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EP3362696A1 - Agencement à palier lisse d'un élément rotatif sur un axe de palier, en particulier d'une roue planétaire sur un axe de roue planétaire d'un engrenage planétaire - Google Patents

Agencement à palier lisse d'un élément rotatif sur un axe de palier, en particulier d'une roue planétaire sur un axe de roue planétaire d'un engrenage planétaire

Info

Publication number
EP3362696A1
EP3362696A1 EP16790516.5A EP16790516A EP3362696A1 EP 3362696 A1 EP3362696 A1 EP 3362696A1 EP 16790516 A EP16790516 A EP 16790516A EP 3362696 A1 EP3362696 A1 EP 3362696A1
Authority
EP
European Patent Office
Prior art keywords
bearing
axial
radial
bearing sleeve
sleeve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP16790516.5A
Other languages
German (de)
English (en)
Inventor
Michael Plogmann
Sebastian Pachner
Sven Claus
Markus Soyka
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3362696A1 publication Critical patent/EP3362696A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact 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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
    • 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
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers

Definitions

  • the invention relates to a sliding bearing arrangement of a rotary element on a bearing element, comprising a bearing element, a rotatably mounted on this bearing sleeve having a formed on the outer circumference first radial tread, and a rotatably mounted on the bearing sleeve rotary element, the che on a second radial Laufflä- on the first radial Tread is slidably mounted.
  • Sliding bearings based on slide bearings are used in a wide variety of applications. Common to them is always the sliding bearing of a rotary element, for. As a gear, on a bearing element, usually in the form of a bearing pin. An example of this is the mounting of a planetary gear on a Planetenradbolzen a planetary gear. Planetary gear units are used in a wide variety of applications. Increasingly, very large-sized planetary gear are built, for example, for use in wind turbines. In particular, in such large transmissions of the longevity of the transmission is of central importance, since a simple replacement of transmission components is not readily possible.
  • a Radalla- gerhülse is fixed by form and / or adhesion on the bearing pin.
  • This bearing sleeve represents the first radial tread on which the planet gear is slidably mounted via a second radial tread.
  • At least the radial bearing sleeve can be provided on the outer circumference with a wear protection layer.
  • Axiallagerung of axially slightly movable planetary gear usually two Axiallagerusionn are provided as separate components, which are usually on their forehead side also wear a wear protection layer.
  • the thrust washers are firmly connected to the planet carrier, for example via screw.
  • the planetary gear runs with its end faces against the thrust washers.
  • the production of such, usually application-specific or user-specific Planetenradffys is highly complex and very expensive.
  • the integration of a plain bearing solution of the form described requires a geometric modification to the planet carrier in order to integrate the thrust bearing in the area of the abutment shoulders, which is structurally difficult to implement, especially with regard to the screwing of the thrust washers for fixing the same.
  • the invention is therefore based on the problem to provide a sliding bearing assembly, which is improved in contrast and can be used without modification of an environmental structure.
  • the thrust bearing disks are arranged on the rotating element itself, ie, for example, the planetary gear and not, as is usually customary, on a surrounding construction or the bearing bolt itself.
  • the axial bearing disks project radially towards the bearing sleeve, against which they engage with their inner bearing surfaces Start axial running surfaces. To form these axial running surfaces serve the axial edges of the bearing sleeve.
  • the bearing sleeve can be made quasi cylindrical, so that flat end faces that form the axial flanks arise.
  • the bearing sleeve can also run stepped, that is, on both sides of the sleeve circumferential steps are formed, the axial Flanks form the two axial treads.
  • the two Axiallagerusionn run with their inner disc surfaces against the axial edges of the bearing sleeve.
  • Shape can be implemented much better in the context of production, compared with the previous embodiments in which cooperate to form the radial and axial bearing a plurality of components. Since the rotary element, that is, for example, the planet gear, is no longer the mating partner for the thrust bearing, no special processing steps of the end faces of the rotary member and the like are required. Also, the radial space can be used very well due to the arrangement of Axiallagerusionn directly on the rotating element, since there is a sufficient wall thickness to attach the thrust washers, for example by screwing, compared with a well-known from the prior art attachment of the thrust washers then sufficiently strong to be sized radial bearing sleeve. The assembly of the slide bearing assembly is much easier, since the thrust washers can be preassembled together with the radial bearing disk, so can be attached to the rotary member, after which the arrangement can be mounted as a preassembled unit on the bearing pin.
  • a bearing element such as a bearing bolt
  • mount the rotary element eg in the form of a shaft
  • a bearing element for example in a bearing bore of a housing.
  • a sliding bearing arrangement of a rotary element can be provided in a bearing element for this purpose, comprising a bearing element, a rotatably arranged in this bearing sleeve having a formed on the inner circumference first radial tread, and rotatably mounted in the bearing sleeve rotary member which is slidably mounted on a second radial tread on the first radial tread, said slide bearing characterized in that the rotary member radially to the bearing sleeve projecting thrust washers are mounted, which run against axial bearing surfaces of the bearing sleeve, wherein axial edges of the bearing sleeve form the axial bearing surfaces for the thrust washers.
  • the thrust washers on the inner rotary element so for example set the shaft and fixed it. They act in the same way as above for the first invention alternative with the outer, for example, arranged in the bearing bore of the housing part bearing sleeve together, so run axially against the axial edges.
  • the bearing sleeve can be made quasi cylindrical, so that flat end faces that form the axial edges result.
  • the bearing sleeve can also be stepped here, that is, circumferential steps are formed on both sides of the sleeve, the axial flanks of which form the two axial running surfaces.
  • the radial and axial running surfaces of the bearing sleeve with a sliding coating or a wear protection coating is formed.
  • the bearing sleeve is a multifunctional component, which offers both the radial bearing and the axial bearing, it is particularly advantageous to provide only on the bearing sleeve, a sliding or wear protection coating over which the corresponding sleeve-side treads are formed.
  • tungsten carbide WC
  • a ceramic layer or a ceramic-like layer may be used as the hard material layer.
  • Bide be used by metals such as titanium, chromium or their mixed phases. Also combination layers of carbon and ceramic layers are conceivable.
  • the hard material layer should have a Vickers hardness HV of at least 800 HV, preferably the Vickers hardness should be at least 1500 HV. It is preferably harder than the second radial tread, which is formed on the inner circumference of the rotary member and the Axiallageimpactn, which in turn should have a hardness of not more than 800 HV.
  • the first radial running surface that is to say the hard material layer, preferably has at least twice to three times the hardness of the running surface of the rotating element. It is also conceivable to provide the second radial tread additionally with an inlet layer. This could be, for example, a burnishing layer, a phosphate layer and / or a plastic-based sliding layer / bonded coating.
  • the bearing sleeve-side hard material layer is preferably applied to a bearing sleeve substrate having an edge hardness of at least 50 HRC.
  • the thickness of the hard material layer is preferably less than 20 ⁇ , preferably it is in the range between 1 - 10 ⁇ and in particular in the range between 2.5 - 4 ⁇ .
  • Particularly suitable has a hard diamond-like coating, as it is known under the trademark "Triondur®” from the house of the applicant, for example, "Triondur® CX +".
  • the rotary member is stepped formed on its front side, wherein the thrust washers are inserted into the stage.
  • This offers the possibility for an axially compact construction, wherein the steps provided on the rotary element can be designed so that the outer surfaces of the axial bearing plates are flush with the end faces of the rotary element.
  • the bearing sleeve is dimensioned accordingly, so it can also be made correspondingly shorter, since, of course, due to the integration of Axiallagerusionn in the end faces of the rotary member, the sleeve side provided axial running surfaces are also arranged correspondingly closer to each other.
  • a receiving groove is provided on the rotary element, wherein the axial bearing washers are inserted into the receiving grooves with a circumferential axial projection.
  • axial space can also be saved, since the thrust bearing discs can be designed slightly narrower overall, because as a result of the circumferential axial projection they are dimensioned sufficiently strong for a fixed screw in this area.
  • the rotational element is not reduced in the tread area in the front side in its width, so that the hydrodynamically effective width is still large for a good radial bearing.
  • the rotary element itself has the second radial running surface, it is therefore mounted with its inner circumference on the first radial running surface of the bearing sleeve, or vice versa in the context of the second alternative with its outer circumference on the inner running surface of the outer bearing sleeve ,
  • the axial bearing disks can also be used to form the second radial running surface of the rotary element.
  • the thrust washers in cross-section T-shaped with a longitudinal and a transverse leg be formed, the two longitudinal legs are formed via hollow cylindrical Axialflan- see, for example, in the first alternative on the inner circumference of the rotary member are arranged and with its inner periphery, forming the second radial tread, slide on the bearing sleeve.
  • the thrust washers thus have a double function here.
  • they serve of course the axial bearing
  • the radial bearing by quasi lining the rotary element on the inner circumference and form with their hollow cylindrical axial flanges respectively the inner periphery of the rotating element side tread.
  • This embodiment of the axial bearing washers can be provided both with a direct attachment of the discs on the flat faces of the rotary member, but also with the arrangement of the thrust washers, then with the transverse leg, in corresponding end-side stepped recesses of the rotary member, or provided with a transverse leg Henen circumferential axial projection which is inserted into a rotary element-side receiving groove.
  • the axial bearing disks are preferably fixed to the rotary element via fastening screws, which applies to all different configurations of the axial bearing disks.
  • a frictional connection interference fit
  • material closure glue, soldering, welding
  • the invention may be provided in a development that the bearing element is designed in the form of a bearing pin, which has at least one opening on the outside of the bolt lubricant channel, and that the bearing sleeve formed on the inner circumference, communicating with the radial lubricant channel Radialnut and at least one radially branching from this, open to the rotary member opening, which merges into a formed on the outer circumference radial groove.
  • This channel and groove configuration makes it possible to bring lubricant through the bearing pin into the plain bearing area. The fed to a longitudinal bore of the bearing pin
  • Lubricant usually an oil, passes via the bolt-side radial bore into the radial groove formed on the inner circumference of the bearing sleeve, where the lubricant is distributed.
  • This radial groove also serves as a lubricant reservoir. From this radial groove branches off from at least one opening, which opens at the outer periphery of the bearing sleeve, wherein preferably a plurality of such apertures are provided distributed circumferentially. Over this the lubricant gets into the direct plain bearing area. In order to be able to distribute the lubricant in the plain bearing area, the opening preferably opens in an outer circumferential groove. This circumferential groove also serves as a lubricant reservoir.
  • At least one axial groove may be provided into which the lubricant passes from the circumferential groove.
  • a circumferential annular groove may be provided on the inner periphery of the rotary member or between the two axial contiguous axial flanges, which communicates with the open aperture of the bearing sleeve. This annular groove is thus also supplied with lubricant, it likewise forms a circulating lubricant reservoir, so that overall a considerably large volume of lubricant absorption results via the perforation or bore and groove structure.
  • the lubricant could be supplied via the internal rotary element, or via the external bearing element, e.g. the housing, etc.
  • the lubricant could be supplied via the internal rotary element, or via the external bearing element, e.g. the housing, etc.
  • appropriate channels or annular and axial grooves are provided on the relevant components in order to allow a lubricant flow.
  • Axial bearing washers are also of particular importance in connection with the lubrication of the sliding bearing. Because due to the fact that they extend radially to the bearing sleeve and open only a short distance to the radial step edges or the rotary member or arranged on spacers, they serve as a lubricant retaining discs at the same time. Because they prevent to some extent drainage of the lubricant from the storage area. This in particular, when the planetary gear rotates, because then the given centrifugal force and gravity hinders the outflow of the lubricant from the radial and Axialgleitla- ger Schemee and the lubricant is inevitably held in large part in the storage area.
  • At least one radial groove opens out at each of the axial running surfaces of the bearing sleeve.
  • These radial grooves are also filled with lubricant, they have a similar function as the axial groove in the radial bearing area.
  • the grooves are preferably arranged offset to the load zone of the thrust bearing, wherein the interpretation of concrete positions for the applied loads is selected depending on the application or situation. It is useful if the lubricant is supplied just before the convergent gap, so that then the lubricant is present in the contact area. The lubricant must always flow through the radial bearing area before it is discharged via the axial bearings so that the lubricant flow is optimally utilized.
  • the circumferential grooves, etc. serve on the bearing sleeve and optionally on the rotary element as a contact-near lubricant reservoir. In any rotational position, even after a standstill, they will contain a residual lubricant volume so that the lubricant can be kept close to the sliding contact even in "coldclimate" conditions. The lubricant warms up during operation and then to the bearing with its different Delivered areas so that even in such a case lubrication is ensured, as well as a sufficient residual lubricant volume is given in Gleitcard publication.
  • the rotary element itself is preferably a planetary gear, which is part of a planetary gear.
  • the invention will be explained below with reference to embodiments with reference to the drawings.
  • the drawings are schematized representations and show:
  • Figure 1 is a schematic representation of a sliding bearing assembly according to the invention in section
  • FIG. 2 shows a representation corresponding to FIG. 1 with a sectional plane which lies in the region of the bore and groove configuration serving for the lubricant supply
  • Figure 3 is an end view of the agerhülse showing the radial groove on the axial edge 4 shows a Phnzipdar ein a second embodiment of a slide bearing assembly according to the invention
  • Figure 5 is a schematic diagram of a third embodiment of a slide bearing assembly according to the invention.
  • the Planetenradbolzen in turn is arranged on a planet carrier.
  • Figure 1 shows in the form of a partial view of a section of a Planetenradgetrie- be comprising a sliding bearing assembly according to the invention.
  • a bearing pin forming a Planetenradbolzen 2 is arranged, which serves as a bearing axis for a rotary element forming a planetary gear 3.
  • a bearing sleeve 4 is set, which is rotatably connected to the Planetenradbolzen 2.
  • the bearing sleeve 4 for example, be positively, positively or materially secured to the Planetenradbolzen 2.
  • first radial running surface 5 which is provided with a sliding or wear protection coating or which is formed over this slip or wear protection coating.
  • a wear-resistant hard material coating is provided for this purpose.
  • the bearing sleeve 4 is used in addition to the radial bearing and the axial bearing. For this purpose, it is provided on both sides in each case with a step 7 which rotates and whose axial flanks form the respective axial running surfaces 8 for the axial bearing of the planetary gear 3. These axial flanks are also covered with the corresponding hard material coating.
  • the axial flanks or running surfaces 8 serve as contact surfaces for thrust washers 9, which are arranged according to the invention on the planetary gear 3 at the end faces 10.
  • two stages 11 are formed on the planetary gear 3, into which the two axial bearing discs 9 are inserted.
  • the steps 1 1 are dimensioned such that the outer surfaces of the axial bearing washers 9 are flush with the end faces 10 of the planetary gear 3.
  • the thrust washers 9 are fastened via fastening screws 12, which are screwed into corresponding threaded bores on the planetary gear 3. Alternatively, a friction or material connection is conceivable.
  • the axial bearing disks 9 jump radially inward and engage in the steps 7 of the bearing sleeve 4. Their inner surfaces 13 are parallel to the axial edges of the bearing sleeve 4, they run against the axial treads 8 formed thereon. Over this, the axial bearing of the planetary gear 3 takes place on the Planetenradbolzen. 2
  • the bearing sleeve 4 has a dual function, namely on the one hand as a radial bearing component, on the other hand as a thrust bearing component. Only the bearing sleeve 4 is to occupy with the hard material layer, so only a single component, which is technically very advantageous manufacturing, since all three functional surfaces, namely the radial and the two axial treads are protected against wear and the corresponding treads are formed. Also, a simple assembly is given, since the bearing sleeve 4 can be pre-assembled with the planetary gear 3 and the thrust washers 9 and then the entire construct can be placed on the Planetenradbolzen 2.
  • a central channel 14 is provided on Planetenradbolzen 2, of which a radial bore, the one
  • Lubricant channel 15 forms, runs to the bolt outside.
  • a circumferential radial groove 16 is formed, depart from the at least one, preferably more to the planetary gear 3 running holes or openings 17, which open on the outside of the bearing sleeve 4. Further communicates with the one or more openings 17 a circumferential radial groove 20 formed on the inner wall of the planetary gear 3. With this radial groove 20 communicate respective axial grooves 19 through which the lubricant is distributed in width.
  • the lubricant is supplied via the central channel 14 and the lubricant channel 15. It is distributed in the first lubricant reservoir forming radial groove 16.
  • the one or more openings 17 it passes into the circumferential on the outside of the bearing sleeve circumferential groove 18, which is optional and can serve as a second lubricant reservoir. From the openings 17 and the optional radial grooves 18, the axial grooves 19 are fed.
  • the third lubricant reservoir is the radial groove 20 on the planetary gear wheel 3. In this way, sufficient lubricant supply is provided.
  • the lubricant is also very well maintained in the sliding area, as a direct outflow into the transmission via the radially inwardly extending thrust washers 9 is prevented. Due to the weight force, the entire lubricating oil can never run out of the radial / thrust bearing and a large part is held in the bearing. In addition, the centrifugal force is the
  • Lubricant anyway urged radially outward, so that it collects mainly in the region of the grooves.
  • FIG. 3 shows a second embodiment of a sliding bearing assembly 1 according to the invention, wherein the same reference numerals are used for the same components. Shown here is the planetary gear 3 and the bearing sleeve 4 and the two Axiallagerusionn 9. Again, only the bearing sleeve 4 is provided on its outer surfaces with the wear protection layer, such as the hard material layer.
  • this axial projection 23 the fastening screws are guided and screwed in the planetary gear 3.
  • a friction or material connection is conceivable. From the axial projections 23 radially inward then extend the remaining portions of the thrust washers 9, which run parallel along the end faces 10 of the planetary gear 3 in the steps 7 on the bearing sleeve 4. With their inner surfaces 13 they also slide here on the axial treads 8, about which the axial bearing is given.
  • a secure attachment can be achieved by the relatively wide-dimensioned axial projection 23.
  • this axial projection 23 also allows the formation of a press fit or a solder joint.
  • the planetary gear 3 is not reduced in its width, since no step is formed here, so that an uninfluenced hydrodynamically effective width is given in the radial sliding region. Nevertheless, here too results in a compact construction, whereby also here the bearing sleeve 4 multifunctional provides both the radial and the axial bearing.
  • FIG. 5 shows an embodiment of a further embodiment of the plain bearing arrangement, again using the same reference numerals for the same components. Shown is the planetary gear 3 and the bearing sleeve 4, which in turn has corresponding stages 7 and formed thereon axial treads 8. By way of example, two differently deep steps are shown, by which it should be shown that the step depth can ultimately be dimensioned arbitrarily. Again, only the bearing sleeve 4 is provided with the sliding or wear protection coating.
  • the thrust washers 9 are here executed in cross-section T-shaped, they each have the actual, the axial bearing serving transverse leg 24 and an axially projecting from this longitudinal leg 25 which is formed via a corresponding, hollow cylindrical axial flange 26.
  • the thrust washers 9 engage in the inner circumference of the planetary gear 3.
  • the inner circumferences of the Axialflansche 26 form in this embodiment, the second radial tread 27, so the tread on the side of the rotary member, ie here the planet 3. That is, the planetary gear 3 via these axial flanges 26 fixed to the planetary gear 3 via the screw connection of the axial bearing washers 9 are connected in the end faces 10 of the planetary gear 3, supported radially.
  • the Axiallagerusionn 9 so here is a double function, namely on the one hand, the pure axial bearing, on the other hand, the radial bearing.
  • the axial flanges 26 do not abut each other directly, but rather a narrow annular gap, that is to say an annular groove, which in turn serves as a lubricant collecting space, remains.
  • the planetary gear 3 is not stored directly on the bearing sleeve 4, but on the Axialflansche 26.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • General Details Of Gearings (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

L'invention concerne un agencement à palier lisse d'un élément rotatif sur un axe de palier, comprenant un axe de palier (2), un coussinet de palier (4) monté de manière solidaire en rotation sur ce dernier, qui est pourvu d'une première surface de roulement radiale (5) formée sur la périphérie extérieure, et un élément rotatif (3) monté de manière rotative sur le coussinet de palier (4), qui est monté en glissement sur la première surface de roulement radiale (5) par l'intermédiaire d'une seconde surface de roulement radiale (6). Selon l'invention, sur les deux faces frontales (10) de l'élément rotatif (3), des disques de palier axial (9) sont fixés en saillie radialement par rapport au coussinet de palier (4) et s'étendent contre des surfaces de roulement axiales du coussinet de palier (4), des flancs axiaux du coussinet de palier (4) formant les surfaces de roulement axiales (8) pour les disques de palier axial (9).
EP16790516.5A 2015-10-12 2016-10-12 Agencement à palier lisse d'un élément rotatif sur un axe de palier, en particulier d'une roue planétaire sur un axe de roue planétaire d'un engrenage planétaire Ceased EP3362696A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015219687 2015-10-12
PCT/DE2016/200469 WO2017063650A1 (fr) 2015-10-12 2016-10-12 Agencement à palier lisse d'un élément rotatif sur un axe de palier, en particulier d'une roue planétaire sur un axe de roue planétaire d'un engrenage planétaire

Publications (1)

Publication Number Publication Date
EP3362696A1 true EP3362696A1 (fr) 2018-08-22

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EP16790516.5A Ceased EP3362696A1 (fr) 2015-10-12 2016-10-12 Agencement à palier lisse d'un élément rotatif sur un axe de palier, en particulier d'une roue planétaire sur un axe de roue planétaire d'un engrenage planétaire

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US (1) US10253817B2 (fr)
EP (1) EP3362696A1 (fr)
CN (1) CN108138838B (fr)
DE (1) DE102016219800A1 (fr)
WO (1) WO2017063650A1 (fr)

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EP3536993A1 (fr) * 2018-03-05 2019-09-11 Siemens Aktiengesellschaft Système de palier lisse, engrenage planétaire, éolienne et application industrielle
AT521598B1 (de) * 2018-08-29 2020-03-15 Miba Gleitlager Austria Gmbh Gleitlagerelement
EP3739226B1 (fr) * 2019-05-16 2022-12-14 Siemens Gamesa Renewable Energy A/S Agencement de palier d'une éolienne et éolienne
DE102019215467A1 (de) * 2019-10-09 2021-04-15 Rolls-Royce Deutschland Ltd & Co Kg Zahnrad mit Keramikhülse
AT523760B1 (de) * 2020-04-15 2022-06-15 Miba Gleitlager Austria Gmbh Bauteilzusammenstellung, sowie eine Windkraftanlage, in welcher die Bauteilzusammenstellung verbaut ist
RU200748U1 (ru) * 2020-06-15 2020-11-11 Сергей Викторович Яблочко Комбинированный подшипниковый узел насоса
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Publication number Publication date
US20180306247A1 (en) 2018-10-25
US10253817B2 (en) 2019-04-09
CN108138838B (zh) 2019-12-06
WO2017063650A1 (fr) 2017-04-20
CN108138838A (zh) 2018-06-08
DE102016219800A1 (de) 2017-04-13

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