Agitating – Rubber or heavy plastic working – Stirrer with specified drive means
Patent
1994-03-23
1996-04-30
Cooley, Charles E.
Agitating
Rubber or heavy plastic working
Stirrer with specified drive means
74395, 74409, 74665GA, B29B 758
Patent
active
055118747
DESCRIPTION:
BRIEF SUMMARY
TECHNICAL FIELD
The present invention relates to a drive transmission mechanism for use in a biaxial extruder for extrusion-molding plastics.
BACKGROUND OF THE INVENTION
A higher torque is required of the drive transmission mechanism for transmitting a drive force to first and second output shafts rotating integrally with the first and second screws of a biaxial extruder. In order to realize the higher torque, counter-measures have been exemplified by raising the power of the motor, by increasing the bearing size for the increase in the radial force which is generated at the meshing portions of gears such as first and second output gears fitted individually on the first and second output shafts, or by enlarging the width of teeth to ensure the tooth bearing. Because of the extremely restricted axial distance between the two shafts, however, troubles occur in case the bearing size is to be increased or in case the tooth width of gears is to be enlarged, thus making it difficult to transmit the drive force of high torque.
This transmission of the drive force of high torque is known to have been achieved by a drive transmission mechanism disclosed in Japanese Patent Laid- Open No. 1185/1987. This drive transmission mechanism 33 for a biaxial extruder of the prior art will be described with reference to FIGS. 5 and 6. Of these, FIG. 5 is a diagram showing a drive line, and FIG. 6 is a side elevation showing the gear arrangement of FIG. 5. Incidentally, rectangles and thick lines appearing in FIG. 5 indicate gears and shafts, respectively.
This drive transmission mechanism 33 is constructed to include: first and second output gears 3 and 4 fitted with an axial displacement respectively on first and second output shafts which are connected to the first and second screws of the biaxial extruder (the reference numerals 1 and 2 generally refer to both the output shafts and the screws) first lower and upper gears 5 and 6 arranged respectively below and above the axis of the first output gear 3, as shown in FIG. 6; second lower and upper gears 7 and 8 arranged respectively below and above the axis of the second output gear 4, as shown in FIG. 6; and a reduction gear train D for quartering the output of a common drive source C equally and distributing the quarters to those first lower and upper gears 5 and 6 and second lower and upper gears 7 and 8.
The reduction gear train D is composed of: gears 24 and 25 meshing with the first upper and lower gears 6 and 5, respectively; gears 22 and 23 rotating integrally with the gears 24 and 25, respectively; gears 29 and 30 meshing with the second upper and lower gears 8 and 7, respectively; gears 27 and 28 rotating integrally with the gears 29 and 30, respectively; a center shaft 32 equipped at its one end with a gear 21 meshing commonly with the gears 22 and 23 and at its other end with a gear 26 meshing commonly with the gears 27 and 28; and a drive gear 31 fitted on a middle portion of the center shaft 32 for transmitting the drive force of the common drive source C. This reduction gear train D provides a gear train having a symmetric structure with respect to the first and second screws. Incidentally, the center shaft 32 is constructed of toothed joint shafts 32a and 32b for correcting both the phase shift due to the torsional rigidity caused by the difference between the lengths of the output shafts 1 and 2 and the phase shift at the time of assembly.
In the drive transmission mechanism 33 for the biaxial extruder thus constructed according to the prior art, the drive force from the common drive source C is transmitted to the center shaft 32 through the drive gear 31. This drive force is halved and distributed by the center shaft 32 to the first screw line and the second screw line. At this time, the toothed joint shafts 32a and 32b composing the center shaft 32 have their diameters and lengths determined to correct the phase shifts due to the torsional rigidity of the output shafts 1 and 2. Moreover, the drive forces thus distributed are quartered from the gears 21 a
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Fukano Norifumi
Ikegami Yoshio
Konno Masashi
Minagawa Koji
Uemura Tatsuya
Cooley Charles E.
Kabushiki Kaisha Kobe Seiko Sho
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