WO2015067261A2 - Structure de palier de support pour un différentiel épicycloïdal - Google Patents

Structure de palier de support pour un différentiel épicycloïdal Download PDF

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Publication number
WO2015067261A2
WO2015067261A2 PCT/DE2014/200551 DE2014200551W WO2015067261A2 WO 2015067261 A2 WO2015067261 A2 WO 2015067261A2 DE 2014200551 W DE2014200551 W DE 2014200551W WO 2015067261 A2 WO2015067261 A2 WO 2015067261A2
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
planetary
planet
bearings
differential
Prior art date
Application number
PCT/DE2014/200551
Other languages
German (de)
English (en)
Other versions
WO2015067261A3 (fr
Inventor
Harald Martini
Thorsten Biermann
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2015067261A2 publication Critical patent/WO2015067261A2/fr
Publication of WO2015067261A3 publication Critical patent/WO2015067261A3/fr

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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F16H2048/405—Constructional details characterised by features of the rotating cases characterised by features of the bearing of the rotating case
    • 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 planetary disk with a drive wheel and two pancake wheel seats mounted in a p-net carrier, one of which is a piano wheel of a planetary red sata m ' a first sun gear engages and a planetary gear of the other Pianetenradsa zes engages in a zw ites sun gear, the tarpaulin carrier on at least one roller bearing on a housing radially rotatable and axially goeitionsbestimrnt, where at least one Impact bearings at least a first and a second bearing shank each have a Flansebendab- section feenaohbart to the treads so. aur lo,
  • a Abtnebswelle of a motor drives a front or Operaerrad as a drive wheel, there along with a dar n mounted Planefentrager to the common ⁇ hese de Pianetendifferentlals (the common. Axis on housing, spur gear, planetary carrier and A drive shaft of the differential, is rotatable.
  • the planetary carrier carries at least two planetary gears meshing over part of their width, each of which also engages in one of two differential springs.
  • the torque is applied over several pairs of pianeta wheels uniformly distributed around the circumference two Sennori riders are connected to the A web worlds of Plaendend erentla,
  • a erfindungagemäSes Planetenraddifferenbai is characterized in that counter-safe to the known prior art adjacent which: the tread Hege lighter * Flansebeudabitese (or "edges" ⁇ of the form are aligned ilzlagerschalen a bearing paraliei each other, are usually Pfanetenradif of Flanetenraddiffarentialen
  • Each Wiklager consists of two Lagerohalen (an inner and an outer, also called ⁇ uEenring and mecanichog), a WilzSystemkifig and the Wilz stressesn, Kugein, cones, rollers, needles, tons or the like Bearing shells designed in such a way that on the one hand they are easy to produce, especially in terms of shape, but on the other hand can be safely changed in the radial wheel differential Erential réellene men.
  • the orientation of the fianschenda - suture on the soap of the flaxan has not been considered welter.
  • the final lift pins are, as the AosfOhrungsbeiapielen clear, more cost-effective, a more compact design of the planetary differential allows.
  • better protection against contamination and subsequent wear of the bearings can be achieved without giving up the stated advantages.
  • an advantageous embodiment is characterized in that both sides of the first bearing shell are in the same axial direction or in the same direction obliquely oriented to the axial direction. If both flanged bushes of the first bearing shaft and the same axial direction are used, this bearing shell can be manufactured by a forming process (Z3, deep drawing of a suitable bleed head) with: a comparatively lower stroke and thus shorter picking speed! As a result, the bearing shell can be produced more cheaply.
  • a further advantageous embodiment of the invention is characterized in that at least one bearing ring of at least one of the rolling bearings has a Li or egg-shaped cross section.
  • Such a cross section is simply Umferrritechnisch in Massehfertigung gehefzustete.
  • a bearing ring in "IT or shape encloses the cage and its cage particularly closely, so that, as a rule, a very compact bearing shape is produced, which in turn contributes to a reduction in the size of the end product.
  • the connecting rings of the two bearing rings point axially or radially toward one another. If the flange end sections face one another, it follows that the bearing surrounds the rolling element.
  • the gap between the Bearing rings maximum 30% of the Wäiz Eisendurcb- diameter. Larger fission mats may cause smolder to penetrate the bearings during operation, shortening the life of the bearing.
  • the above-mentioned and further specified embodiments can limit the contamination of the rolling elements and the running surface, which increases the service life of the bearings.
  • the inner ring of the bearing is radially outwardly of the pitch circle of the rolling elements and the outer surface radially inwardly within the pitch circle of the bodies ⁇ - gesföt t.
  • the situation can be made smaller, more compact and cheaper on this catfish.
  • material can also be saved around the bearing since the bearing seat of the outer ring lies almost at the same diameter as the raceway of the inner ring.
  • the bearing seat, an inner ring of each rolling bearing is arranged at most around the radius of a rolling body further than the bearing seat of the outer ring of the rolling bearing, and / or the bearing seat of the outer ring of each rolling bearing at a maximum about the thickness of a rolling body
  • the bearings can be arranged so that they hug extremely compact in the radial direction
  • the inner ring partially surrounds the rolling elements outside and / or the outer ring surrounds the Wlizessor also inside. This results in a radially extremely compact design of the Rlanefendlfterentials, In the known state of the art, How-in "FIG.
  • the Planetenendifferentlal is characterized in that it is designed as a spur gear, Stirnraddiffeenfiaie are on Gr d Toovas small Sauani and rumble omenienöhertra- Fungägk iten especially in front-wheel drive vehicles sFront
  • the ü- d the inequality 8 (Ü - d)> 1, where B is the distance between the two bearings from each other, the so-called bearing width, D of the outer diameter of the bearing and d is the inner diameter of the bearing.
  • B is the distance between the two bearings from each other
  • D is the distance between the two bearings from each other
  • D is the inner diameter of the bearing.
  • the bearing width is at least equal to or greater than the difference between internal and external diameter.
  • the tolerance is at least as great as the difference between the inner and outer diameter of the bearings, which leads to an effective increase of the tilting moment compared to a conventional Fesf floating bearing or more floating bearing.
  • the inner and outer rings of the bearing are removed without cutting.
  • chip-free production methods are cost-effective, since the material is utilized efficiently, fewer accidents occur than in the case of cutting processes, and the throwing costs per part are also less expensive.
  • the blanks of the inner and / or outer rings of the rolling bearing are toor grown by cold-rolling a bender. Further preferably, both blanks have the same strength for the outer and outer rings and can also be made of the same material. Cold forming of sheet metal parts is an extremely cost effective one leads. So-0 results in high strength in low-caliber bearings in combination with low coefficients, which increases the load capacity of the tag.
  • both blanks have the same thickness, they can be suitably manufactured together in a Ümförmvor- gang.
  • different aterials for inside "and outer ring used a camp could, for example as advertising hergesfeilt to that an easy-to-exchanging component yields faster and comparable sehleiSt, thereby protecting the mounted difficult part.
  • the rolling elements are spherical.
  • Zwa is the afore-mentioned ⁇ yfbau also mi roles, cylinders, cones, tons, nadein or other: Watekdfpem producible, ball bearings are, however, as a mass-produced a sebr costa tion solution,
  • Vorzugswelse enclose the bearing rings laterally over the Bayraum de Wilz analyses outgoing parts of the bearing cage radially, in general W lz analyses are taken in a rolling bearing in a bearing cage.
  • This bearing cage prevents the rolling elements abutting and help them from each other at a uniform distance, so that the bearing load is evenly distributed to the Wälzkör he is, this contributes to an increased bearing life
  • the bearing cage which is usually designed to be weaker than the bearing rings, is enclosed by the bearing rings, it is difficult, if not impossible, to destroy the bearing cage by the action of m.
  • the life of the rolling bearing and thus the differential is increased
  • the lead thickness is a sheet metal finish from which the bearing shell is produced: ird, rnim, 30% of the rolling element diameter.
  • the bearing inner ring as one de bearing shells, is supported axially on the side wall and radially on the flange of the differential housing.
  • the bearing inner ring is set so that when mounting the solid housing provides a defined seat of the inner ring, and the bearing preload is alshnnghar on the outer rings acting on the bias.
  • This facilitates the assembly, as on the outer rings in the assembled state better an adjustable force can be applied as to the inner rings.
  • the legs of the two rings preferably have axially or radially towards each other.
  • the seat of the Innonrlnges in the housing is larger in diameter than the Sit of the planet carrier (Dlfferenzialkorbs) In the Auixenrln and also larger than the circle (ha) Wolter favors the AulSennng with at least a gift! in the Mau, so the "contour" of the inner ring S; ax ai or r dial (if not just an U-profl formed ion ring of the camp is present). Oc welter preferred two such bearings are clamped in D-arrangement,. SehiieSlieh Is mi evonugen, that the campers spanless, in esondero mtemiiec niseh ergestelit are.
  • FIG. 2 shows a section through a hinge arrangement according to the invention for a panel end lens with angular ball bearings in an O arrangement according to a first embodiment
  • FIG. 3 shows a section through a bearing for use in the latch arrangement according to FIG.
  • Figure 4 shows a sonitt, by an inventive Stutzanordriung for a planetary differential with Schr gkugeliagern In O anode according to a second A sfihrungsform
  • FIG. 1 shows a scanning arrangement for a single-wheel differential as an example of a prior art planetary differential plate.
  • W rd also in the other figures S only e? Part shown above the Aehse.
  • the bearings 6 and:? are, as can be seen from Figure 1, constructed substantially mutually mirror-symmetrical.
  • the bearing surfaces lie as can be seen from the figure at approximately the height of Eingrif s the planet Rider in five the sun and at the same approximate hr at the height of the extent de carrier "part.
  • the inner and outer rings of the bearings are extended inwards so as to be uniformly inexpensive to produce uniformly and at the same time to be securely received in the spur gear shaft.
  • FIG. 2 shows a spur gear differential with a suitable bearing arrangement.
  • Comparable components receive the same Benugs elk as in Figure 1 and here only the differences from the arrangement of Figure 1 are explained in more detail In this ⁇ us uhrüngsform falls compared to the prior art shown in Figure 1, first, that the bearings 6, 7 arranged further inside and the tagerschalen / bearing ring 6A, 68, TA, TB are significantly more compact. The inside have the reference numerals 6a and YES.
  • the outer rings have the bowing angles iS and 78 in this arrangement are the differentiated suns 1A ; 18 radially directly in Flarv- see / Gesimousetelen 8. ⁇ , 88 supported the Differeniialgephases 2, instead of being supported in the prior art on ⁇ usformungen La La ernnge.
  • the bearing seat of the outer ring 7A has almost the same diameter as the raceway of the mecanicrlngs 78. It has been found that the difference of the radial ⁇ bsfands the Lagerifze preferably maximally corresponds to the diameter of a rolling element
  • the other components such as the Pfeten wheels 2, the Pianetenlini 3, the pin 4 and the spur gear 5 are arranged substantially as in Figure 1. Only the bearings 6 and 7 and the flanges A, 88 de housing 2 are fundamentally different 1 designed as in the prior art.
  • the flanges 8A, SB can surround the bearings 8 and 7 from outside, now with these bearings.
  • Your inner rings 8A, 7A rest on an inwardly drawn flange of Pianetentrigers 3.
  • the outer ring $:> 7B are the Gehiuseteiien m, 88, welöhe differential suns on "taking .. How u see is” are the tager $ 7 and also mirror mmet- hsc each other.
  • the storage shown in Figure 1 in which only one of the treads 8GA, SGI, 7GA, 7G (namely the running BGA, 70A AuAenlageT 6A, 7 ⁇ E) .
  • the gap A between inner and outer ring is ideally at most 30% of the diameter of the rolling elements 7C.
  • the distance ⁇ is less than 10% of the rolling element diameter on the less polluted inner side, on the outside it is even lower.
  • the thickness of the bearing rings 7A, TB (and analogously also the rings SA, B large should be enough to cushion the prestressing mentioned above with reference to FIG. 2.
  • the thickness and strength should be sufficient According to experience, these requirements can be fulfilled if the bearing rings 7A, TB have a: sheet metal thickness that is at least 30% of the diameter of the rolling bodies,
  • Figure 4 shows a Stirnraddifferenflai as an example of a Plianneraddifferentlals according to another export ngsförm de invention
  • Innebliaelf borrow 78 encompasses an area into which the Flan Registereddsbsohmti the Aufienlayfflache TA protrudes, At the same time could the Aus colfliche TA in this example so
  • the outer ring TA engages with its one flansohendahsohni with 7FA i the inner ring 7B.
  • the flange face 7 ⁇ and 7FI are aligned parallel to each other, a face 7H is not parallel to these faces.
  • Other components not emphasized in Figures 4 and 5 are similar to those of Figures 1 and 2 and who That is why we have not discussed more
  • FIG. 4 an alternative StOt structure for the Irinenhng is shown in Figure 4.
  • a pot-shaped structure of thin and thus resilient sheet metal is used; which stiffens the bearing seat, the insert *, and also leads to a better balance of the forces acting on the inner ring.
  • the stiffening with low yaferial use results in lower-cost operating capabilities for the bearing seat.
  • Scots can also be used as wilzkdfpers instead of bullets, also in Röllen s Nadein or the cone in the camps.
  • a schragverz.a ntes Stirnraddlfferentiai and of course a planetary differential without spur gear can be constructed with the shown tageran eleven. 1 & Dtffer ntialsonne sun / sun wheel / first sun wheel

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

Abstract

L'invention concerne un différentiel épicycloïdal possédant une roue d'entrée (5) et deux jeux de satellites montés dans un portesatellites (3) dont un satellite (2) d'un jeu de satellites engrène dans une première roue planétaire (1A) et un satellite de l'autre jeu de satellites engrène dans une seconde roue planétaire (1B), le porte satellites (3) étant monté de façon rotative radialement et dans une position axiale déterminée sur un carter (8A, 8B) par l'intermédiaire d'au moins un roulement (6, 7), le ou les roulements (6, 7) comprenant au moins une première cuvette de roulement (6A, 7A) et une seconde cuvette de roulement (6B, 7B) qui présentent chacune un segment formant collet (6FA, 6FI, 7FA, 7FI) voisin des surfaces de roulement (6GA, 6GI, 7GA, 7GI), les deux segments formant collet (6FA, 6FI, 7FA, 7FI) étant orientés parallèlement entre eux.
PCT/DE2014/200551 2013-11-11 2014-10-14 Structure de palier de support pour un différentiel épicycloïdal WO2015067261A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013222833.3 2013-11-11
DE201310222833 DE102013222833A1 (de) 2013-11-11 2013-11-11 Stützlageranordnung für ein Planetendifferential

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WO2015067261A2 true WO2015067261A2 (fr) 2015-05-14
WO2015067261A3 WO2015067261A3 (fr) 2015-09-24

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WO (1) WO2015067261A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10760670B2 (en) 2015-09-04 2020-09-01 Schaeffler Technologies AG & Co. KG Distribution gearing and electric drive unit having a distribution gearing
CN108397543B (zh) * 2018-05-11 2023-11-14 浙江吉利变速器有限公司 行星齿轮支架结构及具有该结构的行星齿轮机构

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008110425A2 (fr) 2007-03-13 2008-09-18 Schaeffler Kg Différentiel à pignons droits et différentiel à superposition muni dudit différentiel à pignons droits
DE102007040478A1 (de) 2007-08-28 2009-03-05 Schaeffler Kg Differentialgetriebe mit leichten Trägerteilen
DE102011087581A1 (de) 2011-12-01 2013-06-06 Schaeffler Technologies AG & Co. KG Differenzial für ein Kraftfahrzeug mit aufgeschrumpftem Achsantriebsrad

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104145139B (zh) * 2012-04-19 2017-02-22 舍弗勒技术股份两合公司 差速器的行星齿轮传动机构
WO2013156498A1 (fr) * 2012-04-19 2013-10-24 Schaeffler Technologies AG & Co. KG Engrenage planétaire muni d'un engrenage différentiel

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008110425A2 (fr) 2007-03-13 2008-09-18 Schaeffler Kg Différentiel à pignons droits et différentiel à superposition muni dudit différentiel à pignons droits
DE102007040478A1 (de) 2007-08-28 2009-03-05 Schaeffler Kg Differentialgetriebe mit leichten Trägerteilen
DE102011087581A1 (de) 2011-12-01 2013-06-06 Schaeffler Technologies AG & Co. KG Differenzial für ein Kraftfahrzeug mit aufgeschrumpftem Achsantriebsrad

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DE102013222833A1 (de) 2015-05-13
WO2015067261A3 (fr) 2015-09-24

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