Abstract: Increased friction is generated in a parallel-axis gear differential by wedges 66 having respective bearing surfaces 68 and 70 for rotationally supporting outside diameter surfaces of a pair of planet gears 38 and 40. The wedges 66 react to bearing loads within a differential housing 10 by urging the planet gears 38 and 40 toward a condition of zero backlash with a pair of side gears 34 and 36.

Abstract: A traction control system combines engine output power limiting with a single point brake for controlling wheel slip. The brake is preferably connected to the engine to reduce torque requirements and avoid drive line shock. One friction member of the preferred brake is coupled to the engine block, and another friction member member is coupled together with a drive pulley to the engine output shaft. An electromagnetic actuator moves the two friction members into engagement with each other within a hollow interior of the drive pulley.

Abstract: A new gear mounting system for a parallel-axis gear differential includes three pedestals (14) that are spaced apart between an equal number of pairs of planet gears (32 and 34). Each of the pedestals includes two bearing surfaces (52 and 54) for rotationally supporting outside cylinder surfaces of the planet gear members (32 and 34) of adjacent pairs. Similar pedestals (74) can be made pivotable for increasing frictional resistance to differentiation.

Abstract: In the disclosed torque-proportioning type of automotive differential, a parallel-axis planetary gear arrangement interconnects the ends of a pair of coaxial drive axles. The axles are received, respectively, by a pair of sun/side gears having helical teeth and confronting end faces and being interconnected by planetary sets of combination gears. Each combination gear of each planetary set is provided with a narrowed shank portion intermediate two separate and distinct meshing portions in mesh with a respective one of the side gears and/or another combination gear of its respective planetary set. A washer component is positioned with its opposite sides in engagement with the confronting end faces of the side gears and is restrained from rotation by a plurality of radially-extending support regions positioned, respectively, between the shank portions of two combination gears of said planet gear sets.

Abstract: The preferred embodiments of the invention disclose an automotive torque-proportioning differential of the parallel-axis type having two planetary sets of either three or four combination gears in mesh with sun/side gears that receive respective vehicle axle ends. Each respective combination gear in each set is in meshing engagement with both (a) a respective one of the differential's two sun gears and (b) at least one other combination gear of its set. As compared with the planetary gearing of conventional differentials of similar size and torque-proportioning characteristics, the widely-separated sets of planetary gears occupy remarkably less interior space in the housing, permitting (i) the use of unconventionally large housing windows that significantly reduce the weight of the differential and greatly facilitate lubrication of the differential's gearing, and/or (ii) accommodation of C-clip assembly for the axle ends without increasing the exterior dimensions of the differential.

Abstract: Frictional resistance, resulting from end thrust developed by planetary gearing, is appreciably increased to improve control over torque bias characteristics in parallel-axis/torque-proportioning automotive differentials using an unusual planetary combination gear having a first toothed portion which meshes with one of the differential's sun/side gears and a second toothed portion which meshes with a paired combination gear, these first and second toothed portions being separated by a non-meshing portion that "straddles" (i.e., that provides clearance for avoiding contact with) the sun gear that is in mesh with its paired combination gear. In the most preferred embodiments, the second toothed portion of each combination gear is divided into two separate and distinct meshing areas located, respectively, at the gear's outer axial ends.

Abstract: A torque proportioning differential (10) is modified to vary bias ratio in three distinct stages in response to predetermined levels of drive torque. A pair of side gears (26 and 28) carried within a differential housing (12) generate respective thrust forces (44 and 46) that can be opposed by both high-friction gear mounting surfaces (68 and 70) and low-friction gear mounting surfaces (84 and 86). Outer disc springs (72 and 74) transmit a first portion of the thrust forces (44 and 46) to the low-friction gear mounting surfaces (84 and 86). Inner disc springs (64 and 66) transmit together with the outer disc springs (72 and 74) a second portion of the thrust forces (44 and 46) up to a second magnitude. Either the inner disc springs (64 and 66) or the outer disc springs (72 and 74) transmit the remaining portion of the thrust forces ( 44 and 46) above the second magnitude.

Abstract: A parallel-axis gear differential has pairs of top and bottom planet gears (38 and 40, 42 and 44, and 46 and 48) operatively connecting a pair of side gears (30 and 32). Each of the planet gears has a main gear section (74, 80) and a transfer gear section (76, 82) interconnected by a stem section (78, 84). Teeth (86 and 88) of the side gears (30 and 32) are separated through a clearance space (100) formed by a hub (98) of side gear (32). Within the clearance space (100), teeth (90 and 94) of the main planet gear sections (74 and 80) overlap the side gear teeth (86 and 88). Inner and outer ends (102 and 104) of the side gear teeth (86 and 88) are inclined at a chamfer angle (A) throughout a distance that extends between top and bottom lands (106 and 108) of the side gears.

Abstract: A parallel-axis gear differential includes pairs of element gears (34) mounted within pockets (36) formed in a differential housing (10). Each element gear includes a first gear section (38) for meshing with one of two side gears (30 or 32), a second gear section (40) for meshing with the first gear section of its mating element gear, and a stem section (42 ) for interconnecting the first two gear sections. Associated with each pair of pockets are two passageways (44, 46) for providing respective paths for the flow of lubrication fluid between the exterior of the housing and the respective meshing gear sections (38, 40) of each pair of element gears (34). The profile of the teeth of the element gears is modified with a chamfer-like shape (58) at the intersection of the profile and the top lands of the teeth, the chamfer-like shape making an angle of 10.degree.-30.degree. with the top lands.

Abstract: Frictional resistance, resulting from end thrust developed by planetary gearing, is appreciably increased in parallel-axis/torque-proportioning types of automotive differentials to improve torque bias characteristics. A pair of sun gears receive, respectively, the ends of coaxial drive axles, and the sun gears are interconnected by at least one planetary pair of combination gears positioned in the housing circumferentially around the sun gears. Each combination gear of the pair has a first engagement portion that is in mesh with a respective one of the sun gears, and each also has a second engagement portion that is in mesh with its paired combination gear.

Abstract: A parallel-axis gear differential includes pairs of element gears (34) mounted within pockets (36) formed in a differential housing (10). Each element gear includes a first gear section (38) for meshing with one of two side gears (30 or 32), a second gear section (40) for meshing with the first gear section of its mating element gear, and a stem section (42) for interconnecting the first two gear sections. Associated with each pair of pockets are two passageways (44, 46) for providing respective paths for the flow of lubrication fluid between the exterior of the housing and the respective meshing gear sections (38, 40) of each pair of element gears (34). Further, the shape of each pair of pockets (36) is modified between its apron portions (a) and its opening (b) to increase the space between the pocket and the mating surfaces of the element gears.

Abstract: A parallel-axis gear differential includes pairs of combination gears (66 and 68) mounted within pockets (76 and 78) formed in a differential housing (10, 12). Each combination gear includes a first gear section (70) for meshing with one of two side gears (58 or 60), a second gear section (72) for meshing with the first gear section of its mating combination gear, and a stem section (74) interconnecting the first two gear sections. Each pocket includes two bearing portions (84 and 86) for rotationally supporting the gear sections (70 and 72) and an intermediate portion (88) providing clearance for the stem sections (74). Windows (90) are formed through an exterior (92, 94) of the housing as passageways connecting the exterior of the housing to the intermediate portions (88). A spacing block (50) separates the side gears (58 and 60) through a distance approximately equal to an amount of overlap between the stem sections (74 ) of the combination gear pairs.

Abstract: A parallel-axis gear differential (10) includes a planetary gearing assembly of sun gears (22 and 24) and planet gears (26, 28, 30, 32, 34, and 36) carried within a housing (12). The planet gears (26, 28, 30, 32, 34, and 36), which are mounted in pairs within pockets (38, 40, 42, 44, 46, and 48) formed in the housing (12), include a first point of meshing engagement (74, 76) with one of the side gears (22, 24) and second and third points of meshing engagement (78 and 80) with a paired planet gear. A radial load component "Ws1" at the first point of engagement (74, 76) is adjusted with respect to a combined radial load component "Ws2" of the second and third points of engagement (78 and 80) for maintaining the planet gears (26, 28, 30, 32, 34, and 36) in their proper running positions within pockets (38, 40, 42, 44, 46, and 48).

Abstract: Frictional effects at different gear mounting surfaces within a differential are varied to control bias ratio. The gearing arrangement includes side gears respectively coupled to axle ends and element gears which transfer and divide torque between the side gears. Coefficients of friction at end faces of the element gears are varied between different element gears to control overall bias ratio while minimizing the effect of changes in overall bias ratio on an inherent bias ratio imbalance between opposite directions of differentiation. Helical gear portions are formed at the ends of the element gears to better balance thrust forces acting on different element gears.

Abstract: A warning system alerts a driver of a motor vehicle to different types of traction losses. A first sensing circuit (10) detects a loss of wheel adhesion by monitoring a vehicle drive line for a pronounced vibration within a range of between ten and fifteen hertz. A second sensing circuit (12) monitors a brake light circuit to detect application of a vehicle brake. A logic circuit (28) combines outputs (A and B) from the first and second sensing circuits and outputs command signals (C and D) that distinguish between a loss of wheel adhesion due to wheel skidding and a loss of wheel adhesion due to wheel slipping. A warning device includes two indicators (36 and 38) that receive the respective command signals and produce sensorially distinguishable warning signals for eliciting different responses from the driver.

Abstract: A traction control system includes speed sensors (36, 38) associated with a pair of drive wheels (14, 16) for monitoring a vehicle drive train for a pronounced vibration indicative of wheel slip and other speed sensors (40, 42) associated with a pair of non-driving wheels (18, 20) for monitoring vehicle speed. An electronic control unit (52) compares a magnitude of the vibration to a threshold duration that varies with vehicle speed for detecting wheel slip and outputs two command signals for controlling restriction of a differential (24) and a position of engine throttle (32). Differential restriction is increased as a function of a duration of the vibration and decreased as a function of vehicle speed. Engine output power is decreased as a function of a difference between the duration of the vibration and a threshold duration that decreases with increases in vehicle speed.

Abstract: A gear differential having multiple gear trains interconnecting a pair of output shafts is provided with an arrangement of gearing having an expanded relationship between tooth numbers of the gearing for fitting the gear trains into mesh. The gearing includes two side gears (20 and 21) coupled to respective output shafts and three pairs of combination gears (24 and 25, 26 and 27, and 28 and 29) for interconnecting the two side gears. Each of the combination gears includes a middle gear portion (40) and two end gear portions (42 and 44). The middle and end gear portions have respective numbers of teeth that share a greatest common factor (GCF) that is more than one but less than the number of teeth in the middle gear portion.

Abstract: Frictional resistance is appreciably increased in parallel-axis/torque-proportioning types of automotive differentials to improve torque bias characteristics. A pair of sun gears receive, respectively, the ends of coaxial drive axles, and the sun gears are interconnected by at least one planetary pair of combination gears positioned in the housing circumferentially around the sun gears. Each combination gear of the pair has a first engagement portion that is in mesh with a respective one of the sun gears, and each also has a second engagement portion that is in mesh with its paired combination gear.

Abstract: In the disclosed torque-proportioning type of automotive differential, a parallel-axis planetary gear arrangement is carried within a housing rotatable about a pair of drive axles. A pair of sun/side gears receive, respectively, the ends of the coaxial drive axles. The side gears are interconnected by at least one planetary pair of combination gears. Each combination gear of the pair is in mesh with a respective one of the side gears, and each shares two separate and distinct meshing portions with its paired combination gear. For each combination gear, the two meshing portions shared with its paired gear straddle the portion of the gear which meshes with its respective side gear. In the preferred embodiments, the shared mesh portions are located at the two axial outer ends of the combination gears.

Abstract: The disclosure concerns an improvement for an automotive differential having helical-worm side gears operatively connected through one or more pairs of combination gears, each combination gear having a worm-wheel portion which meshes with one or the other of the side gears and a spur-gear portion which meshes with its paired combination gear. The improvement is a cylindrical mounting arrangement for one or more of the combination gears. Preferably, a cylindrical surface on a mounting washer mates with a cooperating cylindrical surface formed in the differential housing to permit slight positional-adjustment movements of the combination gear, such adjustment movements being limited to a plane perpendicular to the axis of the side gear with which the combination gear is associated.