Abstract: A speed reduction mechanism and a motor equipped with the speed reduction mechanism are provided. A pinion gear is provided with one spiral engagement projected part, and a helical gear is provided with a plurality of engagement recessed parts with which the engagement projected part is engaged. The engagement projected part and the engagement recessed part are formed so that their cross-sectional shapes along a direction orthogonal to an axial direction of the pinion gear are in arc shapes. A shape of helical teeth and a shape of the engagement recessed part are determined based on a shape of the engagement projected part provided on a spiral tooth.

Abstract: A gear transmission includes a first helical-cut gearwheel (1) and a second helical-cut gearwheel (2) engaged for transmitting torques in different directions. The first gearwheel (1) and the second gearwheel (2) each include corresponding ring-shaped thrust collars (4, 5), and corresponding thrust collars (4, 5) each form a race (8, 9, 10, 11) having an overlap region. A first race (8) and a second race (9) form an overlap region for traction torques, and a third race (10) and a fourth race (11) form an overlap region for overrun torques. Each overlap region includes a contact surface or a contact point (14, 15), and each contact point (14, 15) is situated on a contact circle diameter (16, 17). The contact surfaces or contact points (8, 9) for traction torques and the contact surfaces or contact points (10, 11) for overrun torques are radially offset.

Abstract: A gear pairing for a helical gear unit or a spur gear unit, comprising a first gear with a first toothing portion, and a second gear with a second toothing portion, wherein the first gear has a first axis and the second gear has a second axis, which enclose a shaft angle, which is between 0 and 90°, the first toothing portion and the second toothing portion can be brought into meshing engagement and, when engaged, form an involute toothing, the materials of the first and second toothing portions are chosen so that, when engaged, a material pairing metal/plastic results, and the toothing portion made of plastic has a first helix angle and the toothing portion made of metal has a second helix angle.

Abstract: A vehicle drive device includes: an input shaft that receives a driving force of a driving source and that is provided with a first gear; an intermediate shaft that is provided with a second gear meshing with the first gear and a third gear located next to the second gear in a direction of a rotation axis and that is disposed in such a manner that the intermediate shaft is allowed to move in the direction of the rotation axis; an output shaft that is provided with a fourth gear meshing with the third gear; a first gear pair including the first and second gears; and a second gear pair including the third and fourth gears. One of the first gear pair and the second gear pair includes a helical gear, and the other of the first gear pair and the second gear pair includes a double helical gear.

Abstract: The invention relates to a bi-helical toothed wheel (1) with non-encapsulating profile for a hydraulic gear apparatus, of the type bound to a support shaft (5) to form a driving or driven wheel of the hydraulic apparatus and comprising a plurality of teeth (6) extended with variable helix angle with continuous function in the longitudinal direction, wherein the teeth profile keeps a shape continuity in each cross section thereof. More particularly, each tooth of the toothed wheel is longitudinally split in three zones: initial (A), central (B) and terminal (C) zones, and the central zone (B) has a variable helix angle, while the initial (A) and terminal (c) zones have a constant helix angle. The invention allows to manufacture contra-rotating rotors, having a non-encapsulating profile and a helix shape such as to suppress the angular point at the center of the rotors themselves and therefore all the problems related to their machining.

Abstract: A spur gear for transmitting a drive torque in a toothing of a motor vehicle transmission is provided, having a helically toothed first gear body for forming first teeth, a second gear body, which is helically toothed oppositely to the first gear body so as to form a herringbone toothing, for forming second teeth, wherein, on axial sides which face toward one another of the first gear body and of the second gear body, the first teeth and the second teeth point toward one another, so as to at least partially overlap one another, in each case pairwise, wherein, on that axial side of the first gear body which points toward the second gear body, a first tooth flank of the first tooth points in an axial direction toward a second tooth flank of a second tooth which follows the opposite second tooth in a circumferential direction.

Abstract: A single crystal production apparatus using the Czochralski method, includes: a crucible for holding raw material melt; a pedestal that supports the crucible and can be moved upward and downward; a crucible rotating shaft for rotating the crucible via the pedestal; and a melt receiver that is disposed below the crucible and provided with a center sleeve surrounding the pedestal, wherein, on the outer periphery of the pedestal, two or more grooves for preventing the raw material melt leaking from the crucible from dripping are provided. The single crystal production apparatus and single crystal production method can reliably prevent melt from reaching a metal portion below the pedestal even when the raw material melt in the crucible flows to the outside of the crucible in an unexpected accident or the like and runs down along the pedestal and thereby prevent damage to the apparatus and the occurrence of an accident.

Abstract: In a wave gear device, similarity-curve tooth profiles BC and AC are adopted as addendum tooth profile shapes for gears, the tooth profiles being derived from a movement trajectory M1 of an external tooth of a flexible externally toothed gear having zero deviation (?=1), in relation to an internal tooth at a main cross-section. Profile shifting is performed on the external tooth along the tooth trace for a movement trajectory M3 of the external tooth to share a bottom portion with the movement trajectory M1 at the main cross-section from the main cross-section to an inner edge. Profile shifting is performed on the external tooth along the tooth trace for the movement trajectory of the straight-line tooth-profile portion of the external tooth from the main cross-section to the outer edge to be consistent with the movement trajectory of the straight-line tooth-profile portion of the main cross-section.

Abstract: An apparatus for extruding helical teeth in a gear blank includes a press including a die plate and a die base, the die plate being movable along an axis relative to the die base, the die base supporting the gear blank. A mandrel, aligned with the axis and moveable with the die plate along the axis, includes a surface that includes helical die teeth. A servo motor drives the mandrel in rotation about the axis to the required helix angle as the mandrel moves axially relative to the gear blank.

Abstract: Tooth shapes of gears are formed such that a meshing line given by meshing of an inner gear and an outer gear provided in a state of meshing with each other for enabling transmission of a power is configured as a spiral mesh line

Abstract: A hypoid gear set including a ring-shaped gear positioned about an axis and having a plurality of curved gear teeth arranged about the axis. Each tooth has a second side having a forward face with a shallow pressure angle relative to an axially extending line and defining the drive side of the gear. Each tooth has a first side having a rear face with a steep pressure angle relative to an axially extending line and defining the coast side. A pinion gear drives the rear faces of the ring-shaped gear such that the ring-shaped gear rotates in the direction of the forward faces of the teeth of the ring-shaped gear.

Abstract: A screw-rotor machine with two meshing rotors provides with helical lands and intervening grooves and adapted for rotation around parallel axes in a working space in the machine, characterized in that; the profile of rotors uses ellipse as a basic geometry generating curve on the male rotor.

Abstract: An oil-cooled type screw rotor assembly having a female rotor and a male rotor adapted to rotate around parallel axes in meshing relation to each other. The leading side flank of the female rotor is constituted by a first leading side flank formed by an arc of a radius R.sub.1 and a second leading side flank formed by an arc of a radius R.sub.2. Also, the trailing side flank of the female rotor is constituted by a first trailing side flank formed by an arc of the tooth ends of the male rotor having a radius R.sub.5 and a second trailing side flank formed by an arc of a radius R.sub.3 which is smaller than the radius R.sub.2 of the second leading side flank. The configuration of the teeth of the male rotor is materially formed by arcs of the leading and trailing side flanks of the female rotor.

Abstract: An axial thrust compensation system in high speed helical gear engagement includes a thrust collar fixed to a shaft which carries a gear. The collar includes a peripheral groove. Another gear carrying shaft includes a disc element which engages the thrust collar groove. Axial thrust generated in the respective gears and the shafts due to the driving engagement between the gears will be transferred between the shafts by the collar and disc. In one embodiment, the collar and/or disc is formed in one piece with its shaft, while in another embodiment the collar and/or disc is bolted to its shaft. A further embodiment provides a pair of disc shaped collars spaced from opposite sides of one gear with the collars framing a pair of disc elements fixed to the other shaft.

Abstract: The threads of the gate rotor of a screw rotor machine are generated by a rounded crest portion of the main rotor thread so that the flanks of the gate rotor threads will have a contour tangent to a plurality of circles which have progressively decreasing diameters taken from the radially innermost to the radially outermost of said circles, with the circles each having a center which lies on a curved radial line directed forwardly of the direction of rotation of the gate rotor when the machine is operated as a compressor. A crest portion of the gate rotor threads shaped in conformity with the radially outermost of said contour-defining plurality of circles has its center lying within and closely adjacent to the pitch circle of the gate rotor, with the gate rotor thread crest portion projecting beyond the gate rotor pitch circle a distance corresponding approximately to the radius of the radially outermost circle.

Abstract: A cylindrical gear wheel having helical teeth with different pitch diameters for the left hand and right hand sides of the teeth and convergent line of teeth in which one side of the teeth are characterized by positive values of addendum modification while the other side of the teeth has negative values of addendum modification. By positive addendum modification is meant an addition to the nominal pitch diameter to obtain the pitch diameter at one side of a tooth and by negative addendum modification is meant a substration from the nominal pitch diameter to obtain the pitch diameter of the other side of the tooth. In the range of normal values of tooth pitch (mn) from 2 to 6 mm or normal tooth module the angular difference of inclination between the left hand and right hand sides of the teeth is within the range of 30' to 3.degree. for pitch diameters up to 500 mn and the addendum modification values are in the range from 0.01 to 4 mn.

Abstract: A cylindrical gear train comprising first and second gears having helical eth of different thickness with different pitch diameters for the left hand and right hand sides of the teeth and with different nominal angles of inclination and different mesh correction for the mating left hand and right hand flanks of the teeth. Within the normal module range of m.sub.n =2-6 mm, corresponding to the normal module range of 2.pi.(mm) to 6.pi.(mm), and for pitch diameters up to 500 mm, the maximum tooth convergency is 3.degree. and the addendum modification coefficient does not exceed 0.8.