between the planet carrier web and the corresponding adjacent planet gear, and the following applies to the outer diameter d of the planet gear a in the case of: 0.01 ≤ s / da ≤0.5, preferably 0.03 ≤ s / d a ≤0.2, particularly preferably 0.05 ≤ s / d a ≤0.1. The lower side of the planet carrier web facing the planet gears can extend at a substantially constant radius relative to the axis of rotation of the adjacent planet gears in this region, so that the clearance configured therebetween also has a constant clearance width between the lower side and the addendum circle radius of the external teeth of the corresponding planet gear. In the case of this type of clearance spacing, the meshing intermediate region radially inside the internal gear between successive planet gears can be largely occupied by the planet carrier web.

[0021] Preferably, at least three, particularly at least six, preferably at least seven, particularly preferably at least eight planet gears are provided, and in each case, a planet carrier web is provided between each pair of planet gears following one another particularly in the circumferential direction. Since the structure of the planet carrier web saves installation space, a correspondingly large number of planet gears can be configured for a multi-planet gearbox, and these planet gears are arranged closely one after another in the circumferential direction without impairing the rigidity of the planet carrier. Due to the large number of planet gears, the load on a single planet gear can be reduced, whereby a large torque can be transmitted with high efficiency and high power density.

[0022] Particularly preferably, the first planet carrier cheek plate and / or the second planet carrier cheek plate has a thrust washer for the axial extension of the planet gear. The thrust washer is supported by the corresponding planet carrier cheek plate particularly over the entire cross-section of the planet gear.

[0023] In particular, a sliding bearing is arranged between the planet gear and the bearing pin. Thereby, the radial installation space requirement between the planet gear and the bearing pin can be significantly reduced, which is required for an antifriction bearing. For example, a sliding bearing bushing significantly thinner than an antifriction bearing can be inserted on the corresponding bearing pin, and the planet gear can slide rotatably relative to the sliding bearing bushing. This enables the use of planet gears with a correspondingly small diameter and / or an increase in the diameter of the bearing pin, whereby the planet carrier can be further strengthened.

[0024] Preferably, the outer side of the planet carrier web extends at a substantially constant spacing from the addendum circle radius of the internal tooth system of the internal gear at least in a part of the circumferential angle region occupied by the outer side. The outer side of the planet carrier web can extend as close as possible to the internal tooth system at a substantially constant radius relative to the axis of rotation of the planet gearbox. Therefore, the installation space in the circumferential direction and / or radially with respect to the outer side in the meshing intermediate region between the internal gear and successive planet gears can be utilized as satisfactorily as possible, thereby increasing the strength and stability of the planet carrier web.

[0025] Particularly preferably, the planet carrier is mounted in the gearbox housing, and the lubricant for lubricating the internal gear and the planet gears, in particular by means of immersion lubrication and / or splash lubrication, is accommodated in the gearbox housing. The lubricant introduced into the gearbox housing can be reused for lubricating the planetary gearbox. Since the planet carrier webs assist in the lubrication of the planet gears, a simple and low-cost lubrication of the planetary gearbox is sufficient.

[0026] Furthermore, the invention relates to a drive train for a wind power installation, which drive train has a rotor shaft connectable to a rotor driven by wind, a motor shaft of an electric machine operable in generator mode, and a gearbox connecting the rotor shaft to the motor shaft in a torque-transmitting manner for converting torque and speed, the gearbox having at least one planetary gearbox which can be configured and developed as described above, and the gearbox particularly having at least two or at least three planetary gearboxes connected in series and which can be configured and developed as described above. By arranging the planet carrier webs in the meshing intermediate region directly below the internal gear, stable support of the planet carrier cheeks and improved lubrication of the planetary gearbox can be achieved in the case of limited installation space, with the result that a drive train with high power density and low installation space requirements is achieved.

[0027] Furthermore, the invention relates to a wind power installation for generating energy from wind, having a free-standing tower, a nacelle attached to the upper end of the free-standing tower, a rotor drivable by wind, an electric machine operable in generator mode, and a drive train received by the nacelle and configurable and developable as described above, the drive train serving to couple the rotor to the electric machine in a torque-transmitting manner and to convert the torque introduced by the rotor. By arranging the planet carrier webs in the meshing intermediate region directly below the internal gear, stable support of the planet carrier cheeks and improved lubrication of the planetary gearbox can be achieved in the case of limited installation space, with the result that a wind turbine with high power density and low installation space requirements becomes possible.

[0028] Another aspect of the present invention relates to an industrial application. The industrial application may have a drive device, which may be configured, for example, as an electric machine driven by wind power, an internal combustion engine, a hydraulic motor, or a rotor. The drive device may be coupled to a gearbox for converting the torque and rotational speed of the power output generated by the drive device. The gearbox of the industrial application has at least one planetary gearbox that can be configured and developed as described above, and the gearbox of the industrial application can in turn be coupled to a mechanical application in a torque-transmitting manner, where the mechanical energy introduced by the gearbox can be used. The mechanical application is, for example, a mill, a vertical mill, a cane press, a cement mill, a crusher, a conveyor belt, a pump, a roller press, a plate conveyor, a tube mill, a rotary kiln, a rotary device, a stirring device, a lifting device, a compactor, an automobile crusher, a shredder for recyclable materials (waste that may be pre-separated and / or sorted), etc. By arranging the planet carrier web in the meshing area directly below the internal gear, stable support of the planet carrier cheek plates and improved lubrication of the planetary gearbox can be achieved in the case of limited installation space, resulting in an industrial application with high power density and low installation space requirements being possible. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Hereinafter, the present invention will be explained by way of example based on preferred exemplary embodiments with reference to the drawings, and the features shown below may represent an aspect of the present invention individually or in combination. In the drawings:

[0030] Figure 1 A schematic perspective view of a wind power device is shown;

[0031] Figure 2 A schematic cross-sectional plan view of a part of the planetary gearbox for a wind power device from Figure 1 is shown;

[0032] Figure 3 A schematic cross-sectional view of a planetary gearbox from Figure 2 is shown;

[0033] Figure 4 A schematic perspective view of the planet carrier of a planetary gearbox from Figure 2 is shown;

[0034] Figure 5 A schematic perspective detailed view of the planet carrier from Figure 4 is shown;

[0035] Figure 6 A schematic cross-sectional view of the planet carrier from Figure 4 is shown;

[0036] Figure 7 A schematic perspective detailed view of an alternative planet carrier for a planetary gearbox from Figure 2 is shown; and

[0037] Figure 8 shows a schematic diagram of an industrial application. Detailed implementation

[0038] Figure 1 The wind power device 10 shown in can be used to generate electrical energy from wind power. For this purpose, the wind power device 10 has a rotor 12, which can be set to rotate in a wind-powered manner. The rotor 12 is coupled to a drive train 14. For this purpose, the rotor 12 is connected to a rotor shaft 16, which is coupled within the drive train 14 to a gearbox 18 to convert the torque introduced via the rotor 12 and the rotor shaft 16. The torque converted in the gearbox 18 is fed to an electric machine 20 operating in generator mode. The electrical energy generated by the electric machine 20 can be fed to a rechargeable battery and / or the power grid. In the exemplary embodiment shown, the drive train 14 is completely housed in a nacelle 22, which is attached to the upper free end of a freestanding tower 24.

[0039] The gearbox 18 has at least one planetary gearbox 26 shown in more detail in Figure 2 and Figure 3 The gearbox 18 particularly has a plurality of planetary gearboxes 26 connected in series. The planetary gearbox 26 has a sun gear 28 that can rotate about the axis of rotation of the planetary gearbox 26 and meshes with planetary gears 30. Specifically, the planetary gearbox 26 is configured as a multi-planetary gearbox having more than three planetary gears 30, which are particularly arranged one after another in the circumferential direction on a common radius with respect to the axis of rotation of the planetary gearbox 26. The planetary gears 30 in turn mesh with the internal tooth system 34 of an internal gear 36 via their external tooth systems 32, and the internal tooth system 34 of the internal gear 36 is arranged coaxially with respect to the sun gear 28.

[0040] The corresponding planetary gears 30 are rotatably mounted on bearing pins 38, which are fastened to a first planetary carrier cheek 40 and a second planetary carrier cheek 42 of a planetary carrier 44. In the exemplary embodiment shown, the bearing pins 38 are captively held in such a way that they are partially inserted via a through hole 48 in the second planetary carrier cheek 42 into a receiving pocket 46 in the first planetary carrier cheek 40.

[0041] The sliding bearing sleeve 54 is inserted onto the bearing pin 38, so that a sliding bearing is arranged between the planetary gears 30. As an alternative, antifriction bearings can be provided instead of the sliding bearings. On their axial sides facing the planetary gears 30, the first planet carrier cheek plate 40 and the second planet carrier cheek plate 42 each have a thrust washer 56, against which the planetary gears 30 can axially abut during operation. The planet carrier 44 can be rotatably mounted relative to the gearbox housing 66 via antifriction bearings 64, and the internal gear 36 is fixedly connected to the gearbox housing 66 for common rotation via a radius region configured as a fastening flange in the illustrated exemplary embodiment. The gearbox housing 66 can be fixed so as not to move or can be rotatably mounted.

[0042] In Figure 4 and Figure 5 the case of the planet carrier 44 shown separately in, the first planet carrier cheek plate 40 and the second planet carrier cheek plate 42 are positioned at a defined distance from each other via the planet carrier web 68. For this purpose, the planet carrier web 68 has a first partial web 70 and a second partial web 72, wherein the first partial web 70 is configured integrally with the first planet carrier cheek plate 40 and the second partial web 72 is configured together with the second planet carrier cheek plate 42, and these partial webs 70, 72 abut against each other, for example, on their axial sides facing each other. The partial webs 70, 72 merge into the respective planet carrier cheek plates 40, 42 at the outer radius of the planet carrier cheek plates 40, 42, but the planet carrier web 68 extends in a slightly radially inwardly curved manner, so that a particularly small spacing a is arranged between the outer side 74 of the planet carrier web 68 and the internal tooth system 34 in the axial region common with the internal teeth 34 of the internal gear 36. In particular, the planet carrier web 68 largely fills the meshing intermediate region 76 generated between the successively arranged planetary gears 30 and the internal gear 36. In particular, the inner side 78 facing the respective planetary gear 30 can follow the outer radius of the associated planetary gear 30, and a gap 80 with a substantially constant gap width can be arranged between the planet carrier web 68 and the planetary gear 30.

[0043] As Figure 6 shown, in its axial intermediate region located radially inside the addendum circle radius of the internal tooth system 34 of the internal gear 36, the diameter d of the outer side 74 of the planet carrier web 68 can be radially inwardly offset relative to the cheek plate outer diameter D of the planet carrier cheek plates 40, 42 to such an extent that the outer side 74 cannot contact the internal gear 36 and is positioned radially outside the inner diameter of the planetary gear 30, in particular radially outside the root circle radius of the external tooth system 32 of the planetary gear 30. In addition, the outer side 74 merges into the respective planet carrier cheek plates 40, 42 via a radius R and at an angle α, without a significant stress concentration effect, wherein the angle α configures a transition edge 82 on the cheek plate outer diameter D.

[0044] As Figure 7 shown, as an alternative to the structure of the planet carrier 44 as Figure 6 shown, the planet carrier cheeks 40, 42 may have a tapered diameter portion 84 of a diameter d to the outer side 74 of the planet carrier web 68 in the circumferential region of the planet carrier web 68. In this case, the tapered diameter portion 84 may merge into the outer diameter D of the planet carrier cheeks 40, 42 in the circumferential direction in a manner similar to the Figure 6 transition shown between the outer side 74 of the planet carrier web 68 and the planet carrier cheeks 40, 42.

[0045] The gearbox 18, which is explained using the example of a wind power plant 10 having at least one planetary gearbox 26, can also be used in another industrial application 86, as Figure 8 shown. The industrial application 86 has a drive device 88, which is configured, for example, as an electric machine, an internal combustion engine or a hydraulic motor. The drive device 88 is coupled to the gearbox 18 in a torque-transmitting manner, and the gearbox 18 transmits the converted torque to a mechanical application 90. The drive device 88 is configured to output a driving force, which is fed to the gearbox 18 via a first shaft 92 and from the gearbox 18 to the mechanical application 90 via a second shaft 94. In particular, the rotational speed of the first shaft 92 is greater than the rotational speed of the second shaft 94. The mechanical application 90 is, for example, a mill, a vertical mill, a cane press, a cement mill, a crusher, a conveyor belt, a pump, a roller press, a plate conveyor, a tube mill, a rotary kiln, a rotary device, a mixing device, a lifting device, a compactor, a car crusher, a shredder for recyclable materials (possibly pre-separated and / or sorted waste), etc.

Claims

1. A planetary gearbox configured as a multi-planetary gearbox for a wind power installation (10), having a planet carrier (44) having a first planet carrier cheek plate (40) and a second planet carrier cheek plate (42), planet gears (30) each rotatably mounted on the first planet carrier cheek plate (40) and the second planet carrier cheek plate (42) via a bearing pin (38), an internal gear (36) meshing with the planet gears (30), an assembly clearance is provided between the outside diameter (D) of the cheek plates of the first planet carrier cheek plate (40) and the second planet carrier cheek plate (42) on the one hand and the inside diameter of the internal gear (36) on the other hand, wherein the outside diameter (D) of the cheek plates is chosen to be so large that the planet carrier cheek plates (40, 42) can only move axially in the radial inner direction past the internal tooth system (34) of the internal gear (36) during the assembly process, and at least one planet carrier web (68) positioning the first planet carrier cheek plate (40) and the second planet carrier cheek plate (42) relative to each other at a defined spacing, characterized in that the radially outwardly directed outer side (74) of the planet carrier web (68) is spaced from the radially inner tip circle radius of the internal tooth system (34) of the internal gear (36) by a more significant range than the first planet carrier cheek plate (40) and the second planet carrier cheek plate (42) are spaced radially inwards, and is arranged radially outside relative to the inside diameter of the planet gears (30) so as to avoid contact with the internal tooth system (34) of the internal gear (36) even taking into account manufacturing and production tolerances and possible thermal expansion effects and / or centrifugal force effects.

2. The planetary gearbox according to claim 1, characterized in that, The radially outwardly directed outer side (74) of the planet carrier web (68) is arranged at least radially outside the root circle radius of the external tooth system (32) of the planet gears (30) relative to a large circumferential range of the planet gears (30), and the circumferential angle region Δα of the planet gears (30) at the root circle radius of the external tooth system (32) extends radially inwards by 270° ≤ Δα ≤ 360° relative to the maximum radially outer region of the outer side (74) of the planet carrier web (68) configured in the axial region common with the internal tooth system (34) of the internal gear (36).

3. The planetary gearbox according to claim 2, characterized in that, The circumferential angle region Δα of the planet gears (30) at the root circle radius of the external tooth system (32) extends radially inwards by 300° ≤ Δα ≤ 345° relative to the maximum radially outer region of the outer side (74) of the planet carrier web (68) configured in the axial region common with the internal tooth system (34) of the internal gear (36).

4. The planetary gearbox according to claim 3, characterized in that, The circumferential angle region Δα of the planet gears (30) at the root circle radius of the external tooth system (32) extends radially inwards by 315° ≤ Δα ≤ 330° relative to the maximum radially outer region of the outer side (74) of the planet carrier web (68) configured in the axial region common with the internal tooth system (34) of the internal gear (36).

5. The planetary gearbox according to any one of claims 1 to 4, characterized in that, The planet carrier web (68) has a first part web (70) and a second part web (72), the first part web (70) being configured integrally with the first planet carrier cheek plate (40), and the second part web (72) being configured integrally with the second planet carrier cheek plate (42).

6. The planetary gearbox according to claim 5, characterized in that, The first part web (70) and the second part web (72) bear against each other in the axial direction.

7. The planetary gearbox according to claim 5, characterized in that, The first part web (70) and / or the second part web (72) merge into the first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42) substantially at the cheek plate outer diameter (D) in a manner axially spaced apart from the internal gear (36), and the outer side (74) of the planet carrier web (68) provided in the axial region common with the internal gear (36) merges into the first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42).

8. The planetary gearbox according to claim 7, wherein, The outer side (74) of the planet carrier web (68) provided in the axial region common with the internal gear (36) merges into the first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42) via a curved and / or radius-shaped transition region.

9. The planetary gearbox according to claim 5, characterized in that, The first planet carrier cheek plate (40) and the second planet carrier cheek plate (42) have a tapered diameter portion (84) of the radius to the radially outwardly directed outer side (74) of the planet carrier web (68) in the circumferential region common with the planet carrier web (68), and the tapered diameter portion (84) merges into the cheek plate outer diameter of the first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42).

10. The planetary gearbox according to claim 9, characterized in that, The tapered diameter portion (84) merges into the cheek plate outer diameter of the first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42) via a curved and / or radius-shaped path and / or at an angle configuring a transition edge.

11. The planetary gearbox according to one of claims 1 to 4, characterized in that, The planet carrier web (68) extends radially inwards at least as far as the inner diameter of the planet gear (30).

12. The planetary gearbox according to claim 11, characterized in that, The planet carrier web (68) extends radially inwards at least as far as the rotational axis of the planet gear (30).

13. The planetary gearbox according to any one of claims 1 to 4, characterized in that, A spacing a is provided between the internal tooth system (34) of the internal gear (36) and the radially outwardly directed outer side (74) of the planet carrier web (68) in the axial region common with the internal tooth system (34) of the internal gear (36): 3.0 mm ≤ a ≤ 8.0 mm.

14. The planetary gearbox according to claim 13, characterized in that, The spacing a is 4.0 mm ≤ a ≤ 7.0 mm.

15. The planetary gearbox according to claim 14, characterized in that, The spacing a is 5.0 mm ≤ a ≤ 6.5 mm.

16. The planetary gearbox according to claim 15, characterized in that, The spacing a is 5.5 mm ≤ a ≤ 6.0 mm.

17. The planetary gearbox according to one of claims 1 to 4, characterized in that, A gap (80) is provided between the planet carrier web (68) and the respective adjacent planet gear (30), the gap having a gap width s that is substantially constant between the planet carrier web (68) and the respective adjacent planet gear (30), and in the case of the outer diameter d of the planet gear (30) a the following applies: 0.01 ≤ s / d a ≤ 0.

5.

18. The planetary gearbox according to claim 17, characterized in that, 0.03 ≤ s / d a ≤ 0.

2.

19. The planetary gearbox according to claim 18, wherein, 0.05 ≤ s / d a ≤ 0.

1.

20. The planetary gearbox according to one of claims 1 to 4, characterized in that, At least three planet gears (30) are provided, with one planet carrier web (68) provided in each case.

21. The planetary gearbox according to claim 20, wherein, At least six planet gears (30) are provided.

22. The planetary gearbox according to claim 21, characterized in that, At least seven planet gears (30) are provided.

23. The planetary gearbox according to claim 22, characterized in that, At least eight planet gears (30) are provided.

24. The planetary gearbox according to claim 20, characterized in that, One planet carrier web (68) is provided between each pair of planet gears (30) following one another in the circumferential direction.

25. The planetary gearbox according to any one of claims 1 to 4, characterized in that The first planet carrier cheek plate (40) and / or the second planet carrier cheek plate (42) has a thrust washer (56) for the axial extension of the planet gear (30).

26. The planetary gearbox according to any one of claims 1 to 4, characterized in that, A sliding bearing is arranged between the planet gear (30) and the bearing pin (38).

27. The planetary gearbox according to any one of claims 1 to 4, characterized in that, The outer side (74) of the planet carrier web (68) extends at a substantially constant spacing from the addendum circle radius of the internal tooth system (34) of the internal gear (36) at least in a part of the circumferential angle region occupied by the outer side (74).

28. The planetary gearbox according to any one of claims 1 to 4, characterized in that, The planet carrier (44) is mounted in the gearbox housing (66), and the lubricant for lubricating the internal gear (36) and the planet gear (30) is received in the gearbox housing (66).

29. The planetary gearbox according to claim 28, wherein, The lubricant for lubricating the internal gear (36) and the planet gear (30) is received in the gearbox housing (66) by immersion lubrication and / or splash lubrication.

30. A drive train for a wind power installation (10), the drive train having: a rotor shaft (16) which can be connected to a rotor (12) driven by wind; a motor shaft of an electric machine (20) which can operate in generator mode; and a gearbox (18) which connects the rotor shaft (16) to the motor shaft in a torque-transmitting manner to convert torque and rotational speed, the gearbox (18) having at least one planetary gearbox (26) according to one of claims 1 to 29.

31. The powertrain according to claim 30, characterized in that, The gearbox (18) has at least two or at least three planetary gearboxes (26) according to one of claims 1 to 29 connected in series.

32. A wind power installation for generating energy using wind, having an independent tower (24), a nacelle (22) attached to the upper end of the independent tower (24), a rotor (12) which can be driven by wind, an electric machine (20) which can operate in generator mode, and a drive train according to claim 30 or 31, the drive train being received by the nacelle (22) for connecting the rotor (12) to the electric machine (20) in a torque-transmitting manner and converting the torque introduced by the rotor (12).

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