Abstract: 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.

Abstract: 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.

Abstract: A degree of freedom of a hypoid gear is improved. Instantaneous axis in a relative rotation of a gear axis and a pinion axis, a line of centers, intersection between the instantaneous axis and the line of centers, and an inclination angle of the instantaneous axis regarding 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 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 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 selected.

Abstract: 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.

Abstract: 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.

Abstract: A hypoid gear device and a final reduction gear for a vehicle. The drive pinion (12) of the final reduction gear (10) having a hypoid gear is formed of a gear having a cylindrical outline. A drive pinion shaft (16) is projected from both sides of the drive pinion (12), and the drive pinion is supported on bearings (18) and (20) at these both projected portions. Since the outline of the drive pinion is formed in a cylindrical shape, the drive pinion can adopt a both side supporting structure. Thus, the deflection of the shaft can be suppressed and a bearing load can be lowered.

Abstract: In a crankshaft of an in-line four-cylinder engine, an arm that is closest to a flywheel has a greater average thickness in a direction of the rotation axis of the crankshaft than those of other arms. Two of the arms that are coupled to both sides of the third journal from the flywheel each have a center of gravity closer to its own counterweight compared to the centers of gravity of the arms that face the two arms with corresponding crankpins in between. Accordingly, the rigidity against torsional deformation and the thickness of oil films on the journals are reliably maintained while suppressing increase in the weight of the entire crankshaft.

Abstract: A natural frequency and a calculated mode vector are calculated by using a finite-element method models for analysis which include an object of analysis including a plurality of components and a plurality of elements which are positioned between the components of the object of analysis and indicate a boundary condition between the components, the calculated mode vector having high degree of correlation for an experimental mode vector is extracted and set to a pair, and identifying the boundary condition of the elements based on the extracted calculated mode vector and the natural frequency corresponding to the extracted calculated mode vector.

Abstract: In a crankshaft of an in-line four-cylinder engine, an arm that is closest to a flywheel has a greater average thickness in a direction of the rotation axis of the crankshaft than those of other arms. Two of the arms that are coupled to both sides of the third journal from the flywheel each have a center of gravity closer to its own counterweight compared to the centers of gravity of the arms that face the two arms with corresponding crankpins in between. Accordingly, the rigidity against torsional deformation and the thickness of oil films on the journals are reliably maintained while suppressing increase in the weight of the entire crankshaft.

Abstract: A natural frequency and a calculated mode vector are calculated by using a finite-element method models for analysis which include an object of analysis including a plurality of components and a plurality of elements which are positioned between the components of the object of analysis and indicate a boundary condition between the components, the calculated mode vector having high degree of correlation for an experimental mode vector is extracted and set to a pair, and identifying the boundary condition of the elements based on the extracted calculated mode vector and the natural frequency corresponding to the extracted calculated mode vector.

Abstract: Local observer frame LOC which is located near a body and moving on a global coordinate system is used for locally observing the body together with the global coordinate system. The rigid body displacement and elastic vibration of the body are represented by rigid body modes and elastic modes respectively, and analyzed by modal analysis uniformly handling these rigid body modes and elastic modes.