WO2017092740A1 - Transmission planétaire pour une unité d'entraînement de véhicule automobile - Google Patents

Transmission planétaire pour une unité d'entraînement de véhicule automobile Download PDF

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Publication number
WO2017092740A1
WO2017092740A1 PCT/DE2016/200499 DE2016200499W WO2017092740A1 WO 2017092740 A1 WO2017092740 A1 WO 2017092740A1 DE 2016200499 W DE2016200499 W DE 2016200499W WO 2017092740 A1 WO2017092740 A1 WO 2017092740A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
planet
planet carrier
planetary
stepped
Prior art date
Application number
PCT/DE2016/200499
Other languages
German (de)
English (en)
Inventor
Franz Kurth
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 WO2017092740A1 publication Critical patent/WO2017092740A1/fr

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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

Definitions

  • the invention relates to a planetary gear for a motor vehicle drive unit with a first sun gear, a second sun gear, acting as a planet carrier circulation housing, and a planetary gear with a planetary axis rotating planetary arrangement, wherein the power tap is accomplished from the planetary gear via its sun gears.
  • a planetary gear transmission of the aforementioned type which is designed as a spur gear and has a circulation housing with a planetary assembly received therein, wherein the planets of this planetary order with sun gear in engagement are also included in the interior of the circulating housing are.
  • the circulation housing comprises a first housing side part and a second housing side part, wherein these two housing side parts are laterally connected to opposite end faces of an externally toothed toothed ring. Due to the axial extent of this toothed ring results between the two side panels required for receiving the sun gears and the planetary assembly space.
  • the planetary arrangement itself is engaged with the sun gears so that the sun gears are rotatably coupled to each other in opposite directions.
  • the coupling of the drive power in the spur gear is via an external spur gear, which is in engagement with the external toothing of the said toothed ring.
  • the invention has for its object to provide a planetary gear for a motor vehicle drive unit, which is characterized by a robust and compact design and advantageous manufacturing under production aspects.
  • a planetary gear for a motor vehicle drive unit with: a first sun wheel,
  • a planetary assembly received in the planetary carrier having first and second planets in mesh with the two sun gears such that the two sun gears are rotatably coupled to each other in opposite directions;
  • a stepped planetary gear that has a first gear section and a second gear section and is mounted on the planet carrier
  • a ring gear which surrounds the planetary carrier concentrically with its revolution axis and engages with the first gear portion of the stepped planet, and a third sun gear which engages with the second gear portion of the stepped planet and is coaxially disposed with the planet carrier rotational axis;
  • first gear portion of the stepped planet extends on the axial level of the first and the second sun gear and is mounted on a first and a second bearing point on the planet carrier, and
  • the second gear section is cantilevered on the planet carrier and extends on an outer side of the planet carrier facing away from the first gear section.
  • the second toothed section of the stepped planet preferably projects axially beyond an end face of a side part of the planet carrier and is preferably formed by two, the first toothed portion between flying bearings on the planet carrier stored flying.
  • the Umlaufrä- dergetriebe is designed such that the two sun gears, the planetary arrangement and the planet carrier form a spur gear, for symmetrical branching of the guided over the planet carrier drive power to the two sun gears.
  • the two sun gears can be arranged side by side in close proximity by special tip circle dimensioning and supplementary design and mounting of the planetary arrangement, so that the axial length of the first toothed portion of the stepped planetary planet corresponds to the sum of the width dimensions of the toothed rings of the two inner sun gears.
  • the planet carrier is preferably made as a sheet metal forming part and consists of a first side part and a second side part, wherein the two inner sun gears are located axially between these two side parts.
  • the stepped planet may then be integrated into the transmission system in such a way that it radially distances the first side part to the axis of rotation and passes through it axially parallel, so that then the second gear section of the stepped planet on a side of the first side part facing away from the first gear section outside of the first side part Planet carrier extends.
  • this second toothed section there is then a so-called flying bearing, wherein this flying bearing has a high rigidity due to the two-sided support of the first toothed section in the planet carrier.
  • the stepped planet is preferably configured such that the first toothed portion extending on the axial level of the inner sun gears has a pitch circle diameter smaller than the pitch diameter of the second toothed portion. This makes it possible to dimension the diameter of the third toothed wheel engaged with and driving the second toothed portion relatively small and via the engagement of the third sun gear in the second toothed portion of the stepped planet, as well as the tooth engagement of the first toothed portion of the stepped planet in the internal toothing of the ring gear to realize a high overall gear ratio. In a particularly advantageous manner, the concept according to the invention also results in a reduction of the relative movements of the components, since numerous adjacent components which position one another via bearing points or movement surfaces have the same directions of rotation.
  • the third sun gear and coupled to the first sun gear first output shaft via a sun gear bearing rotatably supported against each other can be accomplished in particular by a needle bearing, or cylindrical roller bearing, wherein the running surfaces of the rolling elements can advantageously be provided directly by corresponding peripheral surfaces of that third sun gear (cylindrical inner surface) and the first output shaft (cylindrical outer surface).
  • the bearing of the planet carrier can be accomplished in an advantageous manner by the first side part of the planet carrier and coupled to the first sun gear output shaft via a first planet carrier bearing point are rotatably supported against each other.
  • This bearing point can be realized in an advantageous manner as a sliding bearing point, since in this bearing only the relative movements occurring in the context of the compensating effect of Differentialgetrie- must be permitted.
  • the second side part of the planet carrier and coupled to the second sun gear second output shaft via a second planet carrier bearing point can be rotatably supported against each other, whereby this bearing in turn is preferably realized as a sliding bearing.
  • the main bearing of the circulating system can then be accomplished by supporting the output shafts so that they support the planet carrier radially.
  • the stepped planet preferably forms part of a stepped planetary group, the stepped planets of that stepped planetary group preferably having the same construction and being connected to the planetary carrier in the same circumferential division.
  • This stepped planetary group then preferably comprises at least two, in particular three or even four stepped planets arranged at equal pitch on the planetary carrier.
  • the stepped planets can be designed as helical stepped planets. In this case, the tooth angles can again be selected such that an at least substantial compensation of the axial force components of the reaction forces acting on the stepped planet results.
  • the fixed storage of the stepped planet is preferably carried out via the second storage unit.
  • the relievenplanet can be made in an advantageous manner as a built structure, so that in particular the first toothed portion forms part of a pin which is inserted via a toothing in a second toothed portion forming spur gear.
  • the stepped planet in the second, ie the “rear” planet carrier side member overlapping bearing assembly may be designed so that this allows a push-through of the first toothed portion through the corresponding hole in the second planet carrier side part.
  • the tip circle of the first gear portion is then dimensioned smaller than the inner bore of a rolling bearing receiving bearing seat in the second planet carrier side part.
  • a driver profile in particular a spline
  • the drive of the third sun gear is preferably effected by an electromechanical drive unit. This may comprise a hollow shaft rotor through which an output shaft of the drive assembly extends axially therethrough.
  • the electromechanical drive unit then comprises a coaxially arranged to that output shaft motor.
  • the third sun gear can then be produced directly as a pinion seated on a hollow rotor shaft.
  • the third sun gear by otherwise connecting a drive unit.
  • the drive of the third sun gear via a spur gear, a traction drive or an angular gear can be done.
  • a purely electric drive of the third sun gear it is also possible to drive it by another drive system, for example an internal combustion engine, an oil engine or a hybrid drive system.
  • the drive unit according to the invention can be used advantageously for the realization of a rear axle system, which is compatible for example to the connection points of a conventional rear axle, so that the drive unit according to the invention can be integrated into vehicles whose bottom plate is designed primarily for other types of drives.
  • Figure 1 is a schematic representation to illustrate the structure of a planetary gear according to the invention which can be used in particular for the realization of electromechanical Congressachsantriebs application;
  • Figure 2 is a simplified axial sectional view for explaining further details of the stepped planet and this bearing on the planet carrier storage system.
  • FIG. 1 shows an inventive epicyclic gearbox for a motor vehicle drive system, with a first sun gear S1, a second sun gear S2, a circulation housing G acting as a planet carrier C, a planetary arrangement P with first and second planet P1, P2 with each other and the two sun gears S1, S2 are engaged in such a way that the two sun gears S1, S2 are rotatably coupled in opposite directions via the planets P1, P2.
  • the epicyclic gearbox further comprises a stepped planetary P3 having a first gear portion P3Z1 and a second gear portion P3Z2, and a ring gear H engaged with the first gear portion P3Z1 of the stepped planet P3.
  • the drive of the stepped planet P3 is accomplished via a third sun gear S3, which engages with the second toothed section P3Z2 of the stepped planet P3 and is arranged coaxially to a revolving axis X of the circulating housing G.
  • the first gear portion P3Z1 of the stepped planet P3 extends at the axial level of the first and second sun gear S1, S2 and is mounted in the rotary housing G via first and second bearing points L1, L2.
  • the two sun gears S1, S2, the planetary arrangement P and the circulation housing G form a spur gear differential for the symmetrical branching of the drive power guided via the planet carrier C to the two sun gears S1, S2.
  • the planet carrier C is composed of a first side part C1 and a second side part C2 and the two sun gears S1, S2 are arranged axially between these two side parts C1, C2.
  • the stepped planet P3 passes axially through the first side part C1 and the second toothed section P3Z2 of the stepped planet P3 extends on a side of the first side part C1 facing away from the first toothed section P3Z1.
  • the first toothed section P3Z1 has a pitch circle diameter which is smaller than the pitch circle diameter of the second toothed section P3Z2.
  • the second gear portion P3Z2 is cantilevered on the planet carrier C, i. its end region facing away from the planet carrier C is not supported by any further bearing device.
  • the power tap of the two inner sun gears S1, S2 is accomplished via a first and a second output shaft WS1, WS2.
  • the third sun gear S3 provided for driving the second toothed section P3Z2 of the stepped planetary gear is rotatably mounted on the first output shaft WS1 coupled to the first sun gear S1 via a sun gear bearing point L3. Both components rotate within the scope of operation in the same directions of rotation, so that there is a reduction of the relative movements.
  • the first side part C1 of the planetary carrier C and the output shaft WS1 coupled to the first sun gear S1 are rotatably supported against each other via a first planetary carrier bearing point L4.
  • the second side part C2 of the planetary carrier C and the output shaft WS2 coupled to the second sun gear S2 are rotatably supported against each other via a second planet carrier bearing point L5.
  • the first toothed section P3Z1 of the stepped planet P3 engages radially from the inside into the ring gear H.
  • the ring gear H is stationary anchored in the gear housing HO.
  • the stepped planet P3 forms part of a step planetary group, the step planets P3 of that step planetary group being of identical design and connected to the planetary carrier C in the same circumferential division.
  • the stepped planetary P3 is made as a built structure, ie it is composed of several components.
  • the stepped planetary P3 can in particular be designed in such a way that the first toothing portion P3Z1 part of a pin P3S forms, which is inserted via a toothing in a second toothing portion forming spur gear P3S1.
  • the partial circle P3C3 of the second toothed section P3Z2 shown in the sketch V1 has a larger diameter than the partial circle P3C1 of the first toothed section P3Z1.
  • the first gear section P3Z1 extends within the planet carrier C between the side parts C1, C2 thereof.
  • the planetary arrangement P is designed in such a way that the first and second planets P1, P2 engage with each other at the axial level of the second ("smaller") sun gear S2.
  • the first planet P1 is designed as a "long" planet extends over the entire length of the outer toothing of the first sun gear S1 and the outer toothing of the second sun gear S2.
  • the second planet P2 is designed as a "short" planet and only extends beyond the outer toothing of the second sun gear S2 and engages it so that the first planet P1 does not engage in the second sun gear S2, the sun gears S1, S2 With this measure, it becomes possible to arrange the first planets P1 of the planetary arrangement P on a pitch circle whose diameter is larger than the pitch circle which the second planetary P2 of the planetary arrangement P are arranged and the first planet P1 thus come out of the external toothing of the second sun gear S2 free.
  • three identical stage planets P3 are mounted on the planet carrier C.
  • the planetary arrangement P provided for realizing the differential gear function is in each case located in an intermediate region of successive stepped planets P3.
  • three planetary arrangements P are also provided which each have a first and a second coupling planet P1, P2. Due to the close proximity of the stepped planetary planets P3 and the coupling planets P1, P2 of the planetary arrangement P results in a favorable power transmission within the side parts C1, C2 of the planet carrier C and the realization of the translation effect and the differential function in the smallest space.
  • FIG. 2 illustrates in the form of a simplified Axialteilitess the structure of a stepped planet P3 and the storage thereof in the side parts C1, C2 of the planet carrier C.
  • the stepped planet P3 comprises a core pin P3S on the one hand the first toothing portion P3Z1 forms and on the other hand has a plug-in portion P3Z3, which in a complementary internally toothed bore P3Z4 of the spur gear P3S1 rotatably inserted, in particular einpressbar.
  • the spur gear P3S1 forms on its outer peripheral region the second toothed section P3Z2 of the stepped planet P3.
  • the storage of the stepped planet P3 in the planet carrier C is accomplished as shown by a first rolling bearing L1 in the first side part C1 and by a second rolling bearing L2 in the second side part.
  • the first rolling bearing L1 is located axially between the first and the second toothing section P3Z1, P3Z2 of the stepped planet.
  • This first rolling bearing L1 is designed as a floating bearing and also designed as a cylindrical roller bearing.
  • the rolling elements L1W of this first bearing L1 of the stepped planet run directly on a cylindrical outer peripheral surface of the core pin P3S.
  • the first bearing L1 further comprises a bearing outer ring L1 Ra which is pressed into a corresponding receiving bore C1 B1.
  • the rolling elements L1W are guided in a cage L1 K.
  • the bearing outer ring L1 R1 is axially secured in the receiving bore C1 B1 by a securing device (not shown here, for example, by roll-up flanging).
  • the side part C1 of the planetary carrier C is formed thickened in the area surrounding the receiving bore C1 B1.
  • the corresponding bead is produced by plastic deformation of the starting material used to form the side part C1.
  • the material accumulation is brought about by radial displacement of the material initially located in the area of the receiving bore C1 B1 to the outside.
  • This second bearing L2 forms the fixed bearing and determines the axial position of the core pin P3S in the planet carrier C.
  • This bearing L2 is designed here as a deep groove ball bearing. It comprises a bearing inner ring L2i and a bearing outer ring L2a, and designed as balls rolling elements L2W which are guided in a cage L2C. The bearing inner ring L2i is secured via a locking ring L2R on the core pin P3S.
  • the bearing outer ring L2a of the second bearing L2, similar to the bearing outer ring L1 Ra of the first bearing L1, is press-fitted into a bore C1 B2 formed in a bead-surrounded region of the second side part C2.
  • the axial securing of this bearing outer ring L2a can in turn be accomplished by plastic deformation of the bearing outer ring in the region of its end faces skirting material of the second side part C2.
  • the first bearing L1 is designed such that the inner diameter of the first bearing outer ring L1 Ra is greater than the head circle through knife of the first gear section. This makes it possible to first fix the first bearing outer ring L1 Ra in the first side part and then pass the core pin P3S through the first bearing outer ring L1 Ra.
  • the second bearing L2 can also be fixed first in the second side part C2 before inserting the core pin P3S, and then after inserting the corresponding end portion of the core pin P3S this is axially fixed by inserting the retaining ring L2R in the second bearing.
  • the second toothed section P3Z2 is thus located outside of the planet carrier C and is seated on a pin P3S of the stepped planet P3 which is cantilevered as a result.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une transmission planétaire pour une unité d'entraînement de véhicule automobile, comprenant un premier pignon planétaire, un deuxième pignon planétaire, un boîtier rotatif qui fonctionne en tant que porte-satellites, un ensemble de satellites qui est logé dans le porte-satellites, comprenant des premiers et deuxièmes satellites qui s'engrènent avec les deux pignons planétaires de telle sorte que les deux pignons planétaires sont accouplés en sens inverse l'un à l'autre; un satellite étagé qui comprend une première partie de denture et une deuxième partie de denture et est monté sur le porte-satellites, une couronne qui borde le porte-satellites concentriquement à son axe de rotation et s'engrène avec la première partie de denture du satellite étagé, et un troisième pignon planétaire qui s'engrène avec la deuxième partie de denture du satellite étagé et est disposé de manière à ce que son axe coïncide avec l'axe de rotation du porte-satellites, la première partie de denture du satellite étagé s'étendant au niveau axial du premier et du deuxième pignon planétaire et étant montée sur le porte-satellites par le biais d'un premier et d'un deuxième point de pivotement, et la deuxième partie de denture étant montée de manière mobile sur le porte-satellites et s'étendant sur un côté extérieur, opposé à la première partie de denture, du porte-satellites.
PCT/DE2016/200499 2015-12-01 2016-11-07 Transmission planétaire pour une unité d'entraînement de véhicule automobile WO2017092740A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015223914.4A DE102015223914B4 (de) 2015-12-01 2015-12-01 Umlaufrädergetriebe mit Untersetzungsstufe für eine Kraftfahrzeugantriebseinheit
DE102015223914.4 2015-12-01

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Publication Number Publication Date
WO2017092740A1 true WO2017092740A1 (fr) 2017-06-08

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Application Number Title Priority Date Filing Date
PCT/DE2016/200499 WO2017092740A1 (fr) 2015-12-01 2016-11-07 Transmission planétaire pour une unité d'entraînement de véhicule automobile

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WO (1) WO2017092740A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020216504A1 (fr) * 2019-04-23 2020-10-29 Zf Friedrichshafen Ag Transmission et véhicule équipé d'une transmission
US11852080B1 (en) 2022-08-05 2023-12-26 General Electric Company Gearbox assembly

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019124666B4 (de) * 2019-05-16 2021-09-02 Schaeffler Technologies AG & Co. KG Differenzialgetriebe
DE102022117328A1 (de) 2022-07-12 2024-01-18 Schaeffler Technologies AG & Co. KG Getriebeanordnung
DE102022213301B4 (de) 2022-12-08 2024-06-27 Zf Friedrichshafen Ag Kompakt bauendes Kraftfahrzeuggetriebe mit Stufenplanetenradsatz für ein zumindest teilweise elektrisch angetriebenes Kraftfahrzeug

Citations (3)

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DE102012213392A1 (de) 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Getriebekombination mit einem Planetendifferenzial nach Art eines Wildhaber-Novikov-Stirnraddifferenzials
DE102013222621A1 (de) * 2013-11-07 2015-05-07 Schaeffler Technologies Gmbh & Co. Kg Stützanordnung für ein Leichtbaudifferential
DE102014209942A1 (de) * 2014-05-26 2015-11-26 Schaeffler Technologies AG & Co. KG Umlaufrädergetriebe, insbesondere wälzendes Achsgetriebe für ein Kraftfahrzeug

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Publication number Priority date Publication date Assignee Title
DE19756966A1 (de) 1997-12-20 1999-06-24 Zahnradfabrik Friedrichshafen Planetengetriebe
DE102011079975A1 (de) 2011-07-28 2013-01-31 Schaeffler Technologies AG & Co. KG Antriebseinrichtung für ein Kraftfahrzeug

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012213392A1 (de) 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Getriebekombination mit einem Planetendifferenzial nach Art eines Wildhaber-Novikov-Stirnraddifferenzials
DE102013222621A1 (de) * 2013-11-07 2015-05-07 Schaeffler Technologies Gmbh & Co. Kg Stützanordnung für ein Leichtbaudifferential
DE102014209942A1 (de) * 2014-05-26 2015-11-26 Schaeffler Technologies AG & Co. KG Umlaufrädergetriebe, insbesondere wälzendes Achsgetriebe für ein Kraftfahrzeug

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020216504A1 (fr) * 2019-04-23 2020-10-29 Zf Friedrichshafen Ag Transmission et véhicule équipé d'une transmission
US11884146B2 (en) 2019-04-23 2024-01-30 Zf Friedrichshafen Ag Transmission and vehicle with transmission
US11852080B1 (en) 2022-08-05 2023-12-26 General Electric Company Gearbox assembly

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DE102015223914A1 (de) 2017-06-01
DE102015223914B4 (de) 2021-07-29

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