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DE19917498A1 - Roller bearing swivel connection - Google Patents

Roller bearing swivel connection

Info

Publication number
DE19917498A1
DE19917498A1 DE19917498A DE19917498A DE19917498A1 DE 19917498 A1 DE19917498 A1 DE 19917498A1 DE 19917498 A DE19917498 A DE 19917498A DE 19917498 A DE19917498 A DE 19917498A DE 19917498 A1 DE19917498 A1 DE 19917498A1
Authority
DE
Germany
Prior art keywords
braking
braking surfaces
roller bearing
rolling
slewing ring
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.)
Withdrawn
Application number
DE19917498A
Other languages
German (de)
Inventor
Juergen Holzmueller
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to DE19917498A priority Critical patent/DE19917498A1/en
Publication of DE19917498A1 publication Critical patent/DE19917498A1/en
Priority to DE10012773A priority patent/DE10012773A1/en
Withdrawn legal-status Critical Current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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts
    • 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
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • 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
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F05B2240/52—Axial thrust bearings
    • 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
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F05B2240/54—Radial bearings
    • 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
    • F05B2260/90—Braking
    • F05B2260/902—Braking using frictional mechanical forces
    • 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
    • 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

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)
  • Braking Arrangements (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Roller bearing swivel connection has increased friction between rings (2, 3) on the braking surfaces (15, 16) above outer regulating power feed which swivel movements oppose a braking couple and prevent swivel movements at a correspondingly high braking couple.

Description

Die Erfindung betrifft eine Wälzlager-Drehverbindung, insbesondere für die Maschinenhauslagerung von Windenergieanlagen, bestehend aus zwei Laufringen, welche über abrollende Wälzkörper relative Drehbewegungen zueinander mit geringer Reibung ausführen können und einer integrierten Bremseinrichtung, welche aus mit einem Laufring drehfest verbundenen Bremsflächen und mit dem anderen Laufring drehfest verbundenen Bremsflächen, die über eine Normalkraft gegeneinandergepreßt werden, besteht.The invention relates to a rolling bearing slewing ring, in particular for the storage of nacelles Wind turbines, consisting of two races, which are relative to rolling rolling elements Can perform rotary movements to each other with low friction and an integrated Braking device, which consists of braking surfaces connected in a rotationally fixed manner to one race and to the other Running ring non-rotatably connected braking surfaces, which are pressed against each other by a normal force, consists.

Die Maschinenhauslagerung von Windenergieanlagen ist durch Unwucht und ungleichmäßiger Anströmung des Rotors ständigen Drehschwingungen ausgesetzt. Durch die geringen Schwenkbewegungen kommt es zum Gleiten der Wälzkörper auf der Laufbahn, welches Riffelbildung und Lagerausfall zur Folge haben kann. Ungebremst übertragen sich diese vom Betrag nicht unerheblichen sogenannten Giermomente über die Verzahnung eines Lagerringes auf die zugehörigen Drehwerksantriebe zur Windrichtungsnachführung, welche daher entsprechend größer dimensioniert werden müssen. Außerhalb der Wälzlager-Drehverbindung montierte regelbare Bremsen benötigen viel Bauraum und sind der aggressiven Atmosphäre, in der diese Anlagen aufgestellt sind, ausgesetzt. Permanent wirkende in die Wälzlager-Drehverbindung integrierte Bremseinrichtungen, wie in DE 37 25 972 A1 und DE 41 04 137 C2 vorgeschlagen, erfordern für die Windrichtungsnachführung entsprechend groß dimensionierte Drehwerksantriebe, um neben dem aerodynamischen Giermoment auch das Bremsmoment zu überwinden. Nachteilig wirkt sich bei diesen Ausbildungen ein erhöhter Verschleiß der Bremsflächen aus, was zur Folge hat, daß die Bremsvorspannung, erzeugt durch Federpakete, Stellschrauben oder anderen Mechanismen, nachgestellt werden muß.The machine house storage of wind turbines is due to unbalance and uneven flow exposed to constant torsional vibrations. Because of the small swiveling movements for sliding the rolling elements on the raceway, which results in corrugation and bearing failure can. Unrestrained, these so-called yaw moments, which are not insignificant in terms of amount, are transferred via the Toothing of a bearing ring on the associated slewing gear drives for wind direction tracking, which must therefore be dimensioned larger accordingly. Outside the rolling bearing slewing ring Mounted adjustable brakes take up a lot of space and are the aggressive atmosphere in which Plants are exposed. Permanently integrated in the rolling bearing slewing ring Braking devices, as proposed in DE 37 25 972 A1 and DE 41 04 137 C2, require for Wind direction tracking correspondingly large-sized slewing gear drives, in addition to the aerodynamic yaw moment also overcome the braking moment. This has a disadvantageous effect Training from increased wear of the braking surfaces, which has the consequence that the brake preload, generated by spring packs, set screws or other mechanisms, must be adjusted.

Der Erfindung liegt die Aufgabe zugrunde, eine Wälzlager-Drehverbindung mit integrierter Bremseinrichtung derartig auszubilden, daß das Bremsmoment während des Betriebes regelbar wird.The invention has for its object a rolling bearing slewing ring with integrated To design the braking device in such a way that the braking torque can be regulated during operation.

Diese Ausführung wird erfindungsgemaß durch das kennzeichnende Merkmal des Anspruchs 1 gelöst. Verschiedene vorteilhafte Aus- und Weiterbildungen sind in den Ansprüchen 2 bis 12 beschrieben.This embodiment is achieved according to the invention by the characterizing feature of claim 1. Various advantageous training and further developments are described in claims 2 to 12.

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden nachfolgend näher beschrieben. Es zeigen:Embodiments of the invention are shown in the drawings and are described in more detail below described. Show it:

Fig. 1 den teilweisen Schnitt durch Ausführungsbeispiel 1 der Erfindung Fig. 1 shows the partial section through embodiment 1 of the invention

Fig. 2 die teilweise Draufsicht und den teilweisen Schnitt auf bzw. durch Ausführungsbeispiel 1 der Erfindung. Fig. 2 shows the partial plan view and the partial section on or through embodiment 1 of the invention.

Fig. 3 den teilweisen Schnitt durch Ausführungsbeispiel 2 der Erfindung. Fig. 3 shows the partial section through embodiment 2 of the invention.

Fig. 4 die teilweise Draufsicht auf Ausführungsbeispiel 2 der Erfindung. Fig. 4 is a partial top view of embodiment 2 of the invention.

Die Wälzlager-Drehverbindung 1 besteht aus einem Innenring 2 und einem Außenring 3, die drehbar zueinander über Kugeln 4 als Wälzkörper verbunden sind. Der Außenring besitzt eine Verzahnung 5, in die die nicht dargestellten Ritzel der Drehantriebe eingreifen. Über Befestigungsbohrungen 6, 7 sind die Lagerringe 2, 3 mit den Anschlußkonstruktionen 8, 9 verschraubt. Zwischen den Lagerringen 2, 3 befindet sich ein Lagerspalt 10.The rolling bearing slewing ring 1 consists of an inner ring 2 and an outer ring 3 , which are rotatably connected to each other via balls 4 as rolling elements. The outer ring has a toothing 5 , in which engage the pinions of the rotary drives, not shown. The bearing rings 2 , 3 are screwed to the connecting structures 8 , 9 via fastening bores 6 , 7 . There is a bearing gap 10 between the bearing rings 2 , 3 .

Im ersten Ausführungsbeispiel gemaß Fig. 1 werden über eine Zuleitung 11 durch den Innenring 2 die außen als Lochkreis verteilten Zylinderbohrungen 12 mit Drucköl von außen versorgt. Die Kolben 13, welche über herkömmliche Hydraulikdichtungen 14 die Zylinderbohrungen 12 verschließen, pressen sich gegen die Bremsfläche 15 des Außenringes 3 und die Bremsfläche 16 des mit dem Außenring 3 und der Anschlußkonstruktion 8 verschraubten Zusatzringes 17. Durch die hydraulische über den Druck regelbare Normalkraft auf die sich radial überlappenden Bremsflächen der Kolben 13 und der Ringe 3, 17 entsteht erhöhte Reibung, welche Drehbewegungen ein gegensinnig wirkendes regelbares Bremsmoment entgegensetzt, bzw. bei entsprechend hohem Bremsmoment Drehbewegungen reibschlüssig verhindert. Wird der hydraulische Druck zurückgenommen, gleiten die Kolben 13 und deren Hydraulikdichtungen 14 in den Zylinderbohrungen 12 nicht nennenswert zurück, weshalb die Hydraulikdichtungen 14 nur statischer Auslegung bedürfen. Die verbleibende geringe Restreibung in der Wälzlager-Drehverbindung 1 kann von den Drehantrieben ohne Probleme überwunden werden. Durch eine geeignete Werkstoffauswahl wird bei einer Relativbewegung zwischen den Bremsflächen der Kolben 13 und der Ringe 3, 17 abrasives Verhalten Fressen sowie weitestgehend Verschleiß auch unter hydraulischer Druckbeaufschlagung verhindert. Dadurch, daß die Bremsflächen der Kolben 13 und der Ringe 3, 17 im aus umlaufenden Lippendichtungen 18, 19 bestehenden Dichtungssystem für den Wälzkörper 4 mit integriert sind, genießen sie den gleichen Schutz gegen Verschmutzung und korrosiver Atmosphäre, wie die Wälzkörper 4 selbst. Eine zwischen den Wälzkörpern 4 und der Bremsfläche 15 im Lagerspalt 10 angeordnete zusätzliche Lippendichtung 20 verhindert durch ihre Ausrichtung der Lippe ein Eindringen von Abrieb der Bremsflächen der Kolben 13 und der Ringe 3, 17 in dem Bereich der Wälzkörper 4, läßt aber überschüssiges Wälzlagerfett zu den Bremsflächen der Kolben 13 und der Ringe 3, 17 gelangen, wodurch das abrasive Verhalten weiter verringert wird. Die Zylinderbohrungen 12 sind über Querbohrungen 21 hydraulisch miteinander verbunden, so daß deshalb nur eine Druckanschlußbohrung 11 nötig ist. Wie in Fig. 2 dargestellt, können über eine axiale Bohrung im Zusatzring 17, welche im Betrieb mit einem Stopfen 22 verschlossen ist, die Kolben 13 und deren Hydraulikdichtungen 14 mit Hilfe der Sacklochgewinde 23 zu Wartungszwecken entnommen und wieder eingesetzt werden.In the first embodiment according to FIG. 1, the cylinder bores 12, which are distributed outside as a bolt circle, are supplied with pressure oil from the outside via a feed line 11 through the inner ring 2 . The pistons 13 , which close the cylinder bores 12 via conventional hydraulic seals 14 , press against the braking surface 15 of the outer ring 3 and the braking surface 16 of the additional ring 17 screwed to the outer ring 3 and the connection structure 8 . The hydraulic normal force, which can be regulated via the pressure, on the radially overlapping braking surfaces of the pistons 13 and the rings 3 , 17 results in increased friction, which counteracts rotary movements with oppositely acting, controllable braking torque or, in the case of a correspondingly high braking torque, prevents rotational movements by friction. When the hydraulic pressure is reduced, the slide piston 13 and the hydraulic seals 14 in the cylinder bores 12 do not appreciably back, and therefore the hydraulic seals 14 need only static interpretation. The remaining low residual friction in the rolling bearing slewing ring 1 can be overcome by the rotary drives without problems. A suitable choice of materials prevents abrasive behavior in the event of a relative movement between the braking surfaces of the pistons 13 and the rings 3 , 17, and prevents wear as far as possible, even under hydraulic pressure. Characterized in that the braking surfaces of the pistons 13 and the rings 3 , 17 are integrated in the sealing system for the rolling elements 4 consisting of circumferential lip seals 18 , 19 , they enjoy the same protection against dirt and corrosive atmosphere as the rolling elements 4 themselves the rolling elements 4 and the braking surface 15 arranged in the bearing gap 10 arranged additional lip seal 20 prevents penetration of abrasion of the braking surfaces of the pistons 13 and the rings 3 , 17 in the area of the rolling elements 4 , but leaves excess rolling bearing grease to the braking surfaces of the Piston 13 and the rings 3 , 17 reach, whereby the abrasive behavior is further reduced. The cylinder bores 12 are hydraulically connected to one another via cross bores 21 , so that therefore only one pressure connection bore 11 is necessary. As shown in FIG. 2, the pistons 13 and their hydraulic seals 14 can be removed and reinserted for maintenance purposes by means of the blind hole thread 23 via an axial bore in the additional ring 17 , which is closed with a plug 22 during operation.

Beim zweiten Ausführungsbeispiel nach Fig, 3 und 4 werden über eine Zuleitung 11 durch den Innenring 2 die konzentrisch im Außenbereich des Innenringes 2 eingelassenen Hohlzylinder 24 mit Drucköl von außen versorgt, welches die Bremsflächen 15, 16 der Ringkolben 25 gegen die Bremsflächen des Außenringes 3 und des Zusatzringes 17 preßt. Die Ringkolben 25 sind über spielfrei in dem Innenring 2 und in den Ringkolben 25 selbst eingesetzte Stift 26 gegen Verdrehen um das Zentrum der Wälzlager-Drehverbindung 1 beim Bremsen gesichert. Weil die flächengleichen in axialer Richtung wirkenden Ringkolben 25 vom Betrag gleich große entgegengesetzte Normalkräfte auf die Bremsflächen des Außenringes 3 und des Zusatzringes 17 ausüben, wird die Wälzlagerung als solche nicht mit Bremskräften zusätzlich belastet. In the second embodiment of Fig, 3 and 4 are supplied with pressure oil from outside via a supply line 11 through the inner ring 2, the concentrically embedded in the outer region of the inner ring 2 hollow cylinder 24, which the brake surfaces 15, 16 of the annular piston 25 against the braking surfaces of the outer ring 3 and of the additional ring 17 presses. The ring pistons 25 are secured against rotation about the center of the roller bearing rotary connection 1 when braking, by means of play in the inner ring 2 and in the ring piston 25 itself inserted pin 26 . Because the annular pistons 25, which have the same area and act in the axial direction, exert the same amount of opposite normal forces on the braking surfaces of the outer ring 3 and the additional ring 17 , the rolling bearing as such is not additionally loaded with braking forces.

BezugszeichenlisteReference list

11

Wälzlager-Drehverbindung
Rolling bearing slewing ring

22nd

Innenring
Inner ring

33rd

Außenring
Outer ring

44th

Kugeln, Wälzkörper
Balls, rolling elements

55

Verzahnung
Gearing

66

Befestigungsbohrung innen
Fastening hole on the inside

77

Befestigungsbohrung außen
Mounting hole outside

88th

Anschlußkonstruktion unten
Connection structure below

99

Anschlußkonstruktion oben
Connection structure above

1010th

Lagerspalt
Bearing gap

1111

Druckanschlußbohrung
Pressure connection hole

1212th

Zylinderbohrungen
Cylinder bores

1313

Kolben
piston

1414

Hydraulikdichtungen
Hydraulic seals

1515

Bremsfläche unten
Braking surface below

1616

Bremsfläche oben
Braking surface above

1717th

Zusatzring
Additional ring

1818th

Lippendichtung unten
Lip seal below

1919th

Lippendichtung oben
Lip seal on top

2020th

Lippendichtung mittig
Lip seal in the middle

2121

Querbohrung
Cross hole

2222

Stopfen
Plug

2323

Sacklochgewinde
Blind hole thread

2424th

Hohlzylinder
Hollow cylinder

2525th

Ringkolben
Ring piston

2626

Stift
pen

Claims (12)

1. Wälzlager-Drehverbindung, insbesondere für die Maschinenhauslagerung von Windenergieanlagen, bestehend aus zwei Laufringen, welche über abrollende Wälzkörper relative Drehbewegungen zueinander mit geringer Reibung ausführen können und einer integrierten Bremseinrichtung, welche aus mit einem Laufring drehfest verbundenen Bremsflächen und mit dem anderen Laufring drehfest verbundenen Bremsflächen, die über eine Normalkraft gegeneinandergepreßt werden, besteht, dadurch gekennzeichnet, daß auf den Bremsflächen (15, 16) über äußere, regelbare Krafteinleitung erhöhte Reibung zwischen diesen Ringen (2, 3) entsteht, welche Drehbewegungen ein gegensinnig wirkendes regelbares Bremsmoment entgegensetzt, bzw. bei entsprechend hohem Bremsmoment Drehbewegungen reibschlüssig verhindert.1. Rolling bearing slewing ring, in particular for the nacelle bearing of wind energy plants, consisting of two races, which can perform relative rotary movements with low friction via rolling rolling elements and an integrated braking device, which is made of non-rotatably connected braking surfaces and rotatably connected to the other race ring Braking surfaces which are pressed against each other by a normal force, characterized in that increased friction between these rings ( 2 , 3 ) arises on the braking surfaces ( 15 , 16 ) via external, controllable force application, which counteracts a rotating opposing controllable braking torque, or with correspondingly high braking torque, rotational movements are prevented by friction locking. 2. Wälzlager-Drehverbindung nach Anspruch 1, dadurch gekennzeichnet, daß die drehfest mit den Laufringen (2, 3) verbundenen Bremsflächen (15, 16) sich radial überlappen und über einer senkrecht zu den Bremsflächen (15, 16) wirkenden Normalkraft zusammengepreßt werden, so daß Reibung zwischen den Bremsflächen (15, 16) erzeugt wird.2. roller bearing slewing ring according to claim 1, characterized in that the rotationally fixed to the races ( 2 , 3 ) connected braking surfaces ( 15 , 16 ) overlap radially and are pressed together via a normal force acting perpendicular to the braking surfaces ( 15 , 16 ), so that friction between the braking surfaces ( 15 , 16 ) is generated. 3. Wälzlager-Drehverbindung nach Anspruch 1, dadurch gekennzeichnet, daß die Bremsflächen (15, 16) im Dichtungssystem (18, 19) für den Wälzkörper (4) mit integriert sind und den gleichen Schutz gegen äußere Einflüsse, wie die Wälzkörper (4) selbst, genießen.3. Rolling bearing rotary connection according to claim 1, characterized in that the braking surfaces ( 15 , 16 ) in the sealing system ( 18 , 19 ) for the rolling elements ( 4 ) are integrated and the same protection against external influences as the rolling elements ( 4 ) yourself, enjoy. 4. Wälzlager-Drehverbindung nach Anspruch 1, dadurch gekennzeichnet, daß durch die Werkstoffauswahl der Bremsflächen (15, 16) abrasives Verhalten (Fressen) bei Drehbewegungen auch unter äußerer Krafteinleitung verhindert wird.4. Rolling bearing slewing ring according to claim 1, characterized in that the material selection of the braking surfaces ( 15 , 16 ) prevents abrasive behavior (seizure) during rotary movements even under the application of external forces. 5. Wälzlager-Drehverbindung nach Anspruch 1, dadurch gekennzeichnet, daß durch eine entsprechend gewählte Dichtung (20) zwischen den Wälzkörpern (4) und der Bremseinrichtung die Wälzlagerlaufbahn nicht durch Abrieb der Bremsflächen (15, 16) verunreinigt wird, aber überschüssiger Schmierstoff zu den Bremsflächen (15, 16) gelangen kann.5. rolling bearing slewing ring according to claim 1, characterized in that by a suitably selected seal ( 20 ) between the rolling elements ( 4 ) and the braking device, the rolling bearing raceway is not contaminated by abrasion of the braking surfaces ( 15 , 16 ), but excess lubricant to the Brake surfaces ( 15 , 16 ) can get. 6. Wälzlager-Drehverbindung nach einem oder mehreren der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Normalkraft auf viele Kolben (13), welche in Zylinderbohrungen (12) eingesetzt sind, die sich als Lochkreis an einem Laufring (2) verteilt befinden, hydraulisch erzeugt wird.6. roller bearing slewing ring according to one or more of claims 1 to 5, characterized in that the normal force on many pistons ( 13 ) which are inserted in cylinder bores ( 12 ) which are distributed as a bolt circle on a race ( 2 ), is generated hydraulically. 7. Wälzlager-Drehverbindung nach Anspruch 6, dadurch gekennzeichnet, daß die als Lochkreis an einem Laufring (2) verteilten Zylinderbohrungen (12) über Querbohrungen (21) hydraulisch miteinander kommunizieren und die Zuleitung über eine Druckanschlußbohrung (11) erfolgt.7. Rolling bearing rotary connection according to claim 6, characterized in that the cylinder bores ( 12 ) distributed as a bolt circle on a race ( 2 ) communicate hydraulically with one another via transverse bores ( 21 ) and the supply line takes place via a pressure connection bore ( 11 ). 8. Wälzlager-Drehverbindung nach Anspruch 6, dadurch gekennzeichnet, daß die Kolben (13) mit deren Dichtungssystem (14) über eine axiale Bohrung, welche im Betrieb mit einem Stopfen (22) verschlossen ist, gewartet werden können.8. roller bearing rotary connection according to claim 6, characterized in that the pistons ( 13 ) with their sealing system ( 14 ) via an axial bore, which is closed during operation with a plug ( 22 ), can be serviced. 9. Wälzlager-Drehverbindung nach einem oder mehreren Ansprüchen 1 bis 5, dadurch gekennzeichnet, daß die Normalkraft auf ringförmige Bremsflächen (15, 16) über Ringkolben (25) hydraulisch erzeugt wird.9. roller bearing slewing ring according to one or more of claims 1 to 5, characterized in that the normal force on annular braking surfaces ( 15 , 16 ) is generated hydraulically via annular piston ( 25 ). 10. Wälzlager-Drehverbindung nach Anspruch 9, dadurch gekennzeichnet, daß die Ringkolben (25) durch Stifte (26) spielfrei mit einem Lagerung verbunden sind und ein Verdrehen der Ringkolben (25) um das Zentrum der Wälzlager-Drehverbindung verhindert.10. roller bearing rotary connection according to claim 9, characterized in that the annular piston ( 25 ) by pins ( 26 ) are connected to a bearing without play and prevents rotation of the annular piston ( 25 ) around the center of the roller bearing rotary connection. 11. Wälzlager-Drehverbindung nach Ansprüchen 6 und 9, dadurch gekennzeichnet, daß die Normalkräfte, welche in axialer Richtung des Drehlagers wirken, sich kompensieren.11. roller bearing slewing ring according to claims 6 and 9, characterized in that the normal forces, which act in the axial direction of the pivot bearing compensate each other. 12. Wälzlager-Drehverbindung nach Ansprüchen 6 und 9, dadurch gekennzeichnet, daß die Kolben (13, 25) und ihr statisch ausgelegtes Dichtungssystem (14) im Zylinder nicht nennenswert gleiten.12. Rolling bearing slewing ring according to claims 6 and 9, characterized in that the pistons ( 13 , 25 ) and their statically designed sealing system ( 14 ) do not slide appreciably in the cylinder.
DE19917498A 1999-04-17 1999-04-17 Roller bearing swivel connection Withdrawn DE19917498A1 (en)

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DE19917498A DE19917498A1 (en) 1999-04-17 1999-04-17 Roller bearing swivel connection
DE10012773A DE10012773A1 (en) 1999-04-17 2000-03-16 Rotary joint, especially for machine housing bearing for wind power system, has brake integrated into rotary joint with brake element(s) mounted in one rotary joint part

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DE10127487A1 (en) * 2001-06-07 2002-12-12 Skf Ab Bearing unit with braking and/or holding function has brake element axially movable and able to be pressed against counter-surface to create braking effect
DE102004052598A1 (en) * 2004-10-29 2006-05-04 Aktiebolaget Skf Wind turbine
DE102006029679A1 (en) * 2006-06-28 2008-01-03 Ab Skf Sliding rotary connection for storing turbine house, has actuator connected with inner ring in torque-proof manner and tangentially resting against surface of outer ring, where actuator is provided with conical shaped surface
WO2008089727A1 (en) * 2007-01-24 2008-07-31 Schaeffler Kg Adjustable friction torque bearing unit for providing a braking function
DE102007018158A1 (en) 2007-04-18 2008-10-23 Schaeffler Kg Rolling bearing with a braking device
WO2009049605A2 (en) * 2007-10-18 2009-04-23 Innovative Windpower Ag Azimuth bearing of a wind turbine generator system
DE102010005210A1 (en) 2010-01-21 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Braking bearing
EP2620644B1 (en) 2012-01-30 2015-06-17 Siemens Aktiengesellschaft Improvements to a wind turbine assembly

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DE20208135U1 (en) * 2002-05-24 2003-10-02 AB SKF, Göteborg Plain bearings with integrated teeth
DE20208134U1 (en) * 2002-05-24 2003-10-02 AB SKF, Göteborg/Gotenburg Rotary drive for a machine house of a wind turbine
DE20208133U1 (en) * 2002-05-24 2003-10-02 AB SKF, Göteborg/Gotenburg Plain bearings for axial and radial bearings
DE10223125A1 (en) * 2002-05-24 2004-03-25 Ab Skf Plain bearing for a wind turbine
DE10316005A1 (en) * 2003-04-07 2004-10-21 Ab Skf Procedure for adjusting the clearance or preload of a bearing
DE10316004A1 (en) * 2003-04-07 2004-11-04 Aktiebolaget Skf Bearing for a wind turbine
EP1571334A1 (en) * 2004-03-04 2005-09-07 Gamesa Eolica, S.A. (Sociedad Unipersonal) Wind turbine yawing system and yawing process
DE102007013164A1 (en) * 2007-03-20 2008-09-25 Schaeffler Kg Rolling bearing with a braking device
CN103184973B (en) * 2011-12-30 2015-09-16 华锐风电科技(集团)股份有限公司 Wind driven generator unit yaw system and wind power generating set

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DE10127487A1 (en) * 2001-06-07 2002-12-12 Skf Ab Bearing unit with braking and/or holding function has brake element axially movable and able to be pressed against counter-surface to create braking effect
US7481620B2 (en) 2004-10-29 2009-01-27 Ab Skf Wind power plant
DE102004052598A1 (en) * 2004-10-29 2006-05-04 Aktiebolaget Skf Wind turbine
EP1653079A3 (en) * 2004-10-29 2012-03-07 Ab Skf Wind turbine
DE102006029679A1 (en) * 2006-06-28 2008-01-03 Ab Skf Sliding rotary connection for storing turbine house, has actuator connected with inner ring in torque-proof manner and tangentially resting against surface of outer ring, where actuator is provided with conical shaped surface
WO2008089727A1 (en) * 2007-01-24 2008-07-31 Schaeffler Kg Adjustable friction torque bearing unit for providing a braking function
DE102007003470A1 (en) * 2007-01-24 2008-07-31 Schaeffler Kg Bearing unit with adjustable friction torque to provide a braking function
DE102007018158A1 (en) 2007-04-18 2008-10-23 Schaeffler Kg Rolling bearing with a braking device
WO2009049605A2 (en) * 2007-10-18 2009-04-23 Innovative Windpower Ag Azimuth bearing of a wind turbine generator system
WO2009049605A3 (en) * 2007-10-18 2010-01-07 Innovative Windpower Ag Azimuth bearing of a wind turbine generator system
DE102010005210A1 (en) 2010-01-21 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Braking bearing
WO2011089068A1 (en) 2010-01-21 2011-07-28 Schaeffler Technologies Gmbh & Co. Kg Bearing capable of being braked
EP2620644B1 (en) 2012-01-30 2015-06-17 Siemens Aktiengesellschaft Improvements to a wind turbine assembly

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