WO2012146382A1

WO2012146382A1 - Device for transmitting rotational energy, and wind energy plant which is equipped therewith

Info

Publication number: WO2012146382A1
Application number: PCT/EP2012/001817
Authority: WO
Original assignee: Imo Holding Gmbh
Priority date: 2011-04-28
Filing date: 2012-04-27
Publication date: 2012-11-01
Also published as: EP2702298A1; CN103635713A

Abstract

The invention is directed firstly to a gear mechanism for distributing the input torque from a drive to two or more outputs, comprising one or two rotationally symmetrical connection elements with in each case one flat connection surface for the rotationally fixed connection to two different machine or system elements or firstly to a machine or system element and secondly a chassis or foundation, wherein the two rotationally symmetrical connection elements are oriented in such a way that their axes of symmetry run coaxially with respect to one another and their connection surfaces face away from one another, wherein, furthermore, a gap is situated between the two connection elements, in which gap at least one anti-friction bearing is arranged as main bearing for mounting the two connection elements on one another, such that they can be moved rotationally about a main-bearing rotational axis which corresponds to the common axis of symmetry of both connection elements, and wherein at least one circumferential surface of a connection element is provided with a serration which runs around it, and wherein the non-serrated connection element has a section which faces the serration of the serrated connection element and has one or more cavities which are open towards the serration for receiving toothed gearwheels, wherein an end-side opening is provided in the non-serrated connection element for each gearwheel for discharging the respective output torque, and, approximately aligned with said opening, at least one closed annular region for supporting a bearing, which is arranged in the axial direction between the connection surfaces of the two connection elements, for the relevant gearwheel as the wheel bearing thereof, with the result that the relevant gearwheel rotates about an auxiliary rotational axis which is offset eccentrically with respect to the main-bearing rotational axis but is approximately parallel thereto, and meshes with the serration of the serrated connection element; and secondly is directed to a wind energy plant which is equipped with a gear mechanism of this type.

Description

Device for the transmission of rotational energy

as well as equipped wind turbine

On the one hand, the invention is directed to a transmission having more than two rotary connections, preferably for distributing an input torque from one drive to two or more outputs, in particular for distributing the torque at the hub of a wind turbine to two or more connected generators or energy converters comprising two rotationally symmetrical connection elements, each with a flat connection surface for non-rotatable connection to two different machine or system elements or a machine or system element on the one hand and a chassis or foundation on the other hand, wherein the two rotationally symmetrical connection elements are aligned such that their axes of symmetry coaxially to each other and their pads are facing away from each other, wherein there is also a gap between the two connecting elements, wherein at least one rolling bearing is arranged as a main bearing for supporting the two connecting elements to each other, dre hbeweglich about a main bearing axis of rotation, which corresponds to the common axis of symmetry of both connecting elements, and wherein at least one lateral surface of a connecting element is provided with an all-round toothing; and on the other to a wind turbine with a preferably about an axis extending in the wind direction rotating wind turbine whose rotor is coupled via such a transmission with two or more connected generators or energy converters for power transmission, the transmission has two rotationally symmetrical, preferably annular connection elements, each with at least one flat connection surface for the rotationally fixed coupling to the rotor of the wind turbine on the one hand and to the chassis of the nacelle on the other hand; and also to an energy system with an energy transfer assembly.

CONFIRMATION COPY So far known according to the prior art and in particular prevailed in international markets wind energy or power plants (WKA) with multiple leaves or wings, which are adjustable within the azimuthal plane, and their rotor blades can be rotated in and out of the wind, thus to cause the maximum yield of energy intake. Modern wind turbines are therefore adjustable in wind direction tracking and pitch (single blade adjustment). Such modern wind turbines, consisting essentially of a rotatable nacelle, to which the hub with leaves / wings are attached, and a tower on which this nacelle is mounted, thus serve the technical principle of energy from the wind-induced flow movement resulting rotation of the hub first to transfer into another mechanical energy and then convert it into the electrical energy form usually. In most cases, generators are used for the latter, which are either mounted directly on the shaft of the rotating hub or drive a generator via a main gear. The coupling element between the hub and the generator is usually a main transmission as a transmission element, which may optionally be designed as a planetary gear. As a rule, the hub, which is moved by wind power, drives a main gearbox and subsequently connects a generator. (In gearless, however WKA drives the hub moved by wind power directly to a downstream generator).

Thus, for example, DE 103 189 45 describes such a gear arrangement, referred to above as planetary gear, for a wind turbine (WKA), with a planetary gear rotatably mounted planetary gears mounted in a fixed planet carrier plate planetary gears and a sun gear, the special requirements for the Zahneingriffsgüte due to the great external forces and moments will do justice. Characteristic of planetary gears when used in power plants, such as wind turbines, is that a in the center (where the main axis of rotation is) a shaft is mounted, which is usually coupled to a sun gear of the planetary gear.

It is always conceivable that the transmission and generator form a coupled unit, as shown in the gear-generator combination for wind turbines in the megawatt range of the patent document EP 0811764. This involves a gearbox-generator combination with a single-stage planetary gearbox, where the rotor speed is of the order of 15-20 rpm, the gear ratio of a single-stage gearbox is between 5 and 8, and the rated speed of the generator is between 75 and 75 and 150 rpm. This makes it possible to combine a fully enclosed generator with a light, low-maintenance gear, the Vorerfinder further speaks of a commercially available "Schiffswellenelektrogenerator".

An alternative form of the very new development efforts in the wind energy industry is not to couple gearbox and generator experimentally directly, but for weight reasons no longer integrate the generator assemblies in the nacelle or in the tower structure of the wind turbine, but to place as detached as possible, so in the gondola arrangement are integrated with lower masses. In general, lower moving masses require lower moment of inertia and thus lower force effects than large moving masses. If now the moving masses are smaller within a gondola of a wind turbine, this gondola could build with a smaller mass, be made slimmer and thus possibly also optimized flow dynamic optimized.

The publication by N. Vatheuer, J. Schmitz, and H. Murrenhoff (eds) of the RWTH Aachen, ATK 2011: "Hydrostatic Drive Train in Wind Energy Plants" from the year 2011 reveals a concept whereby the generator is not in the nacelle is placed outside, but also sees this concept Hydromotors and hydrostatic transmission to transmit forces and moments. A planetary gear is not provided. The idea is to couple the wind turbine (hub) directly with a slowly rotating radial piston pump and convert the mechanical power into a high pressure flow.

This arrangement of the RWTH Aachen offers no integrated overall arrangement with only one machine element, which meshes with the spur gears and simultaneously carries one (or more) career (s).

A major disadvantage of the aforementioned concept is that the schematically illustrated combination of respective spur gear and hydraulic module per se is not protected against intrusion from the outside. From the disadvantages of the prior art described results in the invention initiating problem to create a total module with freedom and thus increased accessibility to the most direct energy transfer for modern energy systems, especially WKAs. This should be modular in the overall system intergrierbar and as easy to install and remove.

The solution to this problem is achieved in that the untoothed connection element has a toothing of the toothed connection member facing portion with one or more, the teeth towards open cavities for receiving toothed gears, wherein in the untoothed connection element for each gear an end opening for discharging the respective output torque is provided, as well as with this approximately aligned at least one closed annular region for supporting a arranged in the axial direction between the pads of the two connection elements storage for the relevant gear as the wheel bearing, so that the relevant gear eccentric offset from the main bearing axis of rotation, but for that rotates about parallel sub-axis of rotation and meshes with the teeth of the toothed connection element.

This integrated overall arrangement basically offers the possibility of freedom from the center and only requires a single, annular machine element in the form of the toothed connecting element, of which all gear wheels tap their torque. In this case, the entire energy transmission unit can be designed as a closed system. Since the gears generally have a significantly smaller diameter than the teeth of the toothed connection element and therefore significantly fewer teeth, simultaneously with the torque distribution and a Drehzahlüber- a torque reduction, so that from the slow speed of the hub of a wind turbine results in a faster rotational movement , which is in a much cheaper for electric generators speed range. D _G / D _A for the speed ratio n _G / n _A and the torque ratio between the drive AN and the output AB with the same module of the teeth involved in particular the ratio between the number of teeth z _A of the teeth on the toothed connecting element on one hand and the number of teeth z _G the transmission gears on the other hand of importance; for the torque also the number n of the transmission gears: n _G / n _A = z _A / z _G ;

D _G / D _A = z _G / (n * z _A ).

With suitable dimensioning of these parameters z _A , z _G , therefore, the interposition of other transmission stages is unnecessary.

Another advantage is the increased ease of assembly and disassembly of the invention, since you only need a substantially closed power transmission unit, including all power transmitting Elements, possibly under separate design of retrofit or flange-mounted hydraulic modules or electrical modules.

The following is based on the definition that a so-called "pinion" is the smaller moving wheel of a "tooth-tooth gap pairing": In particular, it is proposed in the sense of the invention, instead of using the spur gears in each case much smaller pinion; In the present case, therefore, the shorter term "pinion" can be used instead of the term of the transmission gears, since its diameter is smaller than that of the toothing of the toothed connection element.

The terms "roller bearings" and "large roller bearings" respectively refer to torque bearings of mechanical and plant engineering, which can accommodate both axial, radial and tilting moment loads. Exactly these moment bearings are in this present invention.

The terms "housing" and "Gondelumhausung" are used interchangeably below to the term "machine house of a WKA" and stand for the respective machine carrier of the relevant energy system.

Overall, the invention is therefore not an interconnection of individual components and combinations, as described above in the prior art, but a cylindrical or annular energy transfer assembly, in particular as a complete assembly ready to install.

The present invention as part of an energy system, as ready to install overall arrangement for transmitting energy from mechanical forces and torque from the drive side to the output side, thereby has at least one Hauptwälzlagerring, in particular as an inner or outer ring of a multi-row slewing or moment bearing, and has at least one the output energy forwarding Main rolling bearing ring, in particular as an inner or outer ring of a multi-row large roller bearing or moment bearing, and further has at least one raceway with rolling elements, wherein the respective at least one career, the Hauptwälzlagerringe rotatably supported against each other. It is characteristic that exactly one of the mechanical elements present for the transmission of energy from mechanical forces and moments from the drive side to the output side (exactly one of the main rolling bearing rings) is toothed and at the same time carries at least one of the named raceways. In particular, it is also characteristic that the energy transfer assembly has center-freedom, ie, has a central opening around the main pivot axis, which of course can optionally be closed by cover plates or other housing, but also allows simplified access, for example, to the hub of a wind turbine , Control cables, etc. can also be placed in this center. In large versions of a transmission according to the invention, the hub is even passable through the middle passage, so that a service technician can get from the side of the machine carrier to the hub, and from there possibly further into the rotor blades and thus all the essential parts of a wind turbine can reach.

In this case, one of these connection elements or Hauptwälzlagerringe be fixed to the nacelle or the nacelle of a wind turbine or on a chassis; his main pivot bearing then carries the rotor hub and thus the entire wind turbine and thus serves as a rotor or main bearing of the wind turbine, thus derives, for example, the weight in the engine house, while in particular tapped by the wind drive torque tapped by means of the gear teeth according to the invention and for the connected energy converter Generators is split, wherein at the same time an increase of the speed and thus an adaptation to the energy converter used takes place. In a wind turbine, the distribution gearbox according to the invention between the hub on the one hand and machine carrier (tower side) is used on the other hand, the transmission except for - possibly with the exception of a central opening around its main or center axis - is surrounded by a housing preferably at least one side.

The connection elements are designed in the manner of an inner and outer ring of a preferably multi-row large roller bearing, each having at least one raceway for rolling elements, so that the connection elements are rotatably mounted against each other, forming a bearing gap.

In this case, at least one connection element is fixed in place, for example, coupled to the machine carrier or the nacelle housing a wind turbine or coupled. Likewise, at least one connecting element with a driving system element, for example, with the hub of a wind turbine, coupled or coupled.

One of the connecting elements absorbs the torque on the drive side and divides this on the coupled by means of meshing engagement with its teeth gear wheels.

Since a plurality of rotatably mounted gear wheels are provided around the main axis of rotation on the untoothed connecting element, which preferably all have the same diameter and thus also the same number of teeth z _G and consequently have approximately the same distance from the center axis, the load distribution is symmetrical, ie when coupling the same components as respective load, the input power P _e symmetrically distributed on all of these assemblies as each have the same output power P _A:

PA = E n, so that neglecting friction losses:

PE = n ^* P _A.

Also noteworthy is serving as a pinion gear housing element: A pinion, in particular each of the existing pinion can be partially enclosed by a separate pinion housing, but is at least radially completed from the main axis of rotation, so that the respective pinion against physical interference from the radial center of the Cylindrical or annular overall arrangement is protected here. In particular, the protective effect should be such that the pinion housing essentially allows only the engagement between the elements meshing with each other. The pinion housing can be made in one piece or several pieces, in particular, a design as a concentric around the center axis housing ring is conceivable. This can be integrated with the untoothed connection element or be connected to this, for example on and unscrewed or flanged. Of course, this acting as a pinion housing ring portion can also be designed as a coaxial extension of the relevant connection element itself, in particular as a single casting.

For receiving the Getrriebezahnräder or pinion recesses and / or holes may be provided, ie exactly where a pinion to be inserted during assembly or disassembly.

The drive-side cover plate is not physically connected to the pinion housing, but preferably anaeschlossen rotationally fixed to the toothed connection element. Therefore, within the enclosure thus enclosing, there remains a gap with the pinion housing not rotating with the drive side with the pinion housing rotating, which ensures smooth rotatability between these elements. Preferably, the toothing is arranged on the radially inner circumferential surface of the inner ring, so that the transmission gears are located radially within the inner ring and the transmission according to the invention has only a minimal space requirement. Incidentally, this smaller design is usually accompanied by a lower weight, which is not insignificant in wind turbines.

The untoothed connection element is configured in such a case in the manner of a non-toothed outer ring of a large roller bearing and can be assembled from several parts, if this is necessary or advantageous for assembly reasons, for example.

Between these two connection elements there is a gap, for whose sealing a sealing system can be present, preferably in the form of an annular sealing system, for example comprising at least one circumferential sealing ring with at least one sealing lip, or else comprising a system of two or more arranged in the gap direction one behind the other sealing rings. A complete seal of the entire transmission makes it possible to fill it with a lubricant, preferably lubricating grease, partially or completely, in order to optimize its running properties.

It is also in a further embodiment of the invention that the housing part is designed as a dynamically loaded component of a Hauptwälzlagerringes a large rolling bearing on the career of the rolling elements, such as rollers, ball, cylinder, tons, or tapered rolling elements roll. If said housing part is designed as an integral part of an untoothed outer ring of a slewing bearing, such as a three-row roller bearing, and thus positively or positively or positively and non-positively coupled to the outer ring or at least can be coupled, so it can even together with the toothed outer ring of this large rolling bearing be designed as a single, zusammenschraubbares, part.

It has proved to be favorable that the toothed connection element is constructed in one piece, whereby on the one hand the assembly is simplified and on the other hand, the relevant connection element receives maximum stability.

Preferably, at least one raceway for a row of rolling elements of the main bearing is arranged on one of the toothing opposite lateral surface of the toothed connection element. A division of career on the one hand and toothing on the other hand on two lateral surfaces has the consequence that with minimal gearbox height maximum meshing engagement is possible and zugeleich also a possibly multi-row main storage. The invention is further characterized by in the toothed connecting element distributed in a hexagonal arranged fasteners, in particular in the terminal surface opening blind holes with internal thread, which is preferably arranged in the radial direction between the teeth and at least one raceway for a row of rolling elements of the main storage. This makes it possible to anchor the relevant connection element by means of (fastened) in these fasteners (machine) screws or (stationary) bolt on a machine or system part or on a chassis or foundation. It has proved to be favorable that the toothing and / or the raceway (s) for the row of rolling elements (s) of the main bearing and / or the fastening elements, in particular blind holes with internal thread, formed by machining or shaping of the same connection element body. In particular, when these machine elements are incorporated in a common clamping of the body, a maximum of precision can be achieved. The invention can be further developed to the effect that on one of the toothing opposite lateral surface of the toothed connection element, a all-round collar is provided on which one or more raceway (s) is arranged for the rolling elements of the main bearing (are). Such a collar has a pointing in the radial direction, cylindrical edge surface and two facing in different axial directions, each flat annular surfaces, which can absorb as the top and bottom of the federal pressure forces in different axial directions. Overall, a variety of radial and axial forces and tilting moments can record.

The main bearing may have several rows of rolling elements, for example. To increase the carrying capacity and / or to provide for special load cases each own, specially adapted rolling elements.

Thus, the invention recommends that the main bearing has at least one thrust bearing with at least one row of rolling elements whose support angle is equal to or greater than 45 °. Due to their large support angle such rolling elements are optimally equipped for the transmission of axial forces and for the absorption of tilting moments.

Furthermore, it is within the scope of the invention that the main bearing comprises a radial bearing with at least one row of rolling elements whose support angle is less than 45 °. These rolling elements are optimized for special loads, namely for about radial loads.

In a preferred embodiment of the invention, the main bearing comprises at least one row of elongated rolling elements, such as roller, barrel, needle or conical rolling elements. Such rolling elements generally have a higher load capacity than spherical rolling elements of comparable size. An advantageous embodiment of the invention is that the toothed connection element is encompassed by the untoothed connection element on one of its end faces and on its two lateral surfaces. This makes it possible to use both lateral surfaces of the toothed connection element for the exchange of forces and / or torques between the two connection elements; At the same time, the not encompassed end face of the toothed connection element remains free for the exchange of forces and / or torques with a machine or system part connected thereto.

The transmission according to the invention undergoes further optimization by fixing elements arranged in a ring-shaped manner in the untoothed connecting element, for example holes opening in its connection surface, in particular blind-hole bores with internal threads, which are preferably arranged in a section facing away from the toothing of the toothed connecting element. This creates a simple and at the same time highly resilient connection option. An alternative to toothed blind holes are untoothed through holes.

Further advantages are obtained in that the raceway (s) for at least one row of rolling elements of the main bearing and / or the fastening elements, for example blind holes with internal thread, are formed by machining or shaping a common (partial) body of the untoothed connecting element. On the one hand, this measure leads to a maximum of precision; On the other hand, so that the raceways can be kept free of any joints along its entire circumference, which can achieve a longer service life. Another design rule states that the untoothed connecting element in its cross-sectional area facing away from the toothing has an approximately aprotic or cross-sectionally approximately L-shaped cross-section. or even C-shaped track portion having at least one, preferably directly incorporated raceway for a row of rolling elements of the main storage. Its cross-sectional shape depends primarily on the number and type of rolling element rows used. For example, in a single-row or multi-row four-point bearing, a skirt-like shape would suffice, while a C-shaped cross-section might be preferable in the case of a more load-bearing roller bearing with a radial row and two axial rows. According to the invention, the cross-section of the untoothed connecting element may have at least one annular disk-shaped connecting portion which engages around the end face of the toothed connecting element. This is primarily responsible for non-rotatably and dimensionally stable to connect the gear teeth receiving gear section of the untoothed connection element with its raceway section beyond the toothed connection element.

The invention prefers an embodiment in that the non-toothed connection element in its toothing facing cross-sectional area has an approximately aprotic or cross-sectionally approximately L-shaped gear portion, which adjoins the annular disc-shaped portion and engages or receives the gears. The transmission gears should be mounted primarily in recesses of the connecting part; a apron-shaped gear portion would surround the gears at their main axis of rotation facing lateral surface and therefore protect against interventions from this direction ehr, which is particularly important if the gear is not completely closed by cover plates, but mid-free. In addition, in the case of an L-shaped cross-section, the gear part also has a flat, annular disk-shaped section which extends parallel to the likewise plane annular disk-shaped connecting section. In the overlapping area of these two planar sections are the Gear wheels arranged such that their axis of rotation passes through both sections. This makes it possible to store a transmission gear in both mutually flat sections. For assembly reasons, it may be advantageous if the untoothed connection element is composed of several parts, for example of at least one raceway part, a connecting part and a transmission part. Since the untoothed connection element on the one hand umgeift the toothed connection element on three sides and on the other hand should store the gears, it receives a very complex overall shape, which can be produced either as a casting due to undercuts neither with a reasonable effort by machining. This complex shape can be subdivided into simpler parts for ease of manufacture, which can be made of simple basic bodies by machining or even manufactured as castings.

In the context of a first embodiment of the invention, the transmission section has an approximately L-shaped cross-section with an all-round cavity for common reception of all gears. Although in this embodiment the gear section itself has a particularly simple geometry; However, together with the connecting portion results in an undercut, which makes a one-piece production as a casting difficult or even impossible. But if the gear portion and the connecting portion made separately and joined together, so you can either produce the simple geometry of each of the two parts as a casting or obtained from simple bodies by machining and / or joining. In the latter case, the transmission part with L-shaped cross-section, for example. By welding a flat, annular disc-shaped part with a skirt-shaped or cylinder jacket-shaped part are made. Another embodiment of the invention is characterized in that the gear portion has a varying approximately in the azimuthal direction cross-section with a plurality of spaced apart by intermediate webs cavities for receiving one gear. Although these webs are not essential for the dynamic function of the transmission; However, they can increase the dimensional stability by angularly mutually extending ring sections are stiffened against each other. Such webs are created simply by the fact that the individual compartments, which each accommodate a single gear wheel, are drilled with mutual distances in a solid annular body, preferably in the axial direction. It is important to ensure that these holes are not placed in the radial direction on the center of the ring in question, but moved to that lateral surface, which is the teeth of the toothed connection element closest, at least so far that the remaining distance of Bohrungsmittelachse to the respective lateral surface is smaller than the radius of the bore. This has the consequence that the individual compartments are each open to the respective lateral surface and thus enable a meshing engagement between the gear wheels on the one hand and the toothing of the toothed connection element on the other. fWeiterhin it is provided that is provided at the connecting portion or part an annular axis closed about a secondary rotational axis edge region for supporting a wheel bearing for the relevant gear. In this case, the / preferably annular disc-shaped connecting portion or part serve as a shield to optimally support the wheel bearing in question. It has been proven that on the transmission section or part an annular region closed around a secondary rotation axis is provided for supporting a wheel bearing for the respective gear wheel. There can be one (Second) wheel bearings are arranged, which gives the gear particular stability.

As wheel bearings are preferably (radial) ball bearings use, especially four-point ball bearings. These offer the advantage that all kinds of forces and moments can be absorbed with only a single row of rolling elements, ie in particular radial and axial forces and tilting moments.

To realize the wheel bearings, the invention makes use of prefabricated rolling bearings with their own raceway rings, the outer raceway ring of which is inserted into the relevant, annularly closed edge region of the untoothed connecting element. In view of the comparatively small diameters of the gear wheels, this measure should in most cases be simpler than the incorporation of the raceways into the connecting element itself.

To fix the outer race ring of a wheel bearing, the invention provides an attached and fixed to the untoothed connection element mounting ring with a tapered inner cross-section, which is fixed in the axial direction of the untoothed connection element, for example. Screwed into an all-round internal thread. Due to its tapered inner diameter, such a fastening ring surrounds in any case the outer ring of a roller bearing in the axial direction and can therefore press this in the axial direction to a second, preferably similar storage.

If an inner raceway ring of a wheel bearing is received in a groove running all the way around the periphery of an end face of the relevant gear wheel, then the gear wheel can not only be guided in the radial direction, but also be positioned in the axial direction. Between the lateral surface of a gear and the two end faces should ever be provided a running around groove, wherein only the radially enlarged cladding region between the two grooves is interlocked. Each bearing placed in such a groove can transmit radial forces to the tapered wheel portion as well as axial forces in the direction of the radially expanded central region. In order to avoid contact with a local toothing, the flat surfaces of these grooves may be provided with an axial step, so that the radially widened and toothed peripheral region with respect to the respective groove in the axial direction recedes.

To transmit the output torque to a non-rotatably connected machine or system part, the invention provides in a front side of a gear at least one connection element, in particular a blind hole, the inner cross-section has at least one radial extension or taper, so that a rotationally fixed connection is possible. If such has a standardized or standardized cross-section, a connection of any system is possible. In this case, different gears with different cross-sectional shapes of the connection element can be kept ready and used as needed to achieve a match to the respective units to be connected. For training a Drehschlusses can bpw. a circumferential toothing be provided, or even a groove extending in the axial direction, wherein a wedge is inserted, etc.

A provided on the untoothed connection element concentric to each sub-axis or fixable base element is used to anchor the housing of a non-rotatably connected to the gear machine or equipment part. For this purpose, in particular a rotationally fixed anchoring, the base element may have radially forward or backward jumping elements and / or screw connections od. Like. The region radially within an annular connection element can be closed by a cover, preferably approximately in the plane of the respective connection surface. As a result, a larger cavity can be created with minimal effort, which can serve as a reservoir for the Schmeirmittel used. Therefore, a large supply of lubricant can be filled in, and consequently, the intervals within which the lubricant must be exchanged can be made larger than without such a supply.

Furthermore, it is the teaching of the invention that the teeth of the toothed connection element is located on the inside. This makes it possible to arrange the pinions radially inside the toothed connection element, whereby the arrangement is particularly space-saving, while maintaining a high transmission ratio. In addition, the two large, annular connection elements can protectively surround even the rather smaller gear wheels or pinions so that damage is scarcely to be feared even in extremely harsh operating conditions. To make the power transmission on the output side ring around the center axis of the power plant and thus ensure symmetrical power and torque distribution, an imaginary, uniform traverse should give a polygon under connection of all sub-axes of rotation or symmetry centers of the pinion, which is stronger a ring shape approximates as a quadrilateral.

In particular, each of these pinions has standardized dimensions, in particular to ensure rapid interchangeability during operation. The thickness of the housing part can be at least 5 mm, where the pinions are positioned, but usually between about 50 mm to 150 mm, in large and heavy Anlagenfomen also up to 250 mm. There are more than four such pinions, for example, eight or more such pinion, but usually ten or more of such pinions, which (as mentioned above) are arranged concentrically and symmetrically about the center axis of the WKA. In addition, these pinions are evenly spaced from each other, wherein the distance angle is designated by angle PHI. If there were ten concentric pinions which were equally spaced, this angle would be 36 degrees each.

The existing pinion according to the invention should have identical dimensions and design, in particular a cylindrical design with an outer diameter of at least 100 mm, for example of 200 mm or more, in particular between 200 mm to 400 mm, with a height of at least 100 mm, for example of 250 mm or more, especially from about 300 mm to 500 mm.

The at least one-side closed housing having a central opening about its center axis may be made in one piece or in several pieces, wherein the multi-piece embodiment contains at least one cover plate which can be connected to the housing part. This at least one cover plate may be of lesser thickness than the housing part, in particular of less than 50 mm thickness, and wherein this cover plate may be detachably connected to the housing part, in particular by means of screw connections can be releasably connected. However, it is also conceivable according to the invention to design everything in one piece, so that this plate is inseparable from the housing part and rather is designed as a unit.

The transmission according to the invention can have a central, for example annular, opening on a first side, wherein this opening is generally arranged centrally about a center axis. On the opposite side, a second side, in particular on the opposite side, a second cover plate may be present parallel to the housing contour of the first side. This second cover plate can from lesser strength than the housing part, for example, of lesser thickness than 50 mm, and this cover plate may be detachably connected to the housing part, or else be releasably connected in particular by means of screw connections. Again, it is possible according to the invention to design everything from a single source.

Another characteristic of the invention is that this parallel distance between the outer housing contour of the first side and the outer housing contour on the second (opposite) side should be at most twice the size of the present in the interior space between the two housing contours height of each pinion. For example, or in particular, this annular energy transfer assembly according to the invention between the two outer housing contours is approximately between about 200 mm and about 1000 mm wide.

The rotor of a wind turbine according to the invention with a preferably about an axis extending in the wind turbine axis is coupled via an inventive transmission with two or more connected generators or energy converters for power transmission, the transmission has two rotationally symmetrical, preferably annular connection elements each having at least one flat pad for the rotationally fixed coupling to the rotor of the wind turbine on the one hand and to the chassis of the nacelle on the other hand, wherein the two connection elements are aligned such that their axes of symmetry are coaxial and their preferred pads are facing away from each other, wherein there is also a gap between the two connecting elements, wherein at least one roller bearing is arranged as a main bearing for supporting the two connection elements to each other, rotatably about a main bearing axis of rotation, which of the common Symmetriachse corresponds to both connecting elements, and wherein at least one lateral surface of a connecting element is provided with an all-round toothing, and wherein the untoothed connecting element a The toothing of the toothed connecting element facing portion having one or more, to the toothing open cavities for receiving toothed gears, wherein in the untoothed connection element for each gear an end opening is provided, whereby its rotationally fixed coupling to a respective generator or energy converter possible is, as well as thus in an axial alignment at least a closed annular region for supporting a arranged in the axial direction between the contact surfaces of the two connecting elements bearing for the relevant gear as the wheel bearing, so that the relevant gear eccentric offset from the main bearing axis of rotation, but this rotates about parallel sub-axis of rotation and meshes with the teeth of the toothed connection element.

Such an arrangement is approximately synonymous with an overall arrangement consisting of an energy system, in particular a wind turbine, and a cylinder or ringfömigen energy transfer assembly according to the invention for transmitting energy from mechanical forces and moments from a drive side to a driven side as part of this energy plant neither the power transmission assembly nor the power plant has central transmission or sun gears which overlay and rotate about the main or center axis; such an overall arrangement comprises:

a plurality, at least four, preferably three per quarter of a circle, distributed around the main or center axis and each separately fixedly attached to the housing part on the driven side or fixedly mounted, each rotatable about its own axis of symmetry pinion with equidistant distances to the center axis,

at least one two- or multi-row main storage in the manner of a large rolling bearing inside the energy transfer assembly according to the invention, for example, including cylindrical Rolling elements in cross-sectionally orthogonally oriented raceways,

a housing of which the energy transmission assembly according to the invention is enclosed at least on one side, in particular for protecting the at least one two- or multi-row slewing bearing before external engagement, for example, with additional attachment of several parallel aligned cover plates, the main bearing at least one Hauptwälzlagerring outer ring, and at least having an energy-conducting inner main rolling bearing ring, wherein the inner main rolling bearing ring the

Forces and moments of the drive side receives and transmits to the output side by means attached directly to the Hauptwälzlagerring, juxtaposed and annularly arranged around the center axis, toothed and meshing elements, in particular in the form of a toothing, wherein a direct or indirect coupling of the at least one Hauptwälzlagerrings with the housing part exists on the output side, in particular with the housing or with the machine frame, and wherein a direct or indirect coupling of a Hauptwälzlagerrings, preferably the other, with the drive side, for example with the hub of a wind turbine.

Here, the term "energy plant" is to be understood as a plant whose primary purpose is the extraction or utilization of energy, in particular by conversion of other forms of energy such as wind or water power or stored chemically in the form of fossil fuels energy into electrical energy ,

The invention is further distinguished by the freedom of the middle and the compactness of the overall arrangement. In particular, a low overall height L of the transmission according to the invention with a large diameter D at the same time is advantageous, for example with a ratio D / L> 3, wherein the diameter D preferably about 3 m or greater, while the height L is preferably about 0.5 m or smaller.

The pinions each have on at least one end face via a central concentric opening, which is adapted to accurately record a centrically arranged shaft fit and rotationally rigid to be able to transmit rotational movements with the intention. Each of such existing pinion provides at least at one point of its peripheral contour, but in particular at two different locations (above and below) on the peripheral contour, mounting options, where the attachment of each pinion bearing is possible, especially as a rotary joint bearing.

In particular, the attachment of a drive-side pinion bearing and an output side hub / tower side storage on the nacelle side layer is being considered. It is important in the sense of this bearing (s) that these bearings neither touch nor contact the circumferential meshing elements of the pinion, but are appropriately spaced from the peripheral meshing elements of the respective pinion. According to the invention, the existing pinions are in each case directly coupled or couplable, in particular coupled or connectable via a separate shaft, with at least one power conversion unit (unit) which can be attached to the housing part or can be mounted or flanged on, such as a hydraulic module or a pump or also an electrical module, as respective force transducer unit. These force transducers are in a particular embodiment in the context of the invention in common that they can be designed as hydraulic pumps for conveying fluid media, for example, high or low viscosity fluid media, in particular oil.

Each of these existing force conversion units or force transducers (aggregates) has within the meaning of the invention average weight and average dimensions, in particular to ensure rapid interchangeability during operation and thus to increase the service capability. In order to make this possible, in the context of the invention, it is also advisable to mount the force transducers (units) specifically adapted to the invention.

Such existing power conversion units are by means of a suitable support structure, in particular by means of a flange, so attached to the housing part or can be introduced or angeflanschbar that a centrally arranged shaft can be introduced through the center of this support structure. This named centrically arranged shaft rotates in each case about the common axis of rotation of pinion and force transducer, in particular with the intention to transmit in this way the rotational movements in the sense of the invention. The carrier construction just mentioned can be attached or inserted or flange-mounted directly on the housing part, so that the attachment can be designed with conventional connecting elements, if necessary by means of re-releasable connecting elements such as in particular screw connections and optionally with additional use of suitable sealing materials for sealing existing fluid media.

In each case between a support structure and the respective pinion, at least one circumferential ring may be present, in particular clamping ring for position stabilization of the pinion bearing or sealing ring for sealing. Here, the ring center is equal to the axis of rotation of the ring encompassed, as described above, wave.

Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of a preferred embodiment of the invention and from the drawing. Hereby shows: Figure 1 is a section through an inventive transmission, parallel to the main axis of rotation, partially broken off.

Fig. 2 is a representation corresponding to Fig. 1 another

Embodiment of the invention;

Fig. 3 is a representation corresponding to Figure 1 of a again modified embodiment of the invention.

Fig. 4a is a plan view of a gear of the transmission of Fig. 1;

4b, the gear of Figure 4a in a perspective view and cut along its axis of rotation ..;

4c shows a section through the Fig. 4a along the plane A - A;

Fig. 5 shows the transmission of Fig. 1 in a perspective view of the

Drive side seen, with the drive-side cover plate and a portion of the untoothed connection element is removed to allow a view into the interior of the transmission;

Fig. 6 shows the transmission of FIG. 1 in a perspective view of the

Seen from the driven side, wherein the section line B - B is drawn, along which the section of Figure 1 is made.

Fig. 7 is a representation corresponding to FIG. 6, wherein the center angle

PHI is registered;

Fig. 8 is a representation corresponding to FIG. 7 another turn

Embodiment of the transmission according to the invention; such as FIG. 9 is a representation corresponding to FIG. 7 of a further modified embodiment of the invention.

Although Figures 1 to 3 show various embodiments of a transmission 1 according to the invention, but which do not differ in their function from each other, but only in their construction in some detail, which will be explained later. First of all, the mode of operation common to all three embodiments will be set forth. In FIGS. 1 to 3, the relevant transmission 1 is reproduced in each case on the basis of a broken section along the main axis of rotation 2; a comparison of the three representations immediately reveals their high similarity.

For clarity, in Figs. 1 to 3, the chassis 7 and the enclosure of the nacelle of a wind turbine, to which the transmission 1 is anchored, indicated only schematically, as well as the hub 30 of the wind turbine of the wind turbine concerned, their rotational energy the transmission 1 is supplied and from this to a plurality of connected power conversion units 17, for example. In the form of generators, units, or a (hydraulic) pump distributed.

Such use in a wind turbine is the primary field of application of a transmission 1 according to the invention, but not the only one.

As shown in FIGS. 1 to 3, a transmission 1 according to the invention is designed as a complete installation ready for installation, in particular as part of an energy system for taking over energy from mechanical forces and moments on the drive side AN and forwarding same to the output side AB. The transmission 1 essentially has a rotationally symmetrical structure. Its essential components extend annularly around a main axis of rotation 2. In the area of the transmission is at best closed by two approximately parallel cover plates 21, 22, but in the intermediate space normally no functionally relevant parts are arranged; Preferably, this gap only serves as a reservoir for a lubricant.

Thus, the transmission 1 is substantially centerless and can be operated without the cover plates 21, 22 in special cases, so that could be passed through a then existing, central opening 10 around the main axis of rotation 2 around cables or other lines. This may be particularly important with hubs of wind turbines, as thus access is provided even during operation from the rear of the nacelle into the hub, so that, with correspondingly large installations, technicians can inspect it even during operation.

After removal of the cover plates 21, 22 remains an annular housing part, which serves to connect to a preferably fixed part of the plant, for example. To the chassis 7 of the nacelle of a wind turbine, and which should be referred to as connecting element 5 for this reason. However, this annular connecting element comprises a plurality of annular portions 5, 5 ', 11 and 23, which are rigidly connected to each other in the installed state and thus are united into a single ring.

For connection to a system part, in particular a nacelle chassis 7 of a wind turbine, the connection element 5 has a flat connection surface in the form of an outer end side, which is shown in Fig. 1 bottom left. When installed, this connection surface lies over a large area and flat against an equally planar connection surface of the nacelle chassis 7 and thus experiences a corresponding orientation. In order to fix this position, fastening elements in the form of ring bores distributed in parallel around the main axis of rotation 2 are provided in the connecting surface in the form of bores parallel to the main axis of rotation 2, either through bores or at least partially provided with internally threaded blind bores. By inserting or screwing machine screws, threaded bolts od. Like. And tightening or countering the same, the connection between the housing of the transmission 1 and the nacelle chassis 7 and the respective chassis or foundation is made.

This connection takes place at the rear or tower end of the transmission 1; At the front or hub end, a connection to the hub 30 of the wind turbine is to be established. Since the hub 30 must be able to rotate relative to the nacelle chassis 7, the hub 30 does not take place on the connection element 5 forming the transmission housing, but instead on a connection element 4 separated therefrom.

Also, the terminal 4 has an annular structure, but is preferably not composed of several pieces, but integrated into a single, annular piece. This connection element 4 also has a flat connection surface in the form of an outer end face, which, however, faces away from the connection surface of the connection ring 5 and is shown on the right in FIG. 1, approximately in the lower third of the drawing. This connection surface is in the installed state over a large area and flat on an equally planar, rear connection surface of the hub 30 and can thereby contribute to a corresponding alignment of the hub 30. In order to fix this position, fastening elements in the form of bores parallel to the main axis of rotation 2, in particular completely or partially internally threaded blind bores, are also provided in the connecting surface of the second connecting element 4 in a circle around the main axis of rotation 2. By screwing machine screws, threaded bolts od. Like. And tightening the same is made the connection between the connection element 4 of the transmission 1 and the hub 30 of the wind turbine.

The easy rotatability of the inner connecting element 4 relative to the housing-like firing element 5 results from a gap X between the two connecting elements 4, 5. Thus, on the other hand, the inner connecting element 4, if necessary, take on the task of an exact positioning of the hub 30 of the wind turbine, it must in turn the gear-like housing part 5 experience a precise guidance. This assumes a arranged in the gap X between the two transmission parts 4, 5 main storage in the form of a one oer preferably multi-row roller bearing with raceways 29 on both connection elements 4, 5, on which rolling elements 6 roll along. Since at the main bearing of a wind turbine in addition to the desired torque also undesirable but unavoidable axial and radial forces and tilting moments occur, the rolling bearing 6, 29 has a robust construction. For reasons of carrying capacity roller-shaped rolling elements 6 are preferably used. There are several, in particular at least three rows of such roller-shaped rolling elements 6 are provided, for example. A radial row, which ensures that the axes of symmetry of the two rotationally symmetrical connection elements are concentric with each other, and at least two axial rows, from which transmits a wind pressure forces, while the other for Traction forces is designed; Tilting moments are equally received by both and delivered to the nacelle chassis 7, whereby a permanent parallel alignment of the two connection elements or a coaxial alignment of their two axes of symmetry is ensured.

In order to provide in each case raceways for the radial row and the two axial rows, one of the two connecting elements 4, 5 is designed as a so-called "nose ring" with a slot X facing it As can be seen Fig. 1, this collar-like elevation 13 has an approximately rectangular cross-section, with - viewed in the axial direction - depending on a flat top and bottom and a cylindrical outer side. While the latter serve as a raceway (s) 29 for the radial bearing (s), runs along the annular top and bottom of each of the two rows of axial.

In order to support all of these rolling element rows, an equal number of raceways 29 must also be provided on the respective other connection element 5, 4. This has for this purpose, for example, a C-shaped geometry, so to speak with an all-round groove in which the collar-like elevation 13 of the other connection element 4, 5 engages.

Because of this entanglement, it is necessary for the assembly of the connection elements 4, 5 that the connection ring 5 is subdivided with C-shaped geometry in the region of the groove base in an upper ring portion 5 'and a lower ring portion 5. The separation can, for example. Along a plane Run surface that is, for example, at the upper or lower end of the radial bearing raceway 29.

The gap X extends up to the connection surface of the rotatable connection element 4 and is preferably filled with lubricant, in particular with lubricating grease. So that this lubricant can not escape, located in the gap opening a seal 26th

Just to let escape lubricant contained and / or no dirt particles to penetrate, the transmission 1 is encapsulated as far as possible. As can be seen in FIG. 1, the outer sides are in each case aligned with one of the two connecting surfaces of the gearbox 1 facing away from one another. These are preferably in each case an all-round groove in the relevant connecting element 4, 5 inserted and, for example, by means of screws fixed, for example by means of countersunk screws. Apart from the rotary connections described below for the transmission output axles, the transmission 1 is thus hermetically sealed. As can further be seen from FIG. 1, in the vicinity of the gap muzzle the local connection surface is raised with respect to the adjacent end side of the other connection element 5, so that when the two surfaces of different connection elements 4, 5 rotate relative to one another, the "uninvolved" end face does not abut the one on the one The distance L between the two connection surfaces-and thus the overall height of the transmission 1 -is thus slightly larger than the axial extent of the larger or higher connection element 5.

The fixed to the nacelle chassis 7 to be anchored connection element 5 consists not only of the two ring sections 5, 5 ', but further comprises an approximately annular disk-shaped connecting part 11, on which the actual pad GA is arranged, and which therefore on the other Anschussfläche GZ opposite lying end face of the ring portion 5 'is placed. Good to see in the drawing, the minimum thickness SG of the connecting part 11. The ring sections 5, 5 ', 11 may, for example, be determined by common screwed together.

The circular ring-shaped connecting part 11 engages over the terminal face GZ opposite end face of the other connection element 4 at a distance, so that the gap X continues there, and also extends beyond the all-round collar or bearing section 13 opposite lateral surface of the other connection element 4 in the radial Direction.

This connection element 4 is on just that, the collar or bearing portion 13 facing away from lateral surface with a running toothing 12th provided, which serves the tap or the forwarding of the received from the hub 30 of the wind turbine rotational energy. This toothing 12 need not extend over the entire height of the toothed connection element 4; it may be a straight toothing, but also a helical toothing.

The tapping of the rotational energy of the toothed connection element 4 by means of a plurality of toothed gears 8, the respective shell-side teeth 16 are in meshing engagement with the teeth 12 of the toothed connection element 4 and driven by this, as soon as from the hub 30 of the wind turbine torque the toothed connection element 4 is initiated. In general, the diameter of the gear wheels 8 will be significantly smaller than the diameter of the teeth 12; for this reason, it is also common to speak of the gear wheels as the smaller gears of pinions; This term is dahr used in this text synonymous with gear (Zahn) wheels.

In order to be able to conduct the tapped off from the teeth 12 energy at defined positions out of the transmission housing, whose position within the housing must be precisely defined; this afford wheel bearings 14, 15 for the gears 8, which rotatably support the latter about their respective sub-axis of rotation 3, but otherwise immovable to the untoothed connection element 5.

As can be seen further in FIG. 1, in the illustrated embodiment there are in each case two such wheel bearings 14, 15 per gearwheel 8 or pinion, one at its upper end and one at its lower end.

The geometry of a gear wheel is shown in FIGS. 4a to 4c. One recognizes clearly the prizipiell cylindrical main body with two levels End faces and each have a groove U1, U2 between each of the two end faces and the jacket for receiving a respective wheel bearing 14, 15. Between the two grooves U1, U2 is the straight, originally purely cylindrical shell provided with an all-round teeth 16, 5 each on the type of teeth 12 on the toothed connection element 4 in the form of a geaden or oblique toothing. In order to protect these teeth 16 from damage due to contact with the wheel bearings 14, 15 inserted in the grooves U1, U2, the respective flat annular surface of the two grooves 111, U2 is provided with a small step, wherein the toothed lateral surface region 16 is opposite the actual groove U1, U2 is set back by the height of the stage and thus a distance between the teeth 16 and the wheel bearings 14, 15 is maintained. The pinion bearings 14, 15 therefore do not contact or touch the toothing elements 16 of the pinion 8. Nor do the

15 wheel bearings 14, 15 with the tooth-shaped elements 12 on the toothed connection element 4 in contact.

One of the two end faces of the gear 8 is concentric with its axis of symmetry 3 with a connection 27 for non-rotatable connection with

In the form of a (electric) generator or a (hydraulic) pump, provided, where the rotational energy can be converted into another form of energy. The connecting element 27 is preferably a bore parallel to the axis of symmetry 3 of the gear wheel 8 whose diameter is approximately between one fifth and one-half of the diameter DR of the gear wheel 8 including its toothing 16, in particular between one fourth and one third of the diameter DR of the teeth 16. This diameter tapers approximately halfway up the gear 8 to a narrow, vorzugsweie to Symmetriachse 3 0 coaxial channel, which, for example, a vent when inserting a shaft 9 od. Like. In the connection element 27 causes. To order between an inserted shaft 9 of a part to be connected, for example. Force converter such as (electric) generator or (hydraulic) pump, and the mantle of the connection bore 27 form a rotationally fixed conclusion, just this bore mantle has no completely rotationally symmetrical, in particular no purely cylindrical shape, but has at least one radial pre- and / or or recess on which a counterpart on the inserted shaft 9 or another connecting part can engage in a form-fitting manner. In the present example, the jacket of the connection bore 27 is provided with radially projecting teeth and radially receding tooth gaps, so that a shaft provided with a complementary toothing is coupled in a rotationally fixed manner to the gear wheel 8 after being inserted into the connection bore 27.

In Fig. 1 is further illustrated how such a pinion or gear 8 is installed in the transmission 1. For this purpose, initially serve the two wheel bearings 14, 15, for which preferably prefabricated or prefabricated bearings are used. These may preferably be ball bearings, for example radial ball bearings or four-point ball bearings. For small to medium size gear units 1, a single row of rolling elements per wheel bearing 14, 15 may be sufficient, with larger or more heavily loaded gears 1, it may also be useful to provide several rows of rolling elements per wheel bearing 14, 15. Shown are a drive-side bearing, in particular a hub-side wheel bearing 14, and a driven-side bearing, in particular a machine carrier or nacelle-side wheel bearing 15th

While the respective inner ring of a wheel bearing 14, 15 of the respective groove U1, U2 is applied directly, are for supporting the respective outer ring on the connecting part or portion 11 and / or on a fixed thereto or attaching transmission part or section 23 in itself annularly closed contact surfaces provided, wherein the outer ring is inserted or even pressed. In the transmission embodiment of Fig. 1, where the transmission part 23 is separated from the connecting part 1 1 and bolted only to that, for example. Via an attaching to the transmission part 23 flange 25 and screwing holes 19 inserted therein, the transmission part 23 with an annular shape two cross-sectional portions, for example, a first, about apron or cylinder jacket-shaped portion, which is in contact with the connecting part 11 and is screwed to that, and a second, approximately annular disc-shaped portion which is in communication with the free edge of the first portion, eg is integrally molded together with that, for example, is solidified together with that in a mold, or which is welded to this, glued, screwed or otherwise united. Overall, the two sections taken together form an approximately L-shaped cross-sectional geometry, as shown in FIG. 1.

The circular disk-shaped portion of the transmission part 23 together with the connecting part 11 each have a kind of bearing plate each one of the two wheel bearings 14, 15. For the production of the bearing seats are in these two parts 11, 23 for each gear in pairs aligned with each other introduced holes, with hollow cylindrical insides , wherein the outer rings are inserted or pressed with their complementary, cylindrical outer sides.

To facilitate the installation and possibly also the disassembly of a gear 8, a bearing seat in the transmission part 23 may have a different, in particular smaller diameter than the associated bearing seat in the connecting part 11. In addition, one of the two bearing seats, preferably the one with the smaller diameter, in Fig. 1, the bearing seat for the wheel bearing 14, be completed by a radially inwardly projecting collar on its axial outside, so that an axial bearing surface for the axial support of the respective wheel bearing 14 - and thus also the gear wheel 8 mounted therein - results. A support in the opposite axial direction is effected by a clamping ring 20, which, for example, in a on the inside of the bore in the connecting part 11 above the bearing seat for the local wheel bearing 15 incorporated, the sub-axis of rotation 3 enclosing internal thread can be screwed; instead of a screw the clamping ring 20 may also be welded or glued. Since its inner diameter is smaller than the outer diameter of the respective wheel bearing 15, this is firmly clamped in the axial direction and thereby the gear 8 held in position such that a rotation of the same about the respective sub-axis of rotation 3 is its only authorized movement.

When plugged into a connection hole 27 shaft is usually the drive shaft of a force transducer for converting the rotational energy into an energy form, eg. In the form of an (electric) generator or a (hydraulic) pump. The like. To the Housing of the connected force transducer or other part of the system to prevent co-rotation with the drive shaft, an anchoring option in the form of a concentric to the respective sub-axis 3 concentric base member 18 is provided, which in turn is fixed to the connecting part or section 11, for example. By means of a mounting flange 28 The base element 18 may have radial projections or recesses and / or screw connections, to which the connected installation part can be anchored in a rotationally fixed manner.

The transmission embodiment of FIG. 2 differs from the one described above in that, according to FIG. 2, a raceway 29 of the main bearing, namely that for the upper row of axial rollers 6, is not provided on a separate raceway part 5, 5 'of the untoothed connecting element 5 but at the connecting part 11 itself. As a comparison of Fig. 1 with Fig. 2 shows, thereby the geometry of the connecting part 11 on be simplified by reducing its shape to a nearly pure disc shape.

On the other hand, this makes it possible to combine the remaining raceways 29 of the main bearing on the untoothed connection element 5 on a single raceway section 5, so that the untoothed connection element 5 in this embodiment only consists of three parts, namely a raceway part 5, a connection part 11 and a transmission part 23rd

In the transmission embodiment of FIG. 3, however, another simplification has taken place: Here, the connecting part 11 was summarized or integrated with the transmission part 23 to a new, one-piece connection and transmission part 24.

While doing the original connection part 11 corresponding connection portion of the integrated connection and transmission part 24 has undergone no substantial change, two different variants are conceivable in the transmission section:

This section of the integrated connection and transmission part 24 could on the one hand have approximately the same cross section as the previously described embodiments, ie on the other hand consist of a apron or zylindermantelfömigen part on the one hand and an annular disc-shaped part. As a result, the integrated part 24 has two flat, mutually parallel sections, wherein for each gear 8 per a bearing seat for their two wheel bearings 14, 15 is incorporated.

In another type, the transmission portion of the integrated connection and transmission part 24 could be made solid, so for example. More completely meet the cavity or Kehlungsbereich between the apron-shaped and the annular disk-shaped portion more or less. In order to create space for the gears 8 in this case, the receiving spaces for those would have to be incorporated into this massive ring body, in particular drilled. Thus, while in the first, previously described design variant, all gear wheels 8 are accommodated in a common, all-round cavity or throat area, a separate cavity is created in the latter construction variant for each gear 8, which of the banachbarten by the left standing part of the originally massive Transmission section as it is separated from each other by webs. However, these individual compartments are all open to the teeth 12 of the toothed connection element 4. The advantage of this embodiment is on the one hand in an increased rigidity of the arrangement, because the remaining between the compartments webs austeifen the gear portion relative to the Vebindungsabschnitt and thereby improve the dimensional stability; On the other hand, the introduction of holes in the joint connecting and gear body 24 may possibly be accomplished simpler than the preparation of an undercut area between two flat but staggered portions of the respective body 24, which almost excludes the production as a casting with a reusable form almost ,

3, the untoothed connection element 5 consists of three parts, namely two raceway parts 5, 5 'and an integrated connection and transmission part 24. If the embodiments according to FIGS. 2 and 3 were combined, the connection element could be 5 further simplified and then would only consist of two parts, namely a raceway part 5 and an integrated connection and transmission part 24. In the arrangement of the gears 8 in the transmission part 23 or the integrated connection and transmission part 24, there are various possibilities : As can be seen from FIGS. 5 to 7, the gearwheels 8 can be distributed at uniform intervals over the circumference, or at the same central angles. In the embodiment illustrated in FIGS. 5 to 7, there are, for example, ten gear wheels 8 distributed equidistantly around the circumference, wherein adjacent gear wheels 8 are each spaced apart by a center angle PHI of 36 °.

In the embodiment of Fig. 8, a plurality of gears 8 are combined into clusters, wherein preferably for each gear 8, another gear 8 is arranged diametrically opposite to the main axis of rotation 2, so that in total results in a symmetrical or balanced arrangement again. On the other hand, this is not mandatory, because the untoothed connection element 5 of the transmission 1 is usually fixed in place, so that asymmetric arrangements or distributions of the gears 8 are conceivable, such as. In Fig. 9 shown. All pinions 8 have the same dimensions in terms of component diameter DR and component height BR. Each of these pinion 8 has approximately the same distance K from the center axis 2, and each of these pinions 8 is directly driven, without intermediary (gear) stages, from the toothing 12 mounted directly on the connection element 4.

Shown in Fig. 6 is the imaginary polygon P for connecting all imaginary secondary axes of rotation or symmetry center points 3 between all pinions 8. This polygon results in a self-contained polygon P with a large number of vertices P = 10. This symmetrical arrangement has been chosen according to the invention to a as uniform (concentric) moment loading around the center axis, and is better from this point of view than other, asymmetric or polygonal polygons. There are in all embodiments of the design according to the invention four or more than four such pinion 8 available. In the embodiment according to FIGS. 5 to 7, the pinions 8 are arranged concentrically and symmetrically about the main axis of rotation or center axis 2 and uniformly spaced from one another at the same distance E. If ten pinions 8 are present and these have the same distances E one below the other , results in an intermediate angle PHI of 36 ° each. Likewise, it can be seen from the drawing, the information that for each connected force transducer 17, a support structure is provided in the form of a base member 18, for example, or in particular by means of a flange 28 on the housing part 11 attachable or einbringbar that a centrally disposed shaft. 9 , with the intention of being able to transmit rotational movements, can be introduced through the center of this support structure 18. This centrically arranged shaft 9 then rotates about the respective secondary rotation axis 3, that is about the common axis of rotation 3 of pinion 8 and force transducer 17, with the intention to transmit rotational movements.

The Trägerkonstuktion 18 can be attached directly to the housing part 11 or introduced or flanged. Its attachment can be designed with conventional connecting elements 31, if necessary, releasable connecting elements 31 such as screw connections 31 can also be used. Optionally, in particular in the case of lubrication by means of oil, suitable sealing elements and / or materials may optionally additionally be used to seal against leakage of the lubricant between the flange 28 of the support structure 18 and the connection or housing part 11. It is also possible that between the indicated shaft 9 and the support structure 18 separate shafts (tight) rings are used. Between a support structure 18 and the respective pinion 8, at least one circumferential ring 20 may be present, for example, a clamping ring 20 for stabilizing the position of the pinion bearing 15 or a sealing ring 20 for additional sealing. The center of the circle of such a ring 20 is then equal to the secondary axis of rotation 3 of the surrounded by the respective ring 20 shaft. 9

FIGS. 5 to 7 each show by way of example that the housing 11, which is essentially closed at least on one side, has a central opening 10 according to the invention about a center axis 2, which ensures center-freedom of the overall arrangement 1. The housing 11 may be made in one piece or even more pieces. There may be a closing cover plate 21, see (see Fig. 1 to Fig. 3) which can be connected to the housing part 11. This plate 21 may be of lesser thickness than the housing part 11, in particular of lesser thickness than 50 mm. The cover plate 21 is detachably connected to the housing part 11, for example connected by means of screw connections. According to the invention would also be a permanent connection between the connecting or housing part 11 on the one hand and the plate 21 on the other. Parallel to the perpendicular to the center axis 2 extending housing contour GA of the first side, ie also parallel to the plane in which the exemplary vorbenannte plate 21 is arranged on a second side, in particular on the opposite side, a second cover plate 22 may be present. This second cover plate 22 may also be of lesser thickness than the connecting or housing part 11, in particular of a thickness less than 50 mm. However, this cover plate 22 is not connected to the connection or housing part 11, but with the toothed connection element 4, and maintains a distance S with respect to the transmission part 23 or the integrated connection and transmission part 24. In FIG. 3, a distance L between the outer housing contour GA of the first transmission side and the outer housing contour GZ is defined on the second, opposite, transmission side. According to the invention this is Distance L at most twice the dimension in relation to the overall height BR of an interior space between the two housing contours GA; GZ arranged pinion 8. Example according to the axial extent or height L of the transmission assembly 1 is between about 100 mm and at most 1000 mm, preferably less than 500 mm.

The gap X between the two main rolling bearing rings 5; 4 is sealed by a conventional sealing system 26 as an annular sealing system. Materials for this are, for example, the common materials such as FPM, ECO, NBR, etc., although other similar rubber-based materials are suitable. This system 26 includes at least one circumferential sealing ring, each having at least one sealing lip. Multi-part designs, including two or more radially juxtaposed sealing rings are also conceivable within the meaning of the invention.

Further, for example, each of the existing pinion 8 could be partially enclosed by a respective separate pinion housing 23, in particular but at least radially enclosed by sides of the center axis 2, so that the respective pinion 8 is spatially separated against physical interference from this direction. Thus, in particular only interventions on the side of the meshing elements 12, 16 are made possible, while interfering with the teeth of the pinion 16 from the side of the center axis 2 forth are prevented by this pinion housing.

In Fig. 1 is shown as an example that the respective pinion housing or transmission part 23 on the connecting part 11 screwed 19 or flange-25; 19 can be executed; but according to the example it could also be welded (see FIG. 2), which would save screws and a wide flange 25. LIST OF REFERENCE NUMBERS

Gear 27 Connecting element

Main axis of rotation 28 Flange

Secondary axis of rotation 29 rolling element track

Connection element 30 hub

Connection element 31 screw connection

Rolling element 32 fastening element

Chassis 33 fastener

Gear wheel ON drive side

Connecting shaft AB output side

Central recess BR pinion height

Section C Cluster

Gearing C1 Cluster

Section C2 Cluster

Wheel bearing DR pinion diameter

Wheel bearing E removal

Gearing GA housing contour

Energy converter GZ housing contour

Base element K radius

Screw connection L distance

Clamping ring P virtual traverse

Cover plate PHI center angle

Cover plate S distance

Section SG Case thickness

Section U1 Scope

Flange U2 circumference

Seal X gap

Claims

claims

1. gear (1) having more than two rotary joints, preferably for distributing an input torque from a drive to two or more outputs, in particular for distributing the torque to the hub of a wind turbine to two or more connected generators or energy converters comprising two rotationally symmetric, preferably annular connection elements (4,5) each having at least one flat connection surface for rotationally fixed connection to two different machine or system elements or on a machine or system element on the one hand and on a chassis or foundation on the other hand, wherein the two connection elements (4,5) aligned are that their axes of symmetry are coaxial with each other and their preferred pads are facing away from each other, wherein further between the two connecting elements (4,5) is a gap (X), wherein at least one roller bearing (6,29) is arranged as a main bearing for storage of both Connection elements (4,5) to each other, rotatably about a main axis of rotation (2), which corresponds to the common axis of symmetry of both connecting elements (4,5), and wherein at least one lateral surface of a connecting element (4) is provided with a completely running toothing (12), characterized in that the untoothed connecting element (5) has a toothing (12) of the toothed connecting element (4) facing portion (23) with one or more, to the toothing (12) open towards cavities for receiving toothed gears (8) , wherein in the untoothed connection element (5) for each gear (8) an end opening is provided, whereby the relevant rotary connection is accessible, and thus about in an axial alignment at least one closed ring area for supporting at least one in the axial direction between the pads of the arranged two connection elements (4,5) Bearing (14,15) for the gear in question (8) as the wheel bearing, so that the gear in question (8) about a relative to the main axis of rotation (2) eccentrically offset, but approximately parallel to the secondary rotation axis (3) rotates and with the toothing ( 12) of the toothed connection element (4) meshes.

2. Transmission (1) according to claim 1, characterized in that the toothed connection element (4) is constructed in one piece.

3. Transmission (1) according to claim 1 or 2, characterized in that on one of the toothing (12) opposite lateral surface of the toothed connection element (4) at least one raceway (29) for a row of rolling elements (6) of the main bearing is arranged.

4. Transmission (1) according to one of claims 1 to 3, characterized by in the toothed connection element (4) distributed in a distributed manner fastening elements (33), in particular in the terminal surface opening blind holes with internal thread, which preferably in the radial direction between the teeth (12 ) and at least one raceway (29) for a row of rolling elements (6) of the main bearing is arranged.

5. Transmission (1) according to one of the preceding claims, characterized in that the toothing (12) and / or the raceway (s) (29) for the row of rolling elements (s) (6) of the main bearing and / or the

Fastening elements (33), in particular blind holes with internal thread, by machining or shaping of the same connection element base body (4) are formed.

6. Transmission (1) according to one of the preceding claims, characterized in that on one of the toothing (12) opposite lateral surface of the toothed connection element (4) around all running collar (13) is provided, on which one or more track (s) (29) for the rolling elements (6) of the main bearing is (are) arranged.

5 7. Transmission (1) according to one of the preceding claims, characterized in that the main bearing has a plurality of rows of rolling elements (6).

8. Transmission (1) according to any one of the preceding claims, characterized i o characterized in that the main bearing has at least one thrust bearing with at least one row of rolling elements (6) whose support angle is equal to or greater than 45 °.

9. gearbox (1) according to one of the preceding claims, characterized in that the main bearing comprises a radial bearing with at least one row of rolling elements (6) whose support angle is smaller than 45 °.

10. Transmission (1) according to any one of the preceding claims, characterized 20 characterized in that the main bearing comprises at least one row of elongate rolling elements (6) such as roller, barrel, needle or conical rolling elements.

11. Gearbox (1) according to one of the preceding claims, characterized in that the toothed connection element (4) is encompassed by the untoothed connection element (5) on one of its end faces and on its two lateral surfaces.

12. gear (1) according to any one of the preceding claims, characterized in by the non-toothed connection element (5) distributed in a circle distributed fastening elements (32), for example, in the connection surface opening holes, Especially blind holes with internal thread, which are preferably in one of the toothing (12) of the toothed connection element (4) facing away from section (5,5 ') are arranged.

13. Transmission (1) according to one of the preceding claims, characterized in that the raceway (s) (29) for at least one row of rolling elements (6) of the main bearing and / or the fastening elements (32), for example blind holes with internal thread, by machining or Forming a common (partial) body of the untoothed connection element (5) are formed.

14. Transmission (1) according to any one of the preceding claims, characterized in that the untoothed connection element (5) in its toothing (12) facing away from the cross-sectional area has a roughly aprotic or cross-sectionally approximately L-shaped track portion (5,5 ') with at least a, preferably directly incorporated raceway (29) for a row of rolling elements (6) of the main storage.

15. Transmission (1) according to any one of the preceding claims, characterized in that the cross section of the untoothed connection element (5) has at least one annular disk-shaped connecting portion (11) which engages around the end face of the toothed connection element (4).

16. Transmission (1) according to one of the preceding claims, characterized in that the untoothed connection element (5) in its the toothing (12) facing cross-sectional area has an approximately aprotic or cross-sectionally approximately L-shaped gear portion (23) which adjoins the annular-shaped (11) section connects and gears (8) engages or receives.

Transmission (1) according to one of the preceding claims, characterized in that the untoothed connection element (5) is composed of several parts, for example at least one raceway part (5,5 '), a connecting part (11) and a transmission part (23).

Transmission (1) according to one of the preceding claims, characterized in that the gear portion (23) has an approximately L-shaped cross-section with an all-round cavity for common reception of all gears (8).

Transmission (1) according to one of the preceding claims, characterized in that the gear portion (23) has a varying approximately in the azimuthal direction cross section with a plurality of spaced apart by intermediate webs cavities for receiving a respective gear (8).

Transmission (1) according to one of the preceding claims, characterized in that on the connecting portion or part (11) about a secondary rotation axis (3) annularly closed edge region for supporting a wheel bearing (15) for the respective gear (8) is provided.

Transmission (1) according to one of the preceding claims, characterized in that on the transmission portion or part (23) about a secondary rotation axis (3) annularly closed edge region for supporting a wheel bearing (14) for the respective gear (8) is provided.

22. Transmission (1) according to one of the preceding claims, characterized by (radial) ball bearings as wheel bearings (14,15), preferably four-point ball bearings.

Transmission (1) according to one of the preceding claims, characterized by rolling bearings with their own raceway rings as a wheel bearing (14,15), the outer raceway ring is inserted into the relevant annularly closed edge region of the untoothed connection element (5).

Transmission (1) according to claim 23, characterized in that an outer raceway ring of a wheel bearing (14,15) by an attached and to the untoothed connection element (5) fixed mounting ring (20) with respect to the local wheel bearing (14,15) tapered inner cross-section is fixed in the axial direction.

Transmission (1) according to claim 23 or 24, characterized in that an inner raceway of a wheel bearing (14,15) is received in a along the periphery of an end face of the respective gear wheel (8) all-round groove.

Transmission (1) according to one of the preceding claims, characterized in that between the lateral surface (16) of a gear wheel (8) and its two end faces per each running around a groove (U1, U2) is provided, wherein only the radially enlarged cladding region (16 ) is toothed between the two grooves (U1.U2).

Transmission (1) according to one of the preceding claims, characterized in that in one end face of a gear wheel (8) at least one connecting element (27) for transmitting the output torque to a non-rotatably connected machine or plant part is provided, in particular a blind hole, whose inner cross-section has at least one radial extension or taper, so that a rotationally fixed connection by a complementary part is possible.

28 transmission (1) according to any one of the preceding claims, characterized in that on the untoothed connection element (5) concentric with each auxiliary rotation axis (3) each have a base element (18) for anchoring the housing of a non-rotatably connected to the gear (8) machines - Part or plant part provided or can be fixed.

29. Transmission (1) according to one of the preceding claims, characterized in that the region is closed radially within an annular connection element (4,5) by a cover (21, 22), preferably approximately in the plane of the respective connection surface.

30. Transmission (1) according to one of the preceding claims, characterized in that the toothing (12) of the toothed connection element (4) is located on the inside thereof.

31. Wind turbine with a preferably about an axis extending approximately in the wind direction rotating wind turbine whose rotor is coupled via a transmission (1) with two or more connected generators or energy converters for power transmission, wherein the transmission has two rotationally symmetrical, preferably annular connection elements (4,5 ), each having at least one flat connection surface for rotationally fixed coupling to the rotor of the wind turbine on the one hand and to the chassis of the nacelle on the other hand, wherein the two connection elements (4,5) are aligned such that their axes of symmetry are coaxial and their preferred connection surfaces facing away from each other are, being further, a gap (X) is located between the two connecting elements (4, 5), wherein at least one rolling bearing (6, 29) is arranged as a main bearing for mounting the two connecting elements (4, 5) against one another, rotatable about a main axis of rotation (2), which corresponds to the common axis of symmetry of both connecting elements (4, 5), and wherein at least one lateral surface of a connecting element (4) is provided with an all-round toothing (12), characterized in that the untoothed connecting element (5) has one of the toothing (12) the toothed connection element (4) facing portion (23) having one or more, the toothing (12) open towards cavities for receiving toothed gears (8), wherein in the untoothed connection element (5) for each gear (8) a The frontal opening is provided, whereby the rotationally fixed coupling to a respective generator or energy converter is possible, and thus at least approximately in an axial flight ens a closed annular region for supporting a in the axial direction between the contact surfaces of the two connecting elements (4,5) arranged bearing (14,15) for the gear in question (8) as the wheel bearing, so that the relevant gear (8) to one opposite the main axis of rotation (2) eccentrically offset, but approximately parallel to the auxiliary rotary shaft (3) rotates and with the toothing (12) of the toothed connection element (4) meshes.

32. Cylindrical or ringfömige energy transmission assembly (1) for transmitting energy from mechanical forces and torque from a drive side (AN) to a driven side (AB) as part of an energy system, wherein both the energy transfer assembly (1) and the power plant on central transmission - or sun gears, which overlap the main or center axis (2) and rotate around the same, omitted, comprising: a plurality, at least four, preferably three per quarter of a circle, about the center axis (2) arranged and each separately on the housing part (11) on the output side (AB) fixedly mounted or fixed attachable, each about their own axis of symmetry (3) 5 rotatably mounted, Pinion (8), each with equidistant distances

(K) to the center axis,

at least one two-row or multi-row large-diameter rolling bearing inside this energy transfer assembly (1), for example comprising cylindrical rolling elements (6) in mutually orthogonal i o oriented raceways (29),

at least one-sided housing closure, in particular as protection of the at least one two- or multi-row slewing bearing before external engagement, for example, with additional attachment of several approximately parallel to each other

15 standing cover plates (21, 22),

wherein the large roller bearing has at least one Hauptwälzlagerring (4; 5) as an outer ring, and at least one energy further conducting inner Hauptwälzlagerring (4), wherein the inner Hauptwälzlagerring (4) receives the forces and moments of the 0 drive side (AN) and on the output side (AB) transmits by means of directly on the Hauptwälzlagerring (4) attached juxtaposed and about the center axis annularly arranged toothed and meshing elements (12), in particular in the form of a toothing (13), wherein direct or 5 indirect coupling of the at least one Hauptwälzlagerrings (4;

5) with the housing part (11) on the output side (AB), in particular with the enclosure (7) or the machine carrier (7), and wherein direct or indirect coupling of the corresponding main rolling bearing rings (4; 5) with the 0 drive side ( AN), for example with the hub (30) one

Wind turbine.