EP2115325A2 - Différentiel à répartition du couple pour un véhicule automobile - Google Patents

Différentiel à répartition du couple pour un véhicule automobile

Info

Publication number
EP2115325A2
EP2115325A2 EP08708419A EP08708419A EP2115325A2 EP 2115325 A2 EP2115325 A2 EP 2115325A2 EP 08708419 A EP08708419 A EP 08708419A EP 08708419 A EP08708419 A EP 08708419A EP 2115325 A2 EP2115325 A2 EP 2115325A2
Authority
EP
European Patent Office
Prior art keywords
differential
gears
differential gears
ausgleichsradträger
side differential
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08708419A
Other languages
German (de)
English (en)
Inventor
Andreas Hohle
Achim Boos
Christoph Chatenay
Josef Fuhs
Kai-Uwe Ustorf
Michael Nagel
Ulrich Kuckertz
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.)
Tedrive Holding BV
Original Assignee
Tedrive Holding BV
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 Tedrive Holding BV filed Critical Tedrive Holding BV
Publication of EP2115325A2 publication Critical patent/EP2115325A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • 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
    • F16H2048/02—Transfer gears for influencing drive between outputs
    • F16H2048/04—Transfer gears for influencing drive between outputs having unequal torque transfer between two outputs
    • 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
    • F16H2048/102—Differential gearings with gears having orbital motion with orbital spur gears with spur gears engaging face 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
    • 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
    • F16H2055/173—Crown gears, i.e. gears have axially arranged teeth
    • 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
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/125—Adjustment of backlash during mounting or assembly of gearing

Definitions

  • the present invention is a differential with torque distribution for a motor vehicle, for which the use of a rotating housing, in which the side differential gears and the differential gears are arranged, is not required.
  • Such caseless differentials have a lower weight and a smaller installation space and are generally less expensive to produce than housings with differentials.
  • the dynamics of the motor vehicle, in which a caseless differential is used, is positively influenced, since lower masses must be rotated or sprung.
  • Object of the present invention is therefore to provide a Drehmoment damagesdes the differential, which is particularly suitable for use as a center differential for a motor vehicle and which has a high torque carrying capacity, a reduced weight and a reduced space requirement.
  • a differential with the features of the main claim.
  • Such a torque part of the differential in this case has two coaxially oriented, axially spaced-apart side differential gears, each side differential wheel being mounted independently rotatable about a common axis of rotation D. Furthermore, at least two differential gears are provided, each differential gear is in engagement with both side differential gears.
  • further embodiments with three, four or more differential gears are possible and technically useful under certain conditions, especially when an increased torque capacity of the torque-dividing differential according to the invention is desired.
  • a Ausretesradffy is arranged on which in turn the differential gears are rotatably mounted.
  • the Ausretesradffy itself is rotatably mounted about the axis of rotation D.
  • the side differential gears are now designed as crown wheels whose toothing has different outer diameters from each other.
  • the front-toothed differential gears however, have substantially identical outer diameter.
  • the construction according to the invention of a torque-dividing differential makes it possible completely to dispense with a separately designed rotating differential case when needed, as is widely used in the previously known from the prior art torque dividing differentials.
  • the weight and space of the torque dividing differential according to the invention over the prior art constructions can be significantly reduced without adversely affecting the torque capacity of the differential.
  • the side differential gears and the Ausretesradisme at least one stub shaft and a recess, wherein the recess is complementary to the shape of the stub shaft and is provided for receiving it.
  • the available alternatives training a stub shaft on a 9.endifferentialrad or on Ausreteradrad basically technically equivalent.
  • one or the other embodiment may offer advantages.
  • two stub shafts are formed, so that the Ausretesradisme is supported on both side differential gears via a respective stub shaft, which engages in each case in a, but not necessarily separately formed, recess on the side differential gears.
  • the radial bearing is advantageously arranged in the region in which engages a stub shaft in the recess. If two stub shafts are provided, advantageously two radial bearings are provided, one of which is assigned to one of the stub shafts.
  • At least one thrust bearing is additionally provided for the axial support of the Aus GmbHsradismes on the side differential gears, wherein each of these thrust bearing is preferably also disposed in that region in which a stub shaft engages in the associated complementary training.
  • the thrust bearing can be dimensioned and arranged so that it directly surrounds the shaft end struck by it.
  • the at least one stub shaft is formed integrally with a side differential wheel.
  • Both secondary differential gears preferably form shaft stumps and are formed integrally therewith.
  • the side differential gears hollow so that an output shaft rotatably connected to a 9.differentialrad can engage through the associated side differential, so that the output shaft on the side of the differential gear side, which faces the Ausretesradvic, forms a stub shaft.
  • the stub shafts are formed on the side differential gears, then the complementary associated recesses are formed on the balance wheel carrier. In particular, it is possible here to form a uniform, extending through the entire Ausretesradyes extending central recess instead of two separately formed recesses.
  • the at least one stub shaft is formed by Ausretesradffy
  • this can be formed by a shaft which is rotatably connected to the Ausretesradffy.
  • two are preferred here Shaft stumps formed, which are arranged on both sides of the Ausretesradyess.
  • the rotatable test is connected to the Ausretesradffy
  • the at least one stub shaft may preferably be the two stub shafts, also integrally formed with the Ausretesradffy.
  • the Austiciansradvic based on at least one thrust bearing on at least one Sodifferentialrad from which has a much larger diameter, so that it can be arranged in the region of the largest outer diameter of the associated side differential between this and the Au GmbHsradvic. It is also particularly preferred here to provide two identically dimensioned thrust bearings of the aforementioned type. The use of large diameter thrust bearings makes it possible to reduce overall bearing dimensions without adversely affecting the axial load bearing capacity of the differential carrier.
  • bearings which, in addition to a load capacity in the axial direction, also have a load capacity in the radial direction, it is possible to completely dispense with separately designed radial bearings for the rotary mounting of the differential carrier on the side differential gears.
  • Said construction is based on side differential gears, which are hollow, and on a Ausreteradradly having a central recess so as to form in the axial direction through both the side differential and the Ausreteradradyes extending central bore.
  • a clamping axis is used, which passes through both the central recess of the Ausretesradyess and through the hollow side differential gears.
  • the clamping axis forms at its two ends supports, which are provided for receiving the axially acting dividing forces between the side differential gears and the differential gears. By varying the distance between these supports, the force can be adjusted, which is introduced via the clamping axis in the differential according to the invention.
  • FIG. 1 shows a section through a first embodiment of a torque dividing differential according to the invention
  • FIG. 3 shows a section through a third embodiment of a torque dividing differential according to the invention
  • 4 shows a section through a second embodiment of a torque dividing differential according to the invention
  • FIG. 5 shows a section through a first development of the differential according to FIG. 1 and FIG
  • FIG. 6 shows a section through a second development of the differential according to FIG. 1.
  • the side differential gears 10, 10' are formed as crown wheels, wherein the outer diameter of the teeth 1 1 of the crown wheels 10, 10 'is different. About the ratio of the outer diameter / the diameter of the teeth of the crown wheels can be achieved with the differential 1 invention achievable torque split between the at the side differential gears 10, 10 'connected (not shown) output shafts.
  • the side differential gears 10, 1 0 ' engage in a plurality of differential gears 20, which are each mounted rotatably on a differential pin 22 on the Ausretesradvic 30.
  • the differential gears 30 have an end toothing, in which engages the toothing of the first and the second side differential 10, 1 0 '.
  • at least two differential gears 20 are provided, which are arranged distributed in equalizing wheel windows 37 of the Ausretesradsange 30 over the circumference of the Ausretesradyess 30.
  • Differentialchanbohronne 33 are provided in the Ausretesradyes, which extend substantially in the radial direction.
  • the differential pins 22 extend transversely through the Ausretesradrome 37 and engage in Differential dampingn 35, which are formed in the central region of the Ausretesradslic 30. Furthermore, the Ausretesradslic 30 forms in its central region on the right side and left side stub shafts 32. These stub shafts 32 engage in complementary cylindrical recesses 12 which are formed in the first and second side differential gears 10, 10 '. An inserted into a cylindrical recess 12 stub shaft 32 forms a slide bearing designed as radial bearing 54 for the Ausretesradexcellent 30 on the respective side differential 10, 1 0 'from.
  • the slide bearing realized here can be used as a radial bearing 54 and rolling bearings are used, preferred here is the use of needle bearings, which may possibly be dispensed with the use of a bearing ring, so that only one bearing sleeve is used.
  • the peripheral surfaces of the shaft stumps 32 form the bearing surfaces for the needles of the roller bearings.
  • the Ausretesradvic 30 is supported via a respective thrust bearing 50 on the first and the second side differential 10, 10 'from. To adjust the bearing clearance between the Ausretesradisme 30 and the first and second side differential 10, 10 'is further inserted in each case one selected for the individual differential 1 spacer 52.
  • the differential side gears 10,10 ' are in a rigid differential housing, which is not shown in Figure 1, rotatably supported about its common axis of rotation D using bearings 40 which are formed in the embodiment shown as angular contact ball bearings, the forces in both the axial and in can accommodate radial direction.
  • bearings 40 which are formed in the embodiment shown as angular contact ball bearings, the forces in both the axial and in can accommodate radial direction.
  • FIG. 2 shows again schematically the relative arrangement of side differential gears 10, 10 ', differential gears 20 and the Ausretesradisme 30, which is shown here with a spur toothing for connection to a drive shaft.
  • FIG. 2 shows that the differential gears 20 are mounted rotatably on the compensating wheel carrier 30 about an axis of rotation oriented in the radial direction relative to the axis of rotation D.
  • the differential gears 20 are designed front-toothed.
  • In the differential gears 20 engage a first side differential 10 with a large outer diameter of the toothing and a second side differential 10 ', which has a smaller outer diameter of the toothing.
  • Both side differential gears 10,10 ' are rotatably mounted on the Ausretesradisme 30.
  • the ratio of the diameters of the toothings of the first and second side differential gears 10, 10 ' can be used to set the torque distribution between output shafts which can be achieved by means of the differential according to the invention, which are non-rotatably connected to the side differential gears 10, 10'.
  • FIG. 3 shows a second embodiment of a torque-dividing differential according to the invention, which essentially corresponds to the first embodiment according to FIG. 1.
  • the schematic representation according to FIG. 2 also applies to the second embodiment according to FIG. 3.
  • the stub shafts 32 are formed by the first and second side differential gears 10, 10 ', wherein the stub shafts 32 engage in a central bore 36, which is embodied in the center of the Ausretesradlys 30.
  • the area of the outer peripheral surfaces of the shaft stumps 32, which come into contact with the inner peripheral surfaces of the central bore 36 of the Aus GmbHsrad manners 30 form again designed as a plain bearing radial bearings for the pivotal mounting of the Ausretesradlys 30 about the axis of rotation D.
  • the Ausretesradffy 30 is supported in the illustrated embodiment via thrust bearings 50 on the side differential gears 10, 10 ', wherein the diameter of the thrust bearing 50 is dimensioned so that the thrust bearings 50 completely within the teeth 1 1 of the first and second side differential gears 10, 10 'is arranged.
  • needle bearings are used as thrust bearings, but it is also conceivable to use ball bearings designed as thrust bearings. If instead of the illustrated needle bearings for the bearing 50 angular contact bearings are used, in particular angular contact ball bearings or tapered roller bearings, so can be completely dispensed with the radial bearing 54 designed as a sliding bearing.
  • FIG. 4 shows a third embodiment of a torque-dividing differential 1 according to the invention.
  • two side differential gears 10, 10 ' whose toothing 11 has different outer diameters are rotatably mounted about a common axis of rotation D.
  • a rotary bearing of the side differential gears 10, 10 'ball bearings 40 are used, with which the side differential gears 10, 10' are rotatably mounted in a fixed differential housing, which is not shown.
  • the side differential gears 10, 10 'and the Ausretesradslic 30 no shaft stumps and no associated complementarily formed cylindrical recesses. Much more The support of the Ausretesradsange 30 completely on the pivot bearing of the Ausretesradslic 30 on the side differential gears 10, 10 '.
  • ball bearings 58 are provided in the illustrated embodiment, which have such a large diameter that they complete the teeth 1 1 of the side differential gears 10, 10' embrace.
  • the Austiciansradffy 30 also forms a bearing seat for receiving the outer ring of the angular bearing 58. Since the angular contact bearings 58, which may be formed, for example, as angular contact ball bearings or tapered roller bearings, have a high load capacity both in the axial and in the radial direction, in the illustrated second embodiment of the invention torque dividing differential 1 completely on the separately formed thrust bearing 50 and radial bearing 54 of first embodiment are omitted.
  • the well-known from the first embodiment support via a combination of stub shaft and complementarily formed cylindrical recess on the side differential gears 10,10 'and the Ausretesradmban 30 is not required in the third embodiment shown.
  • the outer inner peripheral surfaces of the hollow side differential gears 10, 10 ' are provided with internal teeth in the form of splines 80, which are provided for connecting output shafts.
  • FIG. 4 For the sake of simplicity, in contrast to FIG. 1, no ring-wheel flange 90 is shown in FIG. 4, which can serve, for example, for connecting a hypoid-toothed ring gear.
  • FIG. 5 now shows a first development of the first embodiment of a torque-dividing differential 1 according to the invention.
  • the essential difference from the embodiment shown in FIG. 1 is that in addition to the differential gears 20, additional spring washers 85 are inserted into the differential-gear windows 37, which likewise be penetrated by the differential pin 22.
  • the spring washers 24 serve to press the differential gears 20 against bearing surfaces 26 which are formed on the Ausretesradisme 30 in the Ausretesrad donorn 37. In this way, a play-free mounting of the differential gears 20 can be realized on the differential pin 22.
  • the spring disks 24 are formed as convex spring disks, which ensures a substantially independent of their deformation contact pressure of the differential gears 20 on the contact surfaces 26.
  • FIG. 6 shows a second development of the torque divider differential 1 shown in FIG. 1, in which a tensioning axle 70 is provided in order to be able to apply a defined pretensioning force to the differential 1.
  • a tensioning axle 70 is provided in order to be able to apply a defined pretensioning force to the differential 1.
  • both the first and the second side differential 10, 10 ' are hollow and each form an inner bearing surface 18, which is oriented away from the Ausretesradvic 30.
  • the Austiciansradvic 30 is provided with a continuous central bore 36, so that a total of a central bore 60 is formed, which passes through the entire differential 1.
  • a clamping axis 70 is now introduced with a first end 72 and a second end 74.
  • pivot bearing 76 On the first and second ends 72 and 74 are pivot bearing 76, which are designed as thrust bearings, plugged so that the clamping bearing 76 with its first bearing ring to bear against the inner contact surface 18 of the side differential gears 10, 10 'arrive. With the insertion of washers 77 locking nuts 78 are now screwed onto the first and the second end 72, 74 of the clamping axis 70, with which the clamping axes 70 can be clamped as a whole. In this case, the clamping bearings 76 form a pivot bearing of the first and second side differential gears 10, 10 '. By varying the tightening torque of the lock nuts 78, the preload force which is introduced into the differential 1 can now be varied.
  • the axial load which must be borne by the bearings 40, in which the side differential gears 10, 10 'are mounted in the fixed differential housing, can be significantly reduced, which can be used on a smaller sized bearing. It is also possible to trap the entire axial load via the tensioning axis 70, so that pure radial bearings can be used for the bearings 40.
  • the present invention is directed to the general concept of a caseless torque divider differential resulting from the independent claim.
  • the illustrated embodiments are to be considered as preferred embodiments, but the invention is not limited to these preferred embodiments.

Landscapes

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

Abstract

L'invention concerne un différentiel diviseur de couple (1) destiné à un véhicule automobile et comprenant deux planétaires de différentiel (10, 10') orientés coaxialement et placés à distance l'un de l'autre en sens axial, chaque planétaire (10, 10') étant monté rotatif autour d'un axe de rotation commun D. Le différentiel selon l'invention comprend également au moins deux satellites de différentiel (20) dont chacun est en prise avec les deux planétaires (10, 10'). Un porte-satellites (30) qui est placé entre les deux planétaires (10, 10') et sur lequel les satellites (20) sont montés rotatifs est monté de manière à pouvoir tourner autour de l'axe de rotation D. Les planétaires (10, 10') sont réalisés en tant que couronnes dont les dentures respectives ont des diamètres différents. En outre, les satellites (20) présentent une denture droite et le porte-satellites (30) s'appuie de manière rotative sur les planétaires (10, 10').
EP08708419A 2007-01-31 2008-01-30 Différentiel à répartition du couple pour un véhicule automobile Withdrawn EP2115325A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007005730A DE102007005730B4 (de) 2007-01-31 2007-01-31 Differential mit Drehmomentverteilung für ein Kraftfahrzeug
PCT/EP2008/051104 WO2008092886A2 (fr) 2007-01-31 2008-01-30 Différentiel à répartition du couple pour un véhicule automobile

Publications (1)

Publication Number Publication Date
EP2115325A2 true EP2115325A2 (fr) 2009-11-11

Family

ID=39253989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08708419A Withdrawn EP2115325A2 (fr) 2007-01-31 2008-01-30 Différentiel à répartition du couple pour un véhicule automobile

Country Status (4)

Country Link
US (1) US20100179014A1 (fr)
EP (1) EP2115325A2 (fr)
DE (1) DE102007005730B4 (fr)
WO (1) WO2008092886A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011026454A1 (fr) 2009-09-02 2011-03-10 Neumayer Tekfor Holding Gmbh Différentiel
DE102011007698A1 (de) * 2011-04-19 2012-10-25 Neapco Europe Gmbh Differenzial mit integrierter Lagerung der Kronenräder
US11054011B2 (en) 2016-03-15 2021-07-06 Gkn Automotive Limited Automotive differential and method of assembling same
DE102017004933A1 (de) * 2017-05-20 2018-11-22 Daimler Ag Differentialgetriebe für ein Kraftfahrzeug

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
US2408926A (en) * 1944-07-15 1946-10-08 Gen Motors Corp Drive axle
FR1198091A (fr) * 1957-12-27 1959-12-04 Schlepperwerk Nordhausen Veb Différentiel notamment pour véhicules automobiles et tracteurs
US3154969A (en) * 1963-04-30 1964-11-03 Illinois Tool Works Semi-locking differential
DE3926878A1 (de) * 1989-08-16 1990-03-08 Schmetz Roland Dipl Ing Dipl W Gehaeuseloses differentialgetriebe mit kegelraedern
US5472385A (en) * 1993-03-09 1995-12-05 Clark Equipment Company Differential
DE4441163A1 (de) * 1994-11-18 1995-10-05 Daimler Benz Ag Ausgleichsgetriebe in Kegelradbauweise für Kraftfahrzeuge
US6015362A (en) * 1997-05-06 2000-01-18 Kanzaki Kokyukoki Mfg. Co., Ltd. Differential gear assembly with disc-shaped input member
US5980416A (en) * 1997-08-06 1999-11-09 Sven B. Gafvert Differential for a vehicle
DE10353415B4 (de) * 2003-11-15 2006-01-19 Gkn Driveline International Gmbh Verteilergetriebe mit Kronenverzahnung
DE102004001019B4 (de) * 2004-01-02 2006-07-13 Gkn Driveline International Gmbh Differentialgetriebe mit Reibkorb für Giermoment
DE102005036362B4 (de) * 2005-07-29 2008-11-27 Tedrive Holding Bv Gehäuseloses Differential
JP2007147069A (ja) * 2005-10-26 2007-06-14 Ｇｋｎ ドライブライン トルクテクノロジー株式会社 デファレンシャル

Non-Patent Citations (1)

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Title
See references of WO2008092886A2 *

Also Published As

Publication number Publication date
US20100179014A1 (en) 2010-07-15
WO2008092886A2 (fr) 2008-08-07
WO2008092886A3 (fr) 2008-09-18
DE102007005730B4 (de) 2009-01-08
DE102007005730A1 (de) 2008-08-21

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