WO2009027177A1 - Transmission différentielle à composants supports légers - Google Patents

Transmission différentielle à composants supports légers Download PDF

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Publication number
WO2009027177A1
WO2009027177A1 PCT/EP2008/060136 EP2008060136W WO2009027177A1 WO 2009027177 A1 WO2009027177 A1 WO 2009027177A1 EP 2008060136 W EP2008060136 W EP 2008060136W WO 2009027177 A1 WO2009027177 A1 WO 2009027177A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
gear
toothed
planetary
planetary gear
Prior art date
Application number
PCT/EP2008/060136
Other languages
German (de)
English (en)
Inventor
Günter Schmitt
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 WO2009027177A1 publication Critical patent/WO2009027177A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • 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
    • F16H48/06—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
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases

Definitions

  • the invention relates to a differential gear having a sum shaft for distributing torques to a first differential element and to a second differential element via at least one pair of first planetary gear and a second planetary gear, wherein the planetary gears of a pair face each other and are operatively connected, in that axially middle sections of the toothed sections of both planetary gears are meshed with each other, that each of the central sections is formed axially next to a toothed outer section of the respective planetary gear, and that the outer section of the first planet gear meshes with a first gear on the first differential link and the outer portion of the second planet gear meshing with a second toothing on the second differential element.
  • the document EP 0 918 177 A1 shows a spur gear differential of the prior art.
  • the spur gear differential has a drive wheel which is formed by a ring gear but can also be designed as a spur gear preferably with helical gearing.
  • the drive wheel is rotatable together with a planet carrier about the axis of rotation and attached to the planet carrier.
  • the drive wheel, the housing with planet carrier and the output wheels of the spur gear differential together have the axis of rotation. Torques are fed into the spur gear differential to the planet carrier via the drive wheel.
  • the planet carrier or the housing as a planet carrier 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 differential shafts.
  • the differential waves each pass a differential amount of the torque introduced into the differential, for example, to the driven vehicle wheel.
  • the planet carrier or the housing as a planet carrier is the sum shaft 50 of the planetary
  • ring gears or sun gears are equated as output gears the difference waves, since these are each rotatably connected to the output shafts or coupled via further transmission elements with these.
  • the driven wheels are therefore also referred to below as differential links.
  • the differential housing is rotatably connected to the planet carrier.
  • the planetary pins also referred to as bearing journals, are mounted only once in the middle of their length on the planetary carrier. They protrude from both sides of the planet carrier in the differential housing and are rotatably mounted in this. At the projecting portions of the planetary pin planet gears are formed on both sides of the planet carrier fixed or firmly connected to the respective planet pins.
  • a planetary gear is rotatably mounted about the respective pin axis on a portion of the planet pins.
  • the piano bolts are in this case rotationally fixed to the planet carrier.
  • the planetary gears with planet pins are each arranged on an annular orbit about the axis of rotation.
  • the driven wheels may be internal-toothed ring gears, each of which is rotatably coupled to an output shaft.
  • the output shafts are usually in operative connection with a driven vehicle wheel.
  • Each of the planetary gears is paired with another of the planet gears for mutual meshing.
  • the mesh with planet gears one side with a first ring gear and all planetary gears of the other side with a second ring gear. The torque is distributed via the planet gears to the ring gears and thus to the output shafts and passed from there to the driven vehicle wheels.
  • the planetary gears of a pair are in this differential with the longitudinal half the tooth width respectively engaged with each other.
  • the longitudinally outer half of the tooth width of each gear of a pairing meshes with one of the internally toothed ring gears.
  • the longitudinal direction is the direction in which the axis of rotation of the differential is directed.
  • 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.
  • the advantage of the spur gear of the prior art is 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 tooth width is also a criterion for the height of the transmittable torque.
  • the wider the tooth engagement the higher the torque can be transmitted. Due to a broader meshing, the differentials require more space, ie axially, more space and are thus altogether heavier and more expensive.
  • each of the planetary gears of one pair mesh with a different differential link than the other paired planetary gear. If in this differential one or both planetary gears with two differential links (for example, at the same time with both sun gears) would be engaged, the compensation would be blocked in the differential. In the design of the planetary drive is therefore sufficient clearance for the toothing of each of the two differential elements for itself to provide that planetary gear, with the teeth may not be the respective differential element in engagement.
  • the bolt axes of the planet pins of a pair lie circumferentially one behind the other. How many pairs of planetary gears can be arranged circumferentially, depends on the circumferential distance, which is determined by the dimensions of the planetary gears and which is also significantly dependent on the design of the bearings for the planet gears and their surrounding construction.
  • the differential described in the document EP 0 918 177 A1 and the corresponding practical example implemented in the aforementioned technical article each have three pairs of planet gears distributed symmetrically around the circumference - however, EP 0 918 177 A1 mentions that at higher levels through the differential more than three pairs can be used for transmitting moments.
  • the invention is therefore based on the object to provide a differential gear that can absorb high torques to use it at least in small and mid-size cars, and has only a small weight in a small space.
  • a differential gear with a sum shaft for the distribution of torque to a first differential element and to a second differential element via at least one of each of a first planetary and a second planetary gear formed pair, the planetary gears of a pair are so opposite each other and are operatively connected so that axially middle sections of the toothed sections of both planet gears are meshed with each other, that each of the middle sections Weil is formed axially adjacent to a toothed outer portion of the respective planetary gear, and that the outer portion of the first planet gear meshing with a first toothing on the first differential element and the outer portion of the second planet gear meshing with a second toothing on the second differential element, and is characterized in that the sum shaft comprises an axially symmetrical spur gear and a first and a second support member, wherein the planet gears are mounted in the support members and the support members are cold-formed, flanged to the spur gear (20) sheet metal parts.
  • the proposed solution avoids a separate differential with massive differential basket or solid support parts.
  • it is proposed to provide only one massive component. Since the massive spur gear of the total shaft can not be dispensed with, the spur gear is used as a rigid, massively produced carrier component.
  • the tasks of the differential basket are solved cost-effective and weight-saving by two to be flanged drawn parts. Costly machining technologies are avoided for the support parts. Nevertheless, the differential gear due to the two-sided storage of the planetary gears in the support members and the massive Ausbil- fertilizing the spur gear is able to transmit large moments.
  • the first carrier part is a cold-formed, flanged to the spur gear sheet metal part.
  • the second differential element can extend through a central recess in the spur gear. In this way, it is particularly easy to provide a torque transmission to the side of the spur gear facing away from the planet wheels.
  • first toothing and the second toothing are each formed as external toothing.
  • the spur gear and the first and the second carrier part and the lid each have a number of rotationally symmetrical through holes, are guided by the fastening elements for connecting the spur gear to the first and the second carrier part and the lid.
  • first differential element is guided in the first carrier part and a first end of the second differential element is guided in the spur gear.
  • the spur gear has a double-T-shaped cross-section.
  • the planetary gears may be formed identical to each other.
  • the carrier parts and the cover are produced as draw-stamped parts. It may further be provided that the carrier parts are formed identical to one another.
  • the spur gear has a central bore, in which a second end of both the first and the second differential element is guided.
  • An embodiment of the invention is characterized in that each of the middle sections is formed axially between the toothed outer portion of each planetary gear and a non-toothed portion, and that a first, non-toothed portion of the first planetary circumferentially a second, axially outer portion of a is contactlessly opposite the second planetary gear formed second toothed portion, and a second, non-toothed portion of the second planetary circumferentially a first, axially outer portion of a formed on the first planet gear first toothed portion is contactlessly opposite It can be provided that face the second toothing of the first differential element, the first, non-toothed portion of the first planetary gear radially and non-contact.
  • first toothing may be opposite to the second, non-toothed section of the second planetary gear radially and without contact.
  • the non-toothed portions may be formed outside cylindrically.
  • the outer diameter of the non-toothed portions is smaller than the root diameter of the toothed portions, wherein at the root diameter of the tooth root of each of the teeth of the toothed portion emerges from the planetary gear.
  • FIG. 1 is an exploded view of a sum shaft of a differential gear according to the invention in a first embodiment
  • FIG. 2 shows an exploded view of a sum shaft of a differential gear according to the invention in a second embodiment
  • 3 shows a cross-sectional view of a differential gear according to the invention in a first embodiment
  • FIG. 6 shows an embodiment of the construction of the planet wheels of a differential gear according to the invention
  • FIG. 7 shows a further embodiment of the structure of the planet wheels of a differential gear according to the invention.
  • FIG. 8 shows an exploded view of a differential gear according to the invention in a first embodiment
  • Figure 9 is an exploded view of a differential gear according to the invention in a second embodiment.
  • FIGS. 1 to 4 show different views of a sum shaft 10 of a differential gear 100 according to the invention, with FIGS. 1 and 3 representing a first embodiment of the sun shaft 10 and FIGS. 2 and 4 representing a second embodiment of the sun shaft 10.
  • the embodiments differ only in the specific configuration of a first carrier element 30 and a second carrier element 32 and the provision of mass recess 24 in a spur gear 20 and are therefore described across figures.
  • the operation of open Stirnraddifferentialgetrieben is familiar to those skilled in the art and therefore will not be described here in detail again.
  • the sum shaft 10 of the differential gear 100 comprises a spur gear 20, which is solid and has a double-T-shaped cross-section.
  • the spur gear 20 further comprises recesses 22 for planet gears 50, 52, a central recess 26 and through-holes 24, by which it is connected to the first 30 and the second support member 32.
  • first carrier part 30 and the second carrier part 32 likewise have through holes 34 for connection to the spur gear 20.
  • both the first carrier part 30 and the second carrier part 32 in the first embodiment each comprise a pocket or bead 36, 38 for partially receiving the planet gears 50 and 52 and a first 40 and second differential element 42.
  • the bags can be deep-drawn or be fine-cut.
  • the carrier parts 30, 32 are formed as cold-formed sheet-metal parts by means of drawing and / or embossing.
  • the support members 30, 32 are formed identical to each other. In this way, a fast and cost-effective production of the carrier parts 30, 32 is possible.
  • the carrier parts 30, 32 are characterized by their low weight.
  • the solidly manufactured spur gear 20 fulfills supporting, guiding and connecting tasks. It centers both support parts 30, 32 and additionally guides and supports both differential members 40, 42 in the central recess 26. Kidney-shaped recesses 22 are exposures for the space-saving accommodation of the planet wheels 50, 52 Massausussparungen 25 may be provided to the weight of the spur gear 20 without to reduce a reduction in the strength of the spur gear 20.
  • the two-sided recording of the planet gears 50, 52 allows in contrast to a flying bearing transmission of large moments.
  • the first support member 30, the second support member 32, and the spur gear 20 are interconnected by fasteners 60, such as screws or bolts, through the throughbores 24, 34. Welding is therefore completely dispensed with, whereby manufacturing costs are saved and a risk of breakage of the welds is prevented. By dispensing with welding further unnecessary heat influence on the support members 30, 32 and the spur gear 20 is avoided and thus the risk of delay of the corresponding components, prevented
  • FIG. 5 shows various embodiments of a spur gear 20.
  • the number of provided pairs of planet gears 50, 52 can be varied.
  • the embodiment illustrated in FIGS. 5a and 5b is designed for two pairs of planetary gears 50, 52, whereas the embodiment in FIG. 5c is designed for three pairs of planetary gears 50, 52.
  • a second end 45, 47 of a first differential element 40 and a second differential element 42 projects at least with a portion into the central recess 26 of the spur gear 20 and is thus guided in this.
  • the through-hole 24 is to be provided for connection to the support members 30, 32, and as far as the strength design of the spur gear 20 permits, the mass recesses 25 may be provided to reduce the weight of the spur gear 20 become.
  • the planet wheels 50, 52 of the differential gear 100 according to the invention can basically be formed in two different ways.
  • Figure 6 correspondingly shows a first embodiment of the planet wheels 50, 52 of the present invention.
  • first planetary gear 50 and a second planetary gear 52 of each pair of planets via central sections 54, 56 with each other.
  • the first outer portion 55 of each first planetary gear 50 is further engaged with a first toothing 41 of a first differential element 40.
  • the first differential element 40 and the second differential element 42 are formed as sun gears with external teeth.
  • each second planetary gear 52 is in meshing engagement with a second toothing 53 of the second differential element 42.
  • the gears 50, 52 move axially against each other.
  • the first carrier part 30 and the second carrier part 32 are to be designed accordingly in order to compensate for the offset of the gears 50, 52 relative to one another and to prevent axial displacement by axial contact with the toothed wheels 50, 52.
  • FIG. 7 shows a second possible embodiment.
  • the first gear 50 has a first, non-toothed section 58 and the second gear 52 has a second, non-toothed section 59.
  • the non-toothed portions 58, 59 in this case have a diameter which is chosen so that they do not match with the teeth of the first and second differential element 40, 42 in FIG Come in contact.
  • the non-toothed portions 58, 59 provide ientagonal axial extensions of the first and second gears 50, 52, so that the first support member 30 and the second support member 32 need not be formed with a pocket 36, 38 and the offset of Gears 50, 52 do not have to compensate.
  • the production of the gears 50, 52 is slightly more complicated in the embodiment shown in Figure 7, but the support members 30, 32 can be made cheaper and easier.
  • gears 50, 52 shown in FIG. 6 is shown in an overall overview in FIG. 8, from which it can be seen that the gears shown in FIG. 6 are to be provided together with the carrier parts 30, 32 shown in FIG.
  • gears 50, 53 shown in FIG. 7 are shown in an overall view in FIG. 9 according to a second embodiment and together provide the carrier parts 30, 32 shown in FIG.
  • FIG. 8 shows an exploded view of a differential gear 100 according to the invention.
  • the spur gear 20 leads in a central recess 26, the second end 45 of the first differential element 40 and the second end 47 of the second differential element 42.
  • the spur gear 20 is connected to the first support member 30 and the second support member 32, wherein the planet gears 50th , 52 are respectively guided in corresponding pockets 36, 38 of the carrier parts 30, 32.
  • a first end 44 of the first differential element 40 and a first end 46 of the second differential element 42 are also guided in a corresponding carrier part 30, 32.
  • the carrier parts in turn are mounted in radial bearings 80, 82.
  • the bolts 53 of the planetary gears 50, 52 may be formed as full or hollow pin with Quererbhrungsverschmtechnik.
  • the planetary gears 50, 52 can further receive radial and / or axial sliding bearings, if required, and it is also possible to provide needle rings for better support.
  • FIG. 9 shows an overall view of a differential gear 100 according to the invention in a second embodiment.
  • non-toothed sections 57, 59 are provided on the planetary gears 50, 52 in the second embodiment, whereby a simpler shaping of the carrier parts 30, 32 is possible.
  • struts 31 are provided in the second embodiment, to give the support members 30, 32 additional rigidity and strength.
  • struts 31 can also be used in support parts 30, 32 of the first embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une transmission différentielle (100) présentant un arbre cumulant la somme des couples (10) pour la répartition des couples sur un premier élément de différentiel (40) et sur un second élément de différentiel (42), via au moins une paire formée, respectivement, d'un premier satellite (50) et d'un second satellite (52), les satellites (50, 52) d'une paire étant opposés entre eux et liés coopérant, de telle façon que des sections partielles médianes axiales (54, 56) des portions en prise des deux satellites (50, 52) viennent en prise entre elles, de sorte que chacune des sections partielles médianes (54, 56) soit configurée axialement à proximité d'une section partielle extérieure (55, 57) en prise de chaque satellite (50, 52), et que la section partielle extérieure (55) du premier satellite (50) soit en prise avec une première denture (41) sur le premier élément de différentiel (40), et la section partielle extérieure (57) du second satellite (52) soit en prise avec une seconde denture (43) sur le second élément de différentiel (42). L'invention est caractérisée en ce que l'arbre cumulant la somme des couples (10) comprend un pignon droit à symétrie axiale (20) et un premier (30) et un second (32) composant support, et en ce que les satellites (50, 52) sont montés dans les composants supports (30, 32), et les composants supports (30, 32) sont des éléments en tôle formés à froid, montés à bride sur le pignon droit (20).
PCT/EP2008/060136 2007-08-28 2008-08-01 Transmission différentielle à composants supports légers WO2009027177A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710040478 DE102007040478A1 (de) 2007-08-28 2007-08-28 Differentialgetriebe mit leichten Trägerteilen
DE102007040478.8 2007-08-28

Publications (1)

Publication Number Publication Date
WO2009027177A1 true WO2009027177A1 (fr) 2009-03-05

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Application Number Title Priority Date Filing Date
PCT/EP2008/060136 WO2009027177A1 (fr) 2007-08-28 2008-08-01 Transmission différentielle à composants supports légers

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WO (1) WO2009027177A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012222227B4 (de) * 2012-12-04 2018-07-19 Schaeffler Technologies AG & Co. KG Stirnraddifferentialgetriebe
DE102013222833A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Stützlageranordnung für ein Planetendifferential
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
CN106553534B (zh) * 2015-09-25 2019-11-22 比亚迪股份有限公司 动力驱动系统及具有其的车辆
CN106555859B (zh) * 2015-09-25 2019-11-22 比亚迪股份有限公司 动力驱动系统及具有其的车辆
CN106553533B (zh) * 2015-09-25 2019-11-22 比亚迪股份有限公司 动力驱动系统及具有其的车辆

Citations (3)

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Publication number Priority date Publication date Assignee Title
CH354340A (de) * 1955-12-13 1961-05-15 Nsu Werke Ag Ausgleichgetriebe für den Antrieb der Räder von Kraftfahrzeugen
DE1136585B (de) * 1955-12-13 1962-09-13 Nsu Motorenwerke Ag Stirnradausgleichgetriebe fuer Kraftfahrzeuge
EP0918177A1 (fr) * 1997-02-17 1999-05-26 Bernd-Robert Prof. Dr. Ing. Höhn Differentiel à engrenages à axes parallèles

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH354340A (de) * 1955-12-13 1961-05-15 Nsu Werke Ag Ausgleichgetriebe für den Antrieb der Räder von Kraftfahrzeugen
DE1136585B (de) * 1955-12-13 1962-09-13 Nsu Motorenwerke Ag Stirnradausgleichgetriebe fuer Kraftfahrzeuge
EP0918177A1 (fr) * 1997-02-17 1999-05-26 Bernd-Robert Prof. Dr. Ing. Höhn Differentiel à engrenages à axes parallèles

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HOEHN B-R ET AL: "KOMPAKTES ACHSGETRIEBE FUER FAHRZEUGE MIT FRONTANTRIEB UND QUER EINGEBAUTEM MOTOR", ATZ AUTOMOBILTECHNISCHE ZEITSCHRIFT, VIEWEG PUBLISHING, WIESBADEN, DE, vol. 108, no. 1, 1 January 2006 (2006-01-01), pages 46 - 51, XP001238419, ISSN: 0001-2785 *

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