Abstract:
PROBLEM TO BE SOLVED: To enhance a transmission torque of a wave gear device by reducing bending stress by averaging the bending stress generated in gear bottom rim surfaces of the outer teeth due to the flection of a flexible outer gear of the wave gear device.SOLUTION: When a flexing quantity in a radial direction of a longitudinal axis of an elliptical rim neutral line of each axially perpendicular cross section in a tooth trace direction of a flexible externally toothed gear 3 of a wave gear device 1 is w=κmn (m is modules of both the gears, n is a half of tooth number difference of a rigid inner gear and the flexible outer gear, κ is flection coefficient) and a rim thickness in an axially perpendicular cross section is t, dislocation is applied to the outer gear 34 such that the product of t and w becomes constant in each axially perpendicular cross section in the tooth trace direction in the external teeth 34 of the flexible externally toothed gear 3.
Abstract:
PROBLEM TO BE SOLVED: To compensate the effect relative to the positioning control of a load shaft caused by non-linear spring characteristics of a wave gear device using a strict linearization technique in the actuator having the wave gear device.SOLUTION: In the method, a plant model is constructed from the actuator to be controlled, the model being linearized using a strict linearization technique; measurements are taken of the non-linear elastic deformation of the wave gear device relative to load torque; the non-linear spring model τg(θtw) is defined using a cubic polynomial with the constant defined as zero to allow the measurement results to be recreated; and the current input into the plant model and the motor position of the plant model when a load acceleration command is a command value are entered into a semi-closed loop control system for controlling the positioning of the load shaft, as a feed-forward current command and a feed-forward motor position command.
Abstract:
PROBLEM TO BE SOLVED: To provide a wave-motion gear device with a ratchet preventing mechanism having a simple constitution for preventing the generation of ratcheting and the plastic deformation of portions during deceleration/acceleration and stopping.SOLUTION: In the wave-motion gear device 1, a friction disc 7A is sandwiched between a rotation input shaft 5 and a wave generator 4, and input torque is transmitted from the rotation input shaft 5 to the wave generator 4 by a frictional engagement force of the friction disc 7A. Wave generator side torque is sufficiently smaller than output side torque, and does not vary largely at an operating mode (during the deceleration/acceleration and stopping) of the wave-motion gear device 1. The generation of a slide between the wave generator 4 and the rotation input shaft 5 is 60-75% of a ratcheting torque value between a rigid internal gear 2 and a flexible external gear 3 during the deceleration of the wave-motion gear device 1. Therefore, plastic deformation in tooth is prevented before both the gears are brought into ratcheting states.
Abstract:
PROBLEM TO BE SOLVED: To provide a simple-shaped crossed roller bearing retainer which has a grease accumulation section which maintains the fixed spacing between adjacent rollers. SOLUTION: The retainer 6 of a crossed roller bearing has a retainer body plate 11 of rectangular profile corresponding to a rectangular cross-section of a race 4a. Rectangular side surfaces 12, 13 on both sides of the retainer body plate are inclined planes that incline in a direction of approaching one another from one corner 14 to another corner 15 along the diagonal line of the surfaces, and extend towards the bearing center while installed to the race 4a. Recesses 16, 17 for accumulating grease having a predetermined depth are formed in center portions of the rectangular side surfaces 12, 13, the recesses communicating via a through-hole 18. The rectangular side surfaces 12, 13 are in linear contact with the circular external circumferential surfaces of adjacent rollers and hold the rollers at the fixed spacing. COPYRIGHT: (C)2011,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To provide a wave gear device having a three-dimensionally contacting positive shifted tooth profile continuously meshing in the tooth trace direction and having an increased tooth depth. SOLUTION: The deflection coefficients κ of an opening end 34a of an external tooth 34 of a flexible external gear 3, a central principal section 30, and an inner end 34b in the harmonic drive gear device 1 are set at 1+2a, 1+a, and 1 respectively. An addendum tooth profile portion fs1 of the external tooth is obtained using a second similar curve AC obtained by similarly transforming part of a moving locus M0 obtained by a rack approximation of an inner end 34b of the external tooth 34 to define a straight line tooth profile portion fs2 connected thereto and a tooth profile FS1 having a tooth depth of 2mn(1+a) in the principal section 30 of tooth trace center of the external tooth by the addendum tooth profile portion fs3 connected thereto. As tooth profiles for the portion from the principal section 30 to the opening end 34a, and the portion from the principal section 30 to an inner end 34b, shifted tooth profiles FS2, FS3 which are obtained by shifting the tooth profile FS1 in the negative direction of the tooth depth are employed respectively. COPYRIGHT: (C)2011,JPO&INPIT
Abstract:
PROBLEM TO BE SOLVED: To provide a wave gear device having a tooth profile capable of being subjected to gear cutting by a simple process using a typical machining mechanism without generating coning induced interference.SOLUTION: A bending state known as "coning" in which the amount of bending of a flexspline 3 gradually decreases in accordance with the distance from the open end 30 is caused in the cup type or silk hat type wave gear device. A tooth profile in which the tooth depth is kept constant and 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 flexspline 3. Tapers 24d, 34d are formed on a part of the top land at the tooth trace end near the open end 30, whereby a modified tooth profile is obtained. The modified tooth profile is employed as the tooth profile for both of the splines 3. Both of the splines 3 can be caused to mesh together without generating coning-induced interference. Both of the splines 3 can also be subjected to gear cutting by a simple process using a typical machining mechanism.
Abstract:
A phase adjustment unit (100) for effecting phase adjustment between rolls of a multi-color printing press comprises a phase adjustment gear device (10) and a phase adjustment motor (6) fitted to the rear end of the gear device (10). The phase adjustment gear device (10) includes a hollow input shaft (12) inside a hollow casing (11) and an output shaft (14) inside the input shaft (12), and spline shafts (121, 141) for fitting are disposed at the distal ends of these shafts (12, 14). Cup type first and second wave motion gear devices (16, 25) are coaxially disposed at the rear end of the spline shafts, and input rotation returns to the first wave motion gear device (16) from an inner gear (161) of the first wave motion gear device through a gear train (30) and the second wave motion gear device (25), and is transmitted to the output shaft (14). While the motor (6) is locked, each constituent element of the first wave motion gear device rotates integrally, and the input and output shafts rotate in the same way. At the time of phase adjustment, the rotation speed of the motor (6) is drastically reduced and outputted through the gear devices (25, 16). Since the input and output shafts protrude from one of the sides, fitting and removal of the unit can be conducted easily.
Abstract:
An object of this invention is to provide a flexible meshing type gear having improved retaining force for lubricating oil film between gear surfaces. In a flexible meshing type gear (1), a flexture amount (w) in a radial direction of a cross section normal to a reference axis set at a predetermined position along a tooth trace of a flexible external gear (3) thereof is made a negative deflection flexture amount which is smaller than a normal flexture amount (wo), and a rigid internal gear (2) and the flexible external gear (3) are each constituted by a spur gear. The number of teeth of the flexible external gear (3) is made smaller by 2n (n is a positive integer) than that of the rigid internal gear (2). The working tooth profile of one of these two gears (2, 3) is formed into a convex curve, and the configuration thereof is made such that a portion (L1(O, A)) belonging to a convex relative to the other gear of the top portion of a moving path (L1) by a rack approximation drawn by the teeth thereof relative to the other gear on the cross section normal to the reference axis of the tooth trace is formed into a convex curve (L2(O, B)) which is similarity transformed using an extension ratio ( lambda ) with the apex of the moving path as an origin or a similarity curve thereof, while the working tooth profile of the other gear is formed into a concave curve, and the configuration thereof is also formed into a concave curve (L3(O, C)) resulting from similarity transforming of a portion of a moving path which is identical to that portion of the one of the two gears using an extension ratio ( lambda +1) with the apex of the moving path as an origin, whereby the meshing between the two gears is made an over-running type meshing in which continuous contact is made possible at a cross section normal to the reference axis.