WO2005040642A1 - Systeme de differentiel compact - Google Patents

Systeme de differentiel compact Download PDF

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Publication number
WO2005040642A1
WO2005040642A1 PCT/EP2004/009608 EP2004009608W WO2005040642A1 WO 2005040642 A1 WO2005040642 A1 WO 2005040642A1 EP 2004009608 W EP2004009608 W EP 2004009608W WO 2005040642 A1 WO2005040642 A1 WO 2005040642A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
gears
arrangement according
cage
side shaft
Prior art date
Application number
PCT/EP2004/009608
Other languages
German (de)
English (en)
Inventor
Werner Krude
Boris Kracheninnikov
Original Assignee
Gkn Driveline International Gmbh
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
Priority claimed from DE10354998A external-priority patent/DE10354998B4/de
Application filed by Gkn Driveline International Gmbh filed Critical Gkn Driveline International Gmbh
Publication of WO2005040642A1 publication Critical patent/WO2005040642A1/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
    • 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

Definitions

  • the invention relates to a differential arrangement which is part of a differential gear and is used in particular for use in the drive train of a motor vehicle.
  • differential arrangements are well known. They usually include a differential cage in which sideshaft gears are arranged on an axis of rotation, which can be connected to associated sideshafts for torque transmission. The sideshaft gears are driven by differential gears rotating with the differential cage, which are rotatably mounted about journal axes lying radially to the axis of rotation.
  • EP 1 203 900 A2 discloses a crown gear differential with a differential cage and two side shaft gears arranged therein on an axis of rotation in the form of crown gears and a plurality of differential gears in the form of spur gears meshing with them.
  • the differential gears are rotatably mounted on pins of a star-shaped carrier element which rotates with the differential cage.
  • the crown gears which each have a hub for transmitting torque to an associated side shaft, are arranged axially adjacent to the carrier element.
  • US Pat. No. 2,270,567 shows a similar crown gear differential with hubs pointing away from the central plane for torque transmission to an associated side shaft.
  • US 6 413 183 B1 shows a differential which is designed in the form of a bevel gear differential.
  • the differential gears are rotatably held on pins, the pins rotating together with the differential carrier around the axis of rotation.
  • the sideshaft gears like the differential gears, are designed as bevel gears and have a natural be for torque transmission to the side shafts.
  • the two hubs of the sideshaft gears are arranged axially adjacent to the pins.
  • a crown gear differential is known from DE 101 44 200 A1, which is used for use in 5 a rear axle gear.
  • the sideshaft gears are supported in the axial direction by large axial locking rings in the differential carrier.
  • the hubs used for torque transmission to the associated side shafts are directed away from the differential carrier. At the same time, they serve to store the crown gear differential in a housing.
  • US 1 586 861 discloses a bevel gear differential with a plurality of differential gears rotating with the differential gear basket and side shaft gears in meshing engagement therewith.
  • the differential gears are rotatably held on radial supports on a carrier element held in the differential carrier.
  • the side shaft gears each engage with a cylindrical bearing surface in a central opening in the carrier element for radial mounting.
  • a locking differential in the form of a bevel gear differential is known from DE 40 03 331 A1. This includes laterally adjacent to the differential gear set two disc o brakes, the inner disc carriers are each rotatably connected to an associated side shaft gear. The inner disk carriers are in mesh with the associated side shaft for torque transmission. The side shaft gears are rotatably mounted on a bearing section of the associated side shaft.
  • the achievement of the object according to the invention consists in a differential arrangement, in particular for use in the drive train of a motor vehicle, comprising a differential cage which can be rotated about an axis of rotation X; a carrier element held in the center of the differential cage on the axis of rotation X, which together with the differential tialkorb revolves around the axis of rotation X and has a central opening and at least three pins with pin axes Y perpendicular to the axis of rotation X, on each of which an associated differential wheel is rotatably mounted; two side shaft shaft gears which are arranged in the differential cage on opposite sides to a central plane M spanned by the journal axes Y and which can rotate about the axis of rotation X and which mesh with the differential gears; wherein at least one of the side shaft gears has a hub for torque transmission to an associated side shaft, which partially projects into the central opening of the carrier element, a radial gap being formed between the hub and the carrier element; wherein the
  • the differential arrangement is compact overall and has a small axial length and, at the same time, does not place increased demands on manufacturing tolerances due to the radial gap between the hub and the carrier element.
  • the hub of the at least one side shaft gear is immersed in the opening of the carrier element and that the at least one differential gear is designed in the form of a spur gear and the side gear wheels are designed in the form of crown wheels, the differential cage can be made axially short.
  • the differential arrangement according to the invention can also be used in installation situations with a small available axial installation space. It is envisaged that the opening has a larger inner diameter than the outer diameter of the protruding portion of the hub. In this way, the manufacturing tolerances can be kept rough.
  • the crown gears are preferably axially supported with radial surfaces against the differential carrier.
  • the differential cage preferably has a cup-shaped first cage part and a cover-shaped second cage part which is at least partially accommodated in the first cage part with an axial overlap.
  • the second basket part is held axially free of play with a radial cover section between an inner shoulder of the first basket part and a retaining ring inserted into the basket part.
  • the second basket part can also have a flange section for connecting to a corresponding have the flange of the first basket part. Due to the fact that the second basket part is held axially free of play in the first basket part, tilting moments generated due to the torque transmission to the differential basket are well supported and introduced directly into rolling bearings provided for mounting the differential basket.
  • a groove in which the locking ring engages can have a conical surface, so that the second basket part is clamped between the shoulder and the locking ring.
  • the differential gears are slidably mounted on the pins.
  • the pins of the carrier element preferably have flats which run parallel to the pin axis and are opposite each other in the direction of the axis of rotation X, so that lubricant can get between the differential gears and the associated pins.
  • the differential gears are held on the respective pin of the carrier element in a radially floating manner with respect to the axis of rotation X.
  • the differential gears can run radially on the outside at least indirectly against the differential cage.
  • indirect means that the differential gears can run directly against the differential cage or against a component connected to it, for example a bearing washer.
  • the differential gears can run against a contact surface that increases the cross section of the pin. This prevents the differential gears from sliding on the pin in the direction of the axis of rotation.
  • the sideshaft gears are forcibly centered on the axis of rotation X, since a radial displacement due to the meshing engagement with the differential gears is not possible. An additional radial mounting of the sideshaft gears in the differential carrier is then not necessary.
  • the carrier element if it has three or more pins, is in turn positively centered on the axis of rotation X by the engagement of the pins in the differential cage.
  • the at least one of the two side shaft gears can have an extension on its end remote from the central plane, with which it is radially loaded in the differential cage. device. Such guidance of the sideshaft gear or gears is particularly necessary if only two differential gears are used.
  • the axial approaches extend the tooth length to the side shaft, so that higher torques can be transmitted.
  • the carrier element is held with its pin in several recesses distributed over the circumference in the differential carrier.
  • the recesses can be in the form of axial slots. be designed, which extend to the lid-side end of the first basket part. However, they can also be designed in the form of radial bores in which bearing disks are used to support the pins.
  • both sideshaft gears are designed in the form of crown gears and project into the opening of the carrier element.
  • one of the two side shaft gears can also be designed in the form of a crown wheel with a hub and the other of the side shaft gears can be designed in the form of an outer joint part of a constant velocity joint, the outer joint part having a crown gear toothing which meshes with the differential gears.
  • This embodiment comes in particular in relation to a
  • Vehicle longitudinal axis off-center drive shaft for example in the drive train of a front-wheel drive motor vehicle, for use.
  • Axial openings are provided in the first basket part and / or in the second basket part for the inlet of lubricant from a gearbox housing into the differential basket.
  • roller bearings which are designed in particular as tapered roller bearings, feed oil into the differential cage. This can leave the differential cage again along the flats on the pins via the recesses. Openings o can be provided in the jacket of the differential carrier through which the oil can leave the differential carrier again.
  • FIG. 1 shows a first embodiment of a differential arrangement according to the invention in longitudinal section
  • Figure 2 shows a second embodiment of a differential assembly according to the invention in longitudinal section
  • FIG. 3 shows a third embodiment of a differential arrangement according to the invention in longitudinal section;
  • FIG. 4 shows a fourth embodiment of a differential arrangement according to the invention in longitudinal section;
  • Figure 5 shows a fifth embodiment of a differential arrangement according to the invention in longitudinal section;
  • Figure 5 shows a carrier element of one of the differential arrangements according to one of Figures 1 to 5 in plan view.
  • a differential arrangement 1 with a differential cage 2 is shown, which is to be stored in a fixed housing, not shown.
  • the differential arrangement 1 is part of a differential gear in the drive train of a motor vehicle and is used for torque transmission from a longitudinal drive shaft, not shown, to two side shafts.
  • the differential cage 2 which is constructed in several parts and comprises a cup-shaped first cage part 3 and a cover-shaped second cage part 4, has a flange 5 to which a ring gear, not shown, for introducing a torque into the differential arrangement 1 is attached.
  • a carrier element 6 is arranged, which rotates together with the differential cage 2 about the axis of rotation X.
  • the carrier element 6 is star-shaped and has three pins 7, 7 ', 7 "with pin axes Y, Y', Y" perpendicular to the axis of rotation X and a central opening 9.
  • the first basket part 3 one of the Number of pins 7 corresponding number of recesses 10 are provided, in which the pins 7 engage.
  • a compensating wheel 8 in the form of a spur gear is rotatably mounted on each of the pins 7, a sliding bearing being provided as the bearing.
  • the differential gears 8 are axially movable to a limited extent on the associated pin 7, wherein they are held axially floating on the pin 7 by the meshing engagement with the side shaft wheels 11, 12.
  • the differential gears 8 run radially on the outside against an inner wall 19 of the differential cage 2.
  • the differential gears 8 are supported radially on the inside against a stop surface 34 which increases the cross section of the pin 7.
  • the first sideshaft gear 11 and the second sideshaft gear 12 are driven via the carrier element 6 and the differential gears 8.
  • the side shaft gears 11, 12 are designed as crown gears, each of which has crown gear toothings directed toward a central plane M containing the journal axes Y, which mesh with the differential gears 8.
  • the two side shaft gears 11, 12 each have hubs 13, 14 with internal teeth, into each of which a shaft journal 24, 25 (only shown in FIG. 4) of the associated side shafts can be inserted in a rotationally fixed manner.
  • the length of the hubs 13, 14 depends on the torque to be transmitted. In order to keep the axial length of the differential arrangement 1 short, the hubs 13, 14 protrude into the central opening 9 of the carrier element 6.
  • the side shaft gears 11, 12 taper radially outward, so that the tension arising in the side shaft gears 11, 12 due to the torque transmission is kept low.
  • the first sideshaft gear 11 is axially interposed with a friction-reducing thrust washer 15 with a radial surface against a bottom 17 of the first basket part
  • the second is on the axially opposite side Side shaft wheel 12 with a radial surface with the interposition of a second thrust washer 16 axially supported against a cover section 18 of the second basket part 4.
  • the thrust washers 15, 16 are selected after measuring the axial length between the two sideshaft gears 11, 12 in such a way that a minimum play for the toothing between the differential gears 8 and the sideshaft gears 11, 12 is ensured.
  • the differential carrier 2 To mount the differential arrangement 1 in the housing (not shown), the differential carrier 2 has two bearing projections 26, 27 which are directed in opposite directions
  • roller bearings 31, 32 Adjacent to the roller bearings 31, 32, which are preferably designed as tapered roller bearings, there are several axial openings 28, 29 distributed over the circumference in the bottom 17 of the first basket part 3 and in the cover section 18 of the second basket part 4.
  • roller bearings 31, 32 oil
  • each pin 7, 7 ', 7 " flats running parallel to the associated pin axis Y, Y', Y" 21, 21 ', 21 "is provided. The oil flows through these to the bearing surfaces.
  • FIGS. 2 and 4 show differential arrangements 1 2 , 1 4 with recesses 10 2) 10 4 which are designed in the form of radial bores.
  • each bearing washers 30 are used to receive an associated pin 7.
  • the carrier element 6 is first threaded into the differential carrier 2. Then the differential gears 8 by the Ausneh-
  • each a second basket part 4 ⁇ 4 2 which is inserted with a cover section 18 into a recess of the first basket part 3 ⁇ , 3 2 and is held axially free of play by means of a locking ring 23.
  • the second basket parts 4 3 , 4 4 each have a flange section 33 3 , 33, which is used to connect to the flange 5 of the associated first basket part 3 3 , 3 4 .
  • a third difference lies in the design of the hubs 13, 14 of the side shafts 5, 11, 12.
  • a longer toothing between the hub 13, 14 and the associated shaft journal 24, 25 is also necessary.
  • the hubs 13, 14 according to FIGS. 1 to 3 have larger axial lengths for the transmission of larger torques.
  • the hubs 13, 14 each have a section that projects axially outwards relative to the radial surfaces (0) that are supported against the thrust washers 15, 16. With these sections, the side shaft gears 11, 12 can be mounted radially in the differential carrier 2.
  • the side shaft gears 11 4 , 12 4 axially shorter hubs 13 4 , 14 4 for the transmission of smaller torques according to FIG Hubs 13 4 , 14 4 in the direction of the bottom 17 or cover section 18 4 axially flush with the radial surfaces which are supported against the thrust washers 15, 16.
  • the side shaft gears 11 4 , 12 4 are held radially in this case via the inserted side shafts, which are slidably mounted in the bearing lugs 26, 27.
  • FIGS. 1 to 4 can be carried out with any combination of features.
  • the cover-shaped second basket parts 4 3 , 4 4 with integrated flange sections 33 3 , 33 according to FIGS. 3 and 4 can also be arranged in a differential arrangement.
  • I5 of the carrier element 6 in the form of radial bores or longitudinal slots are interchangeable.
  • FIG. 5 shows a further embodiment of a differential arrangement according to the invention.
  • this largely corresponds to the embodiments according to FIGS. 1 to 4, to the description of which reference is made in this respect.
  • the same components are provided with the same reference numbers and different components with correspondingly lower indices.
  • the differential arrangement according to FIG. 5 has a sideshaft gear 12s in the form of an outer joint part of a constant velocity joint 35.
  • Such a differential arrangement is used in particular for use in drive trains of motor vehicles with respect to
  • a vehicle longitudinal axis of an offset drive shaft for example in front-wheel drive motor vehicles with a transversely installed engine.
  • a side shaft is connected to the constant velocity joint 35, which is 5 angularly offset from the axis of rotation X of the differential carrier 2 can make movements.
  • a so-called "left-hand shaft”, not shown, is connected in a rotationally fixed manner to the side shaft gear 11 5 opposite with respect to the center plane M, to the end of which, facing away from the differential arrangement, a second side shaft is connected via a constant velocity joint.
  • the constant velocity joint 35 shown is integrated into the differential carrier 2 5, wherein the joint outer part 12s, and this in turn is supported against the second basket portion 4 5 against a thrust washer sixteenth
  • the constant velocity joint 35 comprises, in addition to the outer joint part 12 & with outer tracks 36, an inner joint part 37 with inner tracks 38 and in each case a pair of outer tracks 36 and inner tracks 38 a torque-transmitting ball 39.
  • the balls 39 are held by a cage 41 in the bisecting plane.
  • a shaft journal 25 ⁇ for torque transmission to the associated side shaft, not shown, is inserted in the inner joint part 37 in a rotationally fixed manner and axially secured by means of a locking ring 42.
  • the second basket portion 4 s a flange portion 33 with the flange 5 of the first basket portion 3 5 and with a ring gear 43, via which a torque is introduced into the differential carrier 2 5, is connected by connecting means 44th
  • the second basket portion 4 5 further has a second bearing lug 27 on which a bearing inner ring of the rolling bearing 32 is seated for supporting the differential carrier 5 in the housing 2 45th
  • openings 32 of the above type are provided radially in the region of the roller bearing, which openings serve for the inlet of lubricant from the housing 45 into the differential basket 2s.
  • a bellows arrangement 46 with a seal 47 is provided which seals the annular space between the housing 45 and the shaft journal 25s.
  • the outer joint part 12s has a crown gear toothing which meshes with the differential gears 8 for torque transmission.
  • the outer joint part 12 5 is kept centered on the axis of rotation X by the three differential gears 8, as already described above, so that no additional radial centering means are required. It goes without saying that each of the exemplary embodiments shown in FIGS. 1 to 4 also has an integrated constant velocity joint according to the exemplary embodiment can be carried out from Figure 5. The features shown are interchangeable with each other.

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

Abstract

L'invention concerne un système de différentiel notamment destiné à être employé dans la chaîne cinématique d'un véhicule. Ledit système différentiel comporte une cage de différentiel (2) pouvant tourner autour de l'axe de rotation (X), un élément support (6) centré dans la cage de différentiel (2), tournant autour de l'axe de rotation (X) avec la cage de différentiel (2), présentant plusieurs tourillons (7) pouvant recevoir des galets de compensation (8) de façon rotative, et deux galets d'arbre latéral (11, 12) s'engrenant avec les galets de compensation (8). Au moins un des galets d'arbre de compensation (11, 12) comporte un moyeu (13, 14) destiné à la transmission du moment sur un arbre latéral correspondant faisait partiellement saillie dans un passage central de l'élément support (6). Un jeu radial est créé entre le moyeu (13, 14) et l'élément support (6).
PCT/EP2004/009608 2003-09-25 2004-08-28 Systeme de differentiel compact WO2005040642A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10344750.4 2003-09-25
DE10344750 2003-09-25
DE10354998.6 2003-11-25
DE10354998A DE10354998B4 (de) 2003-09-25 2003-11-25 Kompakte Differentialanordnung

Publications (1)

Publication Number Publication Date
WO2005040642A1 true WO2005040642A1 (fr) 2005-05-06

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ID=34524025

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/009608 WO2005040642A1 (fr) 2003-09-25 2004-08-28 Systeme de differentiel compact

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WO (1) WO2005040642A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101228366B (zh) * 2005-05-24 2011-03-23 Gkn动力传动国际有限公司 冠形齿轮及包括冠形齿轮的差动组件

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE173811C (fr) *
DE391270C (de) * 1921-07-20 1924-03-06 Timken Detroit Axle Company Einstellvorrichtung fuer ein in das Achsgehaeuse von Kraftfahrzeugen eingebautes, zum Antrieb des Ausgleichgetriebes dienendes Kegelraedergetriebe
US1586861A (en) 1923-10-22 1926-06-01 Taylor Cecil Hamelin Gearing
US2270567A (en) 1940-04-13 1942-01-20 Chrysler Corp Differential mechanism
GB770680A (en) * 1954-07-08 1957-03-20 David Brown And Sons Huddersfi Improvements in or relating to transmission mechanism for motor vehicles
GB776200A (en) * 1955-02-11 1957-06-05 Salisbury Transmission Ltd Improvements in differential gear units
US3344687A (en) * 1965-10-22 1967-10-03 Ford Motor Co Axle subassembly
US3388760A (en) * 1965-12-06 1968-06-18 Eaton Yale & Towne Tandem axle mechanism with locking type differential
FR2359329A1 (fr) * 1976-07-23 1978-02-17 Renault Mecanisme differentiel
DE4003331A1 (de) 1990-02-05 1991-08-08 Kloeckner Humboldt Deutz Ag Selbstsperrendes ausgleichsgetriebe
US5802918A (en) * 1996-10-16 1998-09-08 Mcdonnell Douglas Helicopter Co. Concentric face gear transmission assembly
EP1203900A2 (fr) 2000-11-06 2002-05-08 Crown Gear Holding B.V. Transmission par engrenage
US6413183B1 (en) 1999-04-14 2002-07-02 Tochigi Fuji Sangyo Kabushiki Kaisha Power transmission apparatus
WO2002096692A1 (fr) * 2001-05-26 2002-12-05 Gkn Automotive Gmbh Differentiel a joints homocinetiques integres
DE10144200A1 (de) 2001-09-08 2003-03-27 Daimler Chrysler Ag Kronenraddifferential
EP1321359A2 (fr) * 2001-12-19 2003-06-25 Moog Inc. Limitateur de couple différentiel

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE173811C (fr) *
DE391270C (de) * 1921-07-20 1924-03-06 Timken Detroit Axle Company Einstellvorrichtung fuer ein in das Achsgehaeuse von Kraftfahrzeugen eingebautes, zum Antrieb des Ausgleichgetriebes dienendes Kegelraedergetriebe
US1586861A (en) 1923-10-22 1926-06-01 Taylor Cecil Hamelin Gearing
US2270567A (en) 1940-04-13 1942-01-20 Chrysler Corp Differential mechanism
GB770680A (en) * 1954-07-08 1957-03-20 David Brown And Sons Huddersfi Improvements in or relating to transmission mechanism for motor vehicles
GB776200A (en) * 1955-02-11 1957-06-05 Salisbury Transmission Ltd Improvements in differential gear units
US3344687A (en) * 1965-10-22 1967-10-03 Ford Motor Co Axle subassembly
US3388760A (en) * 1965-12-06 1968-06-18 Eaton Yale & Towne Tandem axle mechanism with locking type differential
FR2359329A1 (fr) * 1976-07-23 1978-02-17 Renault Mecanisme differentiel
DE4003331A1 (de) 1990-02-05 1991-08-08 Kloeckner Humboldt Deutz Ag Selbstsperrendes ausgleichsgetriebe
US5802918A (en) * 1996-10-16 1998-09-08 Mcdonnell Douglas Helicopter Co. Concentric face gear transmission assembly
US6413183B1 (en) 1999-04-14 2002-07-02 Tochigi Fuji Sangyo Kabushiki Kaisha Power transmission apparatus
EP1203900A2 (fr) 2000-11-06 2002-05-08 Crown Gear Holding B.V. Transmission par engrenage
WO2002096692A1 (fr) * 2001-05-26 2002-12-05 Gkn Automotive Gmbh Differentiel a joints homocinetiques integres
DE10144200A1 (de) 2001-09-08 2003-03-27 Daimler Chrysler Ag Kronenraddifferential
EP1321359A2 (fr) * 2001-12-19 2003-06-25 Moog Inc. Limitateur de couple différentiel

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101228366B (zh) * 2005-05-24 2011-03-23 Gkn动力传动国际有限公司 冠形齿轮及包括冠形齿轮的差动组件

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