WO2014056577A1 - Différentiel planétaire - Google Patents

Différentiel planétaire Download PDF

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Publication number
WO2014056577A1
WO2014056577A1 PCT/EP2013/002890 EP2013002890W WO2014056577A1 WO 2014056577 A1 WO2014056577 A1 WO 2014056577A1 EP 2013002890 W EP2013002890 W EP 2013002890W WO 2014056577 A1 WO2014056577 A1 WO 2014056577A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring gear
planet carrier
gear
planetary
bearing
Prior art date
Application number
PCT/EP2013/002890
Other languages
German (de)
English (en)
Inventor
Peter Appeltauer
Original Assignee
Daimler Ag
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 Daimler Ag filed Critical Daimler Ag
Publication of WO2014056577A1 publication Critical patent/WO2014056577A1/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
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H2055/176—Ring gears with inner teeth

Definitions

  • the invention relates to a planetary differential according to the preamble of claim 1 and a motor vehicle drive train according to claim 10.
  • the invention is in particular the object of the weight of the
  • the invention is based on a planetary differential with a ring gear, a
  • Planetary gear and at least one ring gear bearing which supports the ring gear which supports the ring gear.
  • the at least one ring gear bearing supports the ring gear on the planet carrier.
  • the planet carrier can be used to support the ring gear, whereby at least one component of the planetary differential, in particular a differential housing, can be dispensed with without replacement.
  • Reduction of a weight of the planetary differential can be made, such as the machining of outer races of a constant velocity joint of a side shaft in a component. Thereby, the weight of the planetary differential can be reduced, whereby when using the planetary differential in a motor vehicle drive train, a weight of the motor vehicle drive train and thus a Fuel consumption of a motor vehicle powertrain having motor vehicle can be reduced.
  • a planetary differential is in particular a
  • Differential which has at least one planetary gear connected to the planet gear, which is coupled in the radial outward direction with the ring gear and in the radial direction inwardly with a sun gear.
  • Planet differential is preferably formed as an axle differential.
  • the term "radial” is here referred in particular to an axis of rotation of the ring gear, so that the term “radially” denotes a direction which is perpendicular to the axis of rotation.
  • the at least one ring gear is designed as a rolling bearing, whereby the ring gear can be stored particularly wear.
  • Planet differential has at least one carrier bearing, which is intended to support the planet carrier on a housing, whereby the planet carrier can be stored particularly weight-saving.
  • the carrier bearing is designed as a roller bearing, whereby the planet carrier can be stored particularly wear.
  • the planetary differential has at least one further ring gear bearing which supports the ring gear on the planet, and has at least a first intermeshing with the ring gear planet, which is arranged axially between the at least two Hohlradlagern ,
  • the planet carrier supports the at least one planetary gear.
  • the first planetary gear is advantageously directly in engagement with the ring gear.
  • the term "axial” is here in particular related to the axis of rotation of the ring gear, so that the term “axially” denotes a direction which extends on the axis of rotation or parallel to this.
  • the planetary differential has at least one meshing with the first planetary gear second planetary gear, which is arranged axially between the at least two Hohlradlagern, and has a sun gear, which meshes with the second planetary gear.
  • This can a load on an internal toothing of the ring gear can be reduced, whereby the internal toothing can be performed axially narrower compared to an external toothing of the ring gear.
  • the second planetary gear is advantageously directly in engagement with the first planetary gear and with the sun gear.
  • the ring gear has an outer toothing and an inner toothing, wherein an axial extent of the outer toothing is greater than an axial extent of the internal toothing.
  • the ring gear advantageously forms a drive wheel.
  • the internal toothing advantageously meshes with the first planetary gear.
  • the planet carrier at least a first planet carrier member and a second
  • Planet carrier parts at least partially forms a joint housing, which further weight can be saved.
  • at least one planet carrier part is formed integrally with the joint housing.
  • at least one of the at least two planet carrier parts at least partially forms a joint housing of a constant velocity joint of a side shaft of a motor vehicle drive train.
  • the ring gear bearing is a
  • Angular contact ball bearings formed, whereby the ring gear bearing can accommodate axial and radial loads.
  • a motor vehicle drive train having at least one planetary differential according to the invention is proposed. This can be a weight of
  • Motor vehicle powertrain can be reduced, thereby reducing fuel consumption and so that a pollutant emission of the motor vehicle drive train having motor vehicle can be reduced.
  • the sun gear for driving a first motor vehicle wheel and the planet carrier for driving a second motor vehicle wheel is provided, whereby a particularly light final drive can be provided.
  • the drive power is discharged via the sun gear to one of the driven motor vehicle wheels and via the planet carrier to the further driven motor vehicle wheel from the planetary differential.
  • Fig. 1 shows schematically a planetary differential of a final drive for a
  • Fig. 2 is a diagram of a toothing of the planetary differential.
  • Figures 1 and 2 show a part of a final drive of a
  • the final drive has a planetary differential 10, which drives a drive power to both
  • the planetary differential 10 is designed as a spur gear.
  • the planetary differential 10 is advantageously used in front-wheel drive motor vehicles whose engine and transmission are arranged transversely. In principle, the planetary differential 10 can also be used in rear-wheel drive vehicles with a longitudinal drive train.
  • Trained as an axle differential planetary differential 10 has a ring gear 11, a planetary gear 12 and two ring gear bearings 13, 14 which support the ring gear 11, on.
  • the two ring gear bearings 13, 14 support the ring gear 11 respectively on the planet carrier 12.
  • the ring gear 11 is supported by the ring gear bearings 13, 14 on the planet carrier 12 from.
  • the ring gear bearings 13, 14 are each formed as a rolling bearing.
  • the ring gear bearings 13, 14 each as an angular contact ball bearing educated.
  • the ring gear bearings 13, 14 have trained as balls rolling elements 24, 25.
  • the ring gear 11 forms an outer raceway for the rolling elements 24, 25 and the planet 12 an inner raceway for the rolling elements 24, 25 from.
  • the outer race of the ring gear 11 and the inner race of the planet carrier 12 are offset from each other in the direction of a bearing axis.
  • One of the ring gear bearings 13 supports the ring gear 11 at a first end side and the other
  • the ring gear 11 is a spur gear
  • An order of magnitude of the ring gear bearings 13, 14 corresponds to at least approximately one order of magnitude of a so-called thin-ring bearing.
  • the rolling elements 24, 25 have a diameter of 6.35 mm.
  • a pitch diameter is about 180 mm.
  • a helix angle is 30 °.
  • a rolling element cage is made of sheet steel.
  • the roller cage can also consist of a different material. Characterized in that the ring gear bearings 13, 14 of the support of the ring gear 11 rotate only at differential speed of the drive wheels of the axis, no functional limits are set with the comparatively low permissible speed of this type of bearing.
  • the planetary differential 10 For storage of the planet carrier 12, the planetary differential 10 has two
  • the ring gear bearings 13, 14 are arranged axially between the two carrier bearings 15, 16.
  • the carrier bearings 15, 16 are formed as rolling bearings.
  • the carrier bearing 15 is designed as a tapered roller bearing and the carrier bearing 16 as an angular contact ball bearing.
  • the support bearings 15, 16 each have an inner ring 26, 27 which is fixedly arranged on the planet carrier 12, and in each case an outer ring 28, 29 which is fixedly connected to the housing on.
  • the planetary differential 10 further includes three Planetenradpare 30 and a single sun gear 19.
  • the Planetenradprese 30 and the sun gear 19 are arranged axially between the two Hohlradlagern 13, 14.
  • Planetenradstande 30 are distributed along a circumference around the sun gear 19.
  • the Planetenradpare 30 operatively connect the ring gear 1 1 and the sun gear 19 with each other.
  • the planet carrier 12 receives the Planetenradbine 30.
  • Figures 1 and 2 only one of the three Planetenradpare 30 is shown.
  • one to four pairs of planetary gears 30 can be accommodated in an existing installation space with different sizes of the design, which is an adaptation to the required torque class of
  • the three Planetenradstande 30 each have two meshing planetary gears 17, 18.
  • the two planet gears 17, 18 are the same size.
  • the first planet gear 17 meshes with the ring gear 11 and the second planet gear 18 with the sun gear 19.
  • the planet gears 17, 18 are arranged axially between the two Hohlradlagern 13, 14.
  • the planet carrier 12 forms a first output and the central sun gear 19 has a second output.
  • the planet carrier 12 is provided for driving one of the drivable motor vehicle wheels of the axle and the sun gear 19 for driving the other drivable motor vehicle wheel of the axle.
  • Planet differential 10 is initiated, the planet carrier 12 drives one of the drivable motor vehicle wheels of the axle and the sun gear 19 the other
  • Gear sizes can be achieved a range of different ratios of distributed to the two drives drive power. If the diameter of the active circle of the ring gear 11 is exactly twice as large as a diameter of the
  • the planetary differential 10 is symmetrical, whereby the planetary differential 10 distributes the initiated drive power in equal parts to the two drivable vehicle wheels of the axle.
  • the ring gear 11 is formed as a drive wheel.
  • the ring gear 1 1 has an external toothing 20 and an internal toothing 21, wherein an axial extent of the external toothing 20 is greater than an axial extent of the internal toothing 21. Due to the load distribution on the three Planetenradpare 30, the internal toothing 21 of the ring gear 1 1 in comparison to the outer teeth 20 of the ring gear 11 is less loaded, whereby the internal teeth 21 is made narrower than the outer teeth 20.
  • the first planetary gear 17 of each of Planetenradcrue 30 is directly engaged with the
  • the internal toothing 21 of the ring gear 11 is arranged axially between the two Hohlradlagern 13, 14. A portion of the ring gear 11, which by the smaller axial extent of the
  • Planet wheel 12 used.
  • the ring gear 11, the planetary gears 17, 18 and the sun gear 19 are straight-toothed.
  • This design is particularly suitable for motor vehicles, which are equipped with electronic stability programs (ESP), as these not only on no locking effect in the planetary differential
  • the planetary gear can also be performed helical.
  • the resulting axial forces can be used to represent a self-locking effect of the planetary differential 10.
  • additional, additional locking arrangements may be added to the planetary differential 10, such as hydraulic or electro-actuated transverse locks or relative speed independent torque distribution devices.
  • the planet carrier 12 is formed in two parts.
  • the planet carrier 12 has a first planet carrier part 22 and a second planet carrier part 23, wherein the
  • Planet gears 17, 18 are arranged axially between the first planet carrier member 22 and the second planet carrier member 23.
  • the sun gear 19 is also arranged axially between the two planet carrier parts 22, 23.
  • the first planet carrier part 22 forms the raceway for the rolling elements 24 of the ring gear bearing 13 and the second planet carrier part 23, the track for the rolling elements 25 of the ring gear 14.
  • the carrier bearing 15 supports the first planet carrier part 22 and the
  • Carrier bearing 16 the second planet carrier member 23 to the housing, not shown.
  • the planetary differential 10 further has six planet gear 31, which connect the two planet carrier parts 22, 23 with each other.
  • the Planetenradbolzen 31 each have at one axial end a stop and at another axial end a groove. In an assembled state, the stop of the Planetenradbolzen 31 abuts against the first planet carrier member 22.
  • Planetenradbolzen 31 forms a receptacle of a bayonet closure.
  • the figures 1 and 2 is only one of the six planetary wheel 31 visible.
  • the sun gear 19 and all planet gears 17, 18 ground together on a magnetic table axially as a set, whereby both conditions realized cost can be.
  • the first planet carrier part 22 further forms a joint housing of a constant velocity joint, not shown, of a side shaft of the final drive.
  • the first planet carrier member 22 and the joint housing are integral and thus formed as a common component.
  • the side shaft of the final drive, not shown, connects via the unidirectional joint, not shown, the planetary carrier 12 drivingly with one of the drivable motor vehicle wheels of the axis, wherein the joint housing of the
  • Constant velocity joint is formed integrally with the first planet carrier member 22.
  • the final drive has a further, not shown, side shaft, which connects the sun gear 19 in terms of drive technology with the other drivable motor vehicle wheel of the axle via a further, not shown constant velocity joint.
  • the final drive on a connecting shaft 32, which drives the sun gear 19 to the
  • the sun gear 19 is rotatably mounted on the connecting shaft 32.
  • Joint housing is in vehicles with a front-transverse gear on one side, on a side facing away from an engine of the motor vehicle side, and in rear-wheel drive vehicles with longitudinal drive train even on both sides possible.

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

Abstract

La présente invention concerne un différentiel planétaire comportant une couronne (11), un porte-satellites (12) et au moins un palier de couronne (13, 14) qui sert de palier à la couronne (11). Le palier de couronne (13, 14) permet le montage de la couronne (11) sur le porte-satellites (12). La présente invention concerne également un groupe motopropulseur de véhicule à moteur pourvu d'au moins un tel différentiel planétaire (10).
PCT/EP2013/002890 2012-10-11 2013-09-26 Différentiel planétaire WO2014056577A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012019901.5A DE102012019901A1 (de) 2012-10-11 2012-10-11 Planetendifferential
DE102012019901.5 2012-10-11

Publications (1)

Publication Number Publication Date
WO2014056577A1 true WO2014056577A1 (fr) 2014-04-17

Family

ID=49326630

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/002890 WO2014056577A1 (fr) 2012-10-11 2013-09-26 Différentiel planétaire

Country Status (2)

Country Link
DE (1) DE102012019901A1 (fr)
WO (1) WO2014056577A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015002472A1 (de) 2015-02-27 2015-08-06 Daimler Ag Verfahren zum Verbinden von Bauteilen für ein Ausgleichsgetriebe eines Kraftwagens
CN106704540B (zh) * 2017-01-03 2023-07-04 特百佳动力科技股份有限公司 一种结合行星轮减速机构的二级差速器
DE102017119962A1 (de) * 2017-08-31 2019-02-28 Schaeffler Technologies AG & Co. KG Planetengetriebe mit einem Stützlager zur Lagerung mindestens eines Planetenbolzens
DE102021104641A1 (de) 2021-02-26 2022-09-01 Schaeffler Technologies AG & Co. KG Getriebevorrichtung mit einer über Wälzlager gelagerten Welle

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1619051A (en) * 1923-09-04 1927-03-01 Electro Motive Devices Inc Balanced rear-axle drive
US20030024753A1 (en) * 2001-08-02 2003-02-06 Taiji Maruyama Four-wheel drive system for vehicles
DE10140229A1 (de) * 2001-08-16 2003-03-06 Zahnradfabrik Friedrichshafen Differential
DE102005052850A1 (de) * 2005-11-05 2007-05-10 Daimlerchrysler Ag Überlagerungsvorrichtung für ein Lenksystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1619051A (en) * 1923-09-04 1927-03-01 Electro Motive Devices Inc Balanced rear-axle drive
US20030024753A1 (en) * 2001-08-02 2003-02-06 Taiji Maruyama Four-wheel drive system for vehicles
DE10140229A1 (de) * 2001-08-16 2003-03-06 Zahnradfabrik Friedrichshafen Differential
DE102005052850A1 (de) * 2005-11-05 2007-05-10 Daimlerchrysler Ag Überlagerungsvorrichtung für ein Lenksystem

Also Published As

Publication number Publication date
DE102012019901A1 (de) 2014-04-17

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