A worm comprises enveloping worm teeth having relieved ends. The worm is machined in three steps comprising machining a threaded section, machining a first end section, and machining a second end section. The threaded section is machined utilizing a rack-form tool having a rack-form thickness. The first end section and the second end section are machined utilizing a larger rack-form thickness, thereby, providing relieved ends. The teeth of the worm having such relieved ends mesh with the teeth of a mating gear at full depth throughout preventing partial teeth engagement.

A gear pair including at least one first gear with a microstructure and at least one additional gear is provided. The first gear has first teeth with first tooth flanks and the additional gear has additional teeth with additional tooth flanks. In order to transfer power from the first gear to the additional gear, a first tooth flank contacts an additional tooth flank on an imaginary tangential plane which touches both tooth flanks in a contact point. The addition of the speeds of the two tooth flanks in the contact point on the tangential plane produces a sum speed. The microstructure is designed as a depression on the first tooth flank and runs at least partly along a structure line on the first tooth flank, and the structure line is touched by a structure tangent in the contact point. The structure tangent lies on the tangential plane.

A bevel gear set and a method of manufacturing the same are provided. The bevel gear set may include a first bevel gear and a second bevel gear. The first and second bevel gears may be spiral bevel gears or hypoid spiral bevel gears. The first and second bevel gears may each have a gear tooth surface having a plurality of teeth formed thereon, such that the teeth of the first bevel gear and the teeth of the second bevel gear are configured to engage in a meshing engagement. The teeth are machined onto the respective gear tooth surface via a face milling process. Each tooth includes a tooth top, a plurality of meshing surfaces, and at least one chamfer. The chamfer may be formed at an abutment edge disposed between the tooth top and a respective meshing surface via a brushing process directly following the machining of the teeth.

The present invention discloses a line gear mechanism for rotation-movement conversion, comprising a driving line gear (1) and a driven line gear (2). A stagger angle between an axis of the driving line gear and an axis of the driven line gear is any value from 0 to 180. By a point contact meshing between a driving contact curve of a driving line tooth on the driving line gear (1) and a driven contact curve of a driven line tooth on the driven line gear (2), and by utilizing rotation of the driving line gear (1), it achieves that the driven line gear (2) rotates while moving smoothly. The line gear mechanism for rotation-movement conversion is simple in structure, easy to design, can achieve small displacement of movement, and is especially suitable for the conversion of small machinery from rotation to linear motion.

A helical planetary gear for a helical planetary gear unit for an adjusting device in vehicles for adjusting two components which are adjustable with respect to one another, wherein the helical planetary gear defines a planetary gear axis and comprises planetary gear toothing having a first planetary gear toothing end and a second planetary gear toothing end, wherein the first planetary gear toothing end and the second planetary gear toothing end are arranged apart from one another in relation to the planetary gear axis, and the planetary gear toothing has a diameter that increases or decreases proceeding from the first planetary gear toothing end to the second planetary gear toothing end and further relates to an internal helical gear for a helical planetary gear unit as well as a helical planetary gear unit for an adjusting unit for adjusting two components which are adjustable with respect to one another.

An intersecting-axes gear type mechanism includes two gears configured to rotate in mesh with each other. Respective axes of rotation of the two gears being disposed in an intersecting-axes manner, and at least one of the gears has teeth each of which includes a tooth trace extending substantially in a radial direction and a radially inner end face. A chamfered portion is formed on a meeting portion where the radially inner end face and a tooth face of the each of the teeth meet, so as to extend over an overall length of the meeting portion. At least an entirety of an area where the chamfered portion and the radially inner end face meet and an entirety of an area where the chamfered portion and the tooth face meet are each composed of a curved surface in overall length.

A degree of freedom of a hypoid gear is improved. An instantaneous axis in a relative rotation of a gear axis and a pinion axis, a line of centers, an intersection between the instantaneous axis and the line of centers, and an inclination angle of the instantaneous axis with respect to the rotation axis of the gear are calculated based on a shaft angle, an offset, and a gear ratio of a hypoid gear. Based on these variables, base coordinate systems are determined, and the specifications are calculated using these coordinate systems. For the spiral angles, pitch cone angles, and reference circle radii of the gear and pinion, one of the values for the gear and the pinion is set and a design reference point is calculated. Based on the design reference point and a contact normal of the gear, specifications are calculated. The pitch cone angle of the gear or the pinion can be freely selected.

A pressure angle of the worm is set to be greater than a pressure angle of the worm wheel so that a maximum number of meshing teeth becomes smaller than or equal to n (where n is a natural number) with respect to the speed reduction mechanism in which a number of meshing teeth is always n+1 or changed between n+1 and n by rotation under a condition in which the pressure angles of the worm and the worm wheel are the same with respect to each other.

A worm wheel is provided in which a step is not formed near a tooth face meshing with a worm, and noise does not easily occur during power transmission. A worm wheel 1 includes a circular arc-shaped tooth section 5 that is a portion meshing with a worm 101 and configuring a circular tube worm gear, and a helical tooth section 4 that is connected to one end side of the circular arc-shaped tooth section 5. An angle of torsion at an arbitrary reference point 14 in a tooth depth direction of a tooth 3 on a boundary 7 between the circular arc-shaped tooth section 5 and the helical tooth section 4 is equal to an angle of torsion at a second reference point 15 corresponding to the first reference point 14 in the tooth depth direction of the tooth 3 in a diameter portion P0 of a throat of the circular arc-shaped section 5. As a result, a step is not formed on a tooth face on the boundary 7 between the circular arc-shaped tooth section 5 and the helical tooth section 4. A tooth face of the circular arc-shaped tooth section 5 and a tooth face of the helical tooth section 4 are smoothly connected.

A worm gear includes a worm formed with a through hole through which a shaft transmitting the rotation of a motor is inserted, and a worm wheel configured to mesh with the worm and transmit the rotation to an output shaft. Given that a normal pitch is denoted by E and a width of a recess in the direction of a worm axis by H, the worm is configured such that H/E0.6 (1) is met.