WO2023139048A1 - Ensemble roulement à rouleaux de grand diamètre à charge optimisée - Google Patents

Ensemble roulement à rouleaux de grand diamètre à charge optimisée Download PDF

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Publication number
WO2023139048A1
WO2023139048A1 PCT/EP2023/050952 EP2023050952W WO2023139048A1 WO 2023139048 A1 WO2023139048 A1 WO 2023139048A1 EP 2023050952 W EP2023050952 W EP 2023050952W WO 2023139048 A1 WO2023139048 A1 WO 2023139048A1
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WO
WIPO (PCT)
Prior art keywords
inner ring
ring
rolling
bearing arrangement
row
Prior art date
Application number
PCT/EP2023/050952
Other languages
German (de)
English (en)
Inventor
Christian Büker
Marco Burtchen
Nico BUSEMANN
Michael DAHLHOFF
Martin Stolz
Original Assignee
thyssenkrupp rothe erde Germany GmbH
Thyssenkrupp Ag
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
Application filed by thyssenkrupp rothe erde Germany GmbH, Thyssenkrupp Ag filed Critical thyssenkrupp rothe erde Germany GmbH
Publication of WO2023139048A1 publication Critical patent/WO2023139048A1/fr

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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
    • 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
    • F16C19/383—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/52—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers
    • F16C33/523—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers with pins extending into holes or bores on the axis of the rollers
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • F16C2240/34—Contact angles
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones

Definitions

  • the invention relates to a roller bearing arrangement according to the preamble of patent claim 1 .
  • a roller bearing arrangement for a wind turbine which has an outer ring and an inner ring that can rotate about an axis of rotation relative to the outer ring.
  • a first tapered roller bearing with first rolling elements and a second tapered roller bearing with second rolling elements are formed between the outer ring and the inner ring.
  • the axes of rotation of the first and second rolling bodies are each aligned inclined relative to the axis of rotation, with the first and the second tapered roller bearing being designed asymmetrically.
  • the first rolling elements each rotate about a first axis of rotation and have a first running surface arranged concentrically about the first axis of rotation.
  • the second rolling bodies each rotate about a second axis of rotation and have a second running surface arranged concentrically about the second axis of rotation.
  • the extent of the first running surface parallel to the first axis of rotation is in each case greater than the extent of the second running surface parallel to the second axis of rotation.
  • the two differently designed tapered roller bearings ensure that the roller bearing arrangement can be adapted to the uneven loads on the two rows of roller bodies that occur in wind turbines.
  • the inner ring can be screwed to the fixed machine structure (see FIG. 2) and according to another embodiment (FIG. 3) to the part to be rotatably mounted on it, with the outer ring then being connected to the other rotating partner.
  • the inner ring is screwed to the assigned rotating partner, namely the fixed machine structure or the rotating part, via bolts parallel to the ring axis and passing through the inner ring. In this way, for the absorption of the torques occurring during operation about axes perpendicular to the bearing axis, there is a base which essentially corresponds to the diameter of the inner ring.
  • the inner ring can be designed as a symmetrical inner ring with the same raceway pressure angles/support angles for the two rows of rolling elements or as an asymmetrical inner ring with different raceway pressure angles/support angles for the two rows of rolling elements (cf. exemplary embodiment according to FIG. 9).
  • both the outer ring and the inner ring of the bearing arrangement must be designed in one piece.
  • This design results in a bearing arrangement with a significantly higher dimensional stability compared to a solution with a split inner ring and with a significantly simplified assembly compared to an inner ring which in turn is supported on a solid supporting and assembly structure.
  • the raceways of the rows of rolling elements cannot shift against one another because of the one-piece design of the inner ring.
  • DE 10 2010 054 948 A1 proposes forming the inner ring in one piece.
  • the outer ring should also be designed in one piece.
  • the one-piece design of the inner ring and outer ring has the disadvantage that the assembly of the bearing is made considerably more difficult.
  • the outer ring has to be heated to considerably higher temperatures in order to be able to assemble the bearing.
  • the object of the invention is to further develop a bearing arrangement according to the preamble of claim 1 in such a way that unfavorable load distributions and overloads in the rows of rolling elements and the raceways are avoided and the required service life of the raceways and the rolling elements is ensured without a design restriction to a one-piece inner ring.
  • the inner ring has at least one first division arranged on the rotor hub side and a second division arranged on the generator side, the axial extent of one half of the inner ring facing the generator being greater than the axial extent of one half of the inner ring facing the rotor hub, the axial extent of the half of the inner ring facing the generator being dimensioned in the direction of the generator such that the entire inner ring has such a large resistance to deformation under the loads occurring during operation of the bearing arrangement that a maximum permissible surface pressure between the rolling elements and the raceways is maintained and that a required service life of the raceways is achieved.
  • the teaching according to the invention is based on the finding that in rolling bearing arrangements with a multi-part inner ring, the provision of a specifically dimensioned additional mass, which is arranged on the side of the inner ring facing the generator and extends in the direction of the generator, allows the deformation resistance of the inner ring (or, to put it another way, the torsional rigidity of the inner ring) to be increased in a targeted manner in comparison to an inner ring without an additional mass such that the in the prior art of DE 10 2010 054 948 A1
  • the disadvantages criticized for bearing arrangements with multi-part inner rings can be avoided.
  • the above design measures also prevent the ring from tipping over.
  • the roller bearing arrangement according to the invention can be assembled much more easily, quickly and cost-effectively than the bearing arrangement known from DE 10 2010 054 948 A1.
  • the additional mass is dimensioned such that under the loads occurring during operation of the roller bearing arrangement, there is no overloading in the rows of rolling elements and the raceways, and the required service life of the raceways is reliably achieved.
  • the multi-part inner ring can, for example, be designed in two parts with a so-called support ring and a so-called retaining ring.
  • the inner ring can be designed in three parts, for example, with a support ring, a retaining ring and a middle ring arranged between them.
  • the inner ring has a through hole through which a threaded bolt or a screw can be pushed, the inner ring being able to be connected to the rotor hub via this threaded bolt or this screw.
  • This embodiment is particularly useful when there is sufficient space to arrange a screw head or a nut on the rotor hub side and also to provide a nut on the generator side to connect the inner ring to the rotor hub.
  • the inner ring has a threaded bore extending from the first axial end face in the direction of the second axial end face, which is designed as a blind hole and via which the inner ring can be connected to the rotor hub.
  • the threaded bore is formed by a through bore extending through the first partial ring and a blind bore which is aligned with the through bore and extends into the second partial ring.
  • a one-sided, rotor-hub-side attachment of the inner ring can be implemented even in very cramped installation spaces, without the inner ring deforming too much under the loads acting on it during operation.
  • support of the inner ring by the connecting structure to prevent an excessively large deformation of the inner ring under load (which cannot be implemented structurally in the case of extremely cramped installation space conditions) can be dispensed with.
  • a middle ring is arranged between the first partial ring and the second partial ring, the middle ring having a through bore which is aligned with the through bore of the first partial ring and the through bore or the blind hole of the second partial ring.
  • the middle ring has the advantage that the bearing is easier to mount and the bearing play can be adjusted more easily.
  • the rolling bodies of the first and second row of rolling bodies can be guided or held by cages.
  • Different cage designs can be used, for example bolt cages or window or pocket cages.
  • bolt cages the individual rolling elements are held on bolts so that they can rotate, with the bolts being screwed into a circumferential cage ring in their fastening position.
  • window or pocket cages the rolling elements are arranged in receiving windows or receiving pockets.
  • the rolling bodies of the first and second row of rolling bodies are designed as rollers guided on bolts, the middle ring having bolt securing elements which prevent the bolts from loosening or slipping out of their fastening position.
  • the bolt securing elements are designed as support surfaces or securing surfaces which are formed on the central ring and prevent the bolts from slipping.
  • the support surfaces or locking surfaces can be hardened to counteract premature wear of these support surfaces. Due to the fact that the support surfaces are formed on a separate center ring, the support surfaces can be hardened on the center ring in a simple manner without the first pitch or the second pitch also having to be handled.
  • the supporting surfaces can be hardened, for example, by inductive surface layer hardening.
  • the rolling bodies of the first and second row of rolling bodies are arranged in receiving windows of window cages.
  • preferably case-hardened rollers are not required as rolling bodies.
  • the rolling elements of the first row of rolling elements have a different supporting length and/or are arranged with a different supporting angle than the rolling elements of the second row of rolling elements, so that the two rows of rolling elements are optimally designed with regard to the loads acting on them during operation. In this way, an unnecessary oversizing of the less loaded row of rolling elements can be avoided. If the rows of rolling elements are not adapted to the respective loads, but are designed symmetrically and the same, then the row of rolling elements that is subjected to the lower loads during operation must inevitably be oversized, because the row of rolling elements that is subjected to the greater load determines the design. This is achieved with a targeted structural adjustment of the design of the rolling elements and the raceways to the loads that actually occur during operation of the respective Row of rolling elements prevented. By avoiding oversizing, the weight of the rolling body arrangement can be optimized.
  • the bearing arrangement is adapted to the loads that occur during operation by designing the two rows of rolling bodies that differ from one another.
  • other characteristics of the rolling elements and the raceways can also be adapted to the loads to be endured during operation, e.g. the curvature profiles of the rolling elements and the raceways.
  • FIG. 1 shows a first embodiment of the roller bearing arrangement according to the invention with a roller body cage designed as a pin cage and a three-part inner ring with a through hole;
  • FIG. 2 shows a second embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the first embodiment, with a window cage being provided instead of a bolt cage;
  • FIG. 3 shows a third embodiment of the roller bearing arrangement according to the invention with a roller body cage designed as a pin cage and a three-part inner ring with a threaded hole designed as a blind hole;
  • FIG. 4 shows a fourth embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the third embodiment, with a window cage being provided instead of a pin cage;
  • 5 shows a fifth embodiment of the roller bearing arrangement according to the invention with a roller body cage designed as a pin cage and a four-part inner ring with a threaded hole designed as a blind hole;
  • FIG. 6 shows a sixth embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the fifth embodiment, with a window cage being provided instead of a pin cage.
  • FIG. 7 shows a seventh embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the third embodiment, the two rows of roller bodies having differently dimensioned roller bodies and raceways.
  • Fig. 1 shows a roller bearing assembly according to the invention in axial half section.
  • the roller bearing arrangement has an outer ring 1 .
  • the outer ring 1 is fastened to a component (not shown) of a connecting structure of the wind turbine via a screw connection (not shown in FIG. 1 ).
  • the roller bearing arrangement has an inner ring 2 with an end face 20 and an end face 21 .
  • the inner ring 2 is connected on its end face 20 to a hub of the wind turbine, also not shown, via a screw connection 30 (not shown).
  • the inner ring 2 has no further connection or support from the connection structure of the wind turbine.
  • the end face 21 of the inner ring 2 is not connected to a component of the connection structure of the wind turbine.
  • the rolling elements 3, 4 are arranged spaced apart from one another in the axial direction.
  • the first row of rolling elements 3 has rolling elements 8 and the second row of rolling elements 4 has rolling elements 10 .
  • the rolling elements 8, 10 are arranged circumferentially next to one another in the circumferential direction of the roller bearing.
  • the rolling bodies 8, 10 roll on the raceways 7, 9, 11, 13, so that the inner ring connected to the hub of the wind turbine 2 is rotatable relative to the non-rotatable outer ring 1 connected to the adjacent structure of the wind turbine.
  • the rolling elements 8, 10 are arranged in pin cages 60.
  • the rolling elements 8, 10 are guided on bolts 61 such that they can rotate.
  • the rolling bodies 8, 10 have through bores which run coaxially to their axis of rotation and through which the bolts 61 are inserted.
  • the pin cages 60 have first cage rings 64 on the side of the rolling bodies 8 , 10 facing the inner ring 2 and second cage rings 65 on the side of the rolling bodies 8 , 10 pointing radially outwards.
  • the bolts 61 are pushed through the first cage rings 64 and screwed into the second cage rings 65 . In this way, the rolling elements 8, 10 are rotatably held between the first cage rings 64 and the second cage rings 65.
  • the outer ring 1 has two wedge flanks 5, 6 on which raceways 7, 8 for the rolling bodies 8, 10 are formed.
  • the inner ring 2 is designed in three parts.
  • the inner ring 2 has a first partial ring 40 , a second partial ring 41 and a middle ring 42 arranged between the first 40 and second partial ring 41 .
  • a raceway 11 is formed on the first partial ring 40, on which the rolling elements 8 of the first row 3 of rolling elements roll.
  • a raceway 13 is formed on the second partial ring 41, on which the rolling elements 10 of the second row 4 of rolling elements roll. All raceways 7, 9, 11, 13 are preferably hardened, in particular surface layer hardened, for example by inductive surface layer hardening.
  • the inner ring 2 has a through bore 50, via which the inner ring 2 is fastened to the hub of the wind energy installation with its end face 20 facing the hub (not shown).
  • the through hole 50 is formed by three through holes 50A, 50B, 50C aligned with one another.
  • a threaded bolt or a screw is inserted through the through hole 50 and screwed to the hub of the wind turbine.
  • the threaded bolt points to the one facing the generator
  • the end face 21 of the inner ring 2 has a nut (not shown in FIG. 1), or the screw has a screw head (not shown in FIG. 1) on the end face 21 of the inner ring 2 facing the generator.
  • the middle ring 42 has support surfaces 63 which prevent the bolts 61 from slipping or becoming detached unintentionally.
  • the support surfaces 63 thus form bolt securing elements 62 on which the bolts 61 are supported if they are released from their fastening position, i.e. if they are released, for example, from the position screwed into the second cage ring 65 and slip radially inwards towards the inner ring 2.
  • the inner ring 2 is asymmetrical.
  • the axial extent of the half of the inner ring 2 facing the generator is significantly greater than the axial extent of the half of the inner ring 2 facing the rotor hub.
  • the axial extent of the half of the inner ring 2 facing the generator is dimensioned in the direction of the generator in such a way that the entire inner ring 2 has such a great resistance to deformation under the loads occurring during operation of the bearing arrangement that a maximum permissible surface pressure between the rolling elements 8, 10 and the raceways 7, 9, 11, 13 are complied with and a required raceway service life is achieved.
  • the overall rigidity of the inner ring 2 can be increased and the resistance of the multi-part inner ring 2 to the disadvantageous behavior at high loads set out in the prior art can be improved in such a way that the maximum permissible surface pressure between the rolling elements and the raceways is maintained even at high and very high loads during operation and the required service life of the roller bearing arrangement is achieved .
  • the gaping of the individual rings described in the prior art for multi-part inner rings and the occurrence of mutual radial displacements of the individual rings relative to one another and undesired tipping of the inner ring can be effectively avoided by the structural measure according to the invention.
  • FIG. 2 shows a second embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the first embodiment according to FIG. 1, a window cage 70 being provided instead of a bolt cage 60.
  • FIG. The rolling bodies 8, 10 are held in receiving windows of the window cage 70. This has the advantage that no preferably case-hardened rolling bodies 8, 10 have to be used.
  • the rolling bodies 8, 10 do not have to be provided with central bores for the passage of bolts 61.
  • the center ring 42 also does not have to have any special functional surfaces, such as the support surfaces 63 in the embodiment according to FIG. 1.
  • FIG. 3 shows a third embodiment of the roller bearing arrangement according to the invention.
  • What has already been described above with regard to FIG. 1 also applies to the embodiment of the invention shown in FIG.
  • a threaded bolt or a screw can be screwed into the threaded bore 51 designed as a blind bore 52 from the hub side.
  • the space requirement can be minimized in the case of very cramped space conditions, ie when only a very limited space is available for accommodating the roller bearing arrangement.
  • the installation space for accommodating the nuts or screw heads can be saved on the side facing the generator. This can also considerably simplify the assembly and disassembly of the roller bearing arrangement, particularly in the case of extremely cramped installation space.
  • FIG. 4 shows a fourth embodiment of the invention, which essentially corresponds to the third embodiment according to FIG. 3, a window cage 70 being provided instead of a bolt cage 60.
  • FIG. 5 The advantages of the window cage 70 described above for FIG. 2 also apply to the embodiment according to FIG. 4.
  • Fig. 5 a fifth embodiment of the invention is shown.
  • the rolling elements 8, 10 are in turn arranged in pin cages 60, as already described above.
  • a four-part inner ring 2 is provided in the embodiment according to FIG.
  • This four-part inner ring 2 is composed of a first partial ring 40, a second partial ring 41, a middle ring 42 arranged between the two partial rings 40, 41 and a reinforcing ring 43.
  • the first partial ring 40, the middle ring 42 and the second partial ring 41 each have a through hole 50A, 50B or 50C.
  • a threaded bore 51 designed as a blind bore 52 is arranged in the reinforcement ring 43 facing the generator side.
  • the middle ring 42 is comparable to the middle ring 42 according to the embodiments according to FIG. 1 and FIG.
  • the first partial ring 40 corresponds to the first partial ring 40 in the embodiments according to FIGS. 1 and 3 .
  • the second partial ring 41 is designed essentially symmetrically to the first partial ring 40 .
  • the axial extension of the second half of the inner ring 2 is adjusted in the embodiment of the invention shown in FIG.
  • the additional reinforcement ring 43 achieves advantages in the manufacture of the bearing rings.
  • the production process is more complex than the production process for the second partial ring 41 and the reinforcing ring in the embodiment according to FIG. 5 due to the special geometry of the second partial ring 41.
  • the separate reinforcing ring 43 can therefore save production time and costs.
  • FIG. 6 shows a sixth embodiment of the roller bearing arrangement according to the invention, which essentially corresponds to the fifth embodiment according to FIG.
  • the advantages explained in relation to FIG. 5 also apply analogously to the embodiment of the invention shown in FIG. Instead of a bolt cage 60 as in Fig. 5, in Fig. 6
  • a window cage 70 is provided, whereby the advantages already described for the exemplary embodiments according to FIGS. 2 and 4 are achieved.
  • Fig. 7 shows a seventh embodiment of the rolling bearing assembly according to the invention, which is essentially like the third embodiment. 3 corresponds. What has already been described above for Fig. 3 also applies to the embodiment of the invention shown in Fig. 7, wherein the rolling elements 8 of the first row of rolling elements 3 have a different supporting length and/or are arranged with a different supporting angle than the rolling elements 10 of the second row of rolling elements 4, so that the two rows of rolling elements are optimally designed with regard to the loads acting on them during operation.
  • the rolling elements 8, 10 are supported on shelves that ring on the part 40 and 41 are formed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention se rapporte à un ensemble roulement à rouleaux comprenant une bague externe (1) et une bague interne (2) pour le montage d'un rotor d'une éolienne. La bague interne (2) présente un premier côté d'extrémité axiale (20) faisant face à un moyeu de rotor de l'éolienne et un second côté d'extrémité axiale (21) opposé au premier côté d'extrémité axiale (20) et faisant face à un générateur de l'éolienne. La bague interne (2) peut être reliée au moyeu de rotor de l'éolienne sur le premier côté d'extrémité axiale (20) par l'intermédiaire d'un raccord à vis (30) et est agencée sans support supplémentaire à partir d'une construction de liaison de l'éolienne. Selon l'invention, afin d'éviter des distributions de charge défavorables et une surcharge dans les rangées d'éléments roulants et les chemins de roulement et d'assurer la durée de vie requise des chemins de roulement et des éléments roulants, la bague interne (2) présente au moins une première sous-bague côté moyeu de rotor (40) et une seconde sous-bague côté générateur (41), l'extension axiale d'une moitié de la bague interne (2) faisant face au générateur étant supérieure dans la direction axiale d'une moitié de la bague interne (2) faisant face au moyeu de rotor, l'extension axiale de la moitié de la bague interne (2) faisant face au générateur étant mesurée dans la direction du générateur de sorte que, avec le chargement se produisant pendant l'opération de l'ensemble roulement, toute la bague interne (2) présente une résistance à la déformation suffisante pour qu'une pression de surface admissible maximale soit maintenue entre les éléments roulants (8, 10) et les chemins de roulement (7, 9, 11, 13) et une durée de vie de chemin de roulement requise soit obtenue.
PCT/EP2023/050952 2022-01-18 2023-01-17 Ensemble roulement à rouleaux de grand diamètre à charge optimisée WO2023139048A1 (fr)

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DE102022200534.1A DE102022200534A1 (de) 2022-01-18 2022-01-18 Belastungsoptimierte Großwälzlageranordnung

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010054948A1 (de) 2010-12-17 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Lageranordnung
CN102312918B (zh) * 2011-06-14 2014-07-16 安徽枞晨回转支承有限公司 双排斜柱式回转支承
DE102014104862A1 (de) * 2014-04-04 2015-10-08 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102014104863A1 (de) * 2014-04-04 2015-10-08 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102014106558A1 (de) * 2014-05-09 2015-11-12 Thyssenkrupp Ag Lageranordnung und Kegelrollenlager

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017106962A1 (de) 2017-03-31 2018-10-04 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010054948A1 (de) 2010-12-17 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Lageranordnung
CN102312918B (zh) * 2011-06-14 2014-07-16 安徽枞晨回转支承有限公司 双排斜柱式回转支承
DE102014104862A1 (de) * 2014-04-04 2015-10-08 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102014104863A1 (de) * 2014-04-04 2015-10-08 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE202014010876U1 (de) 2014-04-04 2017-04-07 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102014106558A1 (de) * 2014-05-09 2015-11-12 Thyssenkrupp Ag Lageranordnung und Kegelrollenlager

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