JPH02217650A - Transmission gear of bi-axial extruding machine - Google Patents

Abstract

PURPOSE:To accomplish power-up by coupling No.1 screw shaft with a drive shaft, transmitting rotation from a gear fixed on this drive shaft to No.1 idler shaft and No.2 idler shaft, and transmitting torque through gears from the two idler shafts to No.2 screw shaft. CONSTITUTION:No.1 screw shaft 7 is coupled with the driving shaft 9 of a driver device 8, and No.1 gear 1 is fixed. Torque is transmitted from No.2 gear 2, No.1 idler shaft 11, and No.4 gear 4, which are meshing with the No.1 gear 1, to No.6 gear fixed on No.2 screw shaft 10. Further, from No.3 gear meshing with the No.1 gear 1 the torque is transmitted to No.6 gear through No.2 idler shaft and No.5 gear. The No.2-5 gears have the same number of cogs, while the No.1 and No.6 gears have the same. Accordingly the No.2 screw shaft 10 accepts transmitted torque from both idler shafts, No.1 and No.2, which allows lessening of the cog width in the biaxial extruding machine concerned and accomplishes power-up therein.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a transmission gear device for a twin-screw extruder in which two screw shafts are rotationally driven by one drive device.

2. Description of the Related Art Hitherto, various structures of transmission gear devices for twin screw extruders of this type have been known. For example, as shown in FIG. 11, since the distance between the screw shafts is extremely narrow and a large torque is generated due to high input and low rotation, the power of a drive device M such as a motor is directly connected to the drive shaft 51. A first screw gear 53 is fixed to the first screw 52, and a second screw 54 is provided beside the first screw 52. A gear with a large tooth width is directly connected to transmit torque, a first idler gear 55 is meshed with the first screw gear 53, and a second idler gear 57 is attached to the idler shaft 56 to which the first idler gear 55 is attached. Attach this second idler gear 57 to the second screw 5.
The second screw 54 is meshed with the gear 58 of No. 4, so that the second screw 54 rotates in synchronism with the first screw 52.

Problems to be Solved by the Invention However, although the above-mentioned structure has advantages such as a simple gear train and easy assembly, the distance between the screw shafts has not been sufficient to meet the recent demands for increased power of extruders. Due to its narrow size, it was not possible to increase the size of gears and bearings, and there was a problem in that it was not possible to meet the above requirements. One way to solve this problem is to
It is conceivable to increase the tooth width of the gear directly connected to the screw, but increasing the tooth width has the problem of tooth contact.

In addition, when trying to increase the power of an extruder, bearings with a large capacity to support each gear are required, but the narrow distance between the screw shafts causes the problem that such bearings cannot be provided. However, this problem with bearings can be solved to some extent by arranging the bearings in different positions in the axial direction between the two shafts, but the new bearings can be installed on the shafts located at the rear. , a problem arises in that the axial length increases as the bearing moves rearward, and the torsion angle also increases, which also adversely affects the meshing gap between both screws.

Therefore, an object of the present invention is to solve the above-mentioned problems and to provide a transmission gear device for a twin-screw extruder that can meet demands for increased power.

Means for Solving the Problems In order to achieve the above object, the present invention provides a system in which the power of the two screw shafts can be increased by driving both of the two screw shafts to rotate using a dual type, that is, two gears. It was configured as follows.

That is, according to the invention according to claim 1, the first screw shaft is connected to the drive shaft of the drive device, the first gear is fixed to the drive shaft, and the second gear and the third gear are connected to the first gear. A fourth gear is fixed to the first idler shaft to which the second gear is fixed, a fifth gear is fixed to the second idler shaft to which the third gear is fixed, and a sixth gear is fixed to the first idler shaft to which the third gear is fixed. The fourth gear meshes with the fifth gear, and the sixth gear meshes with the second gear.
While being fixed to the screw shaft, the number of teeth of the second to fifth gears are all the same, and the number of teeth of the first gear and the sixth gear are also the same.

Further, according to the invention according to claim 2, the drive gear is fixed to the drive shaft of the drive device, the first gear is fixed to the first screw shaft, and the second gear and the third gear are connected to the drive gear and the above. A fourth gear is fixed to a first idler shaft that meshes with both of the first gears, the second gear is fixed to the first idler shaft, and a fifth gear is fixed to the second idler shaft to which the third gear is fixed,
A sixth gear meshes with the fourth gear and the fifth gear, and the sixth gear is fixed to the second screw shaft,
The number of teeth of the second to fifth gears is the same, and the number of teeth of the first gear and the sixth gear are also the same.

Furthermore, according to the invention according to claim 3, the first gear is fixed to the first screw shaft, the second gear and the third gear both mesh with the first gear, and the fourth gear meshes with the second gear. meshing with the third gear, the third gear is fitted to the first shaft so as to be relatively rotatable, a fifth gear is fixed to the first shaft, and a sixth gear is fitted so as to be relatively rotatable; The fifth gear meshes with the seventh gear and the eighth gear, and the fourth gear meshes with the fifth gear.
The gear and the seventh gear are both fixed to a second shaft, a ninth gear is fixed to the second screw shaft, the sixth gear and the tenth gear mesh with the ninth gear, and the sixth gear and the tenth gear mesh with each other. The ti-th gear meshes with the 10th gear, the 8th gear and the 1st + gear are both fixed to the third shaft, and the drive shaft of the drive device is connected to the first shaft, the second shaft, or While connected to either of the third shafts, the second gear and the third gear have the same number of teeth, the fourth gear and the eleventh gear have the same number of teeth, and the sixth gear has the same number of teeth. The gear and the tenth gear have the same number of teeth, and the seventh gear and the eighth gear have the same number of teeth.
The gears were configured to have the same number of teeth.

Effects of the Invention According to the configuration of the invention according to claim 1, when the drive device is driven and the drive shaft rotates, for example, clockwise, the first screw shaft and the first gear rotate clockwise. However, both the second gear and the third gear rotate counterclockwise. As a result, the fourth gear and the fifth gear are rotated counterclockwise by the first idler shaft and the second idler shaft, and the sixth gear meshing with both gears, and therefore the second screw shaft, is rotated counterclockwise by the first idler shaft and the second idler shaft. 1 Rotates clockwise in the same way as the screw shaft.

Therefore, since the drive shaft is directly connected to the first screw shaft, the first screw shaft is driven by a so-called single drive, but the second screw shaft is transmitted with the driving force from the drive shaft or by two gears. Therefore, it is driven in a so-called dual manner, and with a small number of parts and a simple structure, it is possible to reliably increase the driving force of the two screw shafts. Furthermore, by arbitrarily setting the tooth widths of the two gears that transmit the driving force to the second screw shaft, the degree of power-up can be set in various ways. Furthermore, since the tooth width of the 4th, 5th, and 6th gears can be made smaller, the second screw shaft can be made shorter, the runout of the shaft is reduced, and more stable rotation can be achieved.

That is, in the conventional system, when transmitting the driving force to the second screw shaft driving gear, the driving force was transmitted by one gear, whereas in this configuration, the same driving force as described above is transmitted to the sixth gear. When it is transmitted to a gear, it is transmitted through two gears, so the driving force transmitted from one gear to the 6th gear is halved compared to the conventional method, and the tooth width of the 6th gear and the 4.5th gear is smaller than the conventional one. This can be reduced to about half of that.

According to the configuration of the invention according to claim 2, when the drive device is driven and the drive gear of the drive shaft rotates, for example, clockwise, the second gear and the third gear both rotate counterclockwise. As a result, the first gear and the first screw shaft rotate clockwise. Due to the rotation of the second and third gears, the fourth gear and the fifth gear rotate counterclockwise via the first idler shaft and the second idler shaft, and the sixth gear rotates clockwise. and rotate the second screw.
The shaft rotates clockwise like the first screw shaft.

Therefore, since the driving force is transmitted to both screw shafts by two gears, the driving force of both screw shafts can be reliably increased with a small number of parts and a simple structure. Furthermore, by arbitrarily setting the tooth widths of the two gears that transmit driving force to both screw shafts, the degree of power-up can be set in various ways.

In addition, since the face widths of all other gears in addition to the 1.6th gear can be made smaller, the second screw shaft can be made shorter than the first screw shaft, and the width of these shafts can be reduced. Runout is reduced and rotation can be made more stable. In other words, in the conventional system, when transmitting the driving force to each screw shaft driving gear, the driving force was transmitted by one gear, whereas in this configuration, the same driving force as above is transmitted to the first gear. .6 When transmitting to the gear, it is transmitted through two gears, so compared to the conventional method, the transmission from one gear to the first
．． The driving force transmitted to the 6th gear is halved, and the tooth widths of the 1.6th gear and all other gears that mesh with these gears can be reduced to about half of the conventional width.

According to the configuration of the invention according to claim 3, the first shaft rotates clockwise together with the drive shaft due to the drive of the drive device. As a result, the rotation of the first shaft causes the fifth gear to rotate clockwise, and both the seventh gear and the eighth gear to rotate counterclockwise. Due to the rotation of the seventh gear, the fourth gear rotates counterclockwise via the second shaft, and the second gear and the third gear rotate.
Both gears rotate clockwise, and the first gear and the first screw shaft rotate counterclockwise. On the other hand, due to the counterclockwise rotation of the eighth gear, the first
The first gear rotates counterclockwise, the tenth gear and the sixth gear both rotate clockwise, and the ninth gear and the second screw shaft rotate counterclockwise like the first screw shaft.

Therefore, since the two screw shafts can transmit driving force divided into two shafts, it is possible to transmit a larger driving force than in the conventional system. Adjustment of this transmitted driving force is
Various methods can be achieved by arbitrarily setting the tooth width of each gear fixed to two axes, that is, the second and third axes.

In addition, since the face widths of all other gears in addition to the 1st 9th gear can be made smaller, the 1st and 2nd screw shafts can be shortened, and the runout of these shafts is reduced. , it can be rotated more stably. In other words, in the conventional system, when transmitting the driving force to the driving gear of each screw shaft, the driving force was transmitted by one gear, whereas in this configuration, the same driving force as above is transmitted to the driving gear of each screw shaft. 1
．． When transmitting to the 9th gear, it is transmitted through two gears, so the driving force transmitted from one gear to the 1.9th gear is halved compared to the conventional method, and the driving force transmitted to the 1st and 9th gears as well as all other gears is The tooth width of the gear can be reduced to about half of the conventional width.

Embodiments of the present invention will be described in detail below with reference to FIGS. 1 to 10.

The transmission gear device of the twin-screw press ratio machine according to this embodiment is the first one.
2. As shown in Figure 3, the second ! , the second screw shaft 7.10 is driven by one drive device 8. That is, the first screw shaft 7 is connected to the drive shaft 9 of the drive device 8 . A first gear 1 is fixed to the drive shaft 9, and a second gear 2 and a third gear 3 mesh with the first gear 1. A fourth gear 4' is fixed to the first idler shaft 11 to which the second gear 2 is fixed. A fifth gear 5 is fixed to the second idler shaft 12 to which the third gear 3 is fixed. A sixth gear 6 meshes with the fourth gear and the fifth gear, and the sixth gear 6 is fixed to the second screw shaft IO.

Said second to fifth gears 2, 3, 4. , 5 have the same number of teeth. Further, the number of teeth of the first gear 1 and the sixth gear are the same. Each of the above gears may be a spur gear, a bevel gear, or a helical gear. Further, the fourth gear 4, the sixth gear 6, and the fifth gear 5 are arranged so that their rotation axes are aligned in a straight line A.
Preferably located at the top. If the gears 4, 6.5 are arranged on a straight line in this way, the force acting on the tooth surface of the sixth gear 6 will be transmitted by the teeth of the two gears 4.5 in a tangential direction perpendicular to the straight line and to each other. Since they work in opposite directions, they cancel each other out and become zero, eliminating the need for a large radial bearing that receives the force applied to the tooth surface. In other words, even with a dual drive type, if the gears are not arranged in a straight line, the forces acting on the tooth surface of the central gear from the two gears will not cancel each other out, and a large radial bearing will be required to receive this force. is necessary.

In the above configuration, when the drive device 8 is driven and the drive shaft 9 rotates, for example, clockwise, the first screw shaft 7 rotates clockwise. The clockwise rotation of the drive shaft 9 causes the first gear 1 to rotate clockwise, and the second gear
Both gear 2 and third gear 3 rotate counterclockwise. Then, the fourth gear 4 and the fifth gear 5 rotate counterclockwise by the first idler shaft 11 and the second idler shaft 12, respectively, and the sixth gear 6 meshes with both gears 4 and 5.
rotates clockwise, and the second screw shaft 10 rotates clockwise similarly to the first screw shaft 7.

According to the above embodiment, the first screw shaft 7 is driven by a so-called single drive because the drive shaft 9 is directly connected to the first screw shaft 7, but the second screw shaft 10 is driven by a single drive. Since the driving force is transmitted by the two gears 4.5, so-called dual drive is achieved, and the power can be reliably increased with a small number of parts and a simple structure. In addition, the above two gears 4.
By arbitrarily setting the tooth width etc. of No. 5, the degree of power-up can be set in various ways. Also, Section 4.5
．． Since the tooth widths of the six gears 4, 5.6 can be made smaller, the second screw shaft 10 can be made shorter, the runout of the shaft 10 can be reduced, and it can be rotated more stably. That is, in the conventional system, when transmitting the driving force to the second screw shaft driving gear, the driving force was transmitted by one gear, whereas in this configuration, the same driving force as described above is transmitted to the sixth gear. When it is transmitted to the gear 6, it is transmitted by two gears 4.5, so compared to the conventional method, the driving force transmitted from one gear to the sixth gear is halved. The tooth width of the gear 4.5 can be reduced to about half of the conventional width.

Next, both screw shafts 7. A second embodiment that can power up the IO will be described. This second embodiment is similar to the fourth embodiment. , 5 and 6, the only difference from the first embodiment is the mechanism for transmitting the driving force from the drive device 8 to the second gear 2 and the third gear 3. That is, the drive gear 15 is fixed to the drive shaft 9 of the drive device 8, and the first gear 1 is not fixed to the drive shaft 9,
Further, the first screw shaft 7 is also not connected to the drive shaft 9. The first gear l is the first screw sleeve 7.
and, similar to the first embodiment, the second
It meshes with gear 2 and third gear 3. Each of the above gears may be a spur gear, a bevel gear, or a helical gear.

Therefore, in the above configuration, when the drive device 8 is driven and the drive gear 15 of the drive shaft 9 rotates, for example, clockwise, the second gear 2 and the third gear 3 rotate counterclockwise,
The first gear (3) causes the first screw shaft 7 to rotate clockwise. Due to the counterclockwise rotation of the second gear 2 and the third gear 3, the first idler shaft 11 and the second
The fourth gear 4 and the fifth gear 5 rotate counterclockwise via the idler shaft 12, and the sixth gear 6 meshing with both gears 4 and 5 rotates clockwise to rotate the second screw. I[1I10 rotates clockwise similarly to the first screw shaft 7 described above.

Therefore, according to the second embodiment, both screw shafts 7.
10, the driving force from the drive shaft 9 is connected to two gears 2.3.
and 4.5, the power can be reliably increased with a small number of parts and a simple structure. Furthermore, by arbitrarily setting the tooth widths of these two gears 2, 3 and 4, 5, various degrees of power-up can be set. Also, the 1.6th gear 1.6
In addition to all other gears 2, 3, 4. ．． Since the tooth width of 5.15 can be made smaller, the second screw shaft 10
Of course, the first screw shaft 7 can also be shortened.
The vibrations of these shafts 10 and 7 are reduced, and they can be rotated more stably. In other words, in the conventional system, when transmitting the driving force to each screw shaft drive gear, 1
Whereas the driving force was transmitted by two gears, in this configuration, the same driving force as above is transmitted to the 1st and 6th gears.
6, the driving force is transmitted by two gears 2, 3, 4, and 5, respectively, so the driving force transmitted from one gear to the 1.6th gear is halved compared to the conventional method. gear 1.6
and all other gears 2, 3, 4°5 that mesh with these
．． The tooth width of 15 can be reduced to about half of the conventional width.

Furthermore, a third embodiment will be described which is more powerful than the previous two embodiments. This third embodiment is constructed as follows, as shown in FIGS. 7 to IO. That is, the first gear 21 is fixed to the first screw shaft 7, and the second gear 22 and the third gear 23 mesh with the first gear 21. A fourth gear 24 meshes with the second gear 22 and the third gear 23. The third gear 23 is fitted to the first shaft 35 so as to be relatively rotatable, the fifth gear 25 is fixed to the first shaft 35, and the sixth gear 26 is fitted to the first shaft 35 so as to be relatively rotatable. That is, when the first shaft 35 is rotationally driven, the fifth gear 25 is rotationally driven, but since the other two, the third gear 23 and the sixth gear 26, are relatively rotatable, there is no difference between the two members. If there is friction, the frictional force will cause each gear 23 to rotate in the same direction as the first shaft 35, but if a force that prevents this rotation is applied, each gear 23 will rotate relative to the first shaft 35.
．． 26 stops rotating. A seventh gear 27 and an eighth gear 28 mesh with the fifth gear 25 .

The fourth gear 24 and the seventh gear 27 are both fixed to a second shaft 36. The ninth gear 29 is attached to the second screw shaft 10.
is fixed, and the sixth gear 26 and the tenth gear 30 mesh with the ninth gear 29. An eleventh gear 31 meshes with the sixth gear 26 and the tenth gear 30. The eighth gear 28 and the eleventh gear 31 are both fixed to a third shaft 37. The drive shaft 9 of the drive device 8 may be connected to any one of the first shaft 35, the second shaft 36, or the third shaft 37, and in the third embodiment, as an example, the first shaft 3
Connect to 5. The second gear 22 is independently fixed to the fourth shaft 38, and the ten gears 30 are independently fixed to the fifth shaft 39. The second gear 22, the first gear 21, and the third gear 2
It is preferable that the respective rotation axes of No. 3 are located on a straight line B, and the tenth gear 30, the ninth gear 29, and the fifth gear 35
It is preferable that the respective rotation axes of are also located on a straight line C.

Each of the above gears may be a spur gear, a bevel gear, or a helical gear.

On the other hand, the second gear 22 and the 31st gear 23 have the same number of teeth, and the fourth gear 24 and the 11th gear 31 have the same number of teeth. Further, the sixth gear 26 and the tenth gear
The gear 30 has the same number of teeth, and the seventh gear 27 and the eighth gear 28 have the same number of teeth.

In addition, in the third embodiment, the positions of the gear mechanisms shown in FIGS. 8.9.10 are arranged in order from the drive device 8 toward the tip of each screw shaft, but the arrangement is not limited to this arrangement. Instead, they can be arranged in any order, for example as shown in Figure 8.10.9.

In the above configuration, when the drive shaft 9 rotates clockwise due to the drive of the drive device 8, the first shaft 35 also rotates in the same direction. Then, due to the rotation of the first shaft 35, the fifth
The gear 25 rotates clockwise, and the seventh gear 27 and the eighth gear 28 both rotate counterclockwise. The seventh gear 27 causes the fourth gear 24 to rotate counterclockwise together with the second shaft 36 . The rotation of the fourth gear 24 causes both the second gear 22 and the third gear 23 to rotate clockwise, and the first gear 21 meshing with these gears 22 and 23 rotates counterclockwise, causing the first screw to rotate. The shaft 7 rotates in the same direction.

On the other hand, due to the counterclockwise rotation of the eighth gear 28, the eleventh gear 31 rotates counterclockwise together with the third shaft 37. Due to the rotation of this first I gear 3, the tenth gear 3
The 0 and 6th gears 26 both rotate clockwise, and the 9th gear 29 meshing with these gears 30.26 rotates counterclockwise. Therefore, the second screw shaft 10 rotates counterclockwise similarly to the first screw shaft 7.

According to the third embodiment, therefore, two screw shafts 7.
Both 10 and 10 can transmit driving force divided into two axes,
It is possible to transmit a larger driving force than the conventional one. This transmitted driving force is adjusted by two axes, that is, the second shaft 36.
By arbitrarily setting the tooth width of each gear fixed to the third shaft 37, various methods can be performed. Also, Chapter 1.9
Besides gears 21.29, all other gears 22, 23, 2
Since the tooth widths of 4°25.26, 27.28, and 30.31 can be made smaller, the 1.2nd screw shaft 710
can be made shorter, the runout of these shafts 7 and 10 is reduced, and rotation can be made more stable. In other words, in the conventional system, when transmitting the driving force to the driving gear of each screw shaft, the driving force was transmitted by one gear, whereas in this configuration, the same driving force as above is transmitted to the driving gear of each screw shaft. When the driving force is transmitted to the 1.9th gear 21.29, it is transmitted through the two gears 22, 23, 30, and 26, so the driving force is transmitted from one gear to the 1.9th gear 21.29 compared to the conventional method. is halved, and the 1.9th gear 2129 and all other gears 22, 23, 24, 25, 26, 2
The tooth width of 7, 28, 30.31 can be reduced to about half of the conventional width. Further, the respective rotational axes of the second gear 22, the first gear 21, and the third gear 23 are positioned on a straight line B, and the rotational axes of the first gear 21, the ninth gear 29, and the fifth gear 35 are positioned on the straight line B. is also positioned on the straight line C, so the force acting on each tooth surface of the 1.9th gear 21.29 is perpendicular to the straight line B and C due to the teeth of the two gears 22, 23: 30, 26. Since they act in the tangential direction and in opposite directions, they cancel each other out and become zero, making it unnecessary to use a large radial bearing to receive the force applied to the tooth surface. In other words, even with a dual drive type, if the gears are not arranged in a straight line, the forces acting on the tooth surface of the central gear from the two gears will not cancel each other out, and a large radial bearing will be required to receive this force. is necessary. Therefore, since the radial bearing can be made smaller, the shaft diameter of each screw shaft 7.10 can be increased, and the screw can be driven with a larger driving force.

In each of the above embodiments, the three gears are arranged in a straight line so that the radial bearing can be made smaller, but the present invention is not limited to this, and the radial bearing can be made somewhat larger. If it is possible, the gears of 3g may not be arranged in a straight line.

[Brief explanation of the drawing]

1.2.3 are a schematic front view of a transmission gear device of a twin-screw press ratio machine according to the first embodiment of the present invention, a cross-sectional view along the ■-■ line in FIG. 1, and a cross-sectional view along the line III-III, respectively; Fig. 4.5.6 is a schematic front view of a transmission gear device of a twin-screw press ratio machine according to a second embodiment of the present invention, a sectional view taken along the line ■-V in Fig. 4, and a sectional view taken along the line
A cross-sectional view taken along the line Vl, Figures 7.8 and 9-10 are a schematic front view of the transmission gear device of a twin-shaft press ratio machine according to the third embodiment of the present invention, a cross-sectional view taken along the ■-■ line in Figure 7, and IX. -IX line sectional view, XX line sectional view, and FIG. 11 are schematic front views of a transmission gear device of a conventional twin-screw press ratio machine. 1... 1st gear, 2... 2nd gear, 3... 3rd gear, 4... 4th gear, 5... 5th gear, 6... 6th gear, 7... ...First screw shaft, 8... Drive device, 9... Drive shaft, IO... Second screw shaft, 11
...First idler shaft, 12...Second idler shaft, 1
5. Drive gear, 21 first gear, 22... second gear, 23
...Third gear, 24...Fourth gear, 25...Fifth gear, 26/Sixth gear, 27...Seventh gear, 28...Eighth gear, 29...Ninth gear , 30... 10th gear,
31... 11th gear, 35... 1st sleeve, 36 - 2nd axis, 37... 3rd axis, 38 4th axis, 39... 5th axis
shaft.

Claims (3)

[Claims] (1) A first screw shaft (7) is connected to a drive shaft (9) of a drive device (8), and a first gear (1) is connected to the drive shaft (9).
) is fixed, a second gear (2) and a third gear (3) are meshed with the first gear (1), and the second gear (2) is fixed to the first idler shaft (11). The fourth gear (4) is fixed, the fifth gear (5) is fixed to the second idler shaft (12) to which the third gear (3) is fixed, and the sixth gear (6
) meshes with the fourth gear (4) and the fifth gear (5), the sixth gear (6) is fixed to the second screw shaft (10), and the second to fifth gears ( 2, 3, 4,
5) have the same number of teeth, and the first gear (1
) and the sixth gear (6) have the same number of teeth. (2) The drive gear (15) is attached to the drive shaft (9) of the drive device (8).
) and attach the first gear (1) to the first screw shaft (7).
is fixed, the second gear (2) and the third gear (3) mesh with both the drive gear (15) and the first gear (1), respectively, and the second gear (2) is fixed. A fourth gear (4) is fixed to the first idler shaft (11), a fifth gear (5) is fixed to the second idler shaft (12) to which the third gear (3) is fixed, and a fifth gear (5) is fixed to the second idler shaft (12) to which the third gear (3) is fixed. The gear (6) is the fourth gear (4).
) meshes with the fifth gear (5), and the sixth gear (6
) is fixed to the second screw shaft (10), and
The number of teeth of the second to fifth gears (2, 3, 4, 5) are all the same, and the first gear (1) and the sixth gear (6
1. A transmission gear device for a twin-screw extruder, characterized in that the number of teeth of the two screws ( ) is also the same. (3) A first gear (21) is fixed to the first screw shaft (7), a second gear (22) and a third gear (23) both mesh with the first gear (21), and a fourth gear (24) meshes with the second gear (22) and the third gear (23), and the third gear (23) is fitted to the first shaft (35) so as to be relatively rotatable, and The fifth gear (25) is attached to the shaft (35).
) is fixed, and the sixth gear (26) is fitted in a relatively rotatable manner, and the seventh gear (27) is connected to the fifth gear (25).
and the eighth gear (28) mesh with each other, and the fourth gear (28) meshes with the fourth gear (28).
4) and the seventh gear (27) are both fixed to the second shaft (36), and the ninth gear (29) is fixed to the second screw shaft (10).
is fixed, and the sixth gear (29) is fixed to this ninth gear (29).
6) and the 10th gear (30) mesh with each other, the 11th gear (31) meshes with both the 6th gear (26) and the 10th gear (30), and the 8th gear (28) and the 10th gear (30) mesh with each other. 11th
The gear (31) is fixed to the third shaft (37), and the drive shaft (9) of the drive device (8) is fixed to the first shaft (37).
5), while being connected to either the second shaft (36) or the third shaft (37), the second gear (22) and the third gear (23) have the same number of teeth; The fourth gear (24) and the eleventh gear (31) have the same number of teeth, the sixth gear (26) and the tenth gear (30) have the same number of teeth, and the seventh gear A transmission gear device for a twin-screw extruder, characterized in that (27) and the eighth gear (28) have the same number of teeth.