WO2005019687A2 - Systeme de differentiel a commande de lacet - Google Patents

Systeme de differentiel a commande de lacet Download PDF

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Publication number
WO2005019687A2
WO2005019687A2 PCT/US2004/026933 US2004026933W WO2005019687A2 WO 2005019687 A2 WO2005019687 A2 WO 2005019687A2 US 2004026933 W US2004026933 W US 2004026933W WO 2005019687 A2 WO2005019687 A2 WO 2005019687A2
Authority
WO
WIPO (PCT)
Prior art keywords
torque
axle
component
vehicle
operably connected
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/US2004/026933
Other languages
English (en)
Other versions
WO2005019687A3 (fr
Inventor
Frank A. Folino
John M. Mcclelland
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SYNKINETICS Inc
Original Assignee
SYNKINETICS Inc
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 SYNKINETICS Inc filed Critical SYNKINETICS Inc
Publication of WO2005019687A2 publication Critical patent/WO2005019687A2/fr
Publication of WO2005019687A3 publication Critical patent/WO2005019687A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H48/20—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
    • F16H48/06—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
    • F16H48/12—Differential gearings without gears having orbital motion
    • F16H48/16—Differential gearings without gears having orbital motion with freewheels
    • 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
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • 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

Definitions

  • the present invention relates to mechanical power vehicular differentials, and more particularly, to a system for applying bias torque to drive wheels to correct for the undesirable yaw of a vehicle to enhance vehicle stability and control.
  • the differential applies power as needed to the wheels while they rotate at different speeds on curves.
  • the difference in speeds is necessary because the outer wheels must travel both farther and faster than the inner wheels when the vehicle is going around a turn. This could not occur if the two wheels were rigidly attached to a solid axle.
  • the differential applies to all types of drives, such as front wheel, rear wheel and all wheel drives.
  • this description deals primarily to rear wheel drive vehicles.
  • the two front wheels present no problem, as each is mounted on its own spindle and rotate independently.
  • the rear wheels drive the car, and they must be attached to a strong axle supplying torque from the engine.
  • the rear axle therefore, is in two pieces connected through the differential.
  • the differential works similar to planetary gears, for, depending on need, some gears will move slower or faster than others or even remain stationary.
  • the system turns the wheel that is easiest to turn.
  • the present invention is a yaw control differential system which incorporates standard differential components adapted to cooperate with a speed (or torque) converter that reduces the axle rotation or alternatively increases driving torque for rear wheel, front wheel and all wheel drive systems .
  • a reaction force equivalent to the increased amount of torque is directed to the axle as a braking force and varying the lateral distribution of driving torque between the two axles.
  • the present invention applies the torque biasing directly at the torque transfer location of the differential directly onto the vehicles axles. Thereby, splitting and varying driving torque unequally between the left and right wheels when cornering or when tire slippage is sensed. By applying the torque bias here, the effectiveness is increased and overall yaw correction time decreased.
  • the differential system of the present invention reduces or increases the speed of one axle coupled with the torque increase or reduction of that axle provides a bias torque between the two axles and produces a counter yaw moment to correct the undesirable yaw moment induced on a vehicle as it makes a turn.
  • the present invention responds instantaneously to an indication of a yaw moment to prevent the vehicle from reaching an unstable condition that could result in the vehicle going into an uncontrolled skid.
  • Figure 1 is side cross-sectional view of the differential system of the present invention illustrated the position of two single-stage nested torque converters, one per axle;
  • Figure 2A is a side cross-section view of one of the single-stage nested torque converters used with the present invention of FIG. 1;
  • Figure 2B is a partial cross-section view of one of the single-stage nested torque converter used with the present invention taken along line 2B-2B of FIG. 1; and
  • Figure 2C is a pictorial illustration of one of the single-stage nested torque converter used with the present invention of Fig. 1 showing a partial sectional view of the outer cam.
  • the differential system 8 of the present invention acts as a yaw control differential and includes a pair of independent single-stage nested torque converters 10 of the type described, but not limited to, the converters in U.S. Patent No. 5,989,145 entitled "In-line Speed Converter with Low Parts Count” assigned to the present assignee of this invention and which is incorporated by reference herein.
  • Torque converters (also referred to as SynkDrive Torque Converters) 10 operate a control system 200 to reduce or increase one of the pair of axles 104 rotational speed by increasing or reducing the torque supplied to such axle.
  • the control system 200 will actuate only one of the pair of single-stage nested torque converters 10 depending on the required speed reduction or increase of a predetermined axle 104.
  • torque converter is meant to refer to torque increaser or reducer, and is also used synonymously with rotational speed increaser or reducer.
  • components of differential system 8 also include, for example, housing 102, ring gear 124, differential gear casing 106, spider gear 122, two side gears 108, and two axles 104.
  • Input shaft 118 transmits torque load from the engine drive shaft (not shown) to the present invention 8.
  • the input pinion 118A meshes with ring gear 124, which reduces the input speed by a predetermined ratio, for example 3.73:1.
  • the ring gear 124 conveys the reduced speed at a 1:1 ratio to the axles 104 via the load path through the differential gear casing 106 to the spider gears 122 to the side gear 108.
  • the side gear 108 is coupled to the axles 104 by conventional joining means, such as a spine connection or a pressed fit.
  • the differential gear casing 106 includes features similar to those of a standard differential gear casing, such as spider gear support openings 107. Additionally, the differential gear casing 106 includes elements to interface and couple with the single-stage nested torque converter 10, such as a clutch face 114.
  • the differential gear casing clutch face 114 frictionally couples the single-stage nested torque converter 10 to the differential gear casing 106 when the single-stage nested torque converter 10 is engaged (discussed in detail below).
  • the differential gear casing 106 is referred to as the driving member with regards to the input torque of single-stage nested torque converter 10.
  • the differential system 8 via the differential gear casing 106 and mating components, provides the input torque to the single-stage nested torque converter 10.
  • the differential gear casing clutch face 114 is made of any suitable material that is durable and has a moderate to high coefficient of friction. Although a signal- stage torque converter is described, it may be possible to use multiple stage torque converters as well with the present invention. In addition, for simplicity, only a single stage torque converter is described in detail in operation, with the other operating in a similar manner.
  • bearings 116 are disposed between the housing 102 and the differential gear casing 106 and between the side gear 108 and the differential gear casing 106 to maintain the position of the differential gear casing 106 and side gear 108 under torsional loading conditions when the single-stage nested torque converter 10 is engaged.
  • the single-stage nested torque converter 10 can be fixedly connected, with for example, bolts, to the differential gear casing 106. [0022] Upon engagement of one of the single-stage nested torque converters 10, the torque is diverted through the single-stage nested torque converter 10 to the axle 104 instead of going through the spider gear 122. The speed is further reduced by the single-stage nested torque converter 10, for example 1.08:1, which results in lower speed/higher torque being transmitted to axle 104.
  • the control system 200 may be an independent system used with differential system 8 or considered part of the differential system 8.
  • Control system 200 includes, but is not limited to, a computer 201, a piston 202 (preferably part of differential system 8), piston actuator 203, and bearings 204 (preferably part of differential system 8).
  • the computer 201 includes several sensors such as a vehicle speed sensor, steering wheel position sensor, wheel speed sensors, lateral acceleration (g) sensor, and the engine rpm and torque sources (all not shown), which determines the driver's intention by such factors as steering input, vehicle speed, lateral acceleration, and engine performance, and controls driving torque distribution between the wheels .
  • the piston actuator 203 can be any conventional actuation system including hydraulic, pneumatic, or electronic.
  • the piston 202 is preferably incorporated within the housing 102, and includes a bearing race 206 to support bearing 204.
  • Alternative embodiments of the differential system 8 may include the piston 202 external to housing 102.
  • the bearing 204 interconnects the piston 202 with the retainer 21 of the single-stage nested torque converter 10. Therefore, any longitudinal displacement of the piston 202 results in the same longitudinal displacement of the retainer 21.
  • the retainer 21 includes a base 29 and an annular section 25 having a bearing race 24 along its inner diameter sufficient to seat bearing 204 (FIG. 1), which interconnects the piston 202 with the retainer 21.
  • the retainer 21 further includes a clutch face 26 attached to the retainer base 29.
  • the clutch face 26 is made of material compatible with physical characteristics of the differential interface plate clutch face 114 (FIG. 1), such as coefficient of friction and hardness .
  • FIG. 2B shows a partial cross-sectional view of the single-stage nested torque converter 10 taken along line 2B-2B of FIG. 2A. More specifically, FIG. 2B illustrates the nested components of the single-stage nested torque converter 10, including inner cam 18, retainer 21, and outer cam 27. Any of the three in-line or nested components can function as an input source or an output source or a grounded member. Holding any one of the three components stationary (grounded) results in the other two components forming the input source and output source.
  • the configuration illustrated in the figures and disclosed in detail below presents the outer cam 27 as the grounded member with the retainer 21 acting as the input source and the inner cam 18 acting as the output source. (See above referenced U.S. Patent Number 5,989,145, incorporated herein by reference, for a detailed disclosure of the nested component functional interaction.)
  • retainer 21 further includes rolling element slots 19 spatially disposed substantially evenly through the annular section 25.
  • rolling elements 22 shown here as rollers, but not limited thereto, such as the rolling elements 22 may be ball bearing, for example
  • rolling element slots 19 are located in rolling element slots 19.
  • Rolling elements 22 disposed between the three in-line components provide interdependency among the three components .
  • the inner cam 18 includes at least one bolt hole 36 to connect the single-stage nested torque converter 10 to axle 104 and a bore 38 to receive axle 104 (FIG. 1).
  • the inner cam 18 is bolted to the side gear 108, which in turn is coupled to the axle 104 by conventional means as discussed above.
  • Spacer 110 (shown in FIG. 1) illustrates an optional component to adjust for longitudinal variations of components in different models.
  • the inner cam 18 (See FIGS. 1 and 2A- 2C) can be connected directly to the axle 104 by conventional joining means, such as bolting or spline connection or pressed fit.
  • Another alternative embodiment of the present invention may include an inner cam embodiment include an integral inner cam/axle and integral inner cam/side gear interconnected via conventional joining means or machined from a single piece of metal.
  • the outer cam 27 is fixedly connected to the housing 102 as discussed above.
  • the preferred embodiment includes boltholes 41 to attach the outer cam 27 to the housing 102.
  • the fixed outer cam 27 acts as the grounded member in this embodiment that cooperates with the inner cam 18 and retainer 21 in reducing the axle speed (discussed in further detail below) .
  • input cam 18 has, for example, twenty-six lobes 30 formed on its outer diameter 32, while outer cam 27 has, for example, two lobes 28 formed on its inner diameter 34.
  • the number of lobes and slots may vary in accordance with the intended use or desired speed conversion ratio.
  • the retainer 21 rotates with a first input speed causing the rolling elements 22 to radially displaced in the retainer slots 19, which in turn interact with the lobes 28 of the outer cam 27 and lobes 30 of inner cam 18 to produce a second output speed of inner cam 18.
  • the torsional load path flows from the differential gear casting 106 through the differential interface plate clutch face 114 to the retainer clutch face 26 through the retainer 21 to the rolling elements 22 to the inner cam 18 to the side gear 108 to the axle 104. This action creates conjugate action between the inner and outer cams.
  • Patent Number 5,989,145 incorporated herein by reference, for a detailed disclosure of conjugate cams.
  • the present invention applies the torque biasing directly at the torque transfer location of the differential directly onto the vehicles axles. By applying the torque bias here, the effectiveness is increased and overall yaw correction time decreased.
  • Speed ratios are determined by the number of lobes 30 on the inner cam 18 versus the number of lobes 28 on the outer cam 27 and the number of rolling elements 22. As shown the example of in FIG. 2B and discussed above, there are twenty-four lobes on the inner cam 18 and two lobes 28 on the outer cam 27 with twenty-six rolling elements 22. There are many speed ratios possible for the configuration of inner cam 18, outer cam 27, and rolling elements 22. The present invention can provide a percentage of speed reduction or speed increase less than 10% for yaw control, where greater percentages tend to over-correct the undesirable yaw moment.
  • Table 1 [0035] Now returning the FIG. 1, the process of introducing a torque bias into the differential system 8 when used in a vehicle (not shown) is initiated by the control system 200.
  • the computer 201 determines which axle 104 requires torque conversion to induce a counter yaw moment to the vehicle.
  • the computer 201 generates a signal to the piston actuator 203 to actuate one of the two pistons 202, which traverses longitudinally along a parallel axis with respect to axle 104 for a predetermined displacement. Since piston 202 is interconnected to the retainer 21 through bearing 204, the retainer 21 traverses longitudinally the same predetermined displacement as the piston 202 until the retainer clutch face 26 of retainer 21 contacts differential interface plate clutch face 114.
  • the actuation of the piston 202 from an idle (unengaged) to fully deployed (engaged) state can occur, for example, in milli-seconds after the generation of the signal from computer 201.
  • Conventional Anti-lock Braking Systems employ hydraulic pressure to communication the signal to the wheels to engage for countering the yaw moment, which can take tenths of a second.
  • ABS anti-lock braking systems
  • the reaction time of the present invention is measured in 10 's of milliseconds compare to 100 's of milliseconds for conventional yaw control braking systems.
  • ABS braking systems do not respond as quickly as the present invention to create the desired counter yaw. This is due to the static or grounded state of the ABS system.
  • the ABS system is modulated on the wheel to create a speed reduction. Since the ABS system is grounded (no rotation relative to the axle or wheel), the wheel speed must be reduced relative to the zero speed of the ABS system, which takes a finite period of time depending on the rotational speed of the wheel or axle.
  • the single-stage nested torque converter 10 only requires sufficient reduction in the differential component rotational speed to couple housing 102 to the single-stage nested torque converter 10 rotating at about the same rotational speed.
  • the time difference between complete rotational speed stoppage of the differential components (ABS braking system) and only a speed reduction of the differential components (single-stage nested torque converter 10) can be significant in terms of responding to an emergency situation.
  • the torsional load path of torque from the input shaft 118 to the axle 104 changes.
  • the torque load now travels through the single-stage nested torque converter 10 instead of spider gears 122.
  • the effect is a modified torque based on a predetermined increase or decrease of torque dependent on the number of lobes 30 of the inner cam 18, number of lobes 28 of the outer cam 27, and the number of rolling elements 22.
  • An example of a modified torque includes the increased torque to one of the axles 104 causes that wheel to rotate at a reduced rotational speed than the other wheel, and induces a counter active yaw moment.

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

Abstract

La présente invention a trait à un système permettant la correction de lacet indésirable d'un véhicule comportant un convertisseur de couple (ou de vitesse) adapté à un différentiel classique. Le convertisseur de couple réduit la rotation de l'essieu ou de manière alternative accroît le couple d'entraînement pour des systèmes de traction arrière, avant et intégrale. Le convertisseur de couple comporte une came interne, un arrêtoir, et une came externe. Un système d'interface piston/embrayage engage le convertisseur de couple avec le couple d'entraînement de répartition et de variation du différentiel de manière non uniforme entre les roues de gauche et de droite lors de la détection de prise de virage ou de glissement. Un système informatique actionne un piston de manière instantanée vers une indication d'un moment de lacet pour interdire une condition d'instabilité du véhicule qui pourrait entraîner un dérapage incontrôlé du véhicule. Une force de réaction équivalente à la quantité de couple accrue est orientée vers l'essieu sous la forme d'une force de freinage et de répartition latérale de couple d'entraînement entre les deux essieux.
PCT/US2004/026933 2003-08-20 2004-08-20 Systeme de differentiel a commande de lacet Ceased WO2005019687A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US49647203P 2003-08-20 2003-08-20
US60/496,472 2003-08-20

Publications (2)

Publication Number Publication Date
WO2005019687A2 true WO2005019687A2 (fr) 2005-03-03
WO2005019687A3 WO2005019687A3 (fr) 2005-08-11

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PCT/US2004/026933 Ceased WO2005019687A2 (fr) 2003-08-20 2004-08-20 Systeme de differentiel a commande de lacet

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130166151A9 (en) * 2006-02-15 2013-06-27 Stephan Stabrey Travel direction stabilization system for vehicles
DE102024117936A1 (de) * 2024-06-25 2026-01-08 Schaeffler Technologies AG & Co. KG Betätigungsvorrichtung zur Betätigung einer Reibungskupplung und Differential für Kraftfahrzeug

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3268124B2 (ja) * 1994-06-27 2002-03-25 富士重工業株式会社 車両のトルク配分制御装置
US5655983A (en) * 1995-04-28 1997-08-12 Dana Corporation Hydromechanical system for limiting differential speed between differentially rotating members
US6024182A (en) * 1995-09-11 2000-02-15 Honda Giken Kogyo Kabushiki Kaisha Coupling device between left and right wheels of vehicle
DE19607185A1 (de) * 1996-02-27 1997-08-28 Bayerische Motoren Werke Ag Verfahren zur Sicherstellung eines neutralen Fahrverhaltens bei Kurvenfahrten und gleichzeitigem Lastwechsel
US5989145A (en) * 1998-01-30 1999-11-23 Synkinetics, Inc. In-line speed converter with low parts counts
JP3656502B2 (ja) * 2000-02-28 2005-06-08 豊田工機株式会社 ４輪駆動車のトルク配分装置
KR100628575B1 (ko) * 2001-07-13 2006-09-26 가부시키가이샤 제이텍트 일방향 클러치

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130166151A9 (en) * 2006-02-15 2013-06-27 Stephan Stabrey Travel direction stabilization system for vehicles
US8958953B2 (en) * 2006-02-15 2015-02-17 Robert Bosch Gmbh Travel direction stabilization system for vehicles
DE102024117936A1 (de) * 2024-06-25 2026-01-08 Schaeffler Technologies AG & Co. KG Betätigungsvorrichtung zur Betätigung einer Reibungskupplung und Differential für Kraftfahrzeug

Also Published As

Publication number Publication date
WO2005019687A3 (fr) 2005-08-11

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