WO2012146382A1 - Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif - Google Patents

Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif Download PDF

Info

Publication number
WO2012146382A1
WO2012146382A1 PCT/EP2012/001817 EP2012001817W WO2012146382A1 WO 2012146382 A1 WO2012146382 A1 WO 2012146382A1 EP 2012001817 W EP2012001817 W EP 2012001817W WO 2012146382 A1 WO2012146382 A1 WO 2012146382A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
bearing
connection element
connection
elements
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2012/001817
Other languages
German (de)
English (en)
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IMO Holding GmbH
Original Assignee
IMO Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102011019001A external-priority patent/DE102011019001A1/de
Priority claimed from DE102011019002A external-priority patent/DE102011019002A1/de
Application filed by IMO Holding GmbH filed Critical IMO Holding GmbH
Priority to EP12727779.6A priority Critical patent/EP2702298A1/fr
Priority to CN201280032142.5A priority patent/CN103635713A/zh
Publication of WO2012146382A1 publication Critical patent/WO2012146382A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H1/227—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts comprising two or more gearwheels in mesh with the same internally toothed wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/381—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with at least one row for radial load in combination with at least one row for axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • 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
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • the Vorerfinder further speaks of a commercially available "Schiffswellenelektrogenerator”.
  • 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 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.
  • 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 Drehiereauer- 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.
  • 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.
  • 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.
  • 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.
  • 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 Stilicalzlagerring, 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 Stilicalzlagerringe rotatably supported against each other.
  • 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.
  • 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.
  • connection elements or Haupt michlelzlagerringe 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.
  • 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.
  • 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.
  • connection element is fixed in place, for example, coupled to the machine carrier or the nacelle housing a wind turbine or coupled.
  • 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.
  • 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:
  • PE n * P A.
  • 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.
  • 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.
  • 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.
  • 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 anaenuit 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.
  • 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.
  • a sealing system 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.
  • the housing part is designed as a dynamically loaded component of a Haupt michlewinges a large rolling bearing on the career of the rolling elements, such as rollers, ball, cylinder, tons, or tapered rolling elements roll.
  • 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, rockschraubbares, part.
  • 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.
  • 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.
  • 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).
  • 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.
  • a variety of radial and axial forces and tilting moments can record.
  • the main bearing may have several rows of rolling elements, for example.
  • each own, specially adapted rolling elements To increase the carrying capacity and / or to provide for special load cases each own, specially adapted rolling elements.
  • 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.
  • 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.
  • the main bearing comprises at least one row of elongated rolling elements, such as roller, barrel, needle or conical rolling elements.
  • 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.
  • 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.
  • the raceway (s) for at least one row of rolling elements of the main bearing and / or the fastening elements are formed by machining or shaping a common (partial) body of the untoothed connecting element.
  • this measure leads to a maximum of precision;
  • the raceways can be kept free of any joints along its entire circumference, which can achieve a longer service life.
  • 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.
  • 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 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.
  • the gear part also has a flat, annular disk-shaped section which extends parallel to the likewise plane annular disk-shaped connecting section.
  • 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.
  • the transmission section has an approximately L-shaped cross-section with an all-round cavity for common reception of all gears.
  • the gear section itself has a particularly simple geometry;
  • together with the connecting portion results in an undercut, which makes a one-piece production as a casting difficult or even impossible.
  • 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.
  • the transmission part with L-shaped cross-section for example.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • this measure should in most cases be simpler than the incorporation of the raceways into the connecting element itself.
  • 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.
  • 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 Dreh gleiches 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.
  • the base element may have radially forward or backward jumping elements and / or screw connections od.
  • the region radially within an annular connection element can be closed by a cover, preferably approximately in the plane of the respective connection surface.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • this cover plate may be detachably connected to the housing part, in particular by means of screw connections can be releasably connected.
  • 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.
  • 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.
  • 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.
  • 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
  • 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;
  • an overall arrangement comprises:
  • 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,
  • the main bearing at least one Haupticalzlagerring outer ring, and at least having an energy-conducting inner main rolling bearing ring, wherein the inner main rolling bearing ring the
  • 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.
  • 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.
  • 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.
  • power conversion unit 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 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.
  • At least one circumferential ring may be present, in particular clamping ring for position stabilization of the pinion bearing or sealing ring for sealing.
  • the ring center is equal to the axis of rotation of the ring encompassed, as described above, wave.
  • 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
  • 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;
  • FIG. 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
  • FIG. 6 shows the transmission of FIG. 1 in a perspective view of the
  • Fig. 7 is a representation corresponding to FIG. 6, wherein the center angle
  • Fig. 8 is a representation corresponding to FIG. 7 another turn
  • FIG. 9 is a representation corresponding to FIG. 7 of a further modified embodiment of the invention.
  • 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.
  • the mode of operation common to all three embodiments will be set forth.
  • 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.
  • a transmission 1 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.
  • 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.
  • annular housing part which serves to connect to a preferably fixed part of the plant, for example.
  • annular connecting element 5 To the chassis 7 of the nacelle of a wind turbine, and which should be referred to as connecting element 5 for this reason.
  • 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.
  • connection element 5 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • roller-shaped rolling elements 6 are preferably used.
  • 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.
  • one of the two connecting elements 4, 5 is designed as a so-called "nose ring" with a slot X facing it
  • 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.
  • raceways 29 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.
  • 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.
  • 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
  • the transmission 1 is encapsulated as far as possible.
  • 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.
  • connection surface 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 Anschuss Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stucle Stuclear surface.
  • 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.
  • 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 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.
  • 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.
  • FIGS. 4a to 4c The geometry of a gear wheel is shown in FIGS. 4a to 4c.
  • 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
  • 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
  • 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.
  • the connection element 27 causes. To order between an inserted shaft 9 of a part to be connected, for example.
  • the mantle of the connection bore 27 forms 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.
  • 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.
  • Fig. 1 is further illustrated how such a pinion or gear 8 is installed in the transmission 1.
  • These may preferably be ball bearings, for example radial ball bearings or four-point ball bearings.
  • 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
  • the transmission part 23 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.
  • 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.
  • 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.
  • 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.
  • connection hole 27 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.
  • 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.
  • 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.
  • 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.
  • connection part 11 was summarized or integrated with the transmission part 23 to a new, one-piece connection and transmission part 24.
  • connection part 11 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.
  • 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.
  • the transmission portion of the integrated connection and transmission part 24 could be made solid, so for example. More completely meet the cavity or Kehlungs Colour 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.
  • 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 Veitatisabites and thereby improve the dimensional stability;
  • 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 ,
  • 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.
  • 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 °.
  • 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.
  • 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.
  • 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.
  • Fig. 6 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 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.
  • 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.
  • 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 Jardinkonstutation 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Connection element 31 screw connection

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Wind Motors (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un engrenage servant à répartir un couple de rotation d'entrée d'un organe d'entrée sur au moins deux organes de sortie, comprenant deux éléments de raccordement à symétrie de révolution pourvus chacun d'une surface de raccordement plane destinée à être raccordée de manière solidaire en rotation à deux éléments de machine ou d'installation différents ou à un élément de machine ou d'installation d'une part et un châssis ou une fondation d'autre part, les deux éléments de raccordement à symétrie de révolution étant orientés de sorte que leurs axes de symétrie sont coaxiaux et leurs surfaces de raccordement sont opposées l'une à l'autre. Entre ces deux éléments de raccordement se trouvent une fente dans laquelle est agencé au moins un montage sur palier à roulement en tant que palier principal, servant à monter sur palier les deux éléments de raccordement l'un par rapport à l'autre, de façon à pouvoir tourner autour d'un axe de rotation de palier principal correspondant à l'axe de symétrie commun des deux éléments de raccordement. Au moins une surface latérale d'un élément de raccordement est entièrement pourvue d'une denture. Selon l'invention, l'élément de raccordement non denté comprend une partie qui est orientée vers la denture de l'élément de raccordement denté et qui présente une ou plusieurs cavités ouvertes vers la denture et destinées à recevoir des roues d'engrenage dentées. Une ouverture servant à dévier le couple de rotation de sortie respectif est ménagée dans l'élément de raccordement non denté pour chaque roue d'engrenage. Au moins une zone annulaire fermée, alignée avec ladite ouverture, est destinée à soutenir un palier faisant office de palier de roue pour la roue d'engrenage concernée, ledit palier étant agencé dans le sens axial entre les surfaces de raccordement des deux éléments de raccordement, de sorte que la roue d'engrenage concernée tourne autour d'un axe de rotation secondaire excentré par rapport à l'axe de rotation de palier principal mais parallèle à ce dernier et vient s'engrener dans la denture de l'élément de raccordement denté. L'invention concerne également une éolienne équipée d'un tel engrenage.
PCT/EP2012/001817 2011-04-28 2012-04-27 Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif Ceased WO2012146382A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12727779.6A EP2702298A1 (fr) 2011-04-28 2012-04-27 Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif
CN201280032142.5A CN103635713A (zh) 2011-04-28 2012-04-27 用于传递旋转能量的装置以及配备该装置的风力发电设备

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102011019001A DE102011019001A1 (de) 2011-04-28 2011-04-28 Energieübertragungsbaugruppe mit mehreren Abtriebsaggregaten, insbesondere auch damit ausgestattete Windenergieanlage
DE102011019002.3 2011-04-28
DE102011019002A DE102011019002A1 (de) 2011-04-28 2011-04-28 Energieübertragungsbaugruppe mit mehreren Abtriebsaggregaten
DE102011019001.5 2011-04-28

Publications (1)

Publication Number Publication Date
WO2012146382A1 true WO2012146382A1 (fr) 2012-11-01

Family

ID=46317316

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/001817 Ceased WO2012146382A1 (fr) 2011-04-28 2012-04-27 Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif

Country Status (3)

Country Link
EP (1) EP2702298A1 (fr)
CN (1) CN103635713A (fr)
WO (1) WO2012146382A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017021768A1 (fr) * 2015-08-04 2017-02-09 Imo Holding Gmbh Joint tournant
US20220228628A1 (en) * 2021-01-19 2022-07-21 Aktiebolaget Skf Slewing bearing and applications thereof
US20240183388A1 (en) * 2022-12-05 2024-06-06 Aktiebolaget Skf Rolling bearing with protruding nose and gear

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104329424B (zh) * 2014-10-24 2016-09-14 戴召林 余能叠加助力机
EP3247899B1 (fr) 2015-01-22 2018-10-17 Vestas Wind Systems A/S Nacelle d'éolienne
DE102019201933A1 (de) 2019-02-14 2020-08-20 Robert Bosch Gmbh Lenksystem
DE102019133866A1 (de) 2019-12-11 2021-06-17 Schaeffler Technologies AG & Co. KG Getriebeeinheit für eine Antriebsanordnung sowie Verfahren zur Montage der Getriebeeinheit
CN113629970B (zh) * 2020-05-08 2022-05-27 河北国创石油设备有限公司 一种直线电机动子芯轴短节间等直径连接装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4113624A1 (de) * 1991-04-26 1992-10-29 Heinrich Dr Ing Moesinger Getriebe zum an- oder abtrieb von rotoren fuer maschinen zur umsetzung zwischen mechanischer energie und stroemungsenergie
JPH05164037A (ja) * 1991-12-13 1993-06-29 Mitsubishi Heavy Ind Ltd 風力発電装置
DE29609794U1 (de) * 1996-06-03 1996-08-22 aerodyn GmbH, 24768 Rendsburg Getriebe-Generator-Kombination
DE10318945B3 (de) 2003-04-26 2004-10-28 Aerodyn Gmbh Getriebeanordnung für Windenergieanlagen
DE202005007450U1 (de) * 2004-05-17 2005-07-14 Hehenberger, Gerald, Dipl.-Ing. Adapter zum Befestigen von Rotorblättern einer Windkraftanlage an einer Rotornabe und Windkraftanlage mit solchen Adaptern
JP2006144598A (ja) * 2004-11-17 2006-06-08 Seisa Gear Ltd ウインドタービン装置増速装置
WO2008092448A1 (fr) * 2007-01-31 2008-08-07 Vestas Wind Systems A/S Éolienne à chaîne dynamique
EP1985846A1 (fr) * 2007-04-27 2008-10-29 Greenergy India Private Limited Éolienne
CN101344072A (zh) * 2007-10-25 2009-01-14 姜星柱 一轴多机增速风力发电机组
US20110012360A1 (en) * 2008-06-10 2011-01-20 Mitsubishi Heavy Industries, Ltd. Wind turbine generator and method for constructing the same

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7008348B2 (en) * 2003-02-18 2006-03-07 General Electric Company Gearbox for wind turbine
CN2739383Y (zh) * 2004-10-12 2005-11-09 南京高速齿轮制造有限公司 风力发电机增速齿轮箱

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4113624A1 (de) * 1991-04-26 1992-10-29 Heinrich Dr Ing Moesinger Getriebe zum an- oder abtrieb von rotoren fuer maschinen zur umsetzung zwischen mechanischer energie und stroemungsenergie
JPH05164037A (ja) * 1991-12-13 1993-06-29 Mitsubishi Heavy Ind Ltd 風力発電装置
DE29609794U1 (de) * 1996-06-03 1996-08-22 aerodyn GmbH, 24768 Rendsburg Getriebe-Generator-Kombination
EP0811764A1 (fr) 1996-06-03 1997-12-10 aerodyn Energiesysteme GmbH Combinaison réducteur-générateur pour eolienne
DE10318945B3 (de) 2003-04-26 2004-10-28 Aerodyn Gmbh Getriebeanordnung für Windenergieanlagen
DE202005007450U1 (de) * 2004-05-17 2005-07-14 Hehenberger, Gerald, Dipl.-Ing. Adapter zum Befestigen von Rotorblättern einer Windkraftanlage an einer Rotornabe und Windkraftanlage mit solchen Adaptern
JP2006144598A (ja) * 2004-11-17 2006-06-08 Seisa Gear Ltd ウインドタービン装置増速装置
WO2008092448A1 (fr) * 2007-01-31 2008-08-07 Vestas Wind Systems A/S Éolienne à chaîne dynamique
EP1985846A1 (fr) * 2007-04-27 2008-10-29 Greenergy India Private Limited Éolienne
CN101344072A (zh) * 2007-10-25 2009-01-14 姜星柱 一轴多机增速风力发电机组
US20110012360A1 (en) * 2008-06-10 2011-01-20 Mitsubishi Heavy Industries, Ltd. Wind turbine generator and method for constructing the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
VON DER RWTH AACHEN: "Hydrostatic Drive Train in Wind Energy Plants", 2011

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017021768A1 (fr) * 2015-08-04 2017-02-09 Imo Holding Gmbh Joint tournant
US20220228628A1 (en) * 2021-01-19 2022-07-21 Aktiebolaget Skf Slewing bearing and applications thereof
US11692590B2 (en) * 2021-01-19 2023-07-04 Aktiebolaget Skf Slewing bearing and applications thereof
US20240183388A1 (en) * 2022-12-05 2024-06-06 Aktiebolaget Skf Rolling bearing with protruding nose and gear

Also Published As

Publication number Publication date
CN103635713A (zh) 2014-03-12
EP2702298A1 (fr) 2014-03-05

Similar Documents

Publication Publication Date Title
DE102005026141B4 (de) Windkraftanlage mit einer Lagereinheit für ein langgestrecktes Rotorblatt
EP2702298A1 (fr) Dispositif de transmission d'énergie de rotation et éolienne équipée de ce dispositif
EP0945613B1 (fr) Support de nacelle d'éolienne
EP2795115B1 (fr) Palier pour pales ou nacelle d'une éolienne
EP2630370B1 (fr) Module pour le découplage de l'énergie de rotation du moyeu de rotor de la roue éolienne d'une éolienne
DE102012002203A1 (de) Wälzlageranordnung zur Lagerung von Teilen einer Windkraftanlage, sowie Windkraftanlage mit einem derart ausgestalteten Blattlager
DE102010043946A1 (de) Antriebseinheit für Windturbine
EP3589839B1 (fr) Unité de réglage pour régler l'azimut et/ou le pas d'une éolienne et procédé
EP2671308B1 (fr) Logement de rotor pour une machine électrique
EP3775535B1 (fr) Palier à roulement de grande dimension
EP2708739B1 (fr) Logement de pale pour le logement rotatif d'une pale de rotor au niveau du moyeu d'une installation éolienne et installation éolienne équipée de celui-ci
WO2011042131A1 (fr) Train d'engrenage planétaire sans support
EP2655879B1 (fr) Éolienne
EP3550140A1 (fr) Support de machine pour éolienne
DE102015119173A1 (de) Planetengetriebe sowie Verfahren zur Wartung eines Planetengetriebes
DE102005039434A1 (de) Windenergieanlage
DE102013006281B4 (de) Antriebs- oder Verstellvorrichtung
EP3491238B1 (fr) Bâti machine et rotor pour éolienne et procédé correspondant
DE102011019002A1 (de) Energieübertragungsbaugruppe mit mehreren Abtriebsaggregaten
WO2015018382A1 (fr) Ensemble palier de pale
EP3242013A1 (fr) Éolienne comprenant un dispositif destine a faire tourner une nacelle de l'eolienne et procede de montage d'un dispositif destine a faire tourner une nacelle
DE102021209955B4 (de) Getriebe für ein Flurförderfahrzeug sowie Flurförderfahrzeug mit dem Getriebe
EP3502464B1 (fr) Éolienne pourvue de chaîne cinématique
DE102005016156A1 (de) Windenergieanlage
DE102005063678B3 (de) Verfahren zum Betrieb einer Windkraftanlage mit einer Lagereinheit für ein langgestrecktes Rotorblatt

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12727779

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2012727779

Country of ref document: EP