WO2014064303A1 - Différentiel compact - Google Patents

Différentiel compact Download PDF

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Publication number
WO2014064303A1
WO2014064303A1 PCT/ES2013/000221 ES2013000221W WO2014064303A1 WO 2014064303 A1 WO2014064303 A1 WO 2014064303A1 ES 2013000221 W ES2013000221 W ES 2013000221W WO 2014064303 A1 WO2014064303 A1 WO 2014064303A1
Authority
WO
WIPO (PCT)
Prior art keywords
teeth
pinion
satellite
differential
pinions
Prior art date
Application number
PCT/ES2013/000221
Other languages
English (en)
Spanish (es)
Inventor
Eduardo García Sánchez
Original Assignee
Eduardo García Sánchez
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 Eduardo García Sánchez filed Critical Eduardo García Sánchez
Publication of WO2014064303A1 publication Critical patent/WO2014064303A1/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
    • 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
    • F16H2048/385—Constructional details of the ring or crown gear

Definitions

  • the present invention relates to a differential oriented rear or front-wheel drive vehicles.
  • automotive under normal conditions, it is required to send the same torque to the right wheel and to the left. This is usually achieved with satellites that use conical pinions.
  • This solution implies a larger set dimension than the design to be exposed and, consequently, more weight.
  • the teeth of the pinions of the satellites produce axial forces that make tapered roller bearings, expensive and with greater friction than those of balls, necessary. This requirement is not needed in this design.
  • the present invention uses standard gears with lowered dentures, experienced and usual elements, which guarantee a reliable design while maintaining a reasonable cost.
  • the objective is to achieve the differential "plane” using two planes of mechanisms instead of three. This is achieved as follows: (Fig. 5 and Fig. 6)
  • the first plane of mechanisms consists only of a pinion (2) attached to the first output shaft (6), which meshes with a pinion (l) that makes of satellite, whose axis (7) describes a circle for being housed in a hole (19) of the satellite carrier (8).
  • the second plane of mechanisms consists of a second satellite (3) that forms a single piece with the previous satellite ( l) and that it has fewer teeth than this. Said satellite (3) does not make contact with a pinion (4) integral with the second output shaft (9), but is connected to it by an intermediate pinion (5) that meshes with both.
  • This intermediate pinion rotates with respect to an axis (10) moved by the satellite carrier.
  • the number of teeth of the first satellite (1) divided by the number of teeth of the pinion (2) of the first output shaft is equal to the number of teeth of the second satellite (3) divided by the number of teeth of the pinion (4) of the second output shaft
  • the pinion (5) that connects the second satellite with the pinion of the second output shaft restores the direction of rotation.
  • FIG. 5 A satellite carrier (8) that receives the movement to be transmitted and whose mission is to produce two-axis circular paths (10 and (7)) for each group of satellites.
  • extension (l 1) that enters a cavity of the other (12) in order to make the assembly support a felting moment.
  • FIG. 6 A double satellite, formed by two pifions (1) and (3) being the number of teeth Zl greater than Z3, not having, said pinions, relative movement with each other.
  • the pinion with the largest number of teeth Zl meshes with the pinion (2) belonging to the first output shaft.
  • FIG. 6 Another satellite consisting of a single pinion (5), which meshes with the pinion (3) of the double satellite and with the pinion (4) integral to the second output shaft.
  • the Z 1 / Z2 ratio is equal to the Z3 / Z4 ratio.
  • the bearings (14) or friction surfaces of the satellite carrier (8) can rest exclusively on the differential output shafts, (Fig. 4) in this case said shafts (6) and (9) will rest on the bed by means of bearings (16).
  • the other possibility (Fig. 3) consists of supporting the satellite carrier on the bench using bearings (17), the differential output shafts will use bearings or friction surfaces resting on the satellite carrier.
  • the movement can reach the satellite carrier by means of conical pinions, hypoid pinions (Fig. 4) (23), straight pinions or by means of a crown of inner teeth and pinion, these gears can be, of teeth with straight teeth or (Fig. 3 ) helical (21).
  • the pinions (2) and (4) integral to the output shafts are integral to the pinions (2) and (4) integral to the output shafts.
  • LaFig. (3) represents the complete differential without its bench with an outer crown of helical teeth (21).
  • the differential support with respect to its bench is made through the satellite carrier by means of the bearing (17).
  • Fig. (4) represents the complete differential without its bed with a hypoid gear.
  • the differential support with respect to its bench is made through the output shafts by means of the bearing (16) .E1 axis (22) of the hypoid pinion (23) that goes to the motor is sectioned, the other extension serves to support the bearing base (24)
  • Fig. (5) represents the expanded differential. Only one group of satellites has been represented.
  • Fig. (6) represents, enlarged, the gearing of a group of satellites with the pinions integral to the output shafts.
  • FIG. 5 represents a differential in which the movement reaches the satellite carrier by means of a hypoid gear system.
  • the satellite carrier produces circular paths to the axes of the satellites.
  • the use of three groups of satellites has been chosen. Only one has been represented. The group is formed by a satellite composed of two pifions without relative movement, of different number of teeth Zl and Z3. The largest, of Zl teeth, meshes directly with the Z2 pinion integral to the first output shaft. The minor, of Z3 teeth, communicates the movement to the pipion Z4, integral to the second output axis, by means of an intermediate pipion (5).

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

Abstract

La présente invention concerne un différentiel plus compact, plus léger que les différentiels classiques à satellites coniques, produisant également le même couple dans les arbres de sortie ce qui permet d'éliminer ou de sous-dimensionner les roulements destinés à lutter contre les efforts axiaux, diminuant ainsi les frottements et réduisant les coûts. L'augmentation de la taille des paliers améliore le comportement des suspensions. Dans les véhicules à essieu rigide, la diminution de la masse en suspension est avantageuse. En général, ceci améliore la distance libre par rapport au sol. On utilise un groupe de satellites qui comprend un pignon Z1 qui s'engrène directement avec le pignon Z2 de l'arbre de sortie du différentiel et d'un pignon Z3, solidaire du pignon Z1, avec moins de dents, qui est couplé au pignon Z4 du second arbre de sortie par le biais du pignon Z5. La relation: Z1/ Z2 = Z3/Z4 garantit l'égalité des couples dans les arbres. Pour réduire la taille des arbres de sortie, on utilise des roulements ou des surfaces de frottement couplés dans la partie saillante (11) d'un d'eux et la cavité de l'autre, rendant l'ensemble insensible aux moments de flexion.
PCT/ES2013/000221 2012-10-26 2013-10-07 Différentiel compact WO2014064303A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ES201201068 2012-10-26
ESP201201068 2012-10-26

Publications (1)

Publication Number Publication Date
WO2014064303A1 true WO2014064303A1 (fr) 2014-05-01

Family

ID=50544063

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/ES2013/000221 WO2014064303A1 (fr) 2012-10-26 2013-10-07 Différentiel compact

Country Status (1)

Country Link
WO (1) WO2014064303A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3181950A1 (fr) * 2015-12-16 2017-06-21 Atieva, Inc. Différentiel de trains planétaire à arbres parallèles

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2142575A (en) * 1936-09-29 1939-01-03 Gen Motors Corp Differential gearing
DE811650C (de) * 1948-12-28 1951-08-23 Arthur Gaunitz Stirnrad-Differentialgetriebe fuer Kraftfahrzeuge
FR1269716A (fr) * 1960-07-05 1961-08-18 Boites De Vitesses Ind Dispositif de mécanisme différentiel
GB888263A (en) * 1959-08-20 1962-01-31 Ford Motor Co Improvements in or relating to vehicle differentials
DE102004015278A1 (de) * 2004-03-29 2005-10-20 Josef Gail Differentialgetriebe
FR2944081A1 (fr) * 2009-04-03 2010-10-08 Roger Laumain Differentiel a engrenage cylindrique auto freine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2142575A (en) * 1936-09-29 1939-01-03 Gen Motors Corp Differential gearing
DE811650C (de) * 1948-12-28 1951-08-23 Arthur Gaunitz Stirnrad-Differentialgetriebe fuer Kraftfahrzeuge
GB888263A (en) * 1959-08-20 1962-01-31 Ford Motor Co Improvements in or relating to vehicle differentials
FR1269716A (fr) * 1960-07-05 1961-08-18 Boites De Vitesses Ind Dispositif de mécanisme différentiel
DE102004015278A1 (de) * 2004-03-29 2005-10-20 Josef Gail Differentialgetriebe
FR2944081A1 (fr) * 2009-04-03 2010-10-08 Roger Laumain Differentiel a engrenage cylindrique auto freine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3181950A1 (fr) * 2015-12-16 2017-06-21 Atieva, Inc. Différentiel de trains planétaire à arbres parallèles

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