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
  • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
  • F16C23/02—Sliding-contact bearings
  • F16C23/04—Sliding-contact bearings self-adjusting
  • F16C23/041—Sliding-contact bearings self-adjusting with edge relief
• • 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
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
• • 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
  • F16C17/00—Sliding-contact bearings for exclusively rotary movement
  • F16C17/26—Systems consisting of a plurality of sliding-contact 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
  • F05B2240/53—Hydrodynamic or hydrostatic 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
  • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
  • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
  • F16C2240/50—Crowning, e.g. crowning height or crowning radius
• • 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
  • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
  • F16C25/02—Sliding-contact bearings

Definitions

• the invention relates to a bearing element for the storage of a component.
• the bearing element for the storage of the rotor hub of a wind turbine is known.
• the bearing element comprises an outer ring, an inner ring and a plurality of plain bearing pads, which are arranged between the outer ring and the inner ring.
• the bearing element is designed for a radial or an axial force load and can absorb a superimposed tilting moment only conditionally.
• the object of the present invention was to overcome the disadvantages of the prior art and to provide a bearing element by means of which a component loaded with a radial force, an axial force and a tilting moment can be mounted.
• a bearing element in particular rotor hub bearing, is designed for supporting a component to be loaded with a radial force, an axial force and a tilting moment.
• the bearing element comprises at least one inner ring element and at least one outer ring element, which are arranged in the unloaded state coaxial with respect to a central longitudinal axis to each other, wherein between the inner ring member and the outer ring member a sliding bearing is formed by at least two axially spaced sliding bearings is formed.
• the slide bearings are coupled to a receiving side with one of the ring elements and opposite the receiving side is a sliding surface is formed, which cooperates with a running surface of the opposite ring member.
• the sliding surface of the sliding bearing in cross-section at least a first portion and a second portion, wherein a tangent to the first portion is arranged at a first angle relative to the central longitudinal axis at a first angle and one applied to the second portion Tangent with respect to the central longitudinal axis is arranged at a second angle, wherein the first angle is different in size than the second angle.
• An advantage of the inventive design of the bearing element is that the first portion may be formed such that an axial force acting on the bearing element or a radial force can be well received and the second portion of the sliding bearing can be designed such that an acting on the bearing element tilting moment can be well received.
• the bearing element according to the invention does not result in punctiform loading when the inner ring element is tilted relative to the outer ring element, but at least one linear support of the sliding surface on the running surface can be achieved even with a tilting of the inner ring element relative to the outer ring element become.
• the surface pressure compared to conventional bearing elements can be minimized, whereby the wear on the bearing elements can be minimized.
• Longitudinal axis is arranged at a third angle, wherein in the unloaded state, the third angle of the tread is the same size as the first angle of the first portion of the sliding surface.
• the sliding bearing is coupled to the outer ring element and the sliding surface is formed on the inner side of the sliding bearing and the running surface is formed on the outer side of the inner ring element.
• Such a design of the bearing element is advantageous if the outer ring element is designed as a rotating component and the inner ring element is designed as a fixed component, as this leads to a reduced wear on the bearing element.
• the sliding bearing is coupled to the inner ring element and the sliding surface is formed on the outer side of the sliding bearing and the running surface is formed on the inside of the outer ring element.
• Such a design of the bearing element is advantageous if the inner ring element is designed as a rotating component and the outer ring element is designed as a fixed component, since this leads to a reduced wear on the bearing element.
• at least one of the plain bearings is formed by slide bearing pads distributed in the circumferential direction. The advantage here is that such Gleitlagerpads are easy to change or remove in case of maintenance, without causing the entire bearing element must be disassembled.
• the first angle of the tangent applied to the first section is smaller than the second angle of the second section applied relative to the central longitudinal axis Tangent with respect to the central longitudinal axis and that in a sliding bearing with a sliding surface arranged on the outside of the first angle of the tangent to the first portion relative to the central longitudinal axis is greater than the second angle of the tangent to the second portion in relation to the central longitudinal axis.
• the tangent of the second section is formed or has such an angle that in the unloaded state of the bearing element, the tangent of the tread around the center of the bearing element turned coincident to the tangent of the second section is.
• first section and the second section seen in cross section is formed by straight lines which are interconnected by a transition radius.
• the advantage in this case is that the partial sections formed in the cross section formed by straight lines can interact with corresponding cross-sectional areas which are likewise formed as straight lines in cross-section and in the process form a line-shaped contact.
• the transition radius is preferably chosen as small as possible. Preferably, the transition radius can be approximately zero and therefore the straight lines intersect directly and form a peak.
• an opening angle between the tangent applied to the first section and the tangent applied to the second section is between 175 ° and 179.99 °, in particular between 178 ° and 179.99 °, preferably between 179 ° and 179. 99 °, is.
• the advantage here is that correspondingly low bearing clearance can be achieved by realizing such an opening angle.
• a wind turbine is formed with a rotor hub and a nacelle, wherein the rotor hub is mounted by means of the bearing element described on the nacelle.
• FIG. 1 shows an exemplary embodiment of a wind power plant
• FIG. 2 is a cross-sectional view of a first embodiment of a Lagerelemen- tes in the unloaded state.
• 3 shows a cross-sectional view of the first exemplary embodiment of the bearing element in the state loaded with a tilting moment
• 4 shows a schematic detail of the first embodiment of the bearing element in the unloaded state.
• FIG. 5 shows a schematic detail of the first exemplary embodiment of the bearing element in the state loaded with an axial force and / or a radial force
• FIG. 6 is a schematic detail of the first embodiment of the bearing element in the loaded with a breakdown torque state. 7 is a schematic detail of a second embodiment of the bearing element in the unloaded state.
• Fig. 8 shows a schematic detail of the second exemplary embodiment of the bearing element in the state loaded with an axial force and / or a radial force
• Fig. 9 is a schematic detail view of the second embodiment of the bearing element in the loaded with a breakdown torque state.
• Fig. 1 shows a schematic representation of a wind turbine 1 for generating electrical energy from wind energy.
• the wind turbine 1 comprises a nacelle 2, which is rotatably received on a tower 3.
• the electrical components such as generator of the wind turbine 1 are arranged.
• a rotor 4 is formed which has a rotor hub 5 with rotor blades 6 arranged thereon.
• the rotor hub 5 is received by means of a bearing element 7 rotatably mounted on the nacelle 2.
• the bearing element 7 is designed according to the embodiments described in this document, since both when using only one bearing element 7 for supporting the rotor hub 5 on the nacelle 2 both a radial force 8 and an axial force 9 and a tilting moment 10 must be received by the bearing element 7.
• the axial force 9 results from the force of the wind.
• the radial force 8 corresponds to the weight of the rotor 4 and acts on the center of gravity of the rotor 4. Since the center of gravity of the rotor 4 is outside of the bearing element 7, the tilting moment 10 is caused in the bearing element 7 by the radial force 8.
• the tilting moment 10 can also be caused by an uneven loading of the rotor blades 6.
• bearing element 7 in a wind turbine 1, it is also conceivable that such a trained bearing element 7 is used for example on a turntable of an excavator or other application where both a radial force 8 and / or an axial force 9, as well as a tilting moment 10 act on the bearing element 7.
• the bearing elements 7 according to the invention may, for example, have a diameter between 0.5 m and 5 m. Of course, it is also conceivable that the bearing elements 7 are smaller or larger.
• FIG. 3 shows the first exemplary embodiment of the bearing element 7 from FIG. 2 in a state loaded with a tilting moment 10, again using the same reference numerals or component designations as in the preceding FIG. 2 for the same parts.
• the bearing element 7 is described on the basis of a synopsis of FIGS. 2 and 3.
• the bearing element 7 comprises at least one inner ring element 11, which has an inner side 12 and an outer side 13. Furthermore, an outer ring element 14 is provided, which has an inner side 15 and an outer side 16. In addition, between the inner ring member 11 and the outer ring member 14, a sliding bearing 17 is formed, which comprises at least two spaced apart at an axial distance 18 slide bearing 19. The two plain bearings 19 each have an inner side 20 and an outer side 21.
• the bearing element 7 is shown in an unloaded state.
• an unloaded state in this case that state is defined in which no forces therefore no gravitational forces acting on the bearing element 7.
• This state is fictional and is therefore only shown to illustrate the components or the function of the bearing element 7.
• the inner ring element 11 and the outer ring element 14 and the plain bearings 19 are arranged concentrically with respect to a common central longitudinal axis 22.
• the sliding bearings 19 are coupled to the outer ring member 14.
• the side of the sliding bearing 19 which is coupled to the outer ring member 14 is referred to in the present embodiment as a receiving side 23 of the sliding bearing.
• the sliding bearing 19 is received, for example by means of an adhesive bond in the outer ring member 14.
• the plain bearing 19 it is also possible for the plain bearing 19 to be accommodated in the outer ring element 14 in a form-fitting manner, for example.
• the sliding bearing 19 can be divided into several distributed around the circumference ring segments.
• the sliding bearing 19 is formed as a single circumferential ring. Such a circumferential ring may be inserted, for example, in the outer ring member 14, wherein a co-rotation of the sliding bearing 19 is prevented relative to the outer ring member 14 by a friction connection.
• a sliding surface 24 is formed, which cooperates with a running surface 25 of the inner ring element 11.
• the outer side 13 of the inner ring member 11 is formed as a running surface 25.
• the slide bearing 19 is rotated relative to the inner ring member 11 and a sliding movement between the sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring member 11 is made possible.
• the function of the bearing element 7 can be realized.
• the exact function or the exact relationships of the bearing element 7 are shown in FIGS. 4 to 6 in detail or serve these representations as a supplement to the understanding of the first embodiment of the bearing element. 7 Between the inner ring member 11 and the sliding bearing 19, as shown in FIG. 2, a bearing clearance 26 is formed.
• the bearing clearance 26 is shown exaggerated for illustrative purposes.
• the geometry of the plain bearing is greatly exaggerated in order to illustrate the function and the technical effects can be illustrated.
• two inner ring elements 11 are formed, which are arranged at a distance 27 from each other.
• the outer sides 13 of the inner ring elements 11 are each conical and facing each other.
• the running surface 25 is a surface which is rotationally symmetrical with respect to the central longitudinal axis 22 and which may have the special shape of a truncated cone. Seen in cross section of the bearing element 7, as shown in Fig. 2, the tread 25 forms a straight line. If a tangent 28 is applied to the running surface 25, then this tangent 28 is formed at an angle 29 with respect to the central longitudinal axis 22.
• the sliding bearing 19 has on the sliding surface 24 a first section 30 and a second section 31.
• a tangent 32 applied to the first section 30 is arranged at an angle 33 to the central longitudinal axis 22.
• a tangent 34 applied to the second section 31 is arranged at an angle 35 to the central longitudinal axis 22.
• the angle 35 of the second section 32 and the angle 33 of the first section 30 are different in size. It is also envisaged that the angle 29 of the tread 25 and the angle 33 of the first section 30 are the same size and thus in the unloaded state of the bearing element 7, the tangent 28 of the tread 25 and the tangent 32 of the first section 30 are parallel to each other. In the three-dimensional view, therefore, the running surface 25 and the first section 30 have a lateral surface of a truncated cone with the same opening angle.
• the bearing element 7, as shown in Fig. 5, is loaded with an axial force 9 and / or a radial force 8
• the first portion 30 of the sliding surface 24 of the sliding bearing 19 and the tread 25 of the inner ring member 11 come at a first contact line 36th to each other to concern.
• the sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring element 11 therefore contact each other at the first contact line 36, since a radial displacement of the two components occurs due to the radial force 8 or through the axial force 9.
• the parallel shift moves in the hundredth to tenth of a millimeter range and is greatly exaggerated.
• the two slide bearings 19 are located diagonally opposite one another on the inner ring elements 11.
• a rotation of the outer ring element 14 relative to the inner ring element 11 with respect to a pivot point 38 which lies at the intersection between the central longitudinal axis 22 and a longitudinal central axis 39 occurs.
• the tangent 28 of the tread 25 and the tangent 34 of the second portion 31 of the sliding surface 24 of the sliding bearing 19 are congruent to each other. That's how it comes with a load of the bearing element 7 by a tilting moment 10 to a linear contact between the sliding surface 24 and the tread 25, whereby the surface pressure and thus the wear on the sliding surface 24 can be reduced.
• the congruence of the tangent 24 of the second section 31 and the tangent 28 of the tread 25 after tilting can be achieved that in the construction of the sliding bearing 19 in the unloaded state shown in FIG.
• the tangent 28 is taken to the tread 25 and with respect Fulcrum 38 is rotated by a certain angle, so that it forms the tangent 34 of the second section 31 and intersects with the tangent 32 of the first section 30 approximately centrally of the sliding bearing 19.
• an opening angle 41 formed is formed, which corresponds to an angle of 180 ° minus the maximum deflection angle 40.
• a transition radius 42 is formed, which is due to manufacturing.
• the transition radius 42 will be as low as possible, so that the first Berrindline 36 and the second Berrindline 37 are as long as possible and thus the lowest possible surface pressure between the sliding surface 24 of the sliding bearing 19 and the running surface 25 of the inner ring member 11 occurs.
• the first section 30 and the second section 31 are connected directly or preferably without transition radius 42 to each other.
• FIGS. 7 to 9 in a second exemplary embodiment, a further and optionally independent embodiment of the bearing element 7 is shown, again like reference numerals or component designations are used for the same parts as in the preceding Figures 2 to 6. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding Figures 2 to 6 or reference.
• the sliding bearing 19 is coupled to the inner ring member 11 and a sliding movement between the sliding bearing 19 and the outer ring member 14 takes place.
• the sliding bearing 19 may be coupled to the inner ring member 11 and thus the receiving side 23 of the sliding bearing 19 may be formed on the inner side 20 thereof.
• the sliding surface 24 of the sliding bearing 19 is formed on the outer side 21 and cooperate with the inner side 15 of the outer ring member 14, which in this exemplary embodiment game as a tread 25 is formed.
• first section 30 and the second section 31 of the sliding surface 24 of the sliding bearing 19 and the cooperating tread 25 of the outer ring member 14 behave analogously to the first embodiment already described in FIGS. 2 to 6.
• the second embodiment will not be described in detail separately, but will be apparent to those skilled in the art based on the description of the first embodiment described in FIGS. 2 to 6 or the function of FIGS. 7 to 9.
• Such a second embodiment of the bearing element 7 with an inner slide bearing 19, as shown in FIGS. 7 to 9 is preferably used when the outer ring member 14 is formed stationary and the inner ring member 11 together with the sliding bearing member 19 relative to outer ring member 14 is rotatable.

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• 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)
• Sliding-Contact Bearings (AREA)
• Support Of The Bearing (AREA)
• Wind Motors (AREA)
• Rolling Contact Bearings (AREA)

Priority Applications (7)

Applications Claiming Priority (2)

Publications (1)

Family

ID=60654568

Family Applications (1)

Country Status (9)

Cited By (15)

Families Citing this family (4)

Citations (8)

Family Cites Families (26)

• 2016
  • 2016-10-21 AT ATA50969/2016A patent/AT519288B1/de active
• 2017
  • 2017-10-19 DK DK17811827.9T patent/DK3529508T3/da active
  • 2017-10-19 KR KR1020197014327A patent/KR102416389B1/ko active Active
  • 2017-10-19 WO PCT/AT2017/060273 patent/WO2018071941A1/de not_active Ceased
  • 2017-10-19 ES ES17811827T patent/ES2846974T3/es active Active
  • 2017-10-19 JP JP2019521151A patent/JP6970195B2/ja active Active
  • 2017-10-19 EP EP17811827.9A patent/EP3529508B1/de active Active
  • 2017-10-19 US US16/334,390 patent/US10598214B2/en active Active
  • 2017-10-19 CN CN201780059498.0A patent/CN109790866B/zh active Active

Patent Citations (8)

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