EP3417185A1 - Palier à fils - Google Patents

Palier à fils

Info

Publication number
EP3417185A1
EP3417185A1 EP17710378.5A EP17710378A EP3417185A1 EP 3417185 A1 EP3417185 A1 EP 3417185A1 EP 17710378 A EP17710378 A EP 17710378A EP 3417185 A1 EP3417185 A1 EP 3417185A1
Authority
EP
European Patent Office
Prior art keywords
rolling
raceway
wire
rolling elements
running
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Withdrawn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
EP17710378.5A
Other languages
German (de)
English (en)
Inventor
Hubertus Frank
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
Application filed by IMO Holding GmbH filed Critical IMO Holding GmbH
Publication of EP3417185A1 publication Critical patent/EP3417185A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F16C33/61—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings formed by wires
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C33/37—Loose spacing bodies
    • F16C33/3706—Loose spacing bodies with concave surfaces conforming to the shape of the rolling elements, e.g. the spacing bodies are in sliding contact with the rolling elements
    • 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
    • F16C33/51—Cages for rollers or needles formed of unconnected 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
    • 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
    • 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
    • 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

Definitions

  • the invention is directed to a device for the rotatable coupling of at least two annular, concentric to a common axis of rotation, spaced by a gap connecting elements, of which at least one, preferably each, a flat end face (-en) with annularly arranged fastening means for conditioning and Fixing the respective connection element to a foundation, chassis, plant or machine part, wherein at least one respective raceway is arranged on each of the two connection elements in the region of the gap for at least one row of rolling elements rolling therebetween, and / or at least one respective sliding track is arranged, which slide either directly to each other or between which at least one slider is slidably guided.
  • Such a bearing structure with flat connection surfaces is a typical feature of large bearings, as they are usually used in practice to accommodate high forces or turning or tilting moments or transfer.
  • Spherical rolling elements are only of limited suitability for such high loads, because they only form a contact point area that is nearly punctiform to the respective raceway surfaces, where material overloading then threatens when there are large forces or tilting moments acting from outside.
  • a far more sustainable geometry results when using roller-shaped rolling elements.
  • roller-like rolling elements include in particular cylindrical rollers, but also barrel-shaped or conical rolling elements;
  • roller-type rolling elements are referred to as "roller-like” in the following:
  • roller-like rolling bodies are rotationally symmetrical with respect to precisely one well-defined rotation axis and form linear contact areas with the raceway surfaces, so that external forces or tilting moments are distributed over a much larger contact area and accordingly locally on material technology harmless values are reduced.
  • large warehouses are also subject to further restrictions in many applications; For example, they should not be too heavy and / or too big.
  • the annular connection elements of such a large-scale bearing are then subject to the risk of bending and / or twisting at high loads.
  • the invention initiates the problem of developing a generic device such that running and / or Gleitbahnverformonne be compensated due to external influences or at least minimized to the achievable life expectancy of bearing elements such as. Rolling or sliding bodies not to endanger.
  • the at least one running or sliding track is formed as a cross-section preferably longitudinally flat surface of a wire on its complementary to the running or sliding surface surface area an arcuate, convex cross-sectional profile has and thus at least partially inserted into an all-round recess with a complementary cross-sectional profile in an annular connection element.
  • Such a geometry serves the purpose of creating a degree of freedom of movement between the actual run or slide track and the relevant connecting element, which allows the running or sliding track / even in deformations of the actual connection element their original orientation in space - and especially relative to the opposite running or sliding track - to comply.
  • This serves in rolling bearings the purpose of maintaining the linear contact areas between the raceways rolling rolling elements with the two raceways, so that the rolling elements are not overloaded accordingly;
  • a contact area as large as possible is ge
  • the recess for receiving the running or Gleitbahndra htes at one or preferably both edges by a convex edge limited, so a prominent edge in the manner of a ridge and not in the manner of a valley. Accordingly, the surface areas beyond these recessed rims yield back and make room for contact with rolling or sliding bodies or with an opposite slide track itself, so that they do not abut anywhere even with a strong twist of a terminal member.
  • the all-round recess for receiving the raceway wire has a saddle-shaped curved surface area O sg and a double concave surface area O dk , which taken together preferably form the entire surface of the all-round well.
  • the saddle-shaped curved surface area O sg and the double-concave curved surface area O dk outside or beyond these surface areas O sg , O dk, there is a larger, even or at least linear area.
  • the all-round recess for receiving the run or slideway wire has a circular arc-shaped cross-section.
  • circular arc-shaped cross-section allows a smooth relative movement between the raceway wire and those bedding bed or depression. It is recommended that the circular arc-shaped cross-sectional profile q kb of the all-round recess for receiving the run or slide wire is as long as a semicircular arc with a radius corresponding to the transverse radius of curvature r q of the all-round depression, or shorter:
  • a development of the invention according to which the circular-arc-shaped cross-sectional profile q kb of the all-round depression for receiving the raceway wire is the same length as the length I of a raceway Surface of the rolling element rolling in, or longer: qkb> serves the purpose of allowing the rolling elements a maximum contact area with the raceway wire and thereby minimizing their pressure loading.
  • the annularly arranged fastening means for fixing the respective connection element to a foundation, chassis, plant or machine part are formed as through holes or preferably provided with an internal thread blind holes.
  • the selection of the respectively optimum bore can be based on the application in question and / or local conditions.
  • raceway wires can be arranged one above the other in different planes, in particular two or more raceway wires of the same length.
  • These running or slide wires or the runways or slides formed thereon can optionally be assigned to the same row of rolling elements and receive them directly between them, or they are different, one above the other arranged rows of rolling elements assigned to bias those against each other.
  • the all-round recess for receiving the running or sliding track wire can be arranged both on a protruding nose or a projecting collar of a nose ring, as well as on at least one support or retaining ring. This makes it possible to respond constructively to all requirements and specifications.
  • a raceway lying opposite the raceway ring with respect to the rolling elements rolling thereon can be directly incorporated into the annular body of the relevant connecting element, in particular while hardening a corresponding surface area.
  • a raceway lying opposite the raceway ring with respect to the rolling elements rolling thereon can also be formed on a raceway wire inserted into a depression there.
  • the arrangement can be made to the effect that at least one of two, a common row of rolling elements associated raceway wires has a rectangular cross-section. Although this can not turn or twist in his bed or in his depression; However, this is not necessary because yes, the other raceway has this degree of freedom of movement and can adapt to the cross-sectionally rectangular raceway accordingly.
  • connection element or a part thereof in particular a support or retaining ring is integrated with a machine or system part, in particular with a hub of a wind turbine. This may allow a higher degree of rigidity reach as by screwing a connection element to a machine or plant part to be connected.
  • the cross-section of the actual running or sliding surface should be adapted to the rolling or sliding so that there is a maximum contact area. This is a linear contact area in the case of a rolling body, and a flat contact area in the case of a sliding body.
  • the rolling elements have at least one row exactly one excellent axis of rotation.
  • all rotationally symmetrical body which are not spherical, so for example. Cylindrical or needle rollers, tapered rollers or barrel-shaped rolling elements.
  • the invention further provides that the (excellent) axes of rotation of all rolling elements of the at least one row of rolling elements in the unloaded state of the rolling bearing lie in a common plane, which is traversed vertically by the common axis of rotation. It is preferably an axial row of rolling elements, which is exclusively or predominantly designed to receive and transmit forces parallel to the axis of rotation.
  • roll-shaped rolling elements of an axial bearing row for this purpose require a raceway on the wire which can be inserted in a recess, which is formed as a flat surface; for roller-shaped rolling elements of a radial bearing row preferably run along a cylinder jacket-shaped track, which may possibly be madebidlet on an insertable into a recess wire.
  • a preferred design rule states that - in particular for an axial bearing row - measured within a plane defined by the axis of rotation, radial plane width of an all-round well to Receiving a raceway wire equal to 0.8 times the length I of a rolling on the raceway surface of the inserted raceway wire rolling element is or greater, for example, equal to 0.9 times this length or greater, preferably equal to the 0th , 95 times this length or more, in particular equal to this length of rolling on the respective raceway surface rolling element or more.
  • the rolling elements can rest or roll over almost the entire length of the respective career wire, so that the distribution of forces and relief in the contact area is optimal.
  • the opening width of the circumferential recess measured in the radial direction to the axis of rotation should be equal to or greater than 0.8 times the length l of a rolling element rolling on the raceway surface of the raceway wire inserted therein, for example, equal to 0.9 times this length or greater, preferably equal to 0.95 times this length or more, in particular equal to this length I of a rolling on the respective raceway surface rolling element or more.
  • Such a predominant radial extent of the all-round depression allows the career wire placed therein to form a large, flat contact area for transmitting large axial forces
  • the parallel to the axis of rotation of the rolling bearing extension of the raceway wire should - in an axial bearing row - equal to the diameter of rolling on the raceway surface of the raceway wire rolling element or smaller than that, preferably equal to the radius of the raceway surface of the Track roller rolling rolling element or smaller than that, in particular equal to 0.9 times the radius of a rolling on the raceway surface of the raceway wire rolling element.
  • the smaller the axial extent of a raceway wire the smaller and lighter one can possibly build the relevant rolling bearing.
  • the invention is preferably characterized by a further series of rolling elements, which serves as a radial bearing. Their rolling elements may differ in their nature and size from the other rows of rolling elements.
  • the invention opens up the possibility that preferably roller-shaped rolling elements are guided in a cage or in a plurality of cage segments. As a result, the rolling elements can only move together by rolling instead of moving relative to one another.
  • An alternative embodiment of the invention is characterized in that spacer bodies are inserted between two adjacent Wälzkörpem. Since spacers have no rolling elements at the end sides encompassing longitudinal beams, the gap in the region of these rolling elements can be designed with a minimum radial extent, which space and weight is spared.
  • the invention can be further developed to the effect that in at least one row the rolling elements there, each having an excellent axis of rotation, have a lateral surface which at least in places follows a cylindrical jacket surface.
  • the rolling elements there each with an excellent axis of rotation and an at least partially cylindrical lateral surface, roll along planar raceways.
  • the invention can be further optimized by having in at least one row the local rolling elements each with an excellent axis of rotation a lateral surface which follows a lateral surface of a truncated cone or a barrel.
  • a preferred design rule states that in at least one row, the rolling elements there, each with an excellent axis of rotation and a frustoconical surface roll along at least one conical raceway, ie, a career with a both with respect to the axis of rotation of the device and with respect to the base plane inclined cross-section , This makes it possible to completely avoid friction slippage in axial bearing rows.
  • the rolling elements there each with an excellent rotation axis and a barrel-shaped lateral surface, roll along at least one raceway whose cross-section is adapted to a longitudinal section through the barrel-shaped lateral surface of a barrel-shaped Qälz stressess.
  • FIG. 1 shows a section through the annular connection elements of a roller bearing according to the invention.
  • FIG. 2 shows a section through the annular connection elements of a modified embodiment of the invention, partially broken away, wherein the rolling elements are guided in cages.
  • FIG. 3 is a corresponding to FIG. 2 representation of another
  • Fig. 4 is one of the used in the embodiment of FIG. 3
  • Spacer body in a perspective view shows a representation corresponding to FIG. 3 of a modified embodiment of the invention
  • Fig. 6 is a representation corresponding to Fig. 1 yet another
  • Embodiment of the invention such as
  • Fig. 7 shows a further embodiment of the invention in a section across the annular connection elements.
  • a device according to the invention i for rotatably coupling at least two annular, concentric to a common axis of rotation and spaced terminal elements 2, 3 of the cut surface adjacent the course of the cut rings was omitted.
  • connection element 2 shown on the left can optionally be formed as an outer or inner ring and the connection element 3 shown on the right in each case accordingly as an inner or outer ring.
  • the device 1 is designed as a large rolling bearing, preferably with a diameter of about 1 m or more.
  • the illustrated devices 1 may be provided with various attachments, not shown, for example with a housing, with a toothing on at least one connecting element 2, 3, with which a drive element such as a pinion or a worm meshes, furthermore with a brake, Sensor, etc.
  • a special feature of such slewing bearings is that they are not connected to their outer lateral surfaces 4, 5 due to their dimensions, but they are either with a integrated plant or machine part as in the embodiment of FIG.
  • a part of the right side connecting element 3 is integrated with the hub 6 of a wind turbine to a single piece, or they have at least one flat pad 7, 8, 9, 10 for full-surface or largely full-surface investment in a foundation, chassis, equipment or machine part.
  • a plurality of fastening elements 11, 12 are arranged distributed in a circle in such a flat connection surface 7, 8, 9, 10.
  • These are preferably boreholes, for example through-holes as in the connection element 2 shown on the left in FIG. 1, or blind bores as in the connection element 3 shown on the right in FIG. 1.
  • blind bores preferably have one Internal thread 13, which extends over at least part of its length.
  • a gap 14 is provided in all the illustrated embodiments between the two connecting elements in order to enable a relative rotation between the two connecting elements 2, 3.
  • roller bearings of the illustrated design should in practice accommodate or transmit mostly high forces or turning or tilting moments.
  • spherical rolling elements are less well suited because they each form only a nearly punctiform contact area to the respective raceway surfaces. Within these small contact areas, material overloading can occur soon in the case of large forces or overturning forces acting from outside. Therefore, the invention provides that in the gap 14 at least one row of tire-shaped rolling elements 15, 16, 17 rolls.
  • the roller-shaped rolling elements 15, 16, 17 formed as cylindrical rollers, but other non-spherical geometries would be conceivable, for example barrel-shaped or conical rolling elements.
  • Such rolling elements 15, 16, 17 are characterized in that they are rotationally symmetrical to exactly one, well-defined axis of rotation, which will be referred to below as their longitudinal axis 18.
  • Such tire-shaped rolling bodies 15, 16, 17 are, with suitable design of the raceways, able to form linear contact areas, so that external forces or tilting moments can be distributed over a much larger contact area, so that material overloads are much rarer.
  • roller-shaped rolling elements 15, 16, 17 can only transmit forces radially to their longitudinal axis 18, not also force components in the direction of their longitudinal axis 18, as is possible with spherical rolling elements, in particular in the so-called four-point bearings. Therefore, usually for aixial forces in both directions, ie down and up, each different rows of rolling elements 15, 16 are used, and for the transmission of radial forces, a third row of rolling elements 17 is provided.
  • all rolling bearing embodiments have three or more rows of rolling bearings 15, 16, 17.
  • the roller-shaped rolling elements 15, 6, 17 arranged such that the longitudinal axes 18 of all rolling elements 15, 16, 17 in the row in question either lie in one plane or on a single lateral surface of a single, imaginary, rotationally symmetrical body , ie a conical surface or a cylindrical surface.
  • Rolling elements 15, 16, whose longitudinal axes 18 lie in one plane transmit predominantly or exclusively axial forces between the connection elements 2, 3, ie forces in the direction of the axis of rotation between them, and therefore rows with such oriented rolling elements 15, 16 are referred to as axial rows of rolling elements become.
  • Rolling elements 17 the longitudinal axes 8 are located on a cylindrical surface, transmit predominantly or exclusively radial forces between the connecting elements 2, 3, ie forces radially to the axis of rotation, and therefore rows with such oriented rolling elements 17 are referred to as axial rows of rolling elements.
  • Rolling elements whose longitudinal axes lie on a conical surface, transmit both radial and axial forces between the connecting elements 2, 3. However, in the context of the preferred embodiments, such rolling elements hardly occur.
  • connection element 2 is designed as a so-called nose ring with an all-round nose 19 or an all-round collar 20th
  • such a nose 19 or a collar 20 has a rectangular or square cross-section, with two flat edges 21, 22 and a cylindrical or hollow cylindrical end face 23, which can serve as raceways for rolling elements 15, 16, 17, as shown in FIG 1 can be seen.
  • the connecting element 3, which is not designed as a nose ring has a C-shaped geometry on its lateral surface facing the gap 14, ie, has at least one groove 24 facing the gap 14, in which the nose 19 or the collar 20 engages. spaced by the gap 14.
  • the groove 24 has two flanks 25, 26 and a bottom 27, where each raceways for the rolling elements 15, 16, 17 are located.
  • the all around engaging in the groove 24 nose 19 and the all-around engaging collar 20 obstructs the assembly of the two connection elements 2, 3.
  • the not designed as a nose ring connecting element 3 is divided in the region of the groove 24 in two adjacent rings which adjoin one another along a preferably flat surface 28, namely into a support ring 29 engaging under the lug 19 or the collar 20 and into a retaining ring 30 overlapping the lug 29 or the collar 20
  • Grading are so that support and retaining ring 29, 30 can be put together only at exactly concentric orientation - ie without any offset in the radial direction - to form a full-surface contact.
  • the gap 14 at one or both mouths, so beyond the respective outermost row of rolling elements 15, 16, 17, sealed by a local, preferably annular sealant.
  • a local, preferably annular sealant This makes it possible to fill the cavity in the gap 14 wholly or partially with a lubricant, for example with grease or lubricating oil.
  • slewing bearings according to the invention are often exposed to large external forces or tilting moments, which is why roller-shaped rolling elements 15, 16, 17 are preferred.
  • this by no means precludes the terminal elements 2, 3 from deforming from their originally ideal circular ring shape, for example towards a slightly elliptical shape.
  • Such a deformation could possibly be prevented by massive stiffening, which would lead to an undesirable volume and especially weight gain in many applications.
  • the wings of a wind turbine should be as light as possible. This requirement also applies to the rotor blade bearings, where the individual blades are adjustable, ie, rotatable about their longitudinal axis, connected to the hub of the wind turbine.
  • connection element 2, 3 On the one hand, twisting of a wing as a result of a variety of forces acting from outside leads to a deformation of its connection surface, which inevitably transmits to the connection element 2, 3 connected thereto without a massive countermeasure.
  • the entire windmill, including all vanes and rotor blade bearings as well as the hub, must be carried by the rotor or main bearing and should therefore be as light as possible. Therefore, stiffeners in the field of rotor blade bearings are usually undesirable. It is therefore preferable to slightly deform the connecting elements 2, 3.
  • both connecting elements 2, 3 deform in the same direction but differently, for example elliptically, but in such a way that the longitudinal axes of both ellipses are not concentric or parallel to one another, but mostly so that these longitudinal axes of the two ellipses form an angle with each other or even at right angles stand on each other.
  • the gap width in the region of the mouth of the gap 14 changes in an unpredictable manner, and some gap seal can then no longer fulfill its task of a reliable seal, which leads to a leakage of the lubricant.
  • connection elements 2, 3 may occur, preferably also in both Connection elements 2, 3 different.
  • the carrying capacity of the respective rolling elements 15, 16, 17 decreases, and if the external loads are not reduced immediately, the rolling elements 15, 16, 17 bearing only one of their edges or those supporting tracks can be damaged.
  • the invention provides that at least one track for at least one row of roller-shaped rolling elements 15, 16, 17 is not formed directly on the relevant connection element 2, 3, that is not by shaping or processing of the main body of the respective connection element 2, 3, wherein Also, for example, the mounting holes 11, 12 are incorporated. Rather, there is at least one such track 31, 32, 33 on a track wire 34, 35, 36, which is inserted into a running around recess 37, 38, 39 in the relevant connection element 2, 3.
  • the raceway 31, 32, 33 is adapted to the set and orientation of the rolling elements 15, 16, 17 rolling thereon.
  • cylindrical rollers 15, 16, 17 is a section across the raceway 31, 32, 33 at the respective raceway wire 34, 35, 36 straight stretched, as shown in FIG. 1.
  • the shape of the raceway 31, 32, 33 itself may still be different.
  • the raceways 31, 32 for axial rows of rolling elements 15, 16 are flat
  • the track 33 for a radial row of rolling elements 17 is cylindrical or hollow cylindrical.
  • the raceway wires 34, 35, 36 are inserted into the respective recess 37, 38, 39 and are supported by this on its the runway 31, 32, 33 facing away back 40, 41, 42 over the entire surface.
  • raceway wires 34, 35 and those surrounding recesses 37, 38 there may still be a possibility of movement between raceway wires 34, 35 and those surrounding recesses 37, 38, namely when the cross-sectional profile at the back of the track wire 34, 35 and a cross section through the relevant recess 37, 38 corresponds in each case to a circular arc, as shown in Fig. 1 in the two raceway wires 34, 35 for the axial rows of rolling elements 15, 16 is realized.
  • a twisting and / or twisting of such a track wire 34, 35 within and relative to those receiving recess 37, 38 is possible.
  • raceway wires 34, 35, 36 with a circular arc-shaped cross section of their respective raceway 31, 32, 33 facing away back 40, 41, 42 as follows:
  • the cross-sectional area Q L of a raceway wire 34, 35, 36 is significantly smaller than the cross-sectional area Q A of the relevant connection element 2, 3, so that for a connection of the raceway wire 34, 35, 36 a much lower force is required
  • the track wire 34, 35, 36 is thus "softer" than the connecting element 2, 3 and can therefore compensate for its twisting all together.
  • a track wire 34, 35, 36 may have a relatively small cross-section Q L , for example Q L ⁇ 0.2 * Q A , preferably
  • the roller-shaped rolling elements 15, 16, 1 7 at a rotation of a raceway wire 34, 35, 36 in his bed can not abut the connection element 2, 3 itself, the width of the raceway 31, 32, 33 at the career Wire 34, 35, 36 and thus the width thereof be at least almost equal to or equal to the length of the respective roller-shaped rolling elements 1 5, 16, 1 7 itself.
  • the track 31, 32, 33 of a track wire 34, 35, 36 in the force-free initial state on at least one of its two longitudinal edges 46 is raised above the edge of the bed serving as a recess 37, 38, 39 so that in a relative rotation of the edge of the raceway 31, 32, 33 is not immersed in the recess 37, 38, 39.
  • This can be achieved, for example, by making the maximum depth of the bedding recess 37, 38, 39 smaller than the maximum thickness of the raceway wire 34, 35, 36 in the region of the middle of the raceway.
  • the raceways 43, 44 are formed by the flanks 21, 22 of the nose 19, the raceway 45 through the free end face 23.
  • These raceways are preferably hardened, in particular surface hardened, one recognizes the hardened regions 47, 48, 49 in FIG.
  • the respective raceway wire 34, 35, 36 may also be hardened, but preferably through-hardened, due to its small cross-section Q L also a surface hardening would be possible.
  • Fig. 1 it can also be seen that the relevant bearing 1 is created for a predominantly axial load, as can be found, inter alia, in rotor blade bearings of a wind turbine. Therefore, the axial rolling elements 15, 16 are larger than the radial rolling elements 17, corresponding to a contrast increased axial Capacity. Therefore, the axial rolling elements 15, 16 also tend to be a force overload and are made rotatable by raceway wires 34, 35 in the region of the back 40, 4 in their bed rotatable, while the raceway wire 36 for much less burdened by circular cross-section , Radial rolling elements 17 has a rectangular cross-section and thus is not rotatable in its bed of the same cross-section.
  • a raceway wire 34, 35, 36 could basically be closed to a ring; Preferably, however, it is not completely closed, so that the raceway wire 34, 35, 36 at temperature changes in his bed in the circumferential direction of the Anschlußseseiements 2, 3 stretch as needed or can squeeze and so on its back 40, 41, 42 at the bottom of the recess 37, 38, 39 always experiences a full-surface support. Therefore, a small gap may be provided at a possibly existing joint of its ends, as a margin for possibly necessary strains.
  • the end faces of the raceway wire 34, 35, 36 preferably not innenhlab a spanned by the axis of rotation of the rolling bearing radial plane, but may be a contrast inclined Have course, so for example.
  • the joint in the raceway 31, 32, 33 has a both to a plane spanned by the axis of rotation and radial plane to the rolling direction of the rolling elements 15, 16, 17 obliquely, for example, at an angle from 30 ° to 60 ° relative to the rolling direction of the rolling elements 15, 16, 27 inclined course.
  • raceway wires 34 ', 35', 36 ' can also be received in recesses 37', 38 ', 39' in the connection element 2 'designed as a nose ring, while the respective other raceways 43 ', 44', 45 'in which in support and retaining ring 29', 30 'divided connection element 3' can be formed directly; These can also be hardened there.
  • a roller row 17 ' can also be enclosed between two raceway wires 36', 50.
  • a track wire 36 ' has a circular arc-shaped rear side 42'
  • the other track wire 50 has a rectangular cross-section with a flat back 51.
  • the gap 14' in the axial, roller-shaped Rolling elements 15 ', 16' is wider than the length thereof, to an extent, which is the insertion of a cage 52 in the gap 14 ' allows, in the window-like recesses 53 each have a roller-shaped rolling elements 15 ', 16' is guided.
  • FIG. 3 shows a further modified bearing construction 1 ", which differs from the bearing construction 1 'of FIG. 2 only in that the width of the gap 14" is only slightly larger than the length of the axial rolling elements 15 ", 16". This is made possible by the fact that in the bearing design 1 "the axial rolling elements 15", 16 “are not guided by cages 52, but are kept at a distance only in the direction of rotation by means of spacer bodies 54.
  • Such a spacer body 54 is shown in perspective in Fig. 4. It can be seen that this is essentially bounded by six surfaces:
  • the top 55 is like the bottom 56 also flat.
  • These two sides 55, 56 may be identical or mirror images of each other, relative to a central horizontal plane; they are preferably parallel to each other, but preferably have no rectangular shape; Rather, only their radially extending to the bearing axis of rotation edges 57 are straight; the two remaining edges 58, 59 are circular arcs which surround the bearing axis of rotation concentrically.
  • an upper-side and a lower-side lubrication groove 60, 61 each follow a curved course concentric with the bearing axis of rotation.
  • the radially outer boundary surface 62 of the spacer body 54 is a section of a cylinder jacket surface whose longitudinal axis corresponds to the bearing axis of rotation.
  • the radially inner boundary surface 63 of the spacer body 54 is a section of the lateral surface of a Hohlylinders whose longitudinal axis corresponds to the bearing axis of rotation.
  • Both the radially outer boundary surface 62 and the radially inner boundary surface 63 of the spacer body 54th each have a in the direction of rotation of the raceways 31 ", 32" extending lubrication groove 64, 65.
  • the remaining two sides 66, 67 of the spacer body 54 are the adjacent rolling elements 15 ", 16" facing. These are cutouts from the lateral surface of each Hohlylinder whose longitudinal axis corresponds to the longitudinal axis 18 "of the adjacent rolling bodies 15", 16 ", so that a small lubricating gap remains between the spacer body 54 and the adjacent rolling body 15", 16 " ,
  • the radius of curvature of the two mutually symmetrical, hollow cylindrical sides 66, 67 is slightly larger than the radius of the bearing rolling element 15 ", 16".
  • the spacer body 54 has a symmetry to a running between the top and bottom 55, 56, to those parallel plane. In the region of this central plane of symmetry, the spacer body 54 has a recess 68 passing through between the two mutually symmetrical, hollow cylindrical sides 66, 67, preferably in the form of an oblong hole parallel to the top and / or bottom 55, 56. Also, this through recess 68 serves to distribute the lubricant.
  • a further bearing design 1 (3) can be seen.
  • the raceway wires 71, 72 have as well as those receiving recesses 69, 70 each have a rectangular cross section, preferably an oblong cross section, the depth of which is less than the width of the tracks 43 (3) such an arrangement 44 ( Figure 3).
  • the bearing structure 1 (4) reproduced in FIG. 6 differs from the bearing construction 1 (3) according to FIG. 5 primarily in that the rear sides 73, 74 of the additional raceway wires 71 (4) , 72 ( FIG. 4) have circular arc-shaped cross sections, as well as the complementary inner sides of those receiving recesses 69 (4) , 70 (4) .
  • both tracks can turn as needed in their bed-like receptacle relative to the respective connection element 2 (4) , 3 () and thereby recover, so that the between them enclosed rolling elements 15 (4) , 16 (4) in the ideal case even with twisted connection elements 2 (4) , 3 (4) each have two completely flat tracks 31 (4) , 32 (4) , 43 (4) , 44 (4) .
  • Fig. 7 shows a further bearing design 1 (5) , which differs from the bearing design 1 (4) according to FIG. 6 mainly by the cross-sectional geometry of the two annular connection elements 2 (5) , 3 (5) .
  • connection element 2 (5) has an approximately T-shaped cross section, approximately similar to the cross section of a T-profile.
  • This geometry includes a central pillar 75 and a bar 76 placed transversely above it, and is also referred to as a dagger cross, Egyptian cross, Antonius cross or Antonite cross.
  • the ends of the upper beam 76 project beyond the central pillar 75 laterally and each form a collar 20a, 20b, which performs a similar function as the nose 19 of the connecting element 2 of FIG.
  • a further row of axial rolling elements 80 can roll in the gap 14 (5) between the two connecting elements 2 (5) , 3 (5) centrally above the columnar central part 75.
  • All raceways for all rolling elements 15a, 16a, 17a; 15b, 16b, 17b, 80 may be respectively attached to raceway wires 34a (5) , 71a (5) , 35a (5) , 72a ⁇ 5) , 36a (5) , 50a (5) , 34b ⁇ 5) , 7b (5) , 35b (5) , 72b (5) , 36b (5) , 50b (5) , 81, 82.
  • each raceway wire 50a (5) , 50b (5) may have a rectangular cross-sectional geometry.
  • the described properties of the various bearing designs 1; 1 '; 1 "; 1 (3) ; 1 (4) ; 1 (5) are substantially compatible with each other, for example, all raceways can be hardened, especially all raceway wires."
  • the gap 14 should always be sufficiently dimensioned so that The raceway wires may be closed or interrupted in all embodiments, the geometry of the ends of the raceway wires in all embodiments having the inclination described above.
  • Front side 48 hardened area

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

Abstract

L'invention concerne un palier à roulement comprenant au moins une rangée de corps de roulement en forme de rouleaux servant à transmettre des forces axiales entre deux éléments de raccordement annulaires concentriques par rapport à un axe de rotation commun, lesquels éléments de raccordement sont espacés l'un de l'autre par une fente en vue de la mobilité autour de l'axe de rotation commun, palier à roulement dans lequel ladite au moins une rangée de corps de roulement en forme de rouleaux est disposée de telle sorte que les axes de rotation de tous les corps de roulement en forme de rouleaux de cette rangée sont situés dans un plan commun à l'état non chargé du palier à roulement, lequel plan est traversé perpendiculairement par l'axe de rotation commun, au moins un chemin de roulement pour ladite au moins une rangée de corps de roulement en forme de rouleaux étant réalisé sous forme de surface plane d'un fil qui présente, sur sa région de surface complémentaire à la surface de chemin de roulement, une allure en section transversale arquée et de courbure convexe, et étant par conséquent inséré au moins par endroits dans un renfoncement s'étendant sur tout le pourtour et présentant une allure en section transversale complémentaire à celle-ci dans un élément de raccordement annulaire.
EP17710378.5A 2016-02-16 2017-02-08 Palier à fils Withdrawn EP3417185A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016001751.1A DE102016001751A1 (de) 2016-02-16 2016-02-16 Lager
PCT/IB2017/000082 WO2017141096A1 (fr) 2016-02-16 2017-02-08 Palier à fils

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EP3417185A1 true EP3417185A1 (fr) 2018-12-26

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US (1) US10738829B2 (fr)
EP (1) EP3417185A1 (fr)
CN (1) CN108700120B (fr)
DE (1) DE102016001751A1 (fr)
WO (1) WO2017141096A1 (fr)

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DE102018215961A1 (de) * 2018-09-19 2020-03-19 Thyssenkrupp Ag Blattlagersystem für eine Windkraftanlage, Windkraftanlage, Verfahren zur Herstellung eines Blattlagersystems
DE102018218275A1 (de) * 2018-10-25 2020-04-30 Thyssenkrupp Ag Wälzlageranordnung und Windkraftanlage
DE102019220284A1 (de) * 2019-12-19 2021-06-24 Aktiebolaget Skf Wälzlager mit Drahtlaufringen
DE102019220292A1 (de) * 2019-12-19 2021-06-24 Aktiebolaget Skf Wälzlager mit Drahtlaufringen und Halterippe
DE102020001930A1 (de) 2020-03-25 2021-09-30 Imo Holding Gmbh Großlager
CN112303206B (zh) * 2020-10-29 2022-05-17 中南大学 一种面齿轮支撑结构及传动结构
DE102021102118A1 (de) * 2021-01-29 2022-08-04 Aktiebolaget Skf Wälzlager mit Federsystem
CN114483769B (zh) * 2022-01-25 2023-11-14 中国铁建重工集团股份有限公司 一种具有高偏载承载能力的新型调心回转支承

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FR1440531A (fr) * 1965-07-20 1966-05-27 Rothe Erde Eisenwerk Palier à galets compound
GB1382400A (en) * 1973-03-01 1975-01-29 Hoesch Werke Ag Rolling bearings
CH555012A (de) * 1973-03-02 1974-10-15 Hoesch Werke Ag Mehrreihiges waelzlager.
US3802755A (en) 1973-04-25 1974-04-09 Hoesch Ag Two-row antifriction bearing
CA977021A (en) * 1973-04-26 1975-10-28 Wilhelm Schluter Two-row antifriction bearing
IT1048314B (it) * 1975-01-06 1980-11-20 Hoesch Werke Ag Cuscinetto di sopporto a doppia fila di elementi di rotolamento
JPS51143156A (en) * 1976-02-27 1976-12-09 Hoesch Werke Ag Multiirow rolling bearing
DE2647588C2 (de) * 1976-10-21 1985-06-13 Hoesch Ag, 4600 Dortmund Großwälzlager
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DE3034008A1 (de) * 1980-09-10 1982-04-15 Industriewerk Schaeffler Ohg, 8522 Herzogenaurach Mittenfreie waelzlager-drehverbindung
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DE3909664C1 (en) * 1989-03-23 1990-08-30 Hoesch Ag, 4600 Dortmund, De Centre-free roller revolving connection
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DE102012004329B4 (de) 2012-02-07 2021-04-15 Imo Holding Gmbh Anordnung zur Lagerung von gegeneinander verdrehbaren Teilen einer Energieanlage
CN104136790A (zh) * 2012-02-21 2014-11-05 Skf公司 环形推力轴承组件

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WO2017141096A1 (fr) 2017-08-24
CN108700120B (zh) 2021-04-16
US20190186543A1 (en) 2019-06-20
DE102016001751A1 (de) 2017-08-17
US10738829B2 (en) 2020-08-11
CN108700120A (zh) 2018-10-23

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