Abstract: Since the true power density of gearing is a function of the dynamic load, maximization of this critical performance property can be achieved only if both the static component and the dynamic increment of load are minimized. The invention discloses how these two objectives may be achieved in the same gear set. Both static and dynamic tooth stresses are minimized by forming the gears to have an optimum load distribution, a feature realized by using a new type of modification that minimizes the tooth surface relief area. The second requirement, of minimizing the dynamic increment, is accomplished in helical and spiral bevel gearing by proportioning the teeth to have a fully elastic "self-complementary" tooth pair stiffness curve, which gives a mesh stiffness characteristic that remains substantially constant throughout the entire tooth pair engagement angle at all loads and all speeds.

Abstract: An eccentric gear comprises first and second gear rings (7,10) of which the one (7) has internal, straight cogs and the other (10) a smaller number of external cogs. At least one gear ring has a conical form with a large end (A--A) and a small end (B--B), the other gear ring (10) having a smaller pitch diameter than the first one (7) and being eccentrically mounted in bearings relative to the first one. Axes of symmetry (24,25) of the respective gear rings form an angle (.alpha.) with each other. The contact points or the locations of engagement between the flanks of the cogs in the one gear ring and the opposed flanks of the cogs in the other gear ring are substantially located along a helical line which extends in axial direction between said large and small ends.

Abstract: A planetary gear apparatus comprising an inner tooth gear having an inner peripheral portion formed with a plurality of inner teeth each in the form of a semi-circular cross-section shape and an outer tooth gear positioned within the inner tooth gear and having an outer peripheral portion formed with a plurality of outer teeth each in the form of a wave shape. The outer tooth gear has a center axis offset at an offset amount from the center axis of the inner tooth gear, and revolvable while being held in sliding and meshing contact with the inner tooth gear with the center axis of the outer tooth gear moving on a revolution orbit encircling and spaced from the center axis of the inner tooth gear at a distance equal to the offset amount.

Abstract: In a meshing type gear device (1), spur gears are used for both a rigid internal gear (2) and a flexible external gear (3), and the number of teeth of the flexible gear (3) is made greater by two than that of the rigid internal gear (2). The tooth profile of the flexible external gear (3) is made convex and the shape thereof is that of a curve AC obtained by subjecting a gear tooth portion (curve portion between A and B), which, at the moving path L that the external gear describes relative to the internal gear, as determined by rack approximation, is convex relative to the internal gear, to similarity transformation at a reduction ratio .lambda. using the limiting point A of the contact between the two gears on the path as the origin, while the tooth profile of the rigid internal gear is made concave and the shape thereof is that of a curve AD obtained by subjecting the same portion convex relative to the internal gear at the moving path to similarity transformation at an enlargement ratio (1+.lambda.

Abstract: The present invention relates to a pair of meshed involute gears one of which has work teeth, their tooth-tip circle is larger than that of the said gear, the other has the grooves engaged with the said working teeth. The working teeth and the grooves have the same characters of equal periphery of meshing and rotating as the said involute gears. This composite construction of the gear named "the meshing type rotors" can be used in making internal combustion engine, fluid (liquid or gasous) pump and motor, vacuum pump, conditioner/refrigerator/compressor and hydraulic variator.

Abstract: A gear for use in automotive differentials and a method for its manufacture in which, initially, the gear teeth are roll-formed in a cylindrical rod workpiece between a pair of toothed dies so that a fissure is created in the top land of each rolled tooth, the roll-forming being continued until (a) the diameter of the top land of each tooth is slightly greater than the desired cylindrical outside diameter of said gear and (b) each fissure is narrowed to form a seam at the top land surface of each tooth. The gears are then further processed in a relatively short machining operation that removes the narrowed seam in the top land of each gear tooth to reduce the depth of the fissure so that the normal force vector of the highest point single tooth loading ("HPSTL") on the gear tooth is directed below the bottom of the fissure.

Abstract: A no back-lash gearing mechanism comprises meshing toothed elements. At least one of the toothed elements has a number of teeth having an undulated, "S"-shaped, transverse section. The teeth are arranged such that, when the toothed elements mesh, one of the teeth having the undulated form makes at least one point of contact with each of two opposing adjacent teeth of the other element thus preventing back-lash.

Abstract: In a parallel-axis differential, pocket pairs are formed in an inner periphery of a housing and planetary gear pairs are rotatably received in the pocket pairs, respectively. With outer peripheral surfaces of the planetary gears (i.e., top faces of helical teeth) being in contact with inner peripheral surfaces of the pockets, the planetary gears are rotated relative to the housing. End portions of the helical teeth located on opposite end portions of each planetary gear are gradually reduced in height toward ends of the planetary gear. By this, top faces of end portions of those helical teeth are slightly convexly curved. The top faces of the end portions of those helical teeth are served as contact surfaces which are brought into contact with the inner peripheral surfaces of the pockets when the planetary gears are slightly inclined.

Abstract: A gear structure including an internal gear and an external gear meshed together and moved relative to each other through a rotary motion, the radius of the root arcs of the teeth of the external gear being M, which is the ratio between the diameter of the crest and the number of teeth, and being the line of arc in tangent with the crest arcs of each two adjacent teeth, the tooth form curve of the internal gear being obtained by connecting all engaging points at the crest arcs and root arcs of the external gear.

Abstract: A planetary gear device includes a sun gear, planet gears to be meshed with the sun gear and an internal gear to be meshed with the planet gears each having a tooth profile formed to an involute curve, wherein tooth surfaces on one side of the planet gears meshing with the sun gear and tooth surfaces on the other side of the planet gears meshing with the internal gear are respectively corrected by different amounts of correction on the basis of deformation amounts of teeth of the planet gears caused by meshes with the sun gear and the internal gear so that rotary motion can be smoothly transmitted when the tooth faces of the planet gears meshed with the sun gear and the tooth faces of the planet gears meshed with the internal gear are elastically deformed by the mesh thereof.

Abstract: A spring drive for an electrical switching apparatus has a switch-on shaft to which a switch-on spring is coupled eccentrically and on which a large wheel (16) is seated in a rotationally fixed manner. A small wheel (20), which is driven in order to stress the switch-on spring, interacts with the large wheel (16). A tooth system (52) on the large wheel (16) has a gap (54) for decoupling the wheel pair (18) formed by large wheel (16) and small wheel (20) when the switch-on spring is stressed. In order to connect the switching apparatus, the large wheel (16) is driven in a rotation direction (D), as a result of which the tooth system (52) engages with the small wheel (20) again. In order to prevent blocking when the teeth engage in one another, the teeth (60) on the small wheel (20) are constructed in such a manner that the edges (56, 58) abut against one another radially on an outer side at a common edge (62).

Abstract: In a planet gear type torque transmission device, the internal teeth of an internal gear integrally formed by resin molding are arranged regularly for the ribs for coupling the inner periphery and the outer periphery of the gear. Thus, the mold can also be modified regularly so as to form the internal teeth with high accuracy.

Abstract: In a vertical blind track of the type incorporating a sprocket gear within an end control housing to rotate a fluted pinion gear and vanes carried thereby under action of a pull-chain, and wherein the end control housing includes a first gear and a pair of second gears, one of which is driven by the sprocket gear when rotated, the apparatus of the invention secures the vanes in closed position, against inadvertent "bounce back" to a partially opened position, by utilizing the sprocket gear to effect rotation between the first gear and the pair of second gears, but with a filled recess between a pair of adjacent teeth on the first gear to prevent meshing with the second gears, and causing a binding of the rotating mechanism at a predetermined point which defines the closed position of the vanes.

Abstract: A connection assembly includes at least two components each formed with a body extending along a respective axis and a respective plurality of angularly equispaced alternating tongues projecting radially from the body and grooves for meshing with the tongues and grooves of the other component upon relative angular displacement of the components, so that the components are not able to be separated in a direction transverse to the axis upon the relative angular displacement.

Abstract: A transmission including composite planetary gears supported by a carrier such that the planetary gears are arranged around an axis of the carrier, each planetary gear consisting of a large and a small pinion which mesh with a first and a second gear, respectively, and which have a ratio Zp.sub.1 /Zp.sub.2 equal to an integer not smaller than 2, wherein Zp.sub.1 and Zp.sub.2 represent numbers of teeth of the large and small pinions, respectively. The transmission is assembled by assembling the common second gear and the carrier supporting the planetary gears, such that the small pinion of each composite planetary gear meshes with the common second gear, and assembling the common first gear and the carrier such that the large pinion of each planetary gear supported by the carrier meshes with the common first gear.

Abstract: Disclosed is a high strength, self-lubricating, non-metallic gear which requires no lubrication when running with a metallic gear. The gears are cut with a non-standard tooth form to provide superior power transmission performance and the metallic gear is selected from special pinions having range indicators for assuring proper gear and pinion combination.

Abstract: A gear device improved in lowering the product of the load F acting on a pair of intermeshing teeth and the relative sliding velocity v at the area of contact of the gears, thereby minimizing the frictional heat. The gear device includes a first gear and a second gear each having a tooth profile formed by an involute curve. At least one of the first and second gears is provided with the tooth profile corrected by a combination of a correction curve W and the involute curve. On plane coordinates consisting of an x axis, an origin and a y axis which intersects with the x axis at the origin, the correction curve W is expressed by equations passing through points P.sub.1 (x.sub.1, y.sub.1) and P.sub.2 (x.sub.2, y.sub.2) and satisfying the conditions of: y=0, dy/dx=0 at the origin when x.sub.1 <x.sub.2 and y.sub.1 <y.sub.2. The x axis is the line of action indicative of a locus along which an intermeshing point moves while the first gear transmits a force to the second gear.

Abstract: A coupling for splining together first and second shafts which may be inner and outer, co-axial annular members, abutting co-axial annular members, or intermeshing gears on parallel shafts. One embodiment is a coupling for splining together inner and outer annular members having corresponding inner and outer cylindrical surfaces concentrically disposed about an axis and having splines which are generally circumferentially disposed on the cylindrical surfaces along an axial length of at least one of the members such that the splines having a varying pitch so as to be curved with respect to the axis. The pitch is defined by a function which varies parabolically with respect to a shaft axis and, in a more particular embodiment, the function has a non-zero fixed pitch component and a parabolic component so that the shape of the splines are both helical and parabolic.

Abstract: In a conventional internal gear pair system such as a planetary gear system with a small gear ratio of the internal gear to the driving pinion, common problems include tip interference and limited contact between the teeth of the gears. An internal gear pair system which avoids these problems includes a pinion meshing with an internal gear, the pinion having as few as one tooth less than the internal gear, the only contact between the pinion and the internal gear being on at least one side of a line extending diametrically through the centers of the pinion and the internal gear, and the teeth of the pinion being conjugate to the internal gear teeth.

Abstract: A child's riding vehicle employing a unique and novel gear assembly and engagement structure includes a frame having plural wheels, and a gear assembly fixed on the frame which includes an output gear non-rotatably connected to at least one of the vehicle's wheels. A motor on the frame is mounted on an arm which is movable between an engaged position and a disengaged position, and a segment gear mounted on the frame adjacent the gear assembly engages the motor's pinion and defines a path between the engaged and disengaged position. Unique and novel gear tooth profiles are employed in both the gear assembly and the engagement structure to prevent the same from jamming during transition between the engaged and disengaged positions and vice versa.

Abstract: A new system of modifications for power train gearing, called "differential crowning," has both advantages and disadvantages over the previous system of modifications based on tip and/or root relief. The advantages of differential crowning are three-fold: (1) it affords substantially constant stiffness, so that it is equally effective at all loads; (2) it is adapted to minimize both first and second harmonic excitations, whereas conventional modifications can mitigate only the first harmonic excitation, and that only at one "design load;" and (3), it is as insensitive to manufacturing inaccuracies as conventional gearing is sensitive to them. Differential crowning, however, has two disadvantages in its previously disclosed forms: (1) it is difficult to optimize; and (2), it is more expensive than conventional modifications unless the production runs are very large.

Abstract: The present invention comprises an extended tooth contact harmonic drive gearing apparatus for transmitting rotary motion from an input drive to an output drive through mating contact between a flexspline and a rigid circular spline, the flexspline being swept into a non-circular shape by a wave generator. The wave generator causes the teeth of the flexspline to precess from a normal to an inclined orientation and back to a normal orientation again. The teeth on both the flexspline and the circular spline have a profile which accomodates that tooth inclination, and thus avoids interference therebetween.

Abstract: An involute gearset formed of at least two meshing gear wheels the teeth of which have flanks formed of different curves including an involute in the central region, an arcuate region adjoining the involute, and a straight line segment which intersects the end face of a respective tooth and tangentially passes into the arcuate region.

Abstract: Planetary reduction gear comprising at least one stage consisting of an input plant pinion (7), of spider gears (8, 9, 10) mounted on a spider (11) secured to an output shaft and to a fixed crown wheel (12). The spider gears are mounted so that they can float radially in the spider and the toothings of the meshing elements are offset such that the radial resultant of the forces exerted, on the one hand, between the crown wheel and the spider gears and, on the other hand, between the spider gears and the planet pinion points either toward the planet pinion in order to reduce the noise of the reduction gear, or toward the weakest elements in order to increase the load capability of the reduction gear.

Abstract: Disclosed is a high strength, self-lubricating, non-metallic gear which requires no lubrication when running with a metallic gear. The gears are secured to their shafts with keyless retaining devices, and the gear set is cut with a non-standard tooth form to provide superior power transmission performance.

Abstract: Spectrum analyses of gear noise show that the predominant frequencies are the tooth contact frequency (1.times.TCF) and twice the tooth contact frequency (2.times.TCF). The reason for this is that at two positions in the tooth engagement cycle, the effective mesh stiffness of conventional gearing differs substantially from the ideal mesh stiffness that eliminates the dynamic increment of load. One of these two positions occurs once per tooth engagement cycle and the other one twice, giving rise to the 1.times.TCF and 2.times.TCF excitations respectively. These periodic fluctuations in the effective mesh stiffness, which are in proportion to what is called "static transmission error," produce inertia forces between engaged teeth that increase with both speed and proximity to the critical (resonance) speed of the gear pair. In conventional gearing the dynamic increment of load generated by these inertia forces can be as large as or even larger than the useful transmitted load.

Abstract: The topology of parallel axis gears, such as spur and helical gears is modified to produce quieter and more smoothly operating gear sets with more uniform load distribution. A finite element analysis of the gear in its operating mode is made to produce a plot of radial and tangential deflections of the pinion and gear tooth surfaces which will occur when the gears are loaded during operation. The resultant plot is then inverted to produce a plot, or set of coordinates, which will define the path of travel of the gear tooth grinding wheel, which path is a mirror image of the plot of the finite element analysis. The resulting gears, when subjected to operating loads, will thus be deflected tangentially and radially to their optimum operating, or theoretical true involute, positions so as to produce quieter, smoother, and more evenly loaded gear trains.

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: A drive pinion for an engine starting motor having a lead-in chamfer of the starter pin defined by a geometry formed by rotating the radial gear tooth involute form through 90 degrees across the end of the tooth. The radius and axis of rotation are selected such that the cam surface is full across the height of the tooth and the cam surface intersects the back side of the tooth at the leading edge of the tooth.

Abstract: A family of conjugate gear tooth profiles is taught in which the relative curvature is a maximum near center and decreases toward tip and flank, where sliding is greatest. In one embodiment the radii of curvature of the individual profiles are least at the pitch point and increase toward tip and flank. The permissible tooth heights are limited only by top lands and bottom lands; and any tooth-numbers can be used without resorting to unequal addendums, although unequal addendums can be used if desired.

Abstract: A transmission is provided wherein selected configurational parameters of interacting spur gearing are modified to abate the vibration levels thereof due to the effects of differential thermal expansion of the gearbox housing. The chordal addenda of the gear teeth of the interacting spur gearing are extended by a predetermined amount, based upon the computed relative radial displacement of the centerlines thereof due to the differential thermal expansion effects, to provide modified interacting spur gearing having increased outside diameters. Such modified spur gearing provides an effective centerline spacing for the transmission such that the interacting spur gearing thereof has an operating contact ratio greater than the design contact ratio at engine start up.

Abstract: A non-involute gear used in a gear pair. A first gear has a plurality of radially extending, circumferentially spaced teeth, each with a generally cylindrical, arcuate shaped end surface. A second gear has a plurality of spaced, non-involute shaped teeth. Each tooth of the second gear is formed with opposed base faces disposed at an identical radius. A pair of flats extend in parallel from the ends of each circular base face and terminate in inwardly extending, end portions extending from the flats to the top land of each gear tooth. A tooth space is formed between two adjacent non-involute gear teeth having a semi-circular base portion formed by the opposed circular base faces of two adjacent gear teeth and two parallel flat portions formed by the pair of parallel flats extending from the semi-circular base portion which combine to form a generally U-shaped space for receiving a gear tooth on the first gear.

Abstract: A gear pair having a low tooth number differential and a total contact ratio of .xi..sub..upsilon. =.xi..sub..alpha. +.xi..sub..beta. .gtoreq.1 provided that the profile contact ratio .xi..sub..alpha. <1 and the face contact ratio .xi..sub..beta. >0, wherein the absolute value of the difference of addendum modification coefficients .vertline.X.vertline. is less than one or equal to zero, thus increasing the transmission efficiency. Additionally, a transmission assembly is provided including such a gear pair construction.

Abstract: A jointed fitting is described for vehicle seats comprising a planetary gear enabling the two fitting parts joined by a joint axle to be pivoted relative to each other, a second gear wheel (6) with an external toothing engages a first gear wheel (5) with an internal toothing. Both gear wheels (5, 6) have an involute toothing. Their teeth (7, 8) have a rounded-off head and the number of teeth of the second gear wheel (6) is slightly less than that of the first gear wheel (5). That point on the tooth flanks of the first gear wheel (5) at which the flank section extending along an involute passes into the flank section formed by the rounding-off of the head lies on a circle, the diameter (d.sub.el) of which is chosen so as to be at least approximately the same as the base circle diameter (d.sub.bl) of the first gear wheel (5). The top circle diameter (d.sub.al) of the first gear wheel (5) is smaller than its base circle diameter (d.sub.bl).

Abstract: An elliptic gear having a constant velocity portion, wherein a pitch circle is a closed curve composed of: a constant velocity portion pitch curve, in which the radius from the center of rotation is a constant arc; and an inconstant velocity portion pitch curve, which is expressed by a formula of an ellipse in polar coordinates having its pole located at the center of rotation and which merges smoothly into the constant velocity portion pitch curve.

Abstract: A crescent pump gear including: a housing having a chamber communicating with an intake port and a discharge port; a shaft journaled for rotation within said chamber; an externally toothed inner gear mounted centrally on said shaft about a first axis; an internally toothed annular gear eccentrically mounted for rotational engagement with said inner gear about a second axis; a crescent contacting a portion of said inner gear has a dual cycloidal tooth profile generated about a first generating circle and said outer gear has a dual cycloidal tooth profile generated about a second generating circle.

Abstract: A multistage turbocompressor with a two-stage transmission with a double intermediate cogwheel (5) consisting of two cogwheels (51 and 52). The first cogwheel has a larger module than the second cogwheel and engages only a central cogwheel (2) that drives the pinion shafts (3 & 4) in the first stage. The second cogwheel engages only the pinion shafts (6, 7, & 8) in the second stage.

Abstract: A spur pump gear system comprising; a housing have a sealed chamber communicating with an intake port and a discharge port; a shaft journalled for rotation within said chamber; a drive spur gear mounted concentrically on said shaft about a first axis within said chamber, said drive spur gear presenting epi and hypo cycloid tooth profiles; a driven spur gear disposed internally within said chamber for rotation about a second axis, said driven spur gear presenting epi and hypo cycloid tooth profiles; said epi hypo cycloid tooth profile of said drive spur gear engagedly driving said hypo cycloid tooth profile of said driven spur gear.

Abstract: The arc gear with a rotary transmission of 1:1 has an inner toothed toothwheel, an outer toothed toothwheel, each connected to a shaft, one of the shafts being for drive and one for output. The shafts are arranged eccentrically with an eccentricity and parallel to one another. There are provided concave power transmission surfaces, with a first radius of curvature measured from the centers of first circles, on teeth of one of the toothwheels, and convex power transmisison surfaces, with a second radius of curvature measured from the centers of second circles, on teeth of the other of the toothwheels, both of the toothwheels having the same number of power transmission surfaces. Two of the concave power transmission surfaces lie on the same one of the first circles. Two of the convex power transmission surfaces lie on the same one of the second circles. The first radius and the first circles are bigger than the second radius and the second circles.

Abstract: The usual expedient employed by gear designers seeking to reduce gear noise at all loads has been to specify finer teeth, which in effect trades away torgue capacity for quietness. The present disclosure describes a tooth form that substantially eliminates gear noise while at the same time significantly increasing torque capacity. This tooth form involves (a) the synchronization of the loading and unloading phases of tooth engagement with the inverse phases (i.e., unloading and loading phases, respectively) of another tooth pair, combined with (b) the introduction of particular patterns of topographic tooth surface crowning that transform the elastic tooth pair stiffness curve into a curve that not only maintains this synchronization at loads greater or smaller than the design load but also eliminates transmission error to any extent desired.

Abstract: A modular drive axle having left and right drive wheels and axles that are coupled to a differential. The left and right axles are in line and define a transverse axis. A bevel gear assembly having first and second bevel gears mounted on a drive shaft directs rotary motion from a transmission to the differential for driving the drive wheels. The bevel gear assembly drive shaft is perpendicular to the transverse axis and the transmission which is operatively coupled to the bevel gear assembly and arranged parallel to the transverse axis. The transmission is a collar shift transmission having an input collar with two output surfaces. The first output surface of the input collar drives a fixed countershaft gear having first and second output surfaces. The first and second output surfaces drive first and second intermediate gears.

Abstract: A phenol resin toothed wheel having a toothed portion formed of meta-aromatic polyamide fiber spun cloth impregnated with phenol resin blended with epoxy resin.

Abstract: A double-shaft vacuum pump with pistons (3,4) rotating without contact in the pump chamber (8) and with synchronization gears (16, 17) located in a side chamber (15). In order to dispense with an oil supply in the side chamber the teeth of the synchronization gears (16, 17) are shaped in such a way that contact between the tooth flanks (26) is limited to the immediate vicinity of the pitch circle (29). If any lubrication is needed, it can be supplied by bearing grease suitable for vacuum applications. The side chamber cover (27) is preferably shaped as a "figure-8" to conform to the peripheries of the synchronization gears (16, 17), and a cooling system for the gears may be provided.

Abstract: A Novikov gearing comprising at least two gear elements the teeth of each element consisting of an addendum whose profile in the normal section is described by a convex curve, a dedendum and a fillet between the two. A portion of the fillet adjoining the addendum in the normal section has a convex profile with a radius of curvature smaller than a radius of curvature of the addendum.

Abstract: A gantry robot construction is provided. The construction includes a pair of elongated substantially spaced parallel rails, a bridge spanning and substantially perpendicular to the rails and movable relative to the rails, and a robot head and support mounted on the bridge and movable relative to the bridge. The rails are positioned along the width or shorter side of the work area with the bridge spanning the length or longer side of the work area. An improved rack and pinion apparatus is also disclosed that is used in association with the gantry robot construction. There is a zero degree pressure angle between the rack and pinion. In the pinion the base circle is congruent with the pitch circle.

Abstract: An air compressor, which is embodied as a single or multi-cylinder/piston compressor, and which is driven by gear wheels. The drive gear or pinion of the air compressor is disposed on the air compressor crankshaft and meshes with a gear wheel on the camshaft of an internal combustion engine. Provided on the periphery of the air compressor pinion is, for a single cylinder/piston compressor, one interval having an enlarged tooth gauge, and for a multi-cylinder/piston compressor, several such intervals, the number of which corresponds to the number of times the tangential force passes through zero during one air compressor crankshaft revolution, with the centers of the intervals being coordinated with the respective top dead center position of the air compressor piston.

Abstract: A multispeed winch or gear box wherein an axially-movable gear located on a shaft parallel to the drive shaft is movable by operation of a lift mechanism to be in a first position in engagement with a specific gear train or in a second position out of engagement with the gear train. Further, the winch or gear box can have a gear on the drive shaft with a lip or shoulder which can retain the axially-movable gear in the upper or first position after the lift mechanism has moved the axially movable gear to the first position, and the lift mechanism has been withdrawn. This arrangement will permit the gear box or winch to automatically shift from first speed to second speed to third speed upon reversal of the drive shaft rotation.

Abstract: A multispeed winch or gear box wherein an axially-movable gear located on a shaft parallel to the drive shaft is movable by operation of a lift mechanism to be in a first position in engagement with a specific gear train or in a second position out of engagement with the said gear train. Further, the winch or gear box can have a gear on the drive shaft with a lip or shoulder which can retain the axially-movable gear in the upper or first position after the lift mechanism has moved the axially movable gear to the first position, and the lift mechanism has been withdrawn. This arrangement will permit the gear box or winch to automatically shift from first speed to second speed to third speed upon reversal of the drive shaft rotation.

Abstract: A hob or shaper cutter for making a hub for a misalignment gear coupling having a hub and a sleeve. The hob or shaper cutter has cutting edges. Each cutting edge being inclined at a different angle to the center line of the tooth. The cutting edges are adapted to cut tooth flank surfaces having three adjacent involute shaped areas. Each involute shaped area having a different pressure angle than the involute area adjacent it. The involute areas of each tooth result in teeth with flanks that are generally cylindrical shaped, whereby hub treeth operate with a minimum of interferfence with sleeve teeth when operating with the hub misaligned with the sleeve.

Abstract: A conjugate gear system including a pair of meshingly engageable toothed gears, at least one member of the gear pair having at least one three-component tooth. Each three-component tooth is comprised of a central core, at least one face disposed thereon, and a means for displaceably attaching the face section to the core such that the face section is displaceable with respect to the core in the direction of the sliding component of motion created by meshing engagement of the gear pair. By separating out the sliding component in this fashion, relatively pure rolling contact is maintained between the engaged surfaces of the gear pair at all times, thus reducing sliding friction, thermal expansion, and noise levels created by the engagement of the gears.