WO2003054424A1 - Differentiel controlable - Google Patents

Differentiel controlable Download PDF

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Publication number
WO2003054424A1
WO2003054424A1 PCT/ES2002/000574 ES0200574W WO03054424A1 WO 2003054424 A1 WO2003054424 A1 WO 2003054424A1 ES 0200574 W ES0200574 W ES 0200574W WO 03054424 A1 WO03054424 A1 WO 03054424A1
Authority
WO
WIPO (PCT)
Prior art keywords
satellites
controllable differential
output
half shafts
differential
Prior art date
Application number
PCT/ES2002/000574
Other languages
English (en)
Spanish (es)
Inventor
José Gimenez Vidal
Original Assignee
Rodriguez Castilla, Miguel, Angel
Gimenez Alfonso, Olga, Montserrat
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 ES200102715A external-priority patent/ES2188421B1/es
Application filed by Rodriguez Castilla, Miguel, Angel, Gimenez Alfonso, Olga, Montserrat filed Critical Rodriguez Castilla, Miguel, Angel
Priority to AU2002363904A priority Critical patent/AU2002363904A1/en
Publication of WO2003054424A1 publication Critical patent/WO2003054424A1/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
    • F16H48/05—Multiple interconnected differential sets
    • 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
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/27—Arrangements for suppressing or influencing the differential action, e.g. locking devices using internally-actuatable fluid pressure, e.g. internal pump types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/204—Control of arrangements for suppressing differential actions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/26—Arrangements for suppressing or influencing the differential action, e.g. locking devices using fluid action, e.g. viscous clutches
    • F16H2048/265—Arrangements for suppressing or influencing the differential action, e.g. locking devices using fluid action, e.g. viscous clutches with a fluid throttling means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2071—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using three freewheel mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/26—Arrangements for suppressing or influencing the differential action, e.g. locking devices using fluid action, e.g. viscous clutches

Definitions

  • the present invention is intended to disclose a controllable differential applicable to automotive, which has significant advantages over currently known differentials of the type called self-blocking.
  • the controllable differential object of the present invention will be applicable especially, although not exclusively, to vehicles of the type called 4 4, that is, vehicles with the possibility of permanent or connectable four-wheel drive.
  • vehicles of the type called 4 4 that is, vehicles with the possibility of permanent or connectable four-wheel drive.
  • first, second and third sub-assemblies are arranged in an enclosure or single body.
  • the first of said satellite assemblies is connected to the power input shaft, and the other two are connected to each other by means of an intermediate shaft with tapered sprockets and with intermediate gearwheels are connected with the power output axes being associated one of the sets of second or third satellites with a disc or braking gear, for the regulation of the distribution of torque between both output axes.
  • the second and third satellite assemblies comprise a fixed and the other solidarity, through its box, with the disc or braking crown.
  • both sets of second and third satellites are mobile, their boxes being sympathetic to dentate crowns that engage with a pinion of the controllable axle axis.
  • a feature of the present invention is that all gears have the ability to rotate on their axis.
  • controllable differential object of the present invention has a disc or crown that can be controlled by an adjustable resistant torque, for example, by brake calipers or other system, which allows the torque transmission to be adjusted to the output shafts as desired.
  • the replacement of the fixed satellite assembly in charge of reversing the rotation is foreseen by a gear train or transmission chain system that performs the same function.
  • the system to reverse the rotation could be realized by any other suitable device among those known in the art.
  • the improvements of this variant consist in self-controlling the torque distribution between the two output half shafts with a hydraulic-mechanical system, as well as with this same system obtaining a differential variator controllable speeds.
  • Figure 1 shows a longitudinal section of a differential made according to the present invention, with a control disk.
  • Figure 2 shows a section of a differential similar to that of Figure 1 in which the control disc has been replaced by a brake control axis.
  • Figure 3 shows an embodiment similar to Figure 2 but with a different arrangement of power input shaft and half output shafts.
  • Figure 4 shows a version similar to Figure 3 in which the control axis has been replaced by a disk.
  • Figure 5 shows a version similar to Figure 4 with regulation of the torque distribution by means of a brake control axis.
  • Figures 6 and 7 show two versions based on a normal differential and two satellite boxes geared with the output half shafts, with regulation respectively by means of a disk and by means of a controllable axis.
  • Figure 8 illustrates improvements presented on the execution of Figure 6, according to which the third set of fixed satellites in charge of the turn inversion has been replaced by a gear train with intermediate wheel that performs the same function.
  • Figure 9 illustrates the refinements of Figure 8, in which the third set of fixed satellites in charge of the turn inversion has been replaced by a chain drive system that performs the same function.
  • Figures 10 and 11 show in section the improvements of this invention referred to Figure 8 having added to the differential control system, a hydraulic-mechanical system of pistons that can perform the function of self-control of the differential.
  • Figures 12 and 13 show in section an embodiment similar to Figures 10 and 11 to use the mechanism as a variable speed controllable variator, controlled continuously by the controlled circulation of the hydraulic-mechanical system liquid.
  • Figures 14 and 15 show in section a simplified version of the controllable differential speed variator, also controlled in a continuous progressive manner by the controlled circulation of the liquid of the hydraulic-mechanical system.
  • the differential object of the present invention comprises a single outer shell -1-, with a power input shaft -2- and three sets of satellites indicated respectively with the numerals -3-, -4- and -5-.
  • the differential distributes the driving torque between two output shafts -6- and -7- perpendicular to the power input axis -2-.
  • the first and second sets of satellites -3- and -4- are rotatable with their boxes respectively, while the third set of satellites -5- is fixed.
  • the first set of satellites -3- is driven directly by the power input axis -2- and is connected to the third set of satellites -5- by means of a forwarding axis -8-, which has at its ends the conical pinions -9- and -10- meshed with the respective satellite assemblies.
  • the drive output to one of the output half-shafts is made through the forwarding axis -8- and a crown -11- that meshes with the crown -12- integral with the half-axis -7-.
  • the second power output half shaft -6- is driven by the corresponding toothed crown -13- engaged with the crown -14- integral with a hollow shaft -15- that partially surrounds the forwarding shaft -8- and that through the pinions Conical ends -16- and -17- are connected respectively with the first and second sets of satellites indicated by numerals -3- and -4-.
  • a second hollow shaft -18- also partially wraps the forwarding shaft -8- and features conical pinions -19- and -20- that engage with the satellites of the second and third satellite assemblies, that is, those indicated with the numerals -4- and -5-.
  • the control disk -21- is mounted, with the ability to rotate on a radial and axial bearing -44-, said disk -21- being integral with the box -45- of the second set of satellites.
  • a braking action can be exerted on the disc -21-, for example, by means of a system of drive calipers on the disc that have not been shown. As is evident, the system of braking could be performed by any suitable device among those known in the art, such as friction shoes, friction pads, magnetic systems, etc.
  • the braking effect on the control disc -21- allows the distribution of the driving torque in a controlled manner at will between the two output axles -6- and -7-.
  • the braking effect could also be achieved by an external axis as shown schematically with the numeral -22- in figure 2.
  • Said axis -22- with its pinion -22 "- is connected to the crown -22'- which is integral with the body -71- of the second set of satellites -4-, being rotatable on the hollow shaft -18- through the corresponding bearing or bearings.
  • FIG 3 a variant of the differential object of the present invention is shown in which the single enclosure or differential case is indicated with the numeral -23-, the power input axis -24- being transverse to the axis of forwarding -25-, establishing the connection with one of the output half shafts -26-, in a concept similar to the example of figure 1, through said forwarding axis -25- and a system of straight toothed crowns -27- and -28-, while the second output shaft -29- is driven by a set of straight sprockets -30- and -31-, the first of a hollow shaft -32- being connected by its end sprockets with the satellite assemblies -33- and -34-.
  • a conical crown -36- is mounted with turning capacity when mounted on a radial and axial bearing -46-, being integral with the case -47- of the second satellite set.
  • the crown -36- meshes with the pinion -37- which is integral with the brake control axis -38-.
  • FIG. 4 corresponds to a structure similar to that of Figure 3, with the input shaft -39- perpendicular to the forwarding shaft -40- and with the output half shafts -41- and -42- parallel to said forwarding axis.
  • the only variant with respect to the embodiment of Figure 3 consists of the arrangement of a control disk -43- which, similar to the version of Figure 1, will require some type of adjustable braking.
  • FIG. 5 A version similar to Figure 3 is shown in figure 5, with torque adjustment axis distributed to the output shafts -41- and -42-.
  • the third satellite box is mobile.
  • there is a braking shaft -48- that is engaged with the toothed crowns -49- and -50-, which are in solidarity respectively with the third and second satellite boxes indicated with the numbers -52- and -51- respectively.
  • the relative movement between the second and third set of satellites remains the same as in Figure 3.
  • said half-shafts -57- and -58- have two toothed crowns -59- and -60- which, through other respective toothed crowns -61- and -62- are engaged in the two sets of satellites -63- and -64- interconnected by the intermediate shaft -65- bearing two conical pinions at its ends.
  • the box -66- of the set of satellites -63- is integral with a control disc -67- braking at will to regulate the distribution of the torque to the semi-axles.
  • Figure 7 shows a version similar to that of figure 6 in which the only difference is that the disk -67- of the version represented in figure 6 is replaced by a toothed crown -68- which is integral of the satellite box -66- of the second set of satellites -63-, engaging with a conical pinion -69- of a shaft -70- that is braking to get the torque distribution to the output half shafts -57- and - 58-.
  • the variant of figures 8 and 9 comprises a single external enclosure -121-, with an input shaft -101- that meshes through its conical pinion -102- with the crown -103- integral to the satellite box -104- , through which the output shafts -105- and -106- are driven, this part corresponding to that of a conventional differential.
  • said half-shafts -105- and -106- have two gears -107- and -108-.
  • the gear -107- meshes with the gear -109- which is integral with the input half-shaft -110- which has at its end the conical pinion -111- that connects with the second set of satellites -114-.
  • the Conical pinion -111- connects with satellites -112- and -113- of the box -115- of the satellite assembly -114- which is integral with a control disk -116- braking at will to regulate the torque distribution between the output half shafts -105- and -106-.
  • the satellites -112- and -113- at the same time connect with the conical pinion -117-, which is integral with the input shaft -118-.
  • This input shaft -118- is integral with the gear -119- that meshes directly with the intermediate gear -120-, which is connected to the gear -108- of the half-shaft -106-.
  • the braking system could be realized by any suitable device among those known in the art, such as friction shoes, friction pads, magnetic systems, etc.
  • Figure 9 shows a version similar to Figure 8, in which the only difference is that the intermediate gear -120- is eliminated and a serrated endless chain -120'- is incorporated, which meshes the gear -108 ' - solidarity of the output shaft -106- and with the gear -119'- solidarity of the input shaft -118-, forming a chain drive system.
  • a single outer shell -221- is provided, with an input shaft -201- that meshes through its conical pinion -202- with the crown -203- integral with the satellite box -204-, through which the output half shafts -205- and -206- are driven.
  • said semi-shafts -205- and -206- have two gears -207- and -208-.
  • the gear -207- meshes with the gear -209- which is integral with the input half-shaft -210- which has at its end the conical pinion -211- which connects with the second set of satellites -214-.
  • the conical pinion -211- connects with the satellites -212- and —213- of the box -215- of the set of satellites -214- which is integral with a conical gear -222-, controllable through the hydraulic-mechanical system - 238- which we will explain later.
  • the satellites -212- and -213- simultaneously connect with the conical pinion -217-, which is integral with the semi-axis of -218-.
  • This axle shaft -218- is integral with the gear -219- that meshes directly with the intermediate gear -220-, which is connected to the gear -208- of the half shaft -206-.
  • the hydraulic-mechanical system -238- is connected to the conical control gear -222- by the conical pinion -223- of the control shaft -224- which at its end has the cam -225- integrated, all this of the hydraulic system- mechanical -238-.
  • the control shaft -224- is mounted on bearings incorporated in the body of the hydraulic group.
  • the cam -225- receives at the opposite points of its periphery the continuous contact of the contact rollers -228- and -229- of the pistons -226- and -227- by the elastic action of the springs -230- and -231 -.
  • Each of the cylinders -234- and -235- incorporates its corresponding valve -232- and -233- of hydraulic fluid intake which cut the intake during the compression cycle. Also, each cylinder incorporates a calibrated valve or bore of discharge -236- and -237- which limits the passage of liquid and therefore the travel speed of the pistons -226- and -227- during compression.
  • the intake valves -232-, -233- and discharge valves -236- and -237- of each of the cylinders -234- and -235-, are connected by ducts to a common hydraulic fluid supply tank (not shown).
  • a common hydraulic fluid supply tank not shown
  • control system also allows obtaining a variable speed drive controlled by the hydraulic-mechanical system. It is evident that the control system could be similarly realized by any device among those known in the art such as brake shoes, clutches, hydraulic systems, etc.
  • FIGS 14 and 15 a simplified version of that of figures 12 and 13 is shown, comprising a single casing body -221'-, with an axis of power input -201'- that meshes through its tapered pinion -202'- with the crown -203'- integral with the satellite box -204'-, through which the power output shaft -206 is driven '- and the control shaft -205'- which is integral with cam -225- of the hydraulic-mechanical system -238- already explained previously in Figures 10 and 11.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Retarders (AREA)

Abstract

Ce différentiel comprend, à l'intérieur d'un seul corps enveloppant, des premier, deuxième et troisième ensembles de satellites. Le premier ensemble de satellites est relié à l'axe d'entrée de puissance et les deux autres ensembles de satellites sont reliés entre eux au moyen d'un axe intermédiaire présentant des pignons coniques et sont reliés aux axes de sortie de puissance au moyen desdites roues dentées. Le deuxième ou troisième ensemble de satellites est ainsi associé à un disque ou engrenage freinable pour la régulation de la répartition de couple entre les deux axes de sortie.
PCT/ES2002/000574 2001-12-05 2002-12-04 Differentiel controlable WO2003054424A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2002363904A AU2002363904A1 (en) 2001-12-05 2002-12-04 Controllable differential

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
ES200102715A ES2188421B1 (es) 2001-12-05 2001-12-05 Diferencial controlable.
ESP0102715 2001-12-05
ES200200390A ES2192142B1 (es) 2001-12-05 2002-02-06 Mejoras introducidas en la patente de invencion n.p200102715 por "diferencial controlable".
ESP0200390 2002-02-06
ES200202747 2002-11-29
ESP0202747 2002-11-29

Publications (1)

Publication Number Publication Date
WO2003054424A1 true WO2003054424A1 (fr) 2003-07-03

Family

ID=27240820

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/ES2002/000574 WO2003054424A1 (fr) 2001-12-05 2002-12-04 Differentiel controlable

Country Status (1)

Country Link
WO (1) WO2003054424A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102619953A (zh) * 2012-03-27 2012-08-01 谢建武 四轮驱动油压智能偶合器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB620723A (en) * 1946-10-21 1949-03-29 Ewen Gordon M Ewen Improvements in or relating to differential gearing
US2533611A (en) * 1946-12-28 1950-12-12 Allis Chalmers Mfg Co Controlled differential transmission mechanism
FR1024532A (fr) * 1950-09-13 1953-04-02 Lyonnais Rochet Schneider Ets Dispositif de blocage progressif de différentiel
US3034322A (en) * 1960-05-05 1962-05-15 Eugene J Miller Differential torque equalizer
EP0380899A1 (fr) * 1988-02-15 1990-08-08 Christos Symbardis Transmissions donnant une gamme continue de rapports de vitesse
DE20103129U1 (de) * 2000-02-21 2001-05-03 Oberaigner, Wilhelm, Ing., Rohrbach Vorrichtung zur Veränderung der Drehzahl der angetriebenen Räder eines Kraftfahrzeuges
US6334832B1 (en) * 2000-05-31 2002-01-01 Warn Industries, Inc. Control for vehicle differential

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB620723A (en) * 1946-10-21 1949-03-29 Ewen Gordon M Ewen Improvements in or relating to differential gearing
US2533611A (en) * 1946-12-28 1950-12-12 Allis Chalmers Mfg Co Controlled differential transmission mechanism
FR1024532A (fr) * 1950-09-13 1953-04-02 Lyonnais Rochet Schneider Ets Dispositif de blocage progressif de différentiel
US3034322A (en) * 1960-05-05 1962-05-15 Eugene J Miller Differential torque equalizer
EP0380899A1 (fr) * 1988-02-15 1990-08-08 Christos Symbardis Transmissions donnant une gamme continue de rapports de vitesse
DE20103129U1 (de) * 2000-02-21 2001-05-03 Oberaigner, Wilhelm, Ing., Rohrbach Vorrichtung zur Veränderung der Drehzahl der angetriebenen Räder eines Kraftfahrzeuges
US6334832B1 (en) * 2000-05-31 2002-01-01 Warn Industries, Inc. Control for vehicle differential

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102619953A (zh) * 2012-03-27 2012-08-01 谢建武 四轮驱动油压智能偶合器

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