Abstract: An intermittent transmission apparatus according to this invention, broadly, includes a driving element and a driven element. The driving element comprises a first cam having a first cam surface, a second cam having a second cam surface, and an intermediate member displaced between the first and second cams. The driven element comprises a driven element main body having recesses for contacting a plurality of rollers arranged on the intermediate member, bearings erected on the driven element main body to be pushed by the first cam surface, and bearings erected under the driven element main body to be pushed by the second cam surface. During non-drive period of the driven element, the bearings contact a circular arc surface of the second cam, and further the recesses contact the plurality of rollers, to restrict rotation of the driven element.

Abstract: A synchronous drive apparatus and method, wherein the apparatus comprises a plurality of rotors comprising at least a first and a second rotor. The first rotor has a plurality of teeth for engaging the engaging sections of an elongate drive structure, and the second rotor has a plurality of teeth for engaging the engaging section of the elongate drive structure. A rotary load assembly is coupled to the second rotor. The elongate drive structure engages about the first and second rotors. The first rotor is arranged to drive the elongate drive structure and the second rotor is arranged to be driven by the elongate drive structure. One of the rotors has a non-circular profile having at least two protruding portions alternating with receding portions.

Abstract: In order to provide an operationally reliable compensation in particular for polygon effects, using simple means, the invention proposes a drive to be used for a chain comprising periodically arranged chain links, the drive train of which is driven by a driving motor and has at least one non-circular wheel located on the input side.

Abstract: A driving force transmission device includes a rim having a toothed outer periphery, with bottom lands being formed between respectively adjacent teeth and top lands being formed at teeth crests. Outer ribs are disposed at positions on an inner peripheral surface of the rim corresponding to the bottom lands, whereby there is neither variance in angle speed nor uneven rotation of a member driven by the transmission device. Moreover, the outer ribs are radially offset from inner ribs, whereby tensile forces generated between the outer and inner ribs and caused by material shrinkage cancel each other out and defective molding of teeth crests can be minimized. Accordingly, the radius of an imaginary circle formed by joining the top lands is uniform in a circumferential direction.

Abstract: A rotary piston engine (20) is shown that includes a housing (22) having a toroidal working chamber with inlet (56) and exhaust (54) ports. First and second piston assemblies (30 and 32), each of which includes at least one pair of diametrically opposed pistons (30A and 30B, and 32A and 32B), are located in the working chamber. Piston assemblies (30 and 32) are connected to the engine output shaft through a differential (78) and the Sakita gear sets (74 and 76), each of which gear sets includes a Sakita type 1 gear (74A or 76A) and a Sakita type 2 gear (74B or 76B). The piston assemblies rotate at variable speed, whereby pistons of the slower speed are trailing pistons during portions of the power and intake phases of engine operation. In one embodiment, the Sakita type 1 gear includes teeth in the form of rollers. Also, spark plugs embedded within piston assemblies (30 and 32) are accessible from outside.

Abstract: A rotary piston engine (20) is shown that includes a housing (22) having a toroidal working chamber with inlet (56) and exhaust (54) ports. First and second piston assemblies (30 and 32), each of which includes at least one pair of diametrically opposed pistons (30A and 30B, and 32A and 32B), are located in the working chamber. Piston assemblies (30 and 32) are connected to the engine output shaft through a differential (78) and two pairs of the Sakita gear sets (74 and 76), each of which gear sets includes a Sakita type 1 gear (74A and 76A) and a Sakita type 2 gear (74B and 76B). The piston assemblies rotate at variable speed, whereby pistons of the slower speed are trailing pistons during portions of the power and intake phases of engine operation. In one embodiment, one of the Sakita gears includes teeth in the form of rollers. Also, spark plugs embedded within piston assemblies (30 and 32) are accessible from outside.

Abstract: A rotary piston engine (20) is shown that includes a housing (22) having a toroidal working chamber with inlet (56) and exhaust (54) ports. First and second piston assemblies (30 and 32), each of which includes at least one pair of diametrically opposed pistons (30A and 30B, and 32A and 32B), are located in the working chamber. Piston assemblies (30 and 32) are connected to the engine output shaft through a differential (78) and the Sakita gear sets (74 and 76), each of which gear sets includes a Sakita type 1 gear (74A or 76A) and a Sakita type 2 gear (74B or 76B). The piston assemblies rotate at variable speed, whereby pistons of the slower speed are trailing pistons during portions of the power and intake phases of engine operation. In one embodiment, the Sakita type 1 gear includes teeth in the form of rollers. Also, spark plugs embedded within piston assemblies (30 and 32) are accessible from outside.

Abstract: The escapement includes first (3) and second (4) escapement wheels meshing with each other, one of these wheels being driven by the gear train. It further includes a lever (5) capable of receiving the impulses generated alternately by the first and second wheels and to transmit these impulses to a plate (2) which carries a sprung-balance. The lever is arranged to lock alternately the first and second wheels after each impulse transmitted.

Abstract: The escapement (10) includes first (6) and second (7) wheels meshing with each other. One (6) of these wheels is driven by the gear train. First (9) and second (11) rollers secured to a common arbor (1) support a sprung balance. The wheels (6, 7) and the first roller (9) are provided with means allowing said first roller to receive direct impulses supplied alternately by the first and second wheels for the purpose of maintaining the oscillations of the balance. The second roller (11) is provided with means for driving a locking and rocking member arranged to lock said first and second wheels alternately.

Abstract: This invention comprises a multi-sprocket or cluster gear assembly with a plurality of progressively sized sprockets or gears that are positioned adjacent to each other so as to define an increasing diameter sprocket assembly. Each sprocket comprises a non-circular configuration having at least one long dedendum radius and at least one short dedendum radius, such as an eccentric oval shape. The short radius and the long radius of two adjacent sprockets are aligned and substantially equal in length with each other. The teeth of the sprockets may comprise a chamfer face to better facilitate derailing from one sprocket to the adjacent sprocket. The axial alignment of one sprocket may be retarded by one tooth, relative to the axial alignment of the larger sprocket to better facilitate derailing.

Abstract: A drive unit for a forming machine, comprising a rotary drive and a knuckle-joint drive for a gear transmission operating a ram, the knuckle-joint drive being operationally connected through a gear transmission to the rotary drive. To improve the drive rigidity as regards a forming machine and to be able to improve the drive-unit design and to relatively easily match the drive unit to the specific requirements of different forming methods, the gear transmission offers a periodically varying transmission ratio, at least two mutually engaging non-circular gears being used of which the pitch curves are designed in such manner that in conjunction with the knuckle-joint drive, and especially in conjunction with a subsequent crank drive, the motions of the ram will be optimally matched thereby to the particular work method.

Abstract: A motor having gears which transmit rotations of a rotor to an output shaft through a gear mechanism made of gear trains, comprises a gear mechanism provided with an intermittent rotation mechanism including a primary gear which rotates upon receiving rotations of the rotor and a secondary gear which meshes with the primary gear and rotates intermittently. The primary gear has a tooth unit for driving the secondary gear, a tooth-shaped hole, which is provided adjacent to one side of the tooth unit and with which a meshing tooth of the secondary gear meshes, and a control unit which is provided adjacent to the other side of the tooth unit so as to stop the secondary gear for a given period such that the primary gear is asymmetric around the tooth unit. When the primary gear rotates in a predetermined direction, the meshing tooth meshes with the tooth-shaped hole to intermittently rotate the secondary gear.

Abstract: A variable gear assembly has a cam gear with a plurality of teeth of varying size and configuration, and a rotatably mounted roller gear has a plurality of rollers for meshing engagement with the teeth. The distance of each roller from the rotation axis and the angles between adjacent rollers are predetermined such that, at any time during a rotation cycle, two rollers engage at least one currently active tooth. The assembly provides a variable gear ratio.

Abstract: A gear drive system for a printer designed to print upon a continuous roll of paper and having a blade used to cut off printed portions of paper from the paper roll is implemented. The gear drive system consists of a drive shaft 330, a slip clutch 401, a clutch gear 116, a drive gear 110, and a staggered gear 112 which controls the paper cutter blade 106. During printing, clutch 401 allows the drive shaft 330 shaft to slip relative to the clutch gear 116. When printing stops, clutch 401 locks clutch gear 116 which is engaged with the first portion of staggered gear 112 and causes staggered gear 112 to rotate until the second portion of staggered gear 112 engages the drive gear 110. Staggered gear 112 is then driven by the drive gear 110. A cutter blade is controlled by staggered gear 112, with the blade cutting off the paper as the drive gear 110 is in reverse rotation.

Abstract: A power transmission apparatus adapted for an apparatus such as a camera or the like includes a first toothed wheel having teeth at least one predetermined tooth of which differs in tooth thickness from at least one different tooth of the teeth, a second toothed wheel which meshes with the first toothed wheel, the second toothed wheel having tooth spaces at least one predetermined tooth space of which meshes with the at least one predetermined tooth of the first toothed wheel and differs in space interval from at least one different tooth space of the tooth spaces, a determination device which determines a rotating position of the first toothed wheel, and an operating device which performs a predetermined operation according to a rotating position of the second toothed wheel.

Abstract: A gear drive system for a printer designed to print upon a continuous roll of paper and having a blade used to cut off printed portions of paper from the paper roll is implemented. The gear drive system consists of a drive shaft 330, a slip clutch 401, a clutch gear 116, a fixed gear 110, and a staggered gear 112 which controls the paper cutter blade 106. During printing, clutch 401 allows the drive shaft 330 shaft to slip relative to the clutch gear 116. When printing stops, clutch 401 locks clutch gear 116 which is engaged with the first portion of staggered gear 112 and causes staggered gear 112 to rotate until the second portion of staggered gear 112 engages the fixed gear 110. Staggered gear 112 is then driven by the fixed gear 110. A cutter blade is controlled by staggered gear 112, with the blade cutting off the paper as the fixed gear 110 is in reverse rotation.

Abstract: A motor having gears which transmit rotations of a rotor to an output shaft through a gear mechanism made of gear trains, comprises a gear mechanism provided with an intermittent rotation mechanism including a primary gear which rotates upon receiving rotations of the rotor and a secondary gear which meshes with the primary gear and rotates intermittently. The primary gear has a tooth unit for driving the secondary gear, a tooth-shaped hole, which is provided adjacent to one side of the tooth unit and with which a meshing tooth of the secondary gear meshes, and a control unit which is provided adjacent to the other side of the tooth unit so as to stop the secondary gear for a given period such that the primary gear is asymmetric around the tooth unit. When the primary gear rotates in a predetermined direction, the meshing tooth meshes with the tooth-shaped hole to intermittently rotate the secondary gear.

Abstract: The invention concerns a drive unit for a forming machine, comprising a rotary drive and a knuckle-joint drive for a gear transmission operating a ram, the knuckle-joint drive being operationally connected through a gear transmission to the rotary drive. To improve the drive rigidity as regards a forming machine and to be able to improve the drive-unit design and to relatively easily match the drive unit to the specific requirements of different forming methods, the gear transmission offers a periodically varying transmission ratio, at least two mutually engaging non-circular gears being used of which the pitch curves are designed in such manner that in conjunction with the knuckle-joint drive, and especially in conjunction with a subsequent crank drive, the motions of the ram will be optimally matched thereby to the particular work method.

Abstract: Apparatus to drive a bicycle wherein two pedals move in a non-fixed, non-180 degree relationship to each other. As the pedal that is being powered by the user moves through an arc less than 180 degrees, the unpowered pedal moves through more than 180 degrees to a point where it is in a favorable position to be powered by the user. Two different systems are disclosed, each producing the desired relative pedal motion. The first and preferred system describes the use of non-circular gears. The second system describes the use of circular gears with sections of teeth removed.

Abstract: A windshield wiper drive mechanism which interconnects a motor and a wiper assembly which is movable between an in-wipe position and an out-wipe position on a windshield. The drive mechanism includes an elliptical gear set having a pair of eccentric gears driven by the motor and mounted on first and second idler shafts which are rotatable about first and second axes, respectively. An elliptical output gear is mounted on an output shaft which, in turn, is rotatable about an output axis. The elliptical output gear is disposed between the pair of eccentric gears such that the first and second eccentric gears engage the elliptical gear at positions substantially 180.degree. opposite one another on the elliptical gear and so that the respective axes of the first and second idler shafts as well as the output axis of the output shaft lie in a single fixed plane.

Abstract: An elevator safety based on having the elevator lift-rod, under the influence of the elevator governor, cause to rotate approximately elliptical cams, called quasi-elliptical cams. The cams are wider in one orientation, just as an ellipse has a major axis, wider than its minor axis. The cams are positioned to push against a brake pad as they rotate so that the major axis of each cam changes orientation with the minor axis. The cams can be shaped to simulate a wedge-type safety, even one using a wedge with multiple ramp angles. With essentially no additional complexity, the cam safety can be designed to operate with a bi-directional governor, one which exerts, usually through an intermediate linkage, force on the lift-rod in either the up or down motion depending on the unintended motion of the elevator.

Abstract: A bicycle is disclosed with a rhombus-like (preferably 60.degree.-120 .degree.), with circularly curved apexes, drive sprocket gear and a circular driven sprocket on the ear driven wheel. This gear arrangement varies the overall power input from the drive sprocket to the driven gear. The shape of the drive sprocket and the location of the drive pedal changes the gear ratio so that a low gear ratio is utilized during the horizontal portion of movement of the cyclist's legs and a high gear ratio is utilized during the vertical movement of the legs. The gear ratio with the rhomboidal gear is relatively constant during horizontal movement and abruptly changes at the approach to and during vertical movement of the cyclist's legs. While the rhombus-like, with circularly curved apexes, gear is shown primarily for bicycles it may be used in other systems for converting reciprocal to rotary movement with a change in gear ratio.

Abstract: A tape loading device includes: a plate, cam which moves in a straight line at a constant speed; a rack provided on the plate cam; an arm load gear provided with a gearwheel which engages with the rack and rotates as the plate cam executes linear motion; a lever mechanism which moves as the arm load gear rotates; a tape guide provided at the end of the lever mechanism which withdraws the tape from the cassette starting from the unloaded position and finishing in the loaded position; and a guide member provided with a guide hole which guides the tape guide from the unloaded position to the loaded position. The gearwheel on the arm load gear which engages with the rack includes a first tooth having a pitch circle of a first radius, and a second tooth having a pitch circle of a second radius which is larger than the first radius so as to prevent tape slack by slowing the tape loading process down just before the process ends.

Abstract: An eccentric crank mechanism which communicates motion between a reciprocating piston and a rotary shaft comprising a crank pin having a connecting rod of the piston concentrically journaled thereon. The crank pin has an eccentric motion profile relative to the axis of the rotary shaft, the eccentric motion profile being controlled by a driving connection between a stator and a rotor which carries the crank pin. The rotary motion of the rotor and the rotary shaft is communicated one to the other by a journaled connection between the rotor and an eccentric journal of the rotary shaft. The driving connection comprises toothed grooving. The profile of the stator and rotor determines the eccentric motion profile.

Abstract: A plunger pump suitable for an apparatus for injecting liquid under high pressure through a plurality of nozzles (104) into the turf. A plunger (34) of the pump is connected through a connecting rod (39) to a crank shaft (12) for the reciprocation thereof, and the crank shaft is more quickly rotated through its angle of rotation at the discharge stroke than through the angle of rotation at the suction stroke of the plunger to increase discharge pressure of the liquid upon its intermittent injection.

Abstract: A hardgeared infinitely variable transmission (IVT) is provided in which at least one quick return mechanism is hardgeared to the rotating transmission input shaft. The quick return mechanisms convert the rotating motion of the transmission input shaft to a variable motion consisting of a near constant linear velocity portion and a rapid return portion for each cycle of input rotation. The near constant linear velocity portion of the motion of each quick return mechanism is selectively engaged to a conversion device which translates the motion to an output rotation. The input/output speed ratio is adjusted by varying the amount and direction of quick return mechanism motion which is selectively engaged to the conversion device. An infinite range of speed ratios can be produced, as well as output rotation in both forward and reverse directions relative to the input rotation.

Abstract: Silk-screen printing apparatus is provided for the silk-screen printing of articles such as oval-shaped bottles and containers on the two major curved peripheral surfaces thereof, sequentially, with one printing pass. The apparatus utilizes, in this case, two squeegees positioned one behind the other and synchronized in such a manner as to force ink through a screen provided with two image patterns as each of the two image patterns on the screen moves sequentially over the two curved surfaces to be printed.

Abstract: A rotary piston engine (20) is shown which includes a housing (22) having a cylindrical working chamber with inlet (56) and exhaust (54) ports. First and second piston assemblies (30 and 32) each of which includes at least one pair of diametrically opposed pistons (30A and 30B, and 32A and 32B) are located in the working chamber. Backstopping clutches (44 and 46) limit rotation of the piston assemblies (30 and 32) to one direction (42). Piston assemblies (30 and 32) are connected to the engine output shaft through a differential (78) and non-circular gear sets (74 and 76), each of which gear sets includes a tear-drop shaped gear (74A and 76A) and heart shaped gear (74B and 76B). When the cusp of the tear-drop shaped gear engages the recess in the heart shaped gear, the tear-drop shaped gear is prevented from rotating. The piston assemblies rotate intermittently whereby pistons of the stopped assembly are trailing pistons during portions of the power and intake phases of engine operation.

Abstract: A rotary piston engine (20) is shown which includes a housing (22) having a cylindrical working chamber with inlet (56) and exhaust (54) ports. First and second piston assemblies (30 and 32) each of which includes at least one pair of diametrically opposed pistons (30A and 30B, and 32A and 32B) are located in the working chamber. Backstopping clutches (44 and 46) limit rotation of the piston assemblies (30 and 32) to one direction (42). Piston assemblies (30 and 32) are connected to the engine output shaft through a differential (78) and non-circular gear sets (74 and 76), each of which gear sets includes a tear-drop shaped gear (74A and 76A) and heart shaped gear (74B and 76B). When the cusp of the tear-drop shaped gear engages the recess in the heart shaped gear, the tear-drop shaped gear is prevented from rotating. The piston assemblies rotate intermittently whereby pistons of the stopped assembly are trailing pistons during portions of the power and intake phases of engine operation.

Abstract: A measuring device includes a measuring mechanism, a counting mechanism, a variable transmission gear assembly disposed between the measuring mechanism and the counting mechanism, and an adjustment member that engages at the gear assembly for changing the transmission ratio. The gear assembly includes a first shaft and a second shaft which are arranged parallel to one another. First and second out-of-round toothed spur gears are seated on the first shaft. An overrunning clutch is disposed between each one of the first and second spur gears and the first shaft, both overrunning clutches acting in the same direction of rotation. Third and fourth out-of-round spur gears are seated on the second shaft and mesh with the respective first and second spur gears. The third spur gear is rigidly fastened on the second shaft. The fourth spur gear is rotatably mounted on the second shaft.

Abstract: In a non-circular gear pair comprising two non-circular gears maintained engaged, those gears have first and second intermeshing rotation parts in such a manner that the first intermeshing rotation part forms an intermeshing pitch curve with which the speed of rotation is given to one of the two gears which changes exponentially with respect to the speed of rotation of the other non-circular gear, and the second intermeshing rotation part is extended between the start and en-d points of the first intermeshing rotation part so as to form an intermeshing pitch curve with which the rotation speed ratio and the angular acceleration ratio change continuously, whereby the rotation speed and the angular acceleration change continuously throughout the first and second intermeshing rotation parts including the connecting points thereof.

Abstract: Improved rotary engines and related rotary mechanisms have a pair of interfitted rotor discs with peripheral rotor heads that define a circular series of chambers in a housing. A non-circular gear is secured to the output/control shaft of each rotor, with the non-circular gears meshing with complementary non-circular gears provided on a common power output shaft. The non-circular gears are configured and oriented such that the distance from its output/control shaft at which one of the non-circular gears engages the complementary non-circular gear on the common power output shaft never simultaneously equals the distance from its output/control shaft at which the other non-circular gear engages the corresponding complementary non-circular gear on the common power output shaft.

Abstract: A bidirectional synchronous gearing mechanism includes a first gear with a first and second gear profile and a second gear identical to the first gear and with identical first and second gear profiles. The teeth of the two gears are meshed together and the gears are rotatably secured about their respective central axes. Rotation of one of the gears causes rotation of the other gear in an opposite direction.

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 rolling joint is provided for obtaining slewing maneuvers for various apparatuses including space structures, space vehicles, robotic manipulators and simulators. Two noncircular cylinders, namely a drive and a driven cylinder, are provided in driving contact with one another. This contact is maintained by two pairs of generally S-shaped bands, each pair forming a generally 8-shaped coupling tightly about the circumferential periphery of the noncircular drive and driven cylinders. A stationarily fixed arm extends between and is rotatably journalled with a drive axle and a spindle axle respectively extending through selected rotational points of the drive cylinder and of the driven cylinder. The noncircular cylinders are profiled to obtain the desired varying gear ratio.

Abstract: A driving apparatus with a speed changer for a bicycle using a pair of non-circular gears for performing an exponential function angular velocity modulation for the speed changer. The driving apparatus is provided with a primary angular velocity modulating mechanism having a first non-circular gear fixed to a first rotary shaft receiving driving power and a second non-circular gear supported to a second rotary shaft, a secondary angular velocity modulating mechanism having the second non-circular gear and a third non-circular gear supported to a third rotary shaft generating driving power through a one-way clutch, and a spring for increasing a relative angle between the first and the third rotary shafts around the second rotary shaft.

Abstract: An engine starter apparatus comprising first and second noncircular gears, a pinion, and a starter motor. The pair of noncircular gears is interposed between a crankshaft and a ring gear of an engine, and when the speed of rotation of the first noncircular gear is kept constant, the second noncircular gear rotates the crankshaft while cyclically causing a change in the angular velocity due to its profile. Since the second noncircular gear is positioned so that the change in the angular velocity caused by its rotation can cancel a change in torque of the crankshaft, the change in the torque of the engine are not transmitted to the starter motor, thereby operating the starter motor at constant current at all times, providing such additional advantages as smaller and lighter starter motor design and reduced noise.

Abstract: A steering apparatus capable of changing a steering angle ratio of dirigible road wheels relative to a rotation amount of a steering wheel. The steering apparatus includes an input member arranged to be operatively connected to the steering wheel, a support shaft coaxially arranged with the input member and being interconnected with the input member for relative rotation on aligned axes, an output pinion rotatably mounted on the support shaft and being in mesh with the toothed portion of a rack member for operative connection with the dirigible road wheels, and a differential gear mechanism including an input sun gear mounted on the support shaft at a position adjacent the output pinion, first and second planetary gears respectively in mesh with the input sun gear and the output pinion and being rotatably mounted on a common shaft, and a carrier supporting thereon the common shaft and being arranged to be rotated about the support shaft.

Abstract: A translation cam arrangement comprises a translation cam and an accentric gear rotatably secured to the translation cam, and as the eccentric gear is rotated by a driving gear meshed therewith, the translation cam reciprocates in correspondence with various distances between centers of both the gears. Thus, there is no need of another cam arrangement for moving the translation cam.

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 angular velocity modulating device comprises: a primary angular velocity modulating means including a first non-circular gear which is an internal gear rotatably supported and a second non-circular gear which is an external gear mounted on a second rotary shaft and engaged with the first non-circular gear; a secondary angular velocity modulating means including the first non-circular internal gear and a third non-circular gear which is an external gear mounted on a third rotary shaft and engaged with the first non-circular gear; a first frame rotatably supporting the first non-circular gear and the second rotary shaft; and a second frame rotatably supporting the third rotary shaft, the ratio in angular velocity of the third rotary shaft to the second rotary shaft being the quotient of the secondary angular velocity ratio of the first and second non-circular gears divided by the primary angular velocity ratio of the first and third non-circular gears, whereby the device can be small in size in a radial direc

Abstract: A starter includes a speed changing mechanism for transmitting rotational force of an electric motor to a pinion gear capable of being brought into or out of engagement with a ring gear of an engine. The speed changing mechanism includes a geared stepless speed changer. A speed reduction ratio is controlled responsive to a load change by means of an input shaft, an output shaft, and input and output frames rotatable relative to each other about the input shaft. A ratio of angular velocities of the input and output shafts is related to an angle of rotation between the input and output frames.

Abstract: A modified gear operates in one direction only. The modified gear can be driven in either direction by a standard gear, but will drive another gear in only one direction. Every other tooth of the modified gear is partly cut away to form a step. The remaining sides are cut away to delay engagement with a driven gear. The sides of the teeth preferably have the shape of an involute curve, and each tooth is preferably cut along a line segment beginning at the midpoint of the top land of the tooth, and continuing along a path generally parallel to one side of the tooth. The step is located at a predetermined radial distance from the top land, this distance being a certain fraction of the total depth of the tooth. The modified gear can be used to drive, or be driven by, a conventional unmodified gear. It can also drive, or be driven by, another gear which has been modified in the manner described above.

Abstract: The invention disclosed herein provides a device which a non-linear force/distance relationship of spring or other device and linearizes it in a range of interest. In accordance with the invention, the device comprises a first gear section and a second gear section. The first and second gear sections are pivotally supported in a meshing relationship. The first gear section includes gear teeth extending about an arc of a first circle having a first center, and the second gear section includes gear teeth extending about an arc of a second circle having a second center. The mating pair of sections comprise a non-circular gearing pair. For limited ranges of motion the non-circular gears can be approximated by eccentrically mounted circular gears. The two gear sections thus pivot eccentrically with respect to each other such that a variable torque or force must be applied to one gear section to obtain a constant torque or force from the other gear section, and vice versa.

Abstract: An improved oscillating sprinkler comprising a frame having a sprinkler tube mounted for oscillating movement on the frame. An inlet water housing is mounted on the frame and supplies water to the sprinkler tube. The sprinkler tube is driven in an oscillating path by a crank arm, and an eccentric gear mechanism driven by the water being supplied to the sprinkler tube is operably connected to the crank arm. The eccentric gear mechanism is constructed to provide a variable speed output that balances the varible speed output of the crank arm to provide a substantially uniform velocity of oscillating movement for the sprinkler tube. The sprinkler also includes a mechanism for varying the effective length of the crank arm to change the arc of oscillation of the sprinkler tube, and a slip clutch mechanism interconnects the inner end of the sprinkler tube to the housing to permit the sprinkler tube to be manually rotated to shift the spray pattern to one side or the other.

Abstract: A tooth according to the invention is such that its flank (foot flank) (1B) situated inside the not entirely circular pitch curve (PA) follows an involute of a circle determined by a pressure angle (p), and has a face (2B) outside the pitch curve such that its current point (M) is determined by the intersection of the flank (1A) of the co-operating tooth with the tangent to the circles defining the flank (1A) passing through the instantaneous point of contact (N) of the pitch curves (P'A, P'B). The pitch curves may be circular arcs, logarithmic spiral arcs, elliptical arcs, or a succession of such arcs around an open or a closed curve in order to form gearing. Some lengths of the pitch curves may have no teeth.

Abstract: An internal combustion engine comprising a piston slidably disposed for rectilinear reciprocal movement within a cylinder. A drive rack pivotally mounted to the piston carrys a continuous internally facing row of teeth. A drive gear nonrotatably keyed to a drive shaft and internally adjacent to the continuous row of teeth engages a portion of the drive rack teeth. A runner guides the drive rack such that the drive gear cooperatively associates with the drive rack teeth to convert rectilinear movement of the reciprocating piston into rotary movement. One or both of the drive gear and the drive rack are shaped in accordance with the variable forces exerted on the piston during its motion so as to apply torque more evenly to the crank shaft.

Abstract: A stepless transmission of the non-friction type is provided using intermeshing non-circular gears. The transmission is made up of a number of angular velocity modulators each having first, second, and third shafts. Each shaft carries a non-circular gear thereon which meshes with the gear of a succeeding shaft. The angular velocity ratio .omega. of the third shaft of each modulator relative to the first shaft depends on the pitch curve of the intermeshing non-circular gears and on the position of the third shaft relative to the position of the first and second shafts. By changing the position of the third shaft the angular velocity ratio .omega. of the modulator can be steplessly varied. The output of the third shafts of each modulator are combined onto a common shaft by one the clutches to provide a continuous output. The position of the third shafts, and thus the overall ratio of the transmission, may be controlled automatically by a spring.

Abstract: An intermittent drive mechanism includes a pair of non-circular drive and driven gears for translating a constant velocity rotary motion of an input shaft into a non-uniform velocity rotary motion of an intermediate shaft, the latter-mentioned rotary motion having a sinusoidal angular speed pattern, and a harmonic speed reducer drivingly connecting the intermediate shaft to an output shaft which is connected to a flexible spline of the speed reduce. A rigid circular spline of the speed reducer is angularly reciprocated under the control of an eccentric cam on the input shaft in such a manner that the motion of the sinusoidal angular speed pattern is transmitted from the intermediate shaft to the output shaft in a certain decelerated condition only while the intermediate shaft turns through a half of each turn. The motion transmission takes place gently without causing undesired shock at the beginning and the end of the motion.

Abstract: A timing mechanism controls various functions of an ice maker through cams carried on a camshaft. A harvest rake that removes ice from a receptacle is coupled to the camshaft to be rotated thereby. The camshaft is driven by a motor which is coupled to the timing mechanism through a pair of non-circular meshing gears. The gears are programmed such that a slower speed is imparted to the camshaft when ice is being removed from the receptacle by the harvest rake. This provides a slower speed but higher torque to the harvest rake during ice removal and a faster, more accurate timing rate during filling of the receptacle.