WO2014019744A1 - Différentiel à pignons droits - Google Patents

Différentiel à pignons droits Download PDF

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Publication number
WO2014019744A1
WO2014019744A1 PCT/EP2013/061471 EP2013061471W WO2014019744A1 WO 2014019744 A1 WO2014019744 A1 WO 2014019744A1 EP 2013061471 W EP2013061471 W EP 2013061471W WO 2014019744 A1 WO2014019744 A1 WO 2014019744A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary
gear
gears
spur gear
differential
Prior art date
Application number
PCT/EP2013/061471
Other languages
German (de)
English (en)
Inventor
Thorsten Biermann
Richard Grabenbauer
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 WO2014019744A1 publication Critical patent/WO2014019744A1/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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0826—Novikov-Wildhaber profile
    • 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 spur gear differential for splitting a drive torque to a first and to a second output spur gear, this spur gear differential having a planet carrier with a plurality of peripheral planetary gears revolving therewith, forming a first and a second planetary gear group.
  • the planetary planetary gears of the first planetary gear group mesh with the first output gear and the planetary gears of the second planetary gear group engage with the second output gear.
  • a spur gear of the aforementioned type is known.
  • the planetary planetary gears are configured to each have a spur gear portion and a spigot portion, the axial length of the spigot portion being shorter than the axial length of the spur gear portion.
  • the planetary planet wheels form two planetary gear sets.
  • the planetary gears of these two circulating planetary gear groups are assembled alternately such that between the planetary gears of each planetary gear group the journal sections of the planetary gears of the planetary gears whose circulating planetary gear group come to rest.
  • the engagement zones of the intermeshing planetary gears are located axially between the two output gears associated with the respective group.
  • the invention has for its object to provide a spur gear that is characterized by a compact design, high internal stiffness and advantageous mechanical performance.
  • a planetary carrier provided for circulation about a differential axis
  • a planetary planetary set comprising a plurality of planetary gears whose planetary axes are aligned parallel to the differential axis, the planetary gears forming a first planetary gear group and a second planetary gear group, and
  • the spur gear differential according to the invention is designed in such a way that it has five epicyclic gears per revolving planetary gear group.
  • the output spurs are preferably designed such that the number of teeth of the output spur gears is divisible by the number of planets per Umlaufplanetenrad distr. This makes it possible to uniformly arrange the respective planetary planetary gears of a group at the corresponding angle (here 72 °) around the output spur gears.
  • the two provided for the power tap seen output spurs have identical numbers of teeth.
  • the planetary planet gears also have the same number of teeth, but lower numbers of gears compared to the output spur gears.
  • the gear ratio i between Huaweistirnrad and planetary gear is preferably in the range of 2.5 ⁇ 20%.
  • the planets are designed with numbers of teeth that are only divisible by one and themselves (primes).
  • the numbers of teeth proposed here are for the output spurs 32 and for the planets 13.
  • the ratio of the total diameter of the enveloping circle of the planetary gears to the gearing width of the "long" planetary gears is preferably in the range of 3 ⁇ 20% advantageous ratio of the space requirement and the weight of the component to the carrying capacity of the differential gear.
  • the spur gear differential according to the invention with Wildhaber / Novikov gearing is particularly suitable as a differential for passenger cars.
  • the concept according to the invention is furthermore also suitable for differential gearboxes of commercial vehicles and other heavy duty applications, especially in towing vehicles.
  • the differential according to the invention with a closed by the planetary planets planetary ring can be assembled in an advantageous manner montagetechnisch from inexpensive to produce individual components and is particularly suitable for mass production.
  • the Stirnraddifferential is formed such that the planetary axes of the first Umlaufplanetenradxx are arranged on a first pitch circle and the planetary axes of the second Umlaufplanetenradxx are arranged on a second pitch circle, and the first pitch circle and the second pitch circle substantially the same Have diameter.
  • the output spurs are preferably designed to have equal numbers of teeth.
  • the planetary gears themselves are preferably designed so that they have mutually equal numbers of teeth.
  • the planetary gear wheels are designed as identical components, resulting in cost advantages in terms of the production of the planet gears and also simplifications in the installation of the same.
  • a profile shift is provided on the planetary planet wheels, this is preferably done such that the planetary planets of the first planetary planetary gear group have a positive profile shift and the planetary planets of the second planetary gear group have a negative profile shift.
  • the planet carrier is designed so that it directly carries a provided for initiating a drive torque drive gear.
  • This drive gear can be designed as a solid ring structure.
  • the drive gear is preferably designed such that it forms an inner opening, wherein this inner opening is contoured such that the circulating planets receive a head circle guide on the inner wall.
  • the drive torque applied to the drive gear is transmitted directly to the planetary gears via a plurality of tip contact zones as a lateral force. The structural mechanical load of the planet carrier is thus reduced.
  • the planet carrier is preferably designed as a sheet metal forming part.
  • the planet carrier can be composed of two disk, cup, or pot-like, deep-drawn, preferably identical sheet metal shells, which are attached from both sides to the drive gear or directly assembled.
  • the planet carrier can also be used as a circulation housing be designed which forms other attachment zones for a drive gear, or other zones for initiating a Antriebpitmonnentes.
  • the concept according to the invention makes it possible to provide a spur gear differential provided as an axle transmission, which is distinguished by an extremely short axial length and a relatively low tooth flank loading.
  • the planetary gear group which is composed of preferably four or five planetary gears and acts on the respective output spur wheel, enables a torque introduction into the output spur gear without the output spur wheel having to be supported with considerable radial bearing forces.
  • the teeth of the spur gear teeth of the first Ninstirnrades have in radial section a tooth flank profile which is concave.
  • the teeth of the spur gear toothing of the second output spur gear have a tooth flank profile convexly curved in radial section.
  • the teeth of the gears of the first output gear have concave edge geometries.
  • the concave edge geometries are either continuous, ideally circular arc, running or with uneven course of the flank line inwards into the respective tooth arched, so that between two opposing tooth flanks considered in the cross section of the toothed tooth gap in outline, for example in the form of circular arc profiles, alternatively gothic profiles or profiles with oval or parabolic course (Halbellipse viewed over long axis half) appears.
  • the flank profile of the teeth appears in the same cross-section in the outline corresponding circular arc, cup-shaped or bell-shaped. It is not excluded that the tooth heads and the gaps in the tooth root are flat or circular-arc-shaped, ie that the respective profile appears to be cut off at its tip, so to speak.
  • the engaging in the tooth gaps of the aforementioned first output spur gear teeth formed on the first planetary gears counter teeth have convex edge geometries.
  • the convex flank geometries are arched outwards either continuously or discontinuously so that the flank profile of the teeth in the cross-section of the gear is outlined, for example, in the form of arcuate profiles (classic form of the Novicov serration), alternatively gothic profiles or profiles with oval / parabolic course (half ellipse) appears.
  • the considered in the same cross-section tooth space between two of the opposing teeth then appears accordingly in outline accordingly arcuate, cup-shaped or bell-shaped. It is again not excluded that the tooth heads and the gaps in the tooth root are flat or circular arc-shaped, d. H. that the respective profile at its tip seems to be cut off.
  • Wildhaber-Novikov toothing designated toothing is characteristic that always a part of a concave tooth flank profile of the teeth of a gear is in engagement with each part of a convex tooth flank profile of the teeth of a tooth from the counter gear. Viewed in cross-section transverse to the axis of rotation of the gears by both located in meshing gears, which are in meshing abutting flank lines of the tooth flank profile of the flanks of concave and convex tooth therefore curved in the same direction, so that the flanks of the convexly curved teeth seemingly nestle into the flanks of the concave vaulted teeth. In such a combination results in favorable compression ratios between the teeth.
  • FIG. 1 is a perspective view of a spur gear differential according to the invention
  • Figure 2 is an axial sectional view of the spur gear according to FIG.
  • Figure 3 is a plan view of the planetary planetary gear rim of the differential gear according to Figures 1 and 2.
  • FIG. 1 shows a spur gear differential according to the invention.
  • This spur gear differential comprises a planetary carrier 3 provided for circulation about a differential axis X, a first output spur gear 1 (here concealed) which is arranged coaxially to the differential axis X, and a second Truststirnrad 2 which is also arranged coaxially to the differential axis X, and a planetary planetary gear set 4, which comprises a plurality of planetary planetary gears P1, P2 whose planetary axes XG1, XG2 are aligned parallel to the differential axis X.
  • the planetary planetary set 4 forms a wreath closed in itself by successive engagement zones EG and comprises a first planetary gear group G1 to which the planetary gears P1 are to be assigned and a second planetary gear group G2 to which the planetary planetary gears P2 belong.
  • the planetary planetary gears P1 of the first planetary gear group G1 engage with the first output helical gear 1.
  • the planetary planetary gears P2 of the second planetary gear group G2 are engaged with the second output planetary gear 2, which can be better seen here.
  • two planetary planetary gears P1, P1; P2, P2 of a planetary gear group G1; G2 via a in these two planetary gears P1, P1; P2, P2 engaging planetary gear P2, P1 corresponding to other planetary gear group G2; Coupled G1.
  • the present invention Stirnraddifferential is characterized in that the first Truststirnrad 1 is designed such that this forms a toothing whose tooth flanks are concavely curved in the radial section.
  • the second concertstirnrad 2 is designed such that it forms a toothing whose tooth flanks are convexly curved in the radial section, wherein also the top circle of the first Truststirnrades 1 is smaller than the root circle of the secondönstirnrades 2.
  • Those Umlaufplanetenmann P1, P2 of the two Umlaufplanetenrad tendency G1, G2 coupling planetary gear engagement zones EP extend at the axial level of the first langestirn- Radeingriffszonen EW1.
  • the planetary axes XG1 of the first planetary gear group G1 are arranged on a first pitch circle T1 and the planetary axes XG2 of the second planetary gear group G2 are arranged on a second pitch circle T2.
  • the first pitch circle T1 and the second pitch circle T2 have the same diameter.
  • the output spurs 1, 2 are designed in this embodiment, that they have the same number of teeth.
  • the first dormitorstirnrad 1 and the planetary gears P2 of the second group G2 form a concave toothing to Wildhaber / Novikov. That the second Twistirnrad 2 and the planetary gears P1 of the first group G1 form a Konvexverzahnung to Wildhaber / Novikov.
  • the planetary planetary gears P1, P2 themselves are here designed so that they have the same number of teeth.
  • the planet carrier 3 is designed so that it carries a directly provided for the initiation of a drive torque drive gear 5.
  • This drive gear 5 is designed here as a solid bevel gear ring structure.
  • the planet carrier 3 itself is designed here as a sheet metal forming part and is composed of two sheet metal shells 3 a, 3 b, which are attached from both sides to the annular body of the drive gear 5.
  • the storage of Umlaufplanetenate P1, P2 takes place here by bearing pin 6 in the planet carrier. 3 are anchored and extend through the planetary gears P1, P2 and rotatably support them.
  • the spur gear differential shown here is particularly suitable as an axle drive for a multi-track motor vehicle.
  • the spur gear differential is characterized by an extremely short axial length and a relatively low tooth flank load.
  • the toothings and the bearings can be designed so that they provide a sufficient clearance to avoid any internal tension due to static overdetermination.
  • the planet carrier 3 which is manufactured here as a double-shell sheet metal component forms a first and a second collar portion 3 c, 3d. These collar sections 3c, 3d form a bearing structure in which the two output spur gears 1, 2, more precisely their hub bushing sections 1a, 2a, are radially mounted. Since there results from the inventive design of the planetary gear on the two output wheels 1, 2 in a substantially balanced transverse force distribution, there is no significant load-dependent radial load this Bearing structures. Although not shown here, it is possible to seal the planetary gear carrier 3 and the hub bushing sections 1 a, 2 a and to fill the interior of the planet carrier with a lubricant, so that the differential gear forms a self-contained, permanently lubricated component.
  • the "longer" planetary gears P2 of the second group G2 are designed with respect to their axial length so that they axially overlap the concave flank teeth of the first driven gear 1 and the convex flank teeth of the second driven gear 2. Due to the design and arrangement of the planetary planet gears P2 and the first output spur gear The concave edge teeth of the planetary planetary gears P2 of the second group G2 do not engage with the concave side teeth of the first output spur gear 1.
  • the kinematic coupling between the output spur gear 1 and the planetary gears G2 of the second group G2 takes place with the interposition of the planetary gears P1 provided with a convex flank toothing
  • the axial length of the convex flank spur gear teeth of the planetary gears P1 of the first group G1 is substantially shorter than the axial length of the concave flank gear teeth of the planetary planetary gears or P2 of the second group G2.
  • the axial length of the convex flank spur gear toothing of the first planetary gear wheels P1 preferably corresponds substantially to the axial length of the concave flank spur gear toothing of the first output spur gear 1.
  • the planetary planet gears P1 of the first group G1 are formed and supported so that they can not interfere with the convex-side spur gear teeth of the second output spur gear 2. Possibly. can be used in the differential gear provided with openings or notches separating plate which shields the end faces of the planetary gears P1 of the first group G1 of the toothing of the secondönstirnrades 2.
  • the planetary gears P2 of the second group G2 are designed with respect to their axial length so that they overlap the spur gear of the first output gear 1 axially. Due to the design and arrangement of the planetary planetary gears P2 and the first output spur gear 1, the spur gearing of the planetary gears GP2 of the second group G2 does not engage with the spur gearing of the first output spur gear 1.
  • the kinematic coupling between the output spur gear 1 and the planetary gear wheels P2 of the second group G2 takes place with the interposition of the peripheral planet gears P1 of the first group G1 (see FIG.
  • the axial length of the spur gear teeth of the planetary gears P1 of the first group G1 is substantially shorter than the axial length of the spur gear of the planetary gears G2 of the second group G2.
  • the axial length of the spur gear toothing of the first planetary gear wheels G1 preferably corresponds essentially to the axial length of the spur gear toothing of the first output spur gear 1.
  • the axial securing of the bearing pin 6 takes place in this embodiment by cap elements 7 which are inserted from the inside into corresponding holes 8 of the planet carrier 3. These cap elements act as axial security and at the same time as start-up structure for the corresponding planet.
  • the cap elements also increase the bearing capacity of the bearing.
  • the cap elements are preferably made and hardened as drawing components. Through these cap elements and the wear is reduced. The use of the cap elements makes it possible to dispense with a hardness treatment of the wearer.
  • the drive gear 5 is formed as a hypoid-toothed bevel gear and axially attached and mounted on a formed by the two sheet metal shells 3a, 3b of the planet carrier 3 radial flange.
  • the screws 5a provided for this purpose also couple the two sheet metal shells 3a, 3b.
  • the output spurs 1, 2 are configured and arranged such that the spur gears thereof are in close proximity.
  • the tip diameter of these two output spurs 1, 2 are so different that the tip diameter of the first output spur gear 1 in approximately corresponds to the root diameter of the secondönstirnrades 2.
  • the toothing geometries of these two output spurs 1, 2 are coordinated so that each of the engaged with the secondönstirnrad 2 planetary gears P2 not in the Stirnrad- toothing of the first Pandastirnrades 1, but well on the axial level in the Stirnradveriereung the first planetary gears P1 can intervene.
  • FIG 3 the structure of the differential gear according to the invention is further illustrated.
  • the self-contained circulating planetary gear rim 4 composed of the planetary gear wheels P1, P2 contains an even total number of planetary planetary gears P1, P2.
  • the inventive concept is implemented here with a total of 10 planetary gears P1, P2.
  • Each circulating planetary gear group G1, G2 thus comprises 5 circulating planet wheels P1 or P2.
  • the clearance of the planetary gears P2 from the teeth of the first penetratestirnrades 1 is due to the peculiarity of the realized here Wildhaber / Novikov gearing under any additional low profile shift at least at the first Schwarzsstirnrad first
  • said inner opening may be designed so that the circulation planet P1, P2 at the inner opening wall a Received top guide. This makes it possible to initiate the drive torque applied to the drive gearwheel 5 directly via a plurality of tip contact zones into the planetary gearwheel ring 4.
  • the planetary planet wheels P1, P2 of the two groups G1, G2 rotate in opposite directions.
  • the ring gear 4 formed by the planetary gears P1, P2 is continuously closed in itself via the engagement zones EG, ie each planetary gear P1, P2 is connected to a preceding planet P2, P1 and a subsequent planet P2, P1 over a total of two engagement zones EG per wheel in intervention.
  • the planetary axes XG1 of the first planetary gear group G1 are arranged on a first pitch circle T1 and the planetary axles XG2 of the second planetary gear group are arranged on a second pitch circle, wherein the first pitch circle T1 and the second pitch circle T2 have the same diameter and also the pitch of the planetary axes XG1, XG2 on the ultimately common single pitch circle is uniform.
  • a driving torque abutting the drive gearwheel 5 is first transmitted to the planet carrier 3.
  • the planetary planetary gears P1, P2 form two groups G1, G2, wherein the planetary planetary gears P1 of the first group G1 engage with the first output helical gear 1 and the planetary planetary gears P2 of the second group G2 engage with the second output helical gear 2.
  • the planetary planet wheels P1, P2 engage with each other to form a self-contained gear rim 4 via the engagement zones EG.
  • the planetary planetary gears P1, P2 of the two groups G1, G2 are thus coupled in opposite directions.
  • the radial positions of the axes XG2, the tip diameter of the planetary gears G2 of the second group G2 and the tip diameter of the first output spur gear 1 are adjusted so that within the ring gear 4 exclusively the planetary orbital gears P1 of the first group G1 engage in the first output spur gear 1.
  • the planetary gears P1 of the first group 1 have a Stirnradverzahnungsabexcellent on the axial length substantially corresponds to the axial length of the spur gear teeth of the first Nathanstirnrades 1.
  • the "long" planetary gears G2 of the second group have a spur gear portion whose axial length is approximately twice the length of the spur gear portion of the first planetary gears G1 of the first group G1
  • the planetary gears P2 of the second group G2 thus extend axially over the spur gears of the two driven gears 1, 2 without interfering with the first submitstirnrad 1.
  • the two driven gears 1, 2 are opposed by the self-contained gear rim 4, i.
  • the entire toothing of the planetary gears P1 of the first group G1 acting on the first output spur gear 1 engages on the same axial level also in the teeth of the planetary planet gears G2 of the second group
  • the circumferential toothing of the first output spur wheel prevailing force relationships results in a particularly advantageous internal force compensation and thus a reduced load on the tooth flanks and the bearings of the Umlaufplane- tenmann P1, P2.
  • the design of the gears 1, 2, P1, P2 and the positions of the bearing axes XG1, XG2, for example, by first the first Truststirnrad is dimensioned so that this has a required for the interpretation relevant drive shaft torque strength.
  • the pitch circle diameter, the toothing module and the axial length of the spur gear toothing of the first output spur wheel 1 result.
  • the number of planetary gears of the gear rim is set which is usually either "8” or "10".
  • the Wildhaber / Novikov gearing of the planetary planets P1, P2 and the driven gears 1, 2 meshing therewith are designed as helical gearing.

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

Abstract

L'invention concerne un différentiel à pignons droits comportant une couronne de satellites tournante qui est refermée sur elle-même par l'intermédiaire de zones de prise successives et qui comprend plusieurs satellites tournants dont les axes sont orientés parallèlement à l'axe du différentiel. Selon l'invention, le premier pignon droit de sortie forme une denture dont les flancs de dent sont incurvés de manière concave en coupe radiale et le deuxième pignon droit de sortie forme une denture dont les flancs de dent sont incurvés de manière convexe dans une coupe radiale. En outre, le cercle de tête du première pignon droit de sortie est plus petit que le cercle de pied du deuxième pignon droit de sortie, et les zones d'engrènement entre les satellites tournants se trouvent au niveau axial du pignon droit de sortie entouré par la couronne de satellites tournante.
PCT/EP2013/061471 2012-07-31 2013-06-04 Différentiel à pignons droits WO2014019744A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012213398.4A DE102012213398A1 (de) 2012-07-31 2012-07-31 Stirnraddifferential
DE102012213398.4 2012-07-31

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Publication Number Publication Date
WO2014019744A1 true WO2014019744A1 (fr) 2014-02-06

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WO (1) WO2014019744A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105402354A (zh) * 2015-12-18 2016-03-16 天津天海同步科技有限公司 圆柱螺旋齿应力平衡式限滑差速器
WO2016055255A1 (fr) * 2014-10-10 2016-04-14 Engineering Center Steyr Gmbh & Co Kg Différentiel
CN105909757A (zh) * 2016-07-08 2016-08-31 天津天海同步科技有限公司 紧凑型差速器
CN107327559A (zh) * 2017-09-01 2017-11-07 西南大学 一种圆弧抛物线多点接触的斜齿轮
CN110067833A (zh) * 2019-05-29 2019-07-30 苏州博安捷机器人科技有限公司 一种双圆弧有隙啮合少齿差行星传动装置
WO2024094546A1 (fr) * 2022-10-31 2024-05-10 Mercedes-Benz Group AG Différentiel à engrenage cylindrique à denture droite pour véhicule automobile

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018019324A1 (fr) 2016-07-29 2018-02-01 Schaeffler Technologies AG & Co. KG Essieu électrique d'arbre unique pouvant être commuté à différentiel à roues dentées cylindriques intégré

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3738192A (en) 1971-06-29 1973-06-12 Illinois Tool Works Limited slip differential mechanisms
WO2012041551A1 (fr) * 2010-09-30 2012-04-05 Schaeffler Technologies AG & Co. KG Train épicycloïdal, différentiel épicycloïdal et boîte de vitesses comportant le différentiel épicycloïdal

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3738192A (en) 1971-06-29 1973-06-12 Illinois Tool Works Limited slip differential mechanisms
WO2012041551A1 (fr) * 2010-09-30 2012-04-05 Schaeffler Technologies AG & Co. KG Train épicycloïdal, différentiel épicycloïdal et boîte de vitesses comportant le différentiel épicycloïdal

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016055255A1 (fr) * 2014-10-10 2016-04-14 Engineering Center Steyr Gmbh & Co Kg Différentiel
CN105402354A (zh) * 2015-12-18 2016-03-16 天津天海同步科技有限公司 圆柱螺旋齿应力平衡式限滑差速器
CN105909757A (zh) * 2016-07-08 2016-08-31 天津天海同步科技有限公司 紧凑型差速器
CN107327559A (zh) * 2017-09-01 2017-11-07 西南大学 一种圆弧抛物线多点接触的斜齿轮
CN107327559B (zh) * 2017-09-01 2023-04-07 西南大学 一种圆弧抛物线多点接触的斜齿轮
CN110067833A (zh) * 2019-05-29 2019-07-30 苏州博安捷机器人科技有限公司 一种双圆弧有隙啮合少齿差行星传动装置
CN110067833B (zh) * 2019-05-29 2024-05-07 苏州博安捷机器人科技有限公司 一种双圆弧有隙啮合少齿差行星传动装置
WO2024094546A1 (fr) * 2022-10-31 2024-05-10 Mercedes-Benz Group AG Différentiel à engrenage cylindrique à denture droite pour véhicule automobile

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