USRE26978E - Accessory drive mechanism - Google Patents

Description

Nov. 17, 1970 L. o. HEWKO ACCESSORY DRIVE MECHANISM 2 Sheets-Sheet 1 Original Filed Nov. 27. 1964 INVENTOR. ,CZ/bonyr (2 #2111623 BY gull. 1477M ATTORNFY Nov. 17, 1970 L. O. HEWKO ACCESSORY DRIVE MECHANISM Original Filed NOV. 27- 1964 2 Sheets-Sheet 2 IN VENI'UR 10/60/711" (9 Mal/37 BY I United States Patent 0 26,978 ACCESSORY DRIVE MECHANISM Lubomyr 0. Hewko, Port Clinton, Ohio, assignor to General Motors Corporation, Detroit, Mich., a corporation of Delaware Original No. 3,327,566, dated June 27, 1967, Ser. No. 414,064, Nov. 27, 1964. Application for reissue June 20, 1969, Ser. No. 835,915

Int. Cl. F16c 33/38; Fl6h 13/08, 13/14 U.S. C]. 74-798 10 Claims Matter enclosed in heavy brackets appears in the original patent but forms no part of this reissue specification; matter printed in italics indicates the additions made by reissue.

ABSTRACT OF THE DISCLOSURE between the oppositely disposed spherical surfaces, the

radius of the spherical surfaces may be the same or slightly greater than the radius of the ball planets; a rotatable ring in frictional contact with the ball planets; and an output member secured to the rotatable ring.

This invention relates to an accessory drive mechanism and more particularly to an overdrive structure particularly adapted for driving engine-driven accessories such as generators or alternators commonly used on automotive vehicles.

Engine-drivcn accessories such as generators, alternators and air conditioning compressors are normally driven from the vehicle engines by means of belts and pulleys. In such drive arrangements the pulley diameters may be selected to provide overdrive of engine-driven accessories with respect to engine speed. However, the practical overdrive ratio obtainable is limited due to the relationship between the pulley size and belt life. It is desired to provide an overall step-up ratio between the engine crankshaft and the alternator of 3.6 to 1. This ratio exceeds the practical capabilities of pulley-belt drives in present day automotive vehicles wherein the engines may be operated through a Wide speed range. for example, 500 r.p.m. at idle to a maximum speed of 5000 r.p.m. With a simple belt-pulley arrangement selected to provide a 3.6 to 1 overdrive ratio, belt life is very short and inadequate. While step-up gearing might be employed, such gear type step-up units are not suitable due to objectionable noise at the relatively high speeds involved.

The proposed drive structure herein disclosed provides efficient, quiet and vibration-free overdrive of a generator at a step-up ratio of the order of 3.6 to l and in addition provides for improvement in normal belt life. In order to increase belt life a portion of the desired ratio step-up is accomplished by a planetary friction drive and a second portion of the step-up is provided by the belt and pulleys. In this manner, normal belt life is increased. For example, a total overdrive ratio of 3.6 to l is accomplished by utilizing a 1.6 to 1 step-up planetary traction drive and the remaining 2.25 to l stcp-up is provided by conventional all] Re. 26,978 Reissuecl Nov. 17, 1970 V-belt running on 7.18-inch diameter and 3.18-inch diameter pulleys. With this arrangement, at 500 r.p.m. engine idling speed, the alternator speed is raised from 1150 to 1800 rpm. and its output is increased from approximately 9 amps to 29 amps. At 5000 engine rpm. the alternator speed is 18,000 r.p.m. which is within its permissible speed limit. It will readily be apparent that with the speeds involved that noise is a very important consideration which eliminates the use of simple step-up gearing.

The proposed friction drive structures herein disclosed are of simple structure, are adapted for use in installations where space requirements are critical, are inexpensive to manufacture, are capable of long useful life, and are quiet in operation.

An object of this invention is to provide an accessory drive for driving the accessories of an engine-driven vehicle wherein the accessories are driven at overdrive with respect to engine speed by means including a belt driven friction drive mechanism arranged such that one portion of the final overdrive ratio is obtained by belt drive and driven pulleys and a second portion by means of a friction drive transmission to assure long normal belt life and to provide adequate overall step-up of the accessory speed relative to engine speed to render the accessories more eflicient particularly at relatively low engine speeds.

Another object of the invention is to provide a belt driven accessory drive system wherein one of the belt pulleys rotates as a unit with a carrier of a friction drive transmission to drive the carrier and wherein a ball roller driven by the carrier drives a ring output member at overdrive ratio with respect to speed of rotation of the pulley and carrier.

A further object of this invention is to provide an accessory drive mechanism of the type described including a friction drive assembly including a fixed support housing provided with an axially extending nonrotatable support sleeve, an engine-driven input member including a carrier, bearing means supporting said input member and carrier for rotation on the external surface of the support sleeve, a rotatable ring, spaced reaction suns on the external surface of the sleeve and fixed against rotation by the sleeve, a ball driven by the carrier and contacting said suns and ring, a final power delivery shaft extending through the hollow ground sleeve and a connector connecting the ring to the final power delivery shaft extending into the fixed support sleeve between the final power delivery shaft and the internal surface of said support sleeve for driving said final power delivery shaft.

A still further object of the invention is to provide a power transmitting mechanism wherein the carrier member includes equally spaced axial notches for the insertion of bearing inserts having opposed spherical surfaces for receiving ball planets, the spherical surfaces of the inserts having a slightly larger radius than that of the balls, providing a wedged opening therebetween whereby lubricant in the wedged opening can lift the ball planets for full hydrodynamic spherical bearing lubrication.

An additional object of this invention is to provide an [acessory] accessory drive mechanism of the type described wherein the friction rollcr, ring and connector cooperate to support the power delivery shaft to eliminate the need for providing a power delivery shaft bearing in addition to the bearing for supporting the planet carrier.

These and other objects and advantages of this invention will be apparent from the following description and claims, taken in conjunction with the following drawings, in which:

FIG. 1 is a diagrammatic side view of a vehicle engine equipped with an accessory and belt drive mechanism constructed in accordance with the principles of this invention.

FIG. 2 is an axial section through the friction roller overdrive mechanism.

FIG. 3 is a sectional view taken along the line 3-3 of FIG. 2.

FIG. 4 is a sectional view taken along the line 4-4 of FIG. 2.

FIG. 5 is a fragmentary side view of an alternate carrier construction which may be substituted for the carrier of FIG. 3.

FIG. 6 is a partially sectional view illustrating the contact geometry of the basic drive between the roller and sun and roller and ring as each being of concave profile.

FIG. 7 is a sectional view of an alternate construction wherein the friction contact roller functions both to drive the ring and as a roller bearing to support the power delivery shaft.

FIG. 8 is a sectional view taken along the line FIG. 7.

FIG. 9 is a sectional view of an alternate friction drive arrangement wherein two contacts are provided between the planet and sun and between the planet and ring.

FIG. 10 is a partially sectional view of an arrangement similar to FIG. 9 in that it provides four rolling contacts per planet and in addition illustrates the ring split into two halves with the normal load applied by a suitable axial spring.

FIG. 11 is a partially sectional view of an arrangement wherein the ring has two contacts and the sun at single contact with the planet.

FIG. 12 is a partially sectional view wherein there is only a single contact between the planet and sun and planet and ring and the geometry very closely resembles a radial ball hearing.

In FIG. 1 there is shown an engine 10 and an alternator 14. A crankshaft driven pulley 11 [dirves] drives an alternator pulley 12 by means of a belt 13. As heretofore stated, the pulley diameters are selected to provide a step-up belt drive of 2.25 to 1 in order to maintain the pulley diameters within a range wherein long belt life is possible.

As best shown in FIG. 2, a ball friction roller drive indicated generally at 15 provides an overdrive ratio of 1.6 to 1 between pulley 12 and an alternator input shaft 40. An alternator support housing 16 is provided with a machined surface 17 to which is attached a reaction shaft 18 provided with a machine surface 19 matching surface 17. Bolts 20 maintain the shaft 18 and housing 16 in assembled relationship. Reaction shaft 18 supports the friction drive, carries the reaction force to housing 16 and supports the belt force. Pulley 12 serves both as the housing for the drive assembly and the carrier for the planetary friction drive and is the power input member for the planetary friction drive. A radial ball bearing 21 disposed between outer and inner races 21a and 21b supports pulley 12 for rotation or reaction shaft 18. Pulley 12 has formed integrally therewith a planet carrier 23 extending axially therefrom to receive four balls or planets 24. As best shown in FIG. 3, carrier 23 has formed therein hydrodynamic journal bearing surfaces 25 for receiving balls 24. As shown in FIG. [2] 3 these surfaces 25 are [semicircular] spherical to conform to the spherical surfaces of the balls. The surfaces 25 may, however, be of other than spherical configuration as hereafter set forth. Rollers 24 contact a pair of spaced suns 26 and 27 and a ring 28. Sun 26 is fixed to reaction shaft 18 so as to be incapable of rotation or axial motion and may be pressfitted upon shaft 18. Sun 27 is capable of axial motion but is incapable of rotation with respect to shaft 18. Sun 27 is grounded to reaction shaft 18 by means of a Belleville spring 29.

As best shown in FIG. 4, a pair of axially extending tangs or cars 30 on sun 27 extend into spaced slots 31 formed in Belleville spring 29. Belleville spring 29 is provided with four tangs or ears 32 which extend into spaced radial slots 33 formed in shaft 18. In this manner, Belleville spring transmits reaction torque from sun 27 to reaction shaft 18. Referring again to FIG. 2, a spacer 34 disposed between spring 29 and a snap ring 35 serves as a means for producing proper axial deflection of spring 29 when the spring is assembled to shaft 18. The thickness of spacer 34 is chosen to produce adequate normal load and consequently adequate torque capacity of the drive to withstand the maximum expected torque to be transmitted. A spacer 36 disposed between an upstanding flange 37 on shaft 18 and race [22] 21b and a spacer 38 disposed between race 21b and sun 26 insure proper axial [alignment] spacing of the parts. Ring 28, which is the power delivery member of the roller drive assembly is connected to an alternator drive shaft 40 by means of a drive flange 39. Drive flange 39 includes an car 41 adapted to contact a slot 42 on ring 28 and a threaded cylindrical portion 43 adapted to contact an unthreaded cylindrical sleeve spacer 44 having a radially [extended] extending flange 45 formed on the end thereof. A ball bearing 46 is disposed between alternator housing 16, and shaft 40, the race 47 supporting both the reaction shaft 18 and housing 16 and the race 48 contacting power input shaft 40. A shaft seal 49 contacts the outer surface of cylindrical sleeve spacer 44. A face seal 50 is retained against race 21a of bearing 21 adjacent spacer [38] 36 by a snap ring 51 carried by pulley 12. It will be apparent that drive flange 39 is simply and easily assembled to the unit by rotating the flange relative to shaft 40 until flange 45 contacts bearing race 48. A seal 52 is disposed between a cover 53 and pulley 12. Cover 53 is retained upon pulley 12 by means of a bent-in rim 54 which extends into an annular groove 55 in pulley 12. When assembled, lubricating oil is disposed in chamber 56 enclosed by the pulley and cover. A fan 57 supported on pulley 12 provides cooling for the alternator.

[A] As stated, suns 26 and 27 are prevented from rotation. The reaction torque is split between suns 26 and 27 with one-half carried by each sun. Belleville spring 29 functions both to transmit the reaction torque from sun 27 to reaction shaft 18 and to axially load the two suns toward each other in order to generate normal loads at the sun-planet and ring-planet contacts. The normal load when multiplied by the coefficient of traction and the radius at which it is acting, produces usable torque forces whereby ring 28 is driven. [Semicircular] The spherical openings or surfaces 25 are machined in the carrier 23 and constitute journal surfaces for the ball planets 24. The halls, while rotating about their own centerline, generate a hydrodynamic film of oil between their outside surfaces and the carrier surface 25 capable of supporting the tangential torque force with a minimum of wear and power losses.

As heretofore stated, the surfaces 25 of carrier 23 are [semicircular] spherical in shape and are machined on the carrier. The shape of these surfaces may be modified and may consist of inserts rather than being machined on the carrier itself. In FIG. 5, carrier 23 is shown as having notches 58 formed therein [and adapted to receive] having facing flat or pla'nar parallel side walls providing bearing surfaces for the flat back faces of the bearing inserts 59. Inserts 59 are provided with spherical surfaces 60 which [conform more closely to] cooperate with the outer spherical surface of the ball planets 24 and produce better hydrodynamic load capacity. Here a spherical partial hydrodynamic bearing is generated by machining a spherical seat 60 inside the insert 59. As indicated by the arrows, the radius of the seat is larger than the radius of the ball planet. This geometry generates a wedge action between the ball planet and the seat 60. When oil is trapped in the wedge portion it tends to lift the ball slightly off the centers of the bearing inserts 59 with a relatively high force. The contact geometry of the basic drive is best ShOWn in FIG. 6 wherein the sun rolling surface and ring rolling surface are both concave. However, it is possible to use straight or convex rolling surfaces, if advantageous. The ring rolling surface illustrated as of concave profile might be of straight cylindrical shape.

In operation, pulley 12 is driven by V-belt 13 from crankshaft pulley 11 of FIG. 1 and at a speed greater than crankshaft speed. In order to preserve belt life, the stepup provided by the pulleys is of the order of 2.25 to one. Carrier 23 driven at the speed of rotation of pulley 12 applies a torque force to the ball planets 24 through the partial journal bearing surfaces 25. Suns 26, 27 being fixed to reaction shaft 18 form the reaction surface for ball planets 24, causing the balls to rotate about the suns. This, in turn, causes ring 28 to rotate at an increased speed and in the same direction as pulley 12. Ring 39 drives the alternator input shaft 40 at a ratio of 1.6 times the speed of rotation of pulley 12, such that the shaft 18 is driven at a speed 3.6 times that of pulley 11.

In FIG. 7 there is shown a simplified roller friction drive assembly of more compact nature than those heretofore described. In this figure a double pulley is welded to a cover 71, the cover 71 having bent-over tabs 72 for gripping the planet carrier 73. A reaction shaft 74 splined to alternator housing 75 carries a roller bearing 76 having an outer race 77 contacting carrier 73 and an inner race 78 contacting reaction shaft 74. A seal 79 prevents leakage of oil from a chamber 80 enclosed by cover 71. Race 78 contacts a shoulder 81 on shaft 74 and a spacer 82. Six ball planet rollers 83 contact spaced suns 84 and 85 and a ring 86. Sun 84 is press-fitted on reaction shaft 74 and sun 85 is connected to reaction shaft 74 by means of Belleville spring 87.

As best seen in FIG. 8, Belleville spring 87 is provided with spaced notches 88 adapted to receive ears 89 on sun 85 (shown in FIG. 7) and has bent-over tangs 90 disposed in [semispherical] spherical seats 91 formed in reaction shaft 74.

The operation is the same as that previously described, but the structure is more compact. Belleville spring 87 is of simplified construction and the design eliminates the spacer 34 and snap ring 35 of FIG. 2. Belleville spring 87 is simply snapped into place on shaft 74 and requires no additional means of axial or torsional fastening. Another improvement consists in the elimination of the principal alternator bearing 46 of FIG. 2. In the FIG. 7 embodimentlIs] the friction drive is further modified 80 as to function as a radial support for the alternator power input shaft 93. This is accomplished by providing a pilot diameter 94 between the output flange 92 and the outer diameter of friction drive ring 86. When flange 92 is threaded upon power delivery shaft 93, the annular axially extending boss portion or pilot diameter 94 on flange 92 mates with the outer surface of ring 86 such that the planetary rollers 8-3 support one end of shaft 93 through suns 84, 85 and reaction shaft 74. Deletion of the conventional alternator bearing 46 of FIG. 2 results in considerable cost saving and structural simplification. Belt forces are transmitted to housing 75 through reaction shaft 74. In the embodiment of FIG. 7, six planet balls 83 may be employed if desired. Further, in FIG. 7, a fan 95 is driven by pulley 70. Fan 95 may be disposed within housing 75 and driven by shaft 93 rather than by the pulley 70. Such an arrangement is advantageous in that the fan would then rotate at the output speed of the friction drive unit rather than its input speed.

It has heretofore been explained that the contact profiles of the carrier may be modified to different shapes. In addition the contact arrangements may be varied as shown in FIGS. 9 through 12.

In FIG. 9 a power input carrier causes ball planets 101 to travel around sun 102 fixed to reaction shaft 103 to drive ring 104. In this arrangement there are provided two contacts between the ball planet 101 and sun 102 and two contacts between ball planet 101 and ring 104. This arrangement increases the axial stiffness of the drive. The required normal load between the rolling bodies is generated by interference fit between the three rolling bodies.

6 The flexibility of the various members is effectively utilized as a loading spring.

FIG. 10 shows an additional arrangement having four rolling contacts per planet. Herein the ring 109 is divided into two halves 107 and 108 with the ring portion 107 keyed to portion [109] 108 for axial movement with respect thereto. A Belleville spring 110 seated upon a snap ring 111 provides proper normal loading of the rolling members. Sun 106 is prevented from rotation by a reaction shaft 112. Carrier 105 is the input and ring 109 the power delivery member. This design does not depend upon dimensional interference fit for loading, but uses the separate, preferably flat rate spring 110.

FIG. 11 shows a further contact arrangement wherein the ball planet 113 has two contacts with ring 114 and a single contact with sun 115. The normal loading of the rolling bodies is again accomplished by interference fit using the elasticity of the rolling elements as a spring. Sun 115 is held against rotation by a reaction shaft 116, carrier [112] 112 is input, and ring 114 the output of the assembly.

In FIG. 12 there is only one contact between the ball planet 121 and sun 118 and one contact between the ball 121 and ring 120. The geometry closely resembles a radial ball bearing. Here, again, the normal load in the contact is generated by dimensional interference of the rolling members. Sun 118 is held against rotation by reaction shaft 119, carrier 117 is the input, and ring 120 the output of the unit.

It will readily be understood that the carriers of FIGS. 9 through 12 will be belt-driven and the rings connected to an alternator input shaft (not shown) as described in FIGS. 2 and 7.

Depending upon applications, each of the suggested arrangements has its own advantages. The fixed preload or interference preload arrangements are best suited for drive applications where the drive is required to operate at predominantly constant load. The spring preload arrangement having split sun or split ring is best suited where dimensional accuracy cannot be maintained, thus providing the required contact normal loads with relatively liberal manufacturing tolerance.

There has thus been provided a simple compact and inexpensive overdrive assembly particularly designed for driving an alternator of the type commonly used in automotive vehicles. The axial load required to transmit the peak torque of 36 inch pounds is relatively low. resulting in small loss of etficiency and long useful life. The drive provides a normal step-up of alternator speed which is quiet and vibration-free at all speeds due to the uninterrupted action of the rolling contacts and the continuous balance of all radial and axial force vectors between rolling bodies. In addition to displaying an absence of exciting forces, the traction drives behave dynamically as a staff viscous damper. This characteristic is of great benefit in applications containing objectionable natural vibration frequencies within their operating speed range, since the need for vibration dampeners is eliminated. The application is ideal for engine-driven alternators where quiet operation is essential and belt life is preserved by reducing the step-up provided by the belt and by supplying a portion of the step-up through the friction drive assembly.

What is claimed is:

1. Power transmitting mechanism comprising a nonrotatable housing, a hollow sleeve shaft fixed to said housing, a power input carrier, a bearing supporting said carrier on said sleeve shaft for rotation with respect to said shaft, a first sun carried by said shaft and fixed against movement with respect to said shaft, a second sun carried by said shaft and axially movable with respect thereto, means connecting said second sun to said sleeve shaft comprising a Belleville washer, said washer preventing rotation of said second sun and effective to bias said second sun axially toward said first sun, a ring spaced from said suns, said carrier extending into the space hetween said suns and ring, spaced surfaces on said carrier for receiving ball rollers, a torque transmitting ball disposed in the space between each of said spaced surfaces of said carrier and in nonslipping friction engagement with said ring and suns, a power delivery shaft extending through said hollow sleeve shaft, a bearing between said housing and power delivery shaft, and means connecting said ring to said power delivery shaft. said torque transmitting balls also providing a bearing support for said power delivery shaft] 2. Power transmitting mechanism comprising a housing fixed against rotation, a hollow sleeve support shaft extending outwardly from said housing and fixed thereto, a power input planet carrier, a bearing rotatably supporting said carrier on said sleeve shaft, a first sun supported upon said sleeve shaft in fixed relationship with respect thereto, a second sun supported on said sleeve shaft and movable with respect thereto, a ring spaced from said suns, an extension on said carrier extending into the space between said ring and suns, a plurality of ball receiving pockets on said extension, a ball in each of said pockets, means for biasing said second sun axially with respect to said sleeve shaft to maintain said balls in nonslipping friction contact with said ring and suns comprising a Belleville washer, said washer having one portion thereof fixed to said sleeve shaft and a second portion fixed to said second sun for preventing rotation of said sun with respect to said sleeve shaft, a power delivery shaft extending through said sleeve shaft, and means connecting said power delivery shaft to said ring, said balls providing a support for rotatably supporting said power delivery shaft in said sleeve shaft.

3. Power transmitting mechanism comprising a housing fixed against rotation, a hollow sleeve support shaft fixed to said housing, a power input planet carrier, bearing means between said carrier and support shaft supporting said carrier for rotation with respect to said support shaft, a first sun supported on said support shaft and fixed against rotation with respect to said shaft, a second sun supported upon said support shaft and axially movable with respect thereto, a ring spaced from said suns, an extension on said carrier disposed in the space between said ring and suns, a series of spaced pockets formed on said extension, a ball roller disposed in each of said pockets and contacting said ring and said suns, an axially extending ear on said second sun, a notch on said support shaft, means for biasing said second sun axially toward said first sun to maintain said balls in nonslipping friction contact with said ring and said suns comprising a Belleville spring washer, a notch in said Belleville washer for receiving said ear, a tang on said washer extending into said support shaft notch, a power delivery shaft, and means connecting said power delivery shaft to said ring for rotation therewith, said balls providing a support for rotatably supporting said power delivery shaft in said support shaft.

4. An accessory drive for driving the accessories of an engine driven vehicle comprising a support housing, a support sleeve fixed to said housing, an engine driven planet carrier, a planet roller driven by said carrier, a reaction sun supported on said support sleeve, 3. bearing between said carrier and support sleeve, a ring, said planet roller being in friction contact with said sun and ring, a final power delivery shaft connected to drive an engine accessory and having one end extending into said support sleeve, and means for supporting said one end of said final power delivery shaft and for driving said power delivery shaft comprising a connection between said ring and power delivery shaft, said planet roller being effective to drive said ring and to support said ring and connection to thereby support said one end of said power delivery shaft.

5. In a power transmitting mechanism, a housing reaction member, a power input member, a power output member, plmli'l carrier means rotatably mounted in said housing member and connccred to one of said numbers for transmitting torque, a plurality of equally spaced axial notches formed in said carrier having spaced parallel planar bearing surfaces facing each other, a pair of opposirely disposed bearing inserts in each of said notches and each bearing insert having a flat bearing surface in bearing contact with one of said planar bearing surfaces relative movement and a concave substantially spherical surface formed on the side opposite said flat bearing surfaces to provide two facing spherical surfaces in each notch, a planet ball mounted between the facing concave spherical surfaces of each of said pairs of bearing inserts and extending beyond opposed sides of said carrier, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet balls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication, first ring means connected to another of said members for transmitting torque and in friction-drive contact with said ball, second ring means connected to a third of said members for transmitting torque and in friction-drive contact with said ball, and said first and second ring means axially and radially positioning said ball and including means to load said first and second ring means into rorque-transmirting friction contact with said ball.

6. In a power transmitting mechanism, a housing reaction member, a power input member, a power output member, planet carrier means rotatably mounted in said housing member and connected to said power input memher for transmitting torque, a plurality of equally spaced axial notches formed in said carrier having spaced parallcl planar bearing surfaces facing each olher, a pair of 0ppositely disposed bearing inserts in each of said notches and each bearing insert having a flat bearing surface in bearing contact with one of said planar bearing surfaces and a concave substantially spherical surface formed on the side opposite said flat bearing surfaces to provide two facing spherical surfaces in each notch, a planet ball mounted between the facing concave spherical surfaces of each of said pairs of bearing inserts and extending beyond opposed sides of said carrier, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet balls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication, a first ring means connected to said housing reaction member for transmitting torque and in friction-drive contact with said ball, a second ring means connected to said power output member for transmitting torque and in friction-drive contact with said ball, said first and second ring means axially and radially positioning said ball and including means to loud said first and second ring means into torque-trons mining friction contact with said ball.

7. In a power transmitting mechanism, a housing reaction member, a power input member, a power output member, planet carrier means rotatably mounted in said housing member and connected to said power input memher for transmitting torque, a plurality of equally spaced axial notches formed in said carrier having spaced parallel planar bearing surfaces facing each other, a pair of oppositely disposed bearing inserts in each of said notches and each bearing insert having a flat bearing surface in bearing contact with one of said planar bearing surfaces and a concave substantially spherical surface formed on the side opposite said flat bearing surfaces to provide two facing spherical surfaces in each notch, a plant ball mounted between the facing concave spherical surfaces of each of said pairs of bearing inserts and extending beyond opposed sides of said carrier, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet bulls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication, split sun means connected to said housing reaction member and in friction-drive contact with said ball, ring means connected to said power output member and in friction-drive contact with said ball, said sun and ring means axially and radially positioning said ball and means to load said split sun means into torque-transmitting friction contact with said ball and said ball into torque-transmitting friction contact with said ring means.

8. A power transmitting mechanism for driving the accessories of an engine-driven vehicle, said mechanism comprising a housing, a reaction member secured to said housing, a power input 'member, a power output member, a planet carrier rotatably mounted in said housing and connected to one of said members for transmitting torque, a plurality of equally spaced radial passages having parallel side walls formed in said carrier, a sun member connected to a second of said members, a ring member mounted radially outwardly of said parallel side walls and connected to a third of said members, a pair of oppositely disposed bearing inserts secured by confinement between said parallel side walls of each radial passage, a concave spherical surface formed on each of said bearing inserts, a planet ball mounted between the concave spherical surfaces of each of said pairs of bearing inserts and in frictional contact with said sun and ring members, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet balls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication.

9. A power transmitting mechanism comprising a housing, a reaction member secured to said housing, sun 'means axially slidably mounted on said reaction member, a power input member, a planet carrier rotatably mounted on said reaction member and driven by said input member, a plurality of equally spaced axial notches formed in said carrier, an output ring mounted radially outwardly of said notches, a pair of oppositely disposed bearing inserts secured by confinement within each of said notches, a concave spherical surface formed on each of said bearing inserts, a planet ball mounted between the concave spherical surfaces of each of said pairs of bearing inserts and contacting said sun means and said output ring, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet balls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication.

10. A power transmitting mechanism comprising a housing, a reaction member secured to said housing, a sun member mounted on said reaction member, a power input member, bearing means mounted on said reaction mem ber, a planet carrier rotatably mounted on said bearing means and driven by said input member, a power output member, a plurality of equally spaced axial notches formed in said carrier, a ring member mounted radially outwardly of said notches, said power output member being operatively connected to said ring member, a pair of oppositely disposed bearing inserts secured by confinement within each of said notches, a concave spherical surface formed on each of said bearing inserts, a planet ball mounted between the concave spherical surfaces of each of said pairs of bearing inserts, the concave spherical surface of each of said inserts having a larger radius than the radius of each of said planet balls providing a wedged opening between the ball and each of said concave spherical surfaces whereby lubricant in said wedged openings tends to lift said planet balls for full hydrodynamic spherical bearing lubrication.

References Cited The following references, cited by the Examiner, are of record in the patented file of this patent or the original patent.

UNITED STATES PATENTS 1,399,442 12/1921 Rennerfelt 74-798 1,574,803 3/1926 Erban 74-798 1,585,140 5/1926 Erban 74208 X 1,691,625 11/1928 Chilton 74-796 1,859,502 5/1932 Erban 74-208 X 1,915,287 6/1933 Bott 308-187 2,953,039 9/1960 McRae 74-798 X 2,977,161 3/1961 Cobb 308-187 3,021,730 2/1962 Banker 74-798 3,204,476 9/1965 Rouverol 74-198 2,828,907 4/1958 Oehrli 74-796 2,874,592 2/1959 Oehrli 74-796 2,905,026 9/ 1959 Oehrli 74796 2,913,932 11/1959 Oehrli 74-796 FOREIGN PATENTS 313,969 6/1930 Great Britain.

MARK NEWMAN, Primary Examiner 'I'. C. PERRY, Assistant Examiner US. Cl. X.R.

mg UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No- RE. .978 Dated November 17, 1970 InvenrorL's) Lubomyr O. Hewko It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Column 3, line 54,

"or" should read "on" Column 8, line 8,

"relative movement" should be deleted.

Signed and sealed this 21 at day of December 1 971 (SEAL) Attest:

EDWARD M.FLETCHER,JR. ROBERT GOTISCHALK Attesting Officer Acting Commissioner of Patents

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