A resin helical gear is formed by setting a first machining reference line obliquely coupling a tooth tip side of a first tooth to a tooth root side of a second tooth on another end side in the tooth width direction along a tooth surface, and a second machining reference line obliquely coupling a tooth tip side of the second tooth to a tooth root side of the first tooth along the tooth surface. Then, the tooth surface is cut out from the first machining reference line to the tooth root of the first tooth while the tooth surface is cut out from the second machining reference line to the tooth root of the second tooth. Then, an involute tooth profile form is left on a tooth tip side of the tooth with respect to the first machining reference line and the second machining reference line.

A gear keeping the bending stress at the dedendum from becoming locally high at the time of power transmission and thereby raising the dedendum bending strength. The radius of curvature is maximum at a critical section position determined by the Hofer's 30 tangent method. Both radii of curvature from the critical section position to the first and second connecting points X1 and Y1 are constant or decreasing. In dedendum line segment 23, there are points A1 and B1 where radius of curvature is smaller than the critical section position. In the dedendum line segment 23, the maximum radius of curvature is 3 times or less the minimum radius of curvature. By a cross-sectional view, the critical section position is part of an arc, and the arc extends to the two sides of the critical section position. Thus, the maximum bending stress becomes smaller and dedendum bending strength is improved.

A method of avoiding gear tooth interference in a planetary gear system includes designing and building a planetary gear system having a selected base pitch and tooth length for planet gears, breaking a rim of one of the planet gears, and verifying whether tooth tip interference occurs during operation of the planetary gear system.

Electric motors are disclosed. The motors are preferably for use in an automated vehicle, although any one or more of a variety of motor uses are suitable. The motors include lift, turntable, and locomotion motors.

[Means for Solution] A gear member includes a tooth having a tooth flank whose profile is an involute curve, wherein in a cross-section of the tooth perpendicular to a face width direction, the tooth has a depression, near a top land, hollowed in the tooth flank relative to the involute curve.

A gearbox assembly includes a first gear and a second gear. The first gear includes a plurality of first gear teeth. The second gear includes a plurality of second gear teeth. The plurality of first gear teeth and the plurality of second gear teeth mesh with each other as the first gear and the second gear rotate. A profile shape of at least one first gear tooth of the first gear is characterized by a total profile modification between 66 micrometers and 120 micrometers.

A drive transmission device first and second gears. Each tooth of the first gear includes, between tooth top and bottom, one tooth surface and the other tooth surface on an opposite side. Each tooth of the second gear includes, between tooth top and bottom thereof, one tooth surface and the other tooth surface of the second gear on an opposite side. The one surfaces of the first and second gears engage to each other, and the other surfaces of the first and second gears are not. The one surface extends along respective involute curves. For at least one of the first gear and the second gear, the other surface extends from a tooth top side to a tooth bottom side along a linear line inside a plane which is symmetrical with the one surface with respect to a line connecting the tooth top and the tooth bottom.

Electric motors are disclosed. The motors are preferably for use in an automated vehicle, although any one or more of a variety of motor uses are suitable. The motors include lift, turntable, and locomotion motors.

Thrust chain device, includes a thrust chain with a straight portion along an axis and a curved portion, and links hinged on shafts, a chain guide, a driving sprocket with chain interlocking teeth, the sprocket being in contact with the chain via contact surfaces in the shape of an involute of a circle, the contact surfaces belonging to the teeth, a tooth engaging with the chain while defining a line of action having an angle with the shaft of the straight portion of between ?10? and 10?, the sprocket in contact with the straight portion and not the curved and is mounted such that it can rotate on a shaft on the side of the chain opposite the curved portion's center of curvature, the contact surfaces including a convex front surface directed towards the straight portion and a rear surface directed towards the curved portion when the tooth is interlocking.

The present invention belongs to the field of mechanical transmission technology, and proposes a non-orthogonal elliptical toroidal worm gear pair, including an involute cylindrical gear and an elliptical toroidal worm formed by a primary envelope of the involute cylindrical gear; both adopt spatial non-orthogonal transmission, and the shaft angle satisfies the self-locking condition and the restriction condition of minimum tooth top width; the toroidal generatrix of the elliptical toroidal worm is elliptical, which can increase the number of meshing teeth and the total length of instantaneous contact line. A non-orthogonal elliptical toroidal worm gear pair proposed in this invention has the characteristics of toroidal worm drive and can realize the whole facewidth of the gear to participate in the meshing drive. It can be used in the fields of precision continuous indexing transmission, continuous lapping of cylindrical gear tooth flank, and has good popularization application value and industrialization prospect.