JPH01234223A - Transmission gear device of biaxial extruding machine - Google Patents

Abstract

PURPOSE:To enable the title device to cope with requirement even if high torque is required on screws each without increasing the diameter and a face width of gears each, by dividing power to be transmitted to one side screw into a plurality of power. CONSTITUTION:Transmission gears 8, 10 are stuck respectively to screw shafts 4, 5, a driving motor 15 is connected with a rear end of a driving shaft 14 and driving gears 18, 19 are stuck to the driving shaft 14. Then an intermediate gear 22 gears with the driving gear 18 and transmission gear 8. Then a gear wheel 25 is turnable so that an external gear 27 and internal gear 26 gear respectively with a second driving gear 19 and three second intermediate gears 28 and power is divided and transmitted to the transmission gear 10 with the intermediate gear 28. The screw shafts 4, 5 are provided within the gear wheel 25 in a state of piercing through. The intermediate gears 28 are arranged on the external circumference of the transmission gear 10 at equal intervals, the power is divided into three by the driving gear 19 through the gear wheel 25, turned at equiphase and power transmission is performed to the transmission gear 10. Therefore, at the time of an increase of torque, the title device can cope with that without increasing the diameters and face widths of the gears each and since they turn at equiphase respectively phase register is unnecessary.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a transmission gear device for a twin-screw extruder that kneads, melts, and extrudes resin.

(Prior Art) Conventionally, as a transmission device for a twin-screw extruder, those shown in FIGS. 3 to 7 are known. The device shown in FIGS. 3 and 4 consists of the simplest gear mechanism, and the driving force of the motor 41 is transmitted from the first drive gear 43, 44 fixed to the drive shaft 42.
and is transmitted to each screw shaft 49.50 of the first and second screws 47.48 via the second transmission gear 45.46. Incidentally, recently, in order to increase the capacity of extruders, efforts have been made to increase the torque by high-speed rotation, and as a means to cope with this, the transmission gear 45.
It is necessary to increase the tooth width of gear 46, and because the distance between the axes of the first and second screws 47 and 48 is extremely narrow, it is impossible to increase the diameter, and the tooth contact of gears 43 to 46 is poor. At the same time, the bearings 51 of each screw shaft 49.50.
52 interval increases, the deflection of the shafts of the transmission gears 45 and 46 increases. Furthermore, although it is necessary to increase the capacity of the bearings 51 and 52, there is a problem that the bearing capacity cannot be increased because the distance between the shafts is narrow and the diameter of the bearings cannot be increased.

Therefore, as shown in FIGS. 5 to 7, there is a method in which the transmission path of the power transmitted to the second screw 48 is divided into two, and one drive gear 43 fixed to the drive shaft 42 is connected to the first and second screws. The second transmission gears 45 and 46 are meshed, and the first screw shaft 49 is connected to the first screw 47. On the other hand, the second screw shaft 50 is divided into two parts, and the second transmission gear 46 is fixed to one end of one divided screw shaft 50A, and the first intermediate gear 53 is fixed to the other end of the shaft 50A. A second screw 4 is attached to the tip of the screw shaft 50B.
8 are connected to each other, and a second intermediate gear 54 is fixed to the other end. The first and second intermediate gears 53, 54 each have two idler gears 55, 56, 57. ．． 5
8 are meshed, and these idler gears 55, 56, 57
．． 58 is fixed to each end of two idler shafts 59 and 60.

According to this conventional device, the first and second screws 47.
Even if the distance between the 48 axes is narrow, a large-capacity hair ring can be used, and torque can be increased as power is increased.

(Problems to be Solved by the Invention) By the way, in the conventional devices shown in FIGS. 5 to 7,
There is a limit to the reduction in the face width of transmission gears and the power transmission, and in order to transmit power equally to the idler shafts 59.60 between the two idler shafts 59.60, gear phasing is essential. The problem is that it gets complicated.

The present invention was devised in view of the above-mentioned circumstances, and its objectives are to reduce the face width of transmission gears, increase transmitted power, simplify the structure, and eliminate the need for gear phasing. An object of the present invention is to provide a transmission gear device for a twin-screw pushing machine that can achieve the following.

(Means for Solving the Problems) In order to solve the above problems, the present invention takes the following technical measures.

That is, the present invention provides first and second transmission gears 10 fixed to respective screw shafts 4.5 of first and second screws 1 and 2 fitted in an extrusion cylinder of an extruder;
First and second drive gears 18.1 fixed to the drive shaft 14
9, an intermediate gear 22 meshing with the first driving gear 18 and the transmission gear 8, through which the first and second screw shafts 4, 5 are inserted, and having inner and outer teeth 26, 27, and the outer tooth 27 is a second gear. A gear wheel 25 that meshes with the drive gear 19 and whose internal teeth 26 mesh with the second transmission gear 10 via a plurality of second intermediate gears 28 (1H), the second intermediate gear 28 is connected to the second transmission gear 10. They are characterized by being arranged at equal intervals around the outer circumference.

(Function) According to the present invention, power is transmitted to the first screw 1 from the first drive gear 18 via the intermediate gear 22 and the first transmission gear 8, and on the other hand, power is transmitted to the second screw 2. Transmission is performed from the second drive gear 19 via the gear wheel 25 to the plurality of second intermediate gears 28, and then again via the second transmission gear 10. Since the second intermediate gears 28 are arranged at equal intervals around the outer circumference of the first transmission gear 8 and mesh with each other,
Each of the second intermediate gears 2B rotates in the same phase, and the radial forces acting on the second transmission gear 10 are equal and cancel each other out, theoretically becoming zero. Therefore, the bearings 13 located on both sides of the second transmission gear 10 can be minimized, and the distance between the axes of the first and second screws L2 can be extremely narrow. There's no need.

(Example) Embodiments of the present invention will be described below based on the drawings.

In Figures 1 and 2, ■ is a first screw, 2 is a second screw, and both screws 1 and 2 are rotatably fitted in an extrusion cylinder of an extruder (not shown), and each has a gear box. A first screw shaft 4 and a second screw shaft supported in
It is connected to one end of the screw shaft 5 via a coupling 6.7. The first screw shaft 4 is longer than the second screw shaft 5, and the first transmission gear 8 is fixed to the other end thereof, and the rear shaft end is supported by the gear box 3 via a thrust bearing 9. Further, a second transmission gear IO is fixed to the second screw shaft 5, and the rear shaft end is supported by the gear box 3 via the thrust bearing 11. This is a bearing that supports the front and rear of the second transmission gear 8.10.

14 is a drive shaft, to the rear end of which the output shaft 16 of the drive motor 15 is connected via a coupling 17, the No. 1 and the second drive gears 18, 19 are fixed, and the re-drive gears 18.
19 is supported by the gear box 3 via bearings 20 and 21.

An intermediate gear 22 meshes with both the first drive gear 18 and the transmission gear 8, and the intermediate gear shaft 23 is supported by the gear box 3 via a bearing 24.

Reference numeral 25 denotes a tooth ring, which includes internal teeth 26 and external teeth 27.
meshes with the second drive gear 19, the internal teeth 26 mesh with the three second intermediate gears 28, and the second intermediate gears 28
The first screw shaft 4 and the second
The screw shaft 5 is inserted into the gear ring 25. In particular, by inserting the first screw shaft 4 through the gap between the gears 26 and 28, it is possible to minimize the distance between the screw shafts 4.5.

The second intermediate gears 28 are arranged at equal intervals (120 degree intervals) on the outer periphery of the second transmission gear 10, and each intermediate gear shaft 29 is supported by the gear box 3 via a bearing 30 or the like. The driving gear 19 divides the power into three parts via the gear wheel 25, rotates in the same phase, and transmits the power to the second transmission gear 10, respectively. Therefore, since each second intermediate gear 28 transmits one-third of the power transmitted from the second drive gear 19 via the gear 25, the diameter and face width of each gear are increased when torque is increased. It can be handled without any problems, and since each rotates in the same phase, there is no need for phase alignment. In addition, the radial force acting on the second transmission gear 10 from the second intermediate gear 28 is directed toward the center of the second screw shaft 5 and acts equally, so they cancel each other out and theoretically become zero. Therefore, the number of bearings 13 that support the front and back of the second screw shaft 5 can be minimized, and even a case where the distance between the shafts of the first and second screws 1.2 must be designed to be extremely narrow can be easily accommodated.

In addition, since a large space is obtained in the power transmission path to the first screw 1, it can easily accommodate an increase in the tooth width and diameter of the gear due to an increase in torque.

In the above embodiment, the number of second intermediate gears 28 is three, but it can be increased or decreased to four or two, and may be selected as appropriate depending on the degree of torque increase.

(Effects of the Invention) As described above, the transmission gear device of the twin-screw pushing machine according to the present invention has the first and second screw recesses 2. The first and second transmission gears 10 fixed to each screw shaft 4.5, the first and second drive gears 18.19 fixed to the drive shaft i4, the first drive gear 18 and the transmission gear □ an intermediate gear 22 that meshes with the wheel 8;
A plurality of second intermediate gears 28 are inserted through which the first and second screw shafts 4.5 are inserted, and are provided with inner and outer teeth 26, 27. The second intermediate gear 28 is arranged at equal intervals around the outer circumference of the second transmission gear 10. The power gate that transmits power to the screw can be divided into multiple parts, so even if a high torque layer is required for each screw, it can be handled without increasing the diameter and face width of each gear and with a small bearing capacity. The radial forces of the second intermediate gear 28 acting on the second screw shaft 5 are mutually canceled out toward the center of the second screw shaft 5 and theoretically become zero, so that the capacity of the bearing 13 is reduced. Since it can be made small and the tooth width can be made small, the distance between the supports of the second screw shaft 5 is shortened, the deflection of the shaft is extremely small, and it is possible to maintain appropriate tooth contact of each gear.

In addition, even if the power (sandway) is divided, each second intermediate gear 28 rotates in the same phase, so there is no need for phase matching. It is also possible to minimize the distance between both screw shafts, making maintenance management easy and smooth operation possible.

[Brief explanation of the drawing]

1 and 2 show embodiments of the present invention.
The figure is an overall schematic diagram, Figure 2 is a sectional view taken along line A□-A in Figure 1, Figures 3 to 7 show conventional examples, Figure 3 is a schematic plan view, and Figure 4 is 3 is a sectional view taken along the line B-B in FIG. 3, FIG. 5 is a schematic plan view of another conventional example, FIG. 6 is a front view thereof, and FIG. 7 is a sectional view taken along the line CC in FIG. 1...First screw, 2...Second screw, 4
...first screw shaft, 5...second screw shaft,
8... First transmission gear, 10... Second transmission gear, 14
... Drive shaft, 18... First drive gear, 19... Second drive gear, 22... Intermediate gear, 25... Gear wheel, 2
6... Internal teeth, 27... External teeth, 28... Second intermediate gear.

Claims (1)

[Claims] (1) First and second transmission gears 8 and 10 fixed to the respective screw shafts 4 and 5 of the first and second screws 1 and 2 fitted in the extrusion cylinder of the extruder, and the drive shaft 14 first and second drive gears 18 and 19 fixed to the intermediate gear 22 that meshes with the first drive gear 18 and the transmission gear 8;
The first and second screw shafts 4 and 5 are inserted into the second drive gear 1, and the outer teeth 27 are provided with inner and outer teeth 26 and 27.
9, and the internal teeth 26 mesh with the second transmission gear 10 via a plurality of second intermediate gears 28, and the second
A transmission gear device for a twin-screw extruder, characterized in that intermediate gears 28 are arranged at equal intervals around the outer periphery of the second transmission gear 10.