Abstract: A transmission gear has a tooth surface formed of a free-form surface instead of an involute surface and a root area formed of a free-form surface instead of a trochoid surface. With such a transmission gear, the fatigue strength against contact pressure can be increased by reducing the Hertzian stress in the area around the meshing point of the tooth surface. The tooth surface is formed of a free-form surface in which the smallest radius of curvature in an area around a mating pitch point is maximized, and the fatigue strength against bending can be increased by reducing the bending stress at a tooth root portion of the bottom land. In addition, the gear noise can be reduced. The bottom land is formed of a free-form surface in which the smallest radius of curvature in an area around a tooth root is maximized.

Abstract: A gear includes a gear root defined by a stretched root blended into an involute tooth profile curve within a True Involute Form diameter.

Abstract: A half of a tooth right-angled cross-sectional shape in a tooth bottom side area of a tooth divided at a tooth bottom center is defined by a first involute portion extending from the tooth bottom center P0 toward a tooth surface, an arcuate portion connected smoothly to the first involute portion, a second involute portion connected smoothly to the arcuate portion, a third involute portion connected smoothly to the second involute portion, and a tooth surface connecting curved portion connecting the third involute portion and the tooth surface smoothly. Radii of curvature of the arcuate portion and the first, second and third involute portions are determined so that a stress variation width in a stress state of a so-called partly reverse state caused by tensile stress and compression stress generated in the tooth bottom side area of the tooth before and after the meshing of the tooth can be uniformized.

Abstract: A double involute pinion-face gear drive provides transmission of torque and speed, or direction of movement modification between non-intersecting shafts at right angles to one another. A double involute cylindrical pinion on one axis, engages a rotatable disk-shaped gear on the second axis. The teeth of the pinion are curved in an abridged, normal or extended involute shape. Likewise, the teeth of the face gear are curved in abridged, normal or extended involute shape in the lengthwise direction of the teeth. These gear drives can be simultaneously bi-rotational and bi-directional and allow a relatively wide range of speed ratios, as low as 1:1 and as high as 7.5:1.

Abstract: A rack and pinion arrangement includes rack and pinion rods having a carrier bar, a guide bar and inner rack and pinion teeth for interaction with a driving sprocket. An end tooth at both ends of the each rack and pinion rod has a change in radius of curvature, and the tooth profile of the inner rack and pinion teeth has a change in radius of curvature. The change in radius of curvature of the end teeth is lower than the change in radius of the inner rack and pinion teeth. The end tooth head of the end teeth is lower than the tooth heads of the inner rack and pinion teeth. The end tooth in the region of the change in radius of curvature has a greater tooth width than the inner rack and pinion teeth in the region of the change in radius of curvature.

Abstract: An oilfield pumping unit two-stage transmission gear reducer includes a low speed stage having a low speed shaft configured to receive motion from an intermediate shaft. A first gear pair includes a low speed shaft double circular arc gear mounted on the low speed shaft and configured to be driven by an intermediate shaft double circular arc gear mounted on the intermediate shaft. A high speed stage includes a high speed shaft configured to receive motion from an intermediate shaft. A second gear pair has a high speed shaft involute gear mounted on the high-speed shaft and configured to be driving an intermediate shaft involute gear mounted on the intermediate shaft.

Abstract: An oilfield pumping unit two-stage transmission gear reducer includes a low speed stage having a low speed shaft configured to receive motion from an intermediate shaft. A first gear pair includes a low speed shaft double circular arc gear mounted on the low speed shaft and configured to be driven by an intermediate shaft double circular arc gear mounted on the intermediate shaft. A high speed stage includes a high speed shaft configured to receive motion from an intermediate shaft. A second gear pair has a high speed shaft involute gear mounted on the high-speed shaft and configured to be driving an intermediate shaft involute gear mounted on the intermediate shaft.

Abstract: A functional portion of an edge of each tooth of the toothed wheel has a profile which complies with the parametric double formula (in Cartesian coordinates): x ? ( u ) = R 1 ? [ cos ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) - u ? ? sin ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) ] y ? ( u ) = R 1 ? [ sin ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) + u ? ? cos ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) ] where R1=d1 cos(??a tan ?), ? and d1 being parameters, where ? is a parameter which corresponds to the coefficient of friction at the contact between said edge and an edge of a tooth of another wheel, ? being able to take values between 0.05 and 0.5, and where u is a variable which varies in the interval (0, 1/?) such that by varying u, the profile is passed through.

Abstract: An eccentrically cycloidal gear engagement of tooth profiles having curvilinear teeth is disclosed. One of the engaging profiles represents a gearwheel with at least two helical teeth. The flanks of each tooth of the first tooth profile are outlined, in a principal cross-section of the gearwheel, by corresponding arcs of circular curves, eccentrically shifted from a center of rotation of the gearwheel. The second tooth profile, which is conjugated with the first tooth profile, has helical cycloidal teeth. The teeth of the second tooth profile are outlined, in the same cross-section, by segments of front edges of intersecting cycloidal curves. Tips and troughs between teeth can have any shape, not intersecting with the gearwheel teeth.

Abstract: A space curve mesh driving pair and a polyhedral space curve mesh transmission are disclosed. Said space curve mesh driving pair consists of a driving wheel and a driven wheel. Axes of the driving wheel and the driven wheel are intersected at an angle of 0°˜180°, and power transmission is realized by continuous mesh between the driving tines and the driven tines; a number of driving tines are provided on said driving wheel, and a number of driven tines are provided on the driven wheel; the driving tines are uniformly arranged on an end face of a cylinder of the driving wheel, and the driven tines are uniformly arranged on the circumference of a cylindrical surface of the driven wheel. Said polyhedral space curve mesh transmission consists of an above-mentioned space curve mesh driving pair. Motion is input from an input end, and is passed through a number of pace curve mesh driving pairs to realize the speed change, then is output from one or more output ends.

Abstract: A method for establishing the gearing geometries of a gear pairing of two gears with intersection axes comprises the following steps: predetermining a first gearing geometry of a virtual first gear; calculating the geometry of the gearing of a virtual second gear, this geometry resulting during conjugated creation from a roll-off process of a tooth (1) of the predetermined geometry of the virtual first gear, whereby the roll-off process of the tooth (1) of the virtual first gear, this roll-off process underlying the calculation, is ended in the symmetrical position thereof in the tooth gap (3) of the second virtual tooth; calculating the tooth face geometry of the teeth of the first gear, this tooth face geometry resulting during the reverse conjugated creation, while underlying a full roll-off process of a tooth of the virtual second gear with the first; establishing the final geometry of the gearing of the first gear according to the tooth face geometry of the gearing of the first gear, this tooth face geom

Abstract: A drive unit that is movable between an unfired and a fired position. The drive unit comprises a handle member, a first drive gear having a first axis of rotation, and a second drive gear, engaged to the first drive gear at a mesh point, and having a second axis of rotation. The mesh point moves with respect to the axes of rotation as the handle member moves from the unfired position to the fired position. The drive unit drives an implement only when it is moved from the unfired position to the fired position.

Abstract: A rack-and-pinion steering apparatus comprises pinion teeth formed according to proper tooth specifications in other aspects under a larger pressure angle, thereby stably offering smooth and comfortable steering feeling over a long time. The module (m), number of teeth (z), tooth depth (h) and helix angle (?) of the pinion teeth (4) are set within the following ranges, under a pressure angle (?) set within a range of 24° to 30° and a given stroke ratio. module (m): 1.8 to 2.0 number of teeth (z): 7 to 13 tooth depth (h): 2 m to 2.

Abstract: In a wave gear device (1), radial deflection of a flexible external gear (3) is set at 2?mn (?>1) which is larger than a normal deflection of 2nm (?=1), and the tooth depth of both gears (2, 3) is set larger than a standard tooth depth (in case of ?=1). Meshing movement locus of both gears (2, 3) is approximated by a rack in case of ?>1, and using similarity-transformation curves (AC, AD) obtained by similarly enlarging a curve (AB) on the unmeshing side at the post-stage of meshing from the vertex (deepest meshing position)(A) of the movement locus (M), the dedendum tooth profile portion (21) of a rigid internal gear (2) and the addendum tooth profile portion (31) of the flexible external gear (3) are defined and then both gears (2, 3) are brought into continuous contact.

Abstract: A gear pump rotor is provided including a combination of an inner rotor and an outer rotor whose numbers of teeth are different by one, and the discharge amount of the pump is increased by an increase of the tooth depth. At least one of an addendum curve and a dedendum curve of an inner rotor is formed by a locus of one point on formation circles that satisfy moving conditions that the formation circles move from moving start points to moving end points while changing the distances from an inner rotor center to the centers of the formation circles. The centers of the formation circles move by a distance in the radial direction of a base circle, and the formation circles rotate by an angle at a constant angular velocity in the same directions of the moving directions of the formation circles.

Abstract: A gear and drive system utilizing the gear include teeth. Each of the teeth has a first side and a second side opposite the first side that extends from a body of the gear. For each tooth of the gear, a first extended portion is attached to the first side of the tooth to divert flow of fluid adjacent to the body of the gear to reduce windage losses that occur when the gear rotates. The gear may be utilized in drive systems that may have high rotational speeds, such as speeds where the tip velocities are greater than or equal to about 68 m/s. Some embodiments of the gear may also utilize teeth that also have second extended portions attached to the second sides of the teeth to divert flow of fluid adjacent to the body of the gear to reduce windage losses that occur when the gear rotates.

Abstract: A rotational-to-linear conversion mechanism inhibits interference from occurring in places except for an engagement site to increase the efficiency of conversion mechanism and reliability, which has: a rack rod 1 including thread on its outer peripheral face; a holder member 3 provided on the outer periphery of the rack rod, rotating about the rack rod and moving in the axis direction; and revolving rollers 21 rotatably supported in the holder member, each having ring-shaped grooves formed in its outer peripheral face to be engaged with the thread, and placed at an axis angle with respect to a center axis of the rack rod to allow the ring-shaped grooves to be engaged with the thread on the rack rod. A contact face of the thread with each ring-shaped groove in an engagement site of the thread and the ring-shaped groove is formed as a convex face having different curvatures in a radial direction.

Abstract: An improved geared hydraulic apparatus, comprising a pair of meshing gearwheels, mounted to be reciprocally rotatable in a casing between an inlet side and an outlet side for a fluid having, in use, a substantially transverse flow with respect to the axes of rotation of the gearwheels. The meshing gearwheels create, during their reciprocal rotation, progressive meshing configurations between respective co-operating teeth. In at least one of said progressive meshing configurations is defined, in at least one cross-section of the gearwheels, at least one closed area between respective fluid entrapment teeth. The closed area decreases until it is substantially cancelled out at and around at least one other, separate progressive meshing configuration between the aforesaid respective co-operating teeth.

Abstract: A gear having a tooth form shape including, on a tooth root side of a tooth, a first curved surface connected to a tooth face of an involute tooth form and convex in a direction opposite to the tooth face, a flat surface connected to the first curved surface, and a second curved surface connected to the flat surface and convex in the same direction as the first curved surface. In a normal plane, the shape of the flat surface is a tangent in contact with a tip side end of a trajectory of motion of a tooth of a meshing partner gear and intersecting with a tooth form center line at a 30° angle, the shape of the first curved surface is circular arcs in contact with the tangent, and, the shape of the second curved surface is circular arcs in contact with the tooth face and the tangent.

Abstract: An easily structured swing internal contact type planetary gear device is proposed which can achieve a higher meshing ratio when an involute tooth profile is adapted. Each of an internal tooth of an internally toothed gear wheel and an external tooth of an externally toothed gear wheel is formed with an involute tooth profile. Under a driving condition, one of an internal tooth body of the internally toothed gear wheel and an external tooth body of the externally toothed gear wheel is elastically deformed in an extending direction and the other thereof is elastically deformed in a contracting direction so that the number of meshing teeth becomes larger than the number of meshing teeth under a non-driving condition.

Abstract: A pump rotor is an inner rotor of an internal gear pump, the inner rotor having a tooth profile, wherein a half-tooth portion of the tooth profile is formed of three tooth-profile formation circles that are elliptical or true-circular. Two of the tooth-profile formation circles are a combination of a small tooth-profile formation circle and a large tooth-profile formation circle in which the small tooth-profile formation circle is inscribed and is entirely included. A portion of the small tooth-profile formation circle forms an addendum portion of the half-tooth portion. A portion of the large tooth-profile formation circle in which the small tooth-profile formation circle is inscribed and is entirely included forms an engagement portion of the half-tooth portion. A portion of another tooth-profile formation circle that circumscribes the large tooth-profile formation circle forms a dedendum portion of the half-tooth portion.

Abstract: The invention relates to the gearing of a gearwheel having a plurality of teeth. The gearwheel has a useful area and a base area of the particular tooth flank form. Viewed in normal section, the tooth base area extends from a base circle up to a useful circle. The tooth flanks of adjacent teeth in normal section are each implemented as symmetrical to one another, the axis of symmetry intersecting the base circle in the base point. According to the invention, the tooth flanks are implemented in the tooth base area as a tangent function from a relevant diameter. The tangent function merges at the relevant diameter in a constant tangent into the tooth flank form of the useful area. The tangent function merges in the tooth base area in a constant tangent into an orbit, which is tangentially applied in the base point to the base circle. Significant increases of the tooth base strength may thus be achieved.

Abstract: A transmission gear has a tooth surface formed of a free-form surface instead of an involute surface and a root area formed of a free-form surface instead of a trochoid surface. With such a transmission gear, the fatigue strength against contact pressure can be increased by reducing the Hertzian stress in the area around the meshing point of the tooth surface. The tooth surface is formed of a free-form surface in which the smallest radius of curvature in an area around a mating pitch point is maximized, and the fatigue strength against bending can be increased by reducing the bending stress at a tooth root portion of the bottom land. In addition, the gear noise can be reduced. The bottom land is formed of a free-form surface in which the smallest radius of curvature in an area around a tooth root is maximized.

Abstract: An idler gear assembly for a generator includes a first gear configured for coupling to a second gear. The first gear includes a first shaft aligned along a first shaft axis, the first shaft having a first shoulder with a first axial face and a second shoulder with a second axial face diametrically opposed from the first axial face, diametrically opposed first and second grooves about a circumference of the first shoulder and a first set of teeth circumferentially located about the first shaft axis, the first shaft includes a first axial distance from the first axial face to the second axial face. The second gear includes a second shaft aligned along a second shaft axis, the second shaft having a diametrically opposed first and second tangs, and a second set of teeth circumferentially located about the second shaft axis, the second shaft includes a second axial distance.

Abstract: A gear having a tooth form shape includes, on a tooth root side of a tooth, (1) a first curved surface connected to a tooth face of an involute tooth form and convex in a direction opposite to the tooth face, (2) a flat surface connected to the first curved surface, and (3) a second curved surface connected to the flat surface and convex in the same direction as the first curved surface. The shape of the flat surface in a normal plane is a tangent in contact with a tip side end of a trajectory of motion B of a tooth of a meshing partner gear and intersecting with a tooth form center line at a 30° angle. The shapes of the first and the second curved surfaces in a normal plane are circular arcs.

Abstract: A bending state known as “coning,” in which the amount of bending of the flexspline gradually decreases in accordance with the distance from the open end of the spline, occurs in cup-type or “silk hat”-type wave gear devices. A tooth profile in which the tooth depth is kept constant and in which the bottom lands and top lands are parallel to each other along the tooth trace direction is used as the basic tooth profile for the circular spline and the flexspline of the wave gear device. A taper surface is formed on a part of the top land near the open end of the flexspline in the basic tooth profile, whereby a modified tooth profile is obtained. The modified tooth profile is employed as the tooth profile for both of the splines. Both of the splines can be caused to mesh together without generating coning-induced interference. Both of the splines can also be subjected to gear cutting by a simple process using a typical machining mechanism.

Abstract: A method of designing a gear in which a tooth trace of the tooth flank, which is to be engaged with another mating tooth flank, is curved with respect to an axial direction of the body of the gear. The mating tooth flank of the mating gear is designed in such a manner that a desired tooth contact can be achieved. Accordingly, sufficient design precision can be attained. Furthermore, stress at the tooth flanks can be controlled when the gears are engaged with each other, thereby leading to high durability of the gears.

Abstract: An external gear pump which has a certain flow rate or volumetric capacity at a given speed can be taken apart and the parts rearranged and assembled into a second pump operating at the same speed with a flow rate or volumetric capacity that is different from the original pump. No new parts are required for the second pump configuration and all original parts are used. With this structure, pumps with different flow rates can be built using fewer parts than conventional designs.

Abstract: A gear pair includes a small-diameter conical involute gear having a conical angle, and a large-diameter conical involute gear having a conical angle. The small-diameter conical involute gear and the large-diameter conical involute gear are constituted by an aggregate of imaginary cylindrical gears.

Abstract: A power transmission device is provided with: a first gear having a plurality of teeth that share an identical tooth profile; an intermediate gear that is engaged with the first gear; and a second gear that is engaged with the intermediate gear, and has a plurality of teeth that share an identical tooth profile, wherein the first gear and the second gear have an identical number of teeth, an identical reference diameter, and an identical reference pitch; and the tooth profile of the first gear is different from that of the second gear.

Abstract: In a gear (G1) according to the present invention, which is provided with a plurality of teeth (1) to be mated with teeth of a mating gear to thereby transmit a rotational motion, a predetermined region (A) in at least one tooth flank (7) of each tooth (1) is formed in a configuration such that, from at least one place in a tooth width direction on a crossing (8) of the tooth flank (7) and a tooth tip surface (3), the mating with the teeth of the mating gear is started with the point contact or the line contact shorter than the total tooth width, and thereafter, is gradually shifted to the line contact so that the length of contact line (10) thereof is sequentially increased as the line contact moves from a tooth tip surface (3) side toward a tooth root side.

Abstract: A functional portion of an edge of each tooth of the toothed wheel has a profile which complies with the parametric double formula (in Cartesian coordinates): x ? ( u ) = R 1 ? [ cos ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) - u ? ? sin ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) ] y ? ( u ) = R 1 ? [ sin ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) + u ? ? cos ? ( 1 ? ? ln ? ( 1 - ? ? ? u ) ) ] where R1=d1 cos(??atan ?), ? and d1 being parameters, where ? is a parameter which corresponds to the coefficient of friction at the contact between said edge and an edge of a tooth of another wheel, ? being able to take values between 0.05 and 0.5, and where u is a variable which varies in the interval (0, 1/?) such that by varying u, the profile is passed through.

Abstract: A pump gear includes a pump gear body having involute teeth that each have an involute surface that extends between a tooth tip and a tooth base. The involute surface includes at least reference points A-D, with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D. The reference points A-D have associated respective roll angles, ?A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D, and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis.

Abstract: A gear for driving a linear member comprising a tooth tip, a tooth base, a contact face disposed between the tooth tip and the tooth base, the contact face having the shape, X=L sin(???) and Y=L cos(???), where tan(?)=(B/2+2??/360) /R, L=(R{circumflex over (0)}2+(B/2+2??/360/R){circumflex over (0)}2){circumflex over (0)}0.5, B=width of tooth base, R=pitch radius, ?=relative angle of gear tooth to contacting member, a linear member comprising a plurality of holes, and the contact face engagable with the linear member through a hole.

Abstract: A Cornu's spiral is applied to a tooth profile of a gear. In accordance with the application of the gear, the Cornu's spiral may be modified two-dimensionally by some constant proportion. Since Cornu's spirals have similarity are similar, when a pressure angle is determined, the tooth profile can be standardized by a module, so that it is highly versatile. By replacing the tip of a tooth and the bottom of a tooth by another curve, such as an arc, the range of application can be increased. Since working is always by flank contact between a protrusion and a recess, contact surface stress is low. In addition, the radius of curvature of a dedendum is large. Therefore, tooth bending stress is low, and fatigue strength is high. Even if the number of teeth is small, an undercut is not produced. Even if there is no backlash, a smooth working is achieved, so that the tooth profile is suitable for devices requiring precise alignment.

Abstract: The inventive gear drive comprises toothed wheels with teeth of toothed crowns interacting with single- or multi-flow elements. Working profiles of the interacting teeth comprise piecewise and/or pointwise conjugate, convex at a tooth point and concave at a tooth root arc-shaped sections continuously connectable to each other or to involute sections. The interacting toothed crowns are so embodied that a phase gap of the face tooth intermating at a discrete angle from a point, where the interaction of profiles ends at a point, where the interaction of the face profiles of the next tooth pair starts. The drive is so embodied that the face tooth overlap ratio thereof is less than 1. The so improved teeth provide for high level of the contact tightness and absence of axial forces at engagement, increase the structural flexibility of the gear drive teeth in order to improve their qualities.

Abstract: A rotor gear includes a rotor gear body having involute teeth that each have an involute surface that extends between a tooth tip and a tooth base. The involute surface includes at least reference points A-D, with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D. The reference points A-D have associated respective roll angles, ?A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis.

Abstract: This disclosure relates to a gear pair for power transmission in a speed increaser or reducer and its tooth profile forming method. The tooth profiles of driving gear and driven gear are separately designed from reference points. The upper tooth profiles are composed of conjugate curves, while the lower tooth profiles are composed of smooth convex analytic curves. The reference point of the driven gear is located adjacent the middle of the working depth. The reference point on the tooth profile of the driving gear and the reference point on the driven gear tooth flank are a pair of conjugate points.

Abstract: The invention relates to a gear pair consisting of a crown gear (1) and of a pinion gear (2) provided in the form of a spur gear with an axis crossing angle of 90°. According to the invention, the teeth (3) of the pinion gear (2), in order to reduce an undercut of the teeth (5) of the crown gear (1), have a pressure angle, which increases from the outside inward in a radial direction with regard to the crown gear (1), or in the event of a constant pressure angle, have a profile offset, which decreases from the outside inward in a radial direction with regard to the crown gear (1).

Abstract: A resin gear has a plurality of teeth on an outer periphery thereof. One surface of each tooth has a tooth plane which meshes with another gear. The tooth thickness is substantially uniform from a tooth tip to a tooth root. A reinforcing rib is provided on the surface of each tooth on the opposite side from the tooth plane.

Abstract: A gear set for a generator includes a first gear having a first set of involute teeth and a second gear having a second set of involute teeth circumferentially located about a center axis of rotation. Each set of involute teeth includes respective roll angles, ?A-D. For a diametrically smaller one of the first gear and the second gear the roll angle ?A is 1.51°-3.51°, the roll angle ?B is 7.64°-9.64°, the roll angle ?C is 26.03°-28.03°, and the roll angle ?D is 32.16°-34.16°, and for a diametrically larger one of the first gear and the second gear the roll angle ?A is 15.02°-17.02°, the roll angle ?B is 16.7°-18.7°, the roll angle ?C is 21.73°-23.73°, and the roll angle ?D is 23.41°-25.41°.

Abstract: The present invention discloses a gear and a method for forming a tooth profile thereof. In the method of the present invention, a cubic curve is used to modify a basic tooth shape of a standard rack to obtain an amended basic tooth shape, wherein the cubic curve contacts tangentially with the basic tooth shape at the midpoint of a dedendum, a midpoint of a lateral and a midpoint of an addendum of the basic tooth shape. The amended basic tooth shape is reproduced to obtain an amended rack, and the amended rack is further used to generate a tooth profile of a desired gear.

Abstract: Noise can be effectively reduced without rotative power transmission accuracy being compromised. In a tooth 2 of a resin gear 1, a tooth face that is a predetermined area from a tooth crest 8 towards a tooth root 10 side serves as a tooth profile modification area 11. A tooth surface excluding the tooth profile modification area 11 serves as an involute profile area 12. The tooth profile modification area 11 includes a linear standard profile portion 14 formed by an involute curved line from the tooth crest 8 of the tooth towards the tooth root 10 side and a profile modification portion 16 in which a tooth thickness gradually and smoothly decreases from the standard profile portion 14 along a tooth width direction and the tooth thickness gradually and smoothly decreases from a tooth root end side 15 towards the tooth crest 8. In the tooth profile modification area 11, a contacting section becomes elastically deformed as a result of the resin gear coming into contact with a meshing mating gear.

Abstract: A gear set for a generator includes a first gear having a first set of involute teeth and a second gear having a second set of involute teeth circumferentially located about a center axis of rotation. Each set of involute teeth includes respective roll angles, ?A-D. For a diametrically smaller one of the first gear and the second gear the roll angle ?A is 1.51°-3.51°, the roll angle ?B is 7.64°-9.64°, the roll angle ?C is 26.03°-28.03°, and the roll angle ?D is 32.16°-34.16°, and for a diametrically larger one of the first gear and the second gear the roll angle ?A is 15.02°-17.02°, the roll angle ?B is 16.7°-18.7°, the roll angle ?C is 21.73°-23.73°, and the roll angle ?D is 23.41°-25.41°.

Abstract: A gear set includes a first gear having at least one tooth with a first tooth profile. The first tooth profile may comprise a first segment comprising a first plurality of sections. At least one of the first plurality of sections may have a first profile angle, and at least one of the first plurality of sections may have a second profile angle. The first profile angle and the second profile angle may be different. A differential is also provided that includes a differential case, a pinion shaft disposed inside the differential case, and a pinion gear.

Abstract: The action curve (A), that is, the locus of the gearing contact points throughout the gearing process, is a lemniscate (Lg, Ld) having a double point coinciding with the rolling point (T) of two pitch circles (Prg, Prd). The gearing contact begins at one of the apexes (Sgh) of the lemniscate under a zero Hertzian pressure between two profile points where the profiles have the same curvature centered at the rolling point (T). Wear and operating noise are reduced.

Abstract: A rotor gear includes a rotor gear body having involute teeth that each have an involute surface that extends between a tooth tip and a tooth base. The involute surface includes at least reference points A-D, with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D. The reference points A-D have associated respective roll angles, ?A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis.

Abstract: A pump gear includes a pump gear body having involute teeth that each have an involute surface that extends between a tooth tip and a tooth base. The involute surface includes at least reference points A-D, with reference point A near the base, reference point D near the tip, reference point B between reference points A and D, and reference point C between reference points B and D. The reference points A-D have associated respective roll angles, ?A-D, between a corresponding first line that is perpendicular to the involute surface at the given reference point A-D, and a second line that is tangent at a reference point that lies on a terminal end of the involute surface at the tooth base to a reference base circle having a center origin at the center axis.

Abstract: A fluctuating gear ratio limited slip differential assembly is provided that includes a differential case and a pair of side gears disposed within the differential case. Each of the side gears may have a tooth with a first tooth flank. The differential assembly may further include a pinion shaft disposed within the differential case and a plurality of pinions supported by the pinion shaft. The pinions may be configured for engagement with the pair of side gears and each of the pinions may have a tooth with a second tooth flank. The first and second tooth flanks are configured to cause movement of the plane of action defining all contact points between the first tooth flank of the side gears and the second tooth flank of the pinions in a predetermined and/or controlled manner.

Abstract: Rack gears of far-side paper guides are provided such that manners of meshing with pinion gears are made tighter at respective regions corresponding to locations for constraining paper of standard size, as compared to other regions. In addition, by constituting width guide plates which are upstream in a paper feed directions from far-side paper guides and width guide plates which are downstream in a paper feed directions therefrom such that respective areas of surfaces receiving paper, and respective distances from respective width guide plates to gear mesh locations, are respectively set so as to be substantially mutually equal. Impacts from stacks of paper produced during placement of paper within a paper supply apparatus may be received substantially equal at upstream and downstream from gear mesh of far-side paper guides, and torques acting on far-side paper guides upstream and downstream from gear mesh locations may be made substantially mutually equal.