WO2008110425A2 - Différentiel à pignons droits et différentiel à superposition muni dudit différentiel à pignons droits - Google Patents

Différentiel à pignons droits et différentiel à superposition muni dudit différentiel à pignons droits Download PDF

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Publication number
WO2008110425A2
WO2008110425A2 PCT/EP2008/051847 EP2008051847W WO2008110425A2 WO 2008110425 A2 WO2008110425 A2 WO 2008110425A2 EP 2008051847 W EP2008051847 W EP 2008051847W WO 2008110425 A2 WO2008110425 A2 WO 2008110425A2
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WO
WIPO (PCT)
Prior art keywords
planet carrier
gears
planet
differential
planetary
Prior art date
Application number
PCT/EP2008/051847
Other languages
German (de)
English (en)
Other versions
WO2008110425A3 (fr
Inventor
Thorsten Biermann
Ramon Jurjanz
Norbert Metten
Original Assignee
Schaeffler 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 Kg filed Critical Schaeffler Kg
Publication of WO2008110425A2 publication Critical patent/WO2008110425A2/fr
Publication of WO2008110425A3 publication Critical patent/WO2008110425A3/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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • 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
    • 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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • 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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/204—Control of arrangements for suppressing differential actions
    • 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

Definitions

  • the invention relates to a spur gear differential with a planetary gear and a superposition differential with the spur gear differential having a first planet carrier as the sum shaft and the two differential shafts, wherein at least a first set of rotatable planetary gears and a second set of rotatable planetary gears are mounted on the first planet carrier and planet gears of the engage first planetary gears of the second set and planet gears of the first set are engaged with the first differential shaft and planet gears of the second set with the second differential shaft engaged and wherein the spur gear has at least one second planet carrier with at least a third set of rotatably mounted planet gears and while the planet carrier axially adjacent to each other on a common axis of rotation and are rotatable relative to each other about the axis of rotation and a superposition differential with the Stirnraddifferenzial ,
  • a spur gear differential and a superposition differential with the spur gear differential of the generic type is described at the time when the invention described below is described in the German patent application DE 102006007351.7, not yet published by the Applicant.
  • the first planet carrier of the spur gear differential is the so-called sum shaft of the differential.
  • the sum wave is the link that carries the largest torques.
  • the output shafts are rotatably coupled to the output wheels and are the so-called difference shafts.
  • the differential waves each pass on a difference amount of the torques introduced into the differential, for example to the driven vehicle wheel.
  • the planet carrier made of sheet metal in the region of the respective Planetenradproung is alternately passed through in the longitudinal direction and broken in the radial direction of the planet gears, so that the planetary gears of a pairing approximately along the center of the differential mesh with each other.
  • a criterion for assessing the functional accuracy of a planetary gear is the accuracy of the meshing engagement of the meshing planet-sun and planet-ring gear pairing.
  • the accuracy of the meshing in turn is dependent on the usual manufacturing tolerances of displacements and deformations that occur during operation of the spur gear differential.
  • Planetary bolts which are received centrally only once and generally also laterally are susceptible to deflection, especially in the case of highly loaded differentials, and, as a result, the planet gears seated on the bolt are susceptible to tilting. The consequences can be improper noise, inaccurate meshing and premature wear be. For this reason, differentials of the generic state of the art are preferably used in vehicles in which relatively low torques must be transmitted.
  • the advantage of the spur gear differential of the prior art lies in its lightweight construction of sheet metal.
  • the lightweight construction with sheet metal is particularly useful, as described in the technical essay, for the planet carrier.
  • the settings of the bearing points and openings for the meshing can be easily by pulling or stamping and punching bring into the sheet.
  • the disadvantage may affect the thin sheet on the initially mentioned deformation behavior of the planet carrier, especially because the planet pins are added only once to the carrier and because the plate of the planet carrier is additionally weakened by the breakthroughs.
  • the use of thicker sheet to compensate for the susceptibility to deformation would at least partially offset the advantages of the lightweight differential in such a case.
  • the superposition differential has the spur gear differential with the first planet carrier of a first and second planetary gear set and with the differential waves and also at least one second planet carrier with at least a third set of rotatable planet gears mounted on the second planet carrier.
  • the second planetary carrier like the first planetary carrier, revolves around the axis of rotation of the planetary drive.
  • the planet gears of the third set are so permanently or temporarily engaged via ring gears with the first planet carrier, that between the first planet carrier and the second planet carrier via the third set of planetary torques are transferable.
  • the planetary gears of the third set and one of the differential shafts are temporarily or permanently engaged, so that torques can also be transmitted between the second planet carrier and the respective differential shaft.
  • the switchable temporary engagement is secured, for example, by a speed control member, for example in the form of a clutch, which dwells on the respective planet carrier.
  • the second planet carrier is independent of the differential shaft, with which the third planetary gear set is coupled or coupled rotatably mounted.
  • the planet carrier is arranged at any point around the axis of rotation circumferentially, for example, next to the corresponding differential shaft or on a portion of the differential shaft.
  • the first planet carrier is switchable, for example temporarily coupled via a clutch with the first planet carrier.
  • the circulating second planet carrier can be driven, braked or fixed relative to one of the differential shafts in the differential or to the environment of the differential by targeted external action of speed actuators.
  • the second planetary carrier is for example by belt or multi-plate clutches or in any other suitable manner braked and / or detectable or driven by power branching of the upstream drive or by a separate electric motor, internal combustion engine, hydraulic drive or other drives.
  • the object of the invention is to provide a spur gear differential and a superimposition differential which is particularly compact, whose components can be easily manufactured and which can be easily mounted.
  • the invention provides that the planetary gears of the third set are in mesh with the planetary gears of a further one of the sets of the spur gear differential with one and the same on one of the sun gears formed external teeth.
  • the further of the sets is preferably the set of the spur gear differential which is axially closest to the respective superposition set.
  • a superposition differential with two of the second (overlay) planet carrier of a third set of planetary gears are common and the first set planetary gears with one and the same teeth of the first sun gear in meshing engagement and the other third set planetary gears and the planetary gears of the second set are included and toothed the same toothing of the second sun gear.
  • Each of the third sets is also each toothed with a ring gear, wherein each of the ring gears rotatably coupled to the first planet carrier.
  • the invention provides that the first planet carrier is radially supported by means of the first set on the toothing on the first sun gear and by means of the second set on the toothing on the second sun gear and centered to the axis of rotation.
  • the planet carrier is therefore not stored by means of bearings but supported to the axis of rotation on the sun gears.
  • the sun gears in turn are mounted radially and axially rotatable about the axis of rotation on the second planet carriers.
  • the respective second planet carrier is then mounted rotatably about the axis of rotation in a stationary housing to the axis of rotation.
  • the second planet carrier are each coupled by means of at least one speed actuator with the surrounding construction and disengageable coupled.
  • the second planet carrier are each coupled by means of at least one speed actuator with one of the sun gears and disengageable.
  • the second planetary carrier are coupled by means of at least one speed control member with the first planet carrier and disengageable coupled.
  • a rotational speed difference is imposed on the rear wheels or on different axles via electronically or hydraulically operated superposition stages in the superposition differential. This also results in asymmetric torque distributions and driving forces.
  • the torque vectoring unit described above requires less installation space than those of the prior art and can therefore also be used in front-wheel drive vehicles.
  • the output can be made directly via articulated shaft joints integrated into the sun gears.
  • the second planet carrier is formed from at least two supporting sheet metal components.
  • the sheet metal components are preferably cold components produced by drawing, stamping and / or stamping.
  • the first sheet metal component and the second sheet metal component are fastened to each other and may differ in shape and shape from one another or be identical parts. Between the components is axially, circumferentially and radially space for the planet gears of the third set.
  • the circumferentially spaced apart about the axis of rotation planetary gears of the third set are mounted axially to one side on the first sheet metal component and axially opposite to the second sheet metal component.
  • the planetary gears either axially on both sides pin, with which they are rotatably mounted to one axial side in the one sheet metal component and the other side in the other sheet metal component.
  • the planet gears are rotatably mounted on planet pins and the bolts are preferably held against rotation with the two axial ends in the component.
  • bearings for pins or bolts sliding bearings or rolling bearings are provided.
  • the two-sided bearing of the planetary gears reduces the risk of displacement and deformation. The meshing is more precise.
  • the overlay differential preferably has two of the second (Überlag- rungs-) planet carrier, each with a third set of planetary gears, between which the planetary drive of the spur gear is axially arranged with the first planet carrier.
  • the teeth of the meshing planetary gears and differential shafts are spur gears in all conceivable embodiments.
  • the third set of planet gears is meshed with the first differential link and the other third set on the other second planet carrier is meshed with the second differential link.
  • the differential links in this case are the sun gears.
  • the second planet carrier, as well as the first planet carrier, a structural unit at least from the sheet metal components and from the planetary gears.
  • This unit is a pre-assembly, in which the planetary gears are taken captive.
  • the installation of the overlay differential is simplified, since instead of individual parts, the respective planetary gear sets with the housing-like planetary carrier formed units are easily assembled with each other and also interchangeable with others.
  • the second sheet metal component is formed either disc-shaped or cup-shaped. It is also envisaged that both sheet metal parts are identical parts.
  • the first sheet metal component has either radial and / or axial indentations. Plane flange sections, on which the first sheet-metal component is axially connected to the second sheet-metal component, are preferably formed on the end faces axially on the indentations.
  • the indentations are at least partially passed through in the circumferential direction between the planetary gears to the second sheet metal component, so that there is a meandering shape in the course of the sheet.
  • the resulting chambers are peripherally limited in part by the axially continuous sheet metal of the first sheet metal component.
  • the respective chamber is closed by the first and axially in the other direction by the second sheet metal component.
  • the chambers are preferably not limited, so that the respective received in the chamber planet gear of the third set protrudes radially at least in one direction from the sheet metal components.
  • One of the sheet-metal sections preferably the second sheet-metal section, is mounted so as to be rotatable about the rotational axis radially and axially on the surrounding structure of the spur wheel differential.
  • the surrounding structure is a housing or the like, in contrast, rotate the rotatable components and assemblies of Stirnraddifferenzials and also the overlay differential about the axis of rotation (rotation axis of the planetary drive).
  • FIG. 1 schematically shows the operating principle of an overlay differential
  • FIG. 2 schematically shows the operating principle of another overlay differential
  • FIG. 3 schematically shows the operating principle of another overlay differential
  • Figure 4 shows an embodiment of a heterodyne differential in
  • FIG. 5 shows the overall view of a spur gear differential from the overlay differential according to FIG. 4, FIG.
  • Figure 6 shows the embodiment of the overlay differential in another longitudinal section, without couplings
  • Figure 7 is an overall view of the overlay differential of Figure 4, without couplings 8 is an overall view of an assembly of planet carrier and
  • FIGS. 1 to 3 schematically show the active principles of possible overlapping differences 1, 2, 3.
  • Each of the overlap differentials is formed from a simple spur gear differential 4 and from two superposition stages in the form of the subassembly 5 as well as couplings designated in each case by two speed actuators in this case with K1 to K6.
  • the assembly 5 is formed from the two-part second planetary carrier 6 with a third set of planet gears 7.
  • the spur gear differential 4 has the (first) planet carrier 8 as a sum shaft 9 and two differential shafts 10 and 11.
  • the planet carrier 8 is power input and has as input element for a spur toothing.
  • the differential shafts 10 and 11 are the output shafts and, in this case, sun gears 19 and 20, which are each connected to a non-illustrated propeller shaft for driving front wheels of a motor vehicle.
  • the spur gear differential 4 is provided for driving rear wheels or for distributing power flows on front and rear axles.
  • a first set of planetary gears 12 and a second set of planetary gears 13 are rotatably mounted on rolling or sliding bearings. As symbolized by the dashed line in FIGS. 1 to 3, one of the planetary gears 12 of the first set meshes with another of the planetary gears 13 of the second set. The planet gears 12 and 13 are engaged with sun gears 19 and 20.
  • the planet carrier 6 and 8 rotate while driving about the same axis of rotation 14 of the respective overlay differential 1, 2 or 3 with differential speeds or at the same speed, are therefore independent of one another common axis of rotation 14 rotatably mounted.
  • Each of the planet carrier 6 of the superimposition stage is independent of the other Plane- tenwhere of the opposite superposition stage speed controlled by means of a speed actuator K1, K2, K3, K4, K5 or K6 simultaneously or with a time delay.
  • the respective speed control element K1 or K2 according to FIG. 1 can be a clutch, a brake or a drive with which each planet carrier is brakable, lockable or drivable relative to one of the differential shafts rotatable about the rotation axis.
  • the speed control members K3 to K6 are preferably clutches.
  • Overlay differential 1 according to FIG. 1 is the second planetary carrier 6 by means of the speed control element K1 or K2 with the surrounding construction (not shown),
  • the second planetary carrier 6 is in each case connected to one of the differential shafts 9 and 10 by means of the speed control element K3 or K4,
  • FIG. 4 shows an exemplary embodiment of an overlay differential 54 according to the invention, which has substantially the same structure as the overlay differentials 1, 2 and 3, without rotational speed actuators in longitudinal section axially along the longitudinal axis, the longitudinal axis being identical to the axis of rotation 14.
  • FIG. 5 shows the spur gear differential 4 of the relevant overlay differential 1, 2 or 3 in an overall view and
  • FIG. 6 shows a further longitudinal section along the axis of rotation 14. The frontal overall view of the overlay differential 1, 2 or 3 without speed actuators is shown in FIG.
  • the Stirnraddifferenzial 4 has a drive wheel 17, which is an annular spur gear. Furthermore, the spur gear differential 4 is combined in a two-part housing which forms the first planet carrier 8. The housing is the sum shaft 9. In the housing four pairs of planet gears 12 and 13 are added. Each of the planetary gears 12 of a pair is associated with the first set and each of the planetary gears 13 of the same pair with the second set.
  • the two-part housing of the first planetary carrier 8 is formed from two pot-shaped housing sections 21 and 22.
  • the housing sections 21 and 22 are cup-shaped and cold-formed parts, for. As drawing and stamping parts, made of sheet metal and almost identical to each other.
  • the receptacles 18 for the planet pins 23 (FIG. 6). Of the receptacles 18 are only visible in the housing section 21 in Figure 5.
  • Both housing sections 21 and 22 are each provided with a radial flange 24 or 25 (FIG. 4).
  • the pot of the respective housing section 21 and 22 is formed on the circumference at several points inwardly in the direction of the axis of rotation 14, so that in each case between two peripherally adjacent pairs of planetary gears 12 and 13 radial indentations 26 are formed on the pot (Fig. 5).
  • the Shape of the pot reminds in the view of Figure 5 to a four-leaf clover.
  • the radial flange 24 and 25 extends in the direction of the axis of rotation 14 into the indentations 26 and there has the through holes 29 and 30 for the attachment of the housing sections 21, 22 to each other and for the attachment of the drive wheel 17 to the planet carrier 8 (Fig. 4).
  • Fasteners such as screws 31 are at least partially circumferentially disposed between two adjacent pairs of planetary gears 12 and 13.
  • cylindrical guide pins 32 with the through-holes 30 are arranged on the radial flange 25 of the housing section 22 on the circumference.
  • the preferably hollow cylindrical guide pins 32 project axially out of the flange in the direction of the other housing section.
  • the guide pin 32 is formed integrally with the radial flange 25 of its material.
  • Each of the guide pins 32 protrudes through a through hole 29 of the opposite radial flange 24 and into a guide hole 34 on the drive wheel 17.
  • the guide pin 32 is followed by a through hole 33 in the drive wheel 17 for a rivet connection or a through hole 33 with internal thread 35 in the drive wheel 17 for a screw connection, for example with screws 31.
  • the circular inner contour of the guide hole 34 viewed in cross-section corresponds exactly to the outer contour of the guide pin 32.
  • Drive wheel 17 and housing sections 21 and 22 are centered on the guide pins 32 concentric to one another with respect to the axis of rotation 14.
  • the drive wheel 17 is provided with a spur toothing 36.
  • a ring gear 15 and 16 is axially fixed.
  • the ring gear is cup-shaped.
  • the radially outer edge of the cup is a radial flange 37, with which the respective ring gear 15 and 16 is fixed to the drive wheel 17 and thus to the first planetary carrier 8.
  • the bottom 38 of the cup-shaped ring gears 15 and 16 is perforated and has an internal toothing 39 at the edges of the hole.
  • FIG. 8 An overlay stage on the example of the assembly 5 is shown in Figure 8 in an overall view.
  • the assembly 5 is formed from the two-part second planetary carrier 6 and the third set planetary gears 7.
  • the planet carrier 6 is formed in two parts from the first sheet metal component 40 and the second sheet metal component 41.
  • the first sheet-metal component 40 is inserted radially between the circumferentially mutually adjacent planetary gears 7 and in the direction of the second sheet-metal component 41 such that two sheet-metal portions 42 are opposite one another at each circumferential gap between two adjacent planetary gears.
  • the sheet-metal sections 42 merge in the axial direction on the second sheet-metal component 41 into a flange section 43 which is perpendicular to the axis of rotation and rests flat axially against the second sheet-metal component and is provided with a through-hole 45 for riveting, for example, with rivets 46 (FIG. 4).
  • the sheet-metal sections 42 merge into a peripheral section 44 curved circumferentially about the axis of rotation.
  • Each of the planet wheels 7 is accommodated in a chamber which is delimited in both circumferential directions by the sheet metal sections 42 and axially to one side by the sheet metal component 40 and in the other axial direction by the sheet metal component 41.
  • the bolts 47 on which the planetary gears are seated or the pins 48 on the planetary gears are mounted on the second sheet metal component 41 in an axial side in the first sheet metal component 40 and toward the opposite side.
  • Each second sheet-metal component 41 has a hollow-cylindrical section 55 rectified with the axis of rotation 14.
  • a roller bearing 56 which in this case is an angular contact ball bearing and with which the respective second planetary carrier 6 rotates about the axis of rotation 14 for non-tilting.
  • the hollow-cylindrical section 55 is designed on the inside as a plain bearing.
  • one or more sliding and / or rolling bearings are / are included in section 55.
  • the respective one of the sun gears 19 and 20 (differential shafts 9 and 10) is supported radially in the respective second planet carrier 6 but rotatable relative to the second planet carrier 6 about the rotation axis 14.
  • the sun gear 19 is on the outer peripheral side with a toothing 57 and the sun gear 20 is lubmonys press provided with a toothing 49.
  • the toothing 57 extends axially into both the Stirnraddifferenzial 4 and axially into one of the second planet carrier 6 inside.
  • the teeth 57 penetrates both axially the housing portion 21 of the first planet carrier and the first sheet metal component 40 of a second planetary carrier 6, which is the housing portion 21 closest.
  • the toothing 49 passes through both axially the housing portion 22 of the first planet carrier and the first sheet metal component 40 of a second planetary carrier 6, which is closest to the housing portion 22.
  • the planet gears 12 of the first set and the planetary gears 7 of the third set of one of the second planet carriers 6 are each in engagement with a part of the same toothing 57.
  • the planet gears 13 of the second set and the planet gears 7 of the other third set are in each case with a part of the same teeth 49 in engagement.
  • Overlap differential 54 different from the overlay differentials 1, 2 and 3 with respect to meshing.
  • the spur gear differential 4 is supported radially on the sun gear 19 via the planetary gears 12 and radially on the planetary gears 13 on the sun gear 20, and is centered on the rotation axis 14 at least during operation of the differential 4.
  • Axial is the Stirnraddifferenzial 4 with ring gears 15 and 16 in both directions in each case via an axial roller bearing 50 to the respective second planet carrier. 6 supported.
  • the sun gears 19 and 20 are each axially opposite to each other by means of sliding or rolling bearings 51 on the respective second planetary carrier 6 and axially together possibly with a further thrust bearing 52, such as sliding or rolling bearings, supported.
  • the sun gears 19 and 20 simultaneously have elements of output shafts (differential links).
  • the respective sun gear 19 and 20 at the same time the housing (joint bell) of a constant velocity joint, not shown.
  • the elements are the raceways 53 for rolling elements of a compensating element.

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  • General Engineering & Computer Science (AREA)
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Abstract

L'invention concerne un différentiel à pignons droits (4) muni d'un train planétaire qui présente un premier porte-satellites (8) faisant office d'arbre cumulant la somme des couples (9) et deux roues planétaires (19, 20) faisant office d'arbres différentiels (10, 11). Au moins un premier jeu de pignons planétaires (12) rotatifs et un second jeu de pignons planétaires (13) rotatifs sont prévus sur un premier porte-satellites (8). A cet effet, des pignons planétaires (12) du premier jeu s'engrènent dans des pignons planétaires (13) du second jeu et simultanément, des pignons planétaires (12) du premier jeu s'engrènent dans une première roue planétaire (19) et des pignons planétaires (13) du second jeu s'engrènent dans une seconde roue planétaire. Le différentiel à pignons droits (4) présente au moins un deuxième porte-satellites (6) muni d'au moins un troisième jeu de pignons planétaires (7) montés rotatifs. A cet effet, les pignons planétaires (6, 8) sont montés de manière adjacente dans le sens axial sur un axe de rotation (14) commun et peuvent tourner les uns par rapport aux autres autour dudit axe de rotation (14).
PCT/EP2008/051847 2007-03-13 2008-02-15 Différentiel à pignons droits et différentiel à superposition muni dudit différentiel à pignons droits WO2008110425A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007011894.7A DE102007011894B4 (de) 2007-03-13 2007-03-13 Stirnraddifferenzial und Überlagerungsdifferenzial mit dem Stirnraddifferenzial
DE102007011894.7 2007-03-13

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Publication Number Publication Date
WO2008110425A2 true WO2008110425A2 (fr) 2008-09-18
WO2008110425A3 WO2008110425A3 (fr) 2008-11-20

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WO (1) WO2008110425A2 (fr)

Cited By (6)

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Publication number Priority date Publication date Assignee Title
CN103851132A (zh) * 2012-12-05 2014-06-11 舍弗勒技术股份两合公司 行星齿轮传动装置
DE102013222832A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Stützanordnung für ein Leichtbauplanetendifferential mit versteifender hohler Stützstruktur
DE102013222831A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies AG & Co. KG Stützanordnung für ein Leichtbauplanetendifferential
DE102013222833A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Stützlageranordnung für ein Planetendifferential
CN109563917A (zh) * 2016-07-29 2019-04-02 舍弗勒技术股份两合公司 行星差速装置以及制造该行星差速装置的方法
CN109891130A (zh) * 2017-10-31 2019-06-14 罗灿 非锥齿轮差速器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008049971A1 (de) * 2008-10-01 2010-04-08 Schaeffler Kg Differentialgetriebeeinheit
DE102011085121A1 (de) * 2011-10-24 2013-04-25 Schaeffler Technologies AG & Co. KG Differential, insbesondere Stirnraddifferential

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DE102013222833A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Stützlageranordnung für ein Planetendifferential
WO2015067260A1 (fr) 2013-11-11 2015-05-14 Schaeffler Technologies AG & Co. KG Structure de support pour différentiel à train planétaire de construction légère
WO2015067261A2 (fr) 2013-11-11 2015-05-14 Schaeffler Technologies AG & Co. KG Structure de palier de support pour un différentiel épicycloïdal
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