A transmission gear system for a twin-screw extruder or twin-screw kneader, a twin-screw extruder using the same, and a twin-screw kneader

Abstract

To provide a gear transmission device that can transmit greater driving force without changing the distance between the centers of the two screw shafts. [Solution] The transmission gear device comprises a drive shaft, first and second driven shafts, first and second opposing gears, and first and second transmission gears. The drive shaft has first and second drive gears. The first driven shaft is connected to a first screw shaft and comprises a first driven gear that engages with the first drive gear, and the second driven shaft is connected to a second screw shaft and comprises a second driven gear that engages with the second drive gear. The first opposing gear is positioned opposite the first drive gear with respect to the first driven gear and engages with the first driven gear. The second opposing gear is positioned opposite the second drive gear with respect to the second driven gear and engages with the second driven gear. The first transmission gear transmits the rotational drive of the first drive gear to the first opposing gear, and the second transmission gear transmits the rotational drive of the second drive gear to the second opposing gear.

Description

Technical Field

[0001] The present disclosure relates to a transmission gear device for a twin-screw extruder or a twin-screw kneader that rotationally drives two screw shafts disposed in a barrel by one drive device and performs an extrusion process or a kneading process on a material supplied into the barrel by the two screw shafts, a twin-screw extruder using the same, and a twin-screw kneader.

Background Art

[0002] Conventionally, various configurations of transmission gear devices for such twin-screw extruders or twin-screw kneaders (hereinafter referred to as twin-screw kneading machines, etc.) are known. A transmission gear device that rotationally drives two output shafts connected to two screw shafts with one drive shaft is widely adopted (for example, see Patent Document 1). In such a transmission gear device, two output shafts can be rotationally driven in synchronization with one drive shaft, and a simple structure such as a three-axis configuration can be adopted.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In material development and production, the compositeization of molding materials is progressing, and in many cases, the transmitted load power applied to the material increases depending on the type of target material. In order to process such target materials with a twin-screw kneading machine or the like, it is necessary to transmit a larger driving force to the two output shafts connected to the two screw shafts.

[0005] When increasing the driving force to drive the output shafts, the diameter of the output shafts must be increased, and the diameter of the bearings supporting these output shafts must also be increased. In twin-shaft mixers, the distance between the centers of the two screw shafts is fixed, and therefore the distance between the centers of the two output shafts is also fixed. For this reason, the increase in diameter of the two output shafts and the increase in bearing diameter must be adjusted within that distance range. Furthermore, changing the distance between the centers of the two screw shafts has a significant impact on the performance of the mixing process and the design of the screws, so it cannot be done lightly.

[0006] Therefore, the object of this disclosure is to solve the above-mentioned problems by providing a transmission gear system for a twin-screw extruder or twin-screw kneader that has two screw shafts arranged in a barrel and performs extrusion or kneading on a material supplied to the barrel, which can achieve greater transmission of driving force without changing the distance between the centers of the two screw shafts. [Means for solving the problem]

[0007] To achieve the above-mentioned objectives, the transmission gear apparatus of this disclosure is configured as follows.

[0008] A gear transmission system according to one aspect of the present disclosure is a gear transmission system for a twin-screw extruder or twin-screw kneader that has two screw shafts arranged in a barrel and performs extrusion or kneading on a material supplied to the barrel. The gear transmission system comprises a drive shaft, a first driven shaft, a second driven shaft, a first opposing gear, a second opposing gear, a first transmission gear, and a second transmission gear. The drive shaft has a first drive gear and a second drive gear positioned axially apart from the first drive gear. The first driven shaft is axially connected to the first screw shaft and includes a first driven gear that engages with the first drive gear. The second driven shaft is axially connected to the second screw shaft and includes a second driven gear that engages with the second drive gear. The first opposing gear is positioned opposite the first drive gear with respect to the first driven gear and engages with the first driven gear. The second opposing gear is positioned opposite the second drive gear with respect to the second driven gear and engages with the second driven gear. The first transmission gear engages with the first drive gear and the first opposing gear and transmits the rotational drive of the first drive gear to the first opposing gear. The second transmission gear engages with the second drive gear and the second opposing gear and transmits the rotational drive of the second drive gear to the second opposing gear. The first drive gear, the second drive gear, the first opposing gear, and the second opposing gear have the same reference circle diameter and number of teeth, and the first driven gear and the second driven gear also have the same reference circle diameter and number of teeth. [Effects of the Invention]

[0009] According to this disclosure, in a transmission gear system for a twin-screw extruder or twin-screw kneader that has two screw shafts arranged in a barrel and performs extrusion or kneading on a material supplied to the barrel, it is possible to provide a transmission gear system that can achieve greater driving force transmission without changing the distance between the centers of the two screw shafts. [Brief explanation of the drawing]

[0010] [Figure 1] A schematic diagram of a twin-shaft kneader equipped with a transmission gear system according to Embodiment 1 of the present disclosure. [Figure 2] Figure 1 is a perspective view showing the schematic arrangement of the gears and shafts in the transmission gear system. [Figure 3] Schematic diagram of the gear and shaft arrangement as viewed from the axial direction of the screw shaft. [Figure 4] A schematic diagram of the arrangement of gears and shafts as viewed from the axial direction of the screw shaft in a transmission gear device according to Embodiment 2 of the present disclosure. [Modes for carrying out the invention]

[0011] A first aspect of the present disclosure is a gear transmission device for a twin-screw extruder or twin-screw kneader that has two screw shafts arranged in a barrel and performs extrusion or kneading on a material supplied to the barrel. The gear transmission device comprises a drive shaft, a first driven shaft, a second driven shaft, a first opposing gear, a second opposing gear, a first transmission gear, and a second transmission gear. The drive shaft has a first drive gear and a second drive gear positioned axially apart from the first drive gear. The first driven shaft is axially connected to the first screw shaft and includes a first driven gear that engages with the first drive gear. The second driven shaft is axially connected to the second screw shaft and includes a second driven gear that engages with the second drive gear. The first opposing gear is positioned opposite the first drive gear with respect to the first driven gear and engages with the first driven gear. The second opposing gear is positioned opposite the second drive gear with respect to the second driven gear and engages with the second driven gear. The first transmission gear engages with the first drive gear and the first opposing gear and transmits the rotational drive of the first drive gear to the first opposing gear. The second transmission gear engages with the second drive gear and the second opposing gear and transmits the rotational drive of the second drive gear to the second opposing gear. The first drive gear, the second drive gear, the first opposing gear, and the second opposing gear have the same reference circle diameter and number of teeth, and the first driven gear and the second driven gear also have the same reference circle diameter and number of teeth.

[0012] A gear transmission device according to a second aspect of the present disclosure is a gear transmission device according to the first aspect, wherein the reference circle diameters of the first drive gear, second drive gear, first opposing gear, and second opposing gear are larger than the reference circle diameters of the first driven gear and second driven gear, and smaller than the reference circle diameters of the first transmission gear and second transmission gear.

[0013] A third aspect of the present disclosure is a gear transmission device according to the first or second aspect, wherein, as viewed from the axial direction of the drive shaft, the angle formed by the line segment connecting the center of the first drive gear and the center of the first driven gear and the line segment connecting the center of the second drive gear and the center of the second driven gear is 60 degrees or less.

[0014] The transmission gear device according to the fourth aspect of the present disclosure is the transmission gear device according to any one of the first to third aspects, wherein the acute angle formed by the line connecting the center of the first driving gear and the center of the first driven gear and the line segment connecting the center of the first opposing gear and the center of the first driven gear is the same as the acute angle formed by the line connecting the center of the second driving gear and the center of the second driven gear and the line segment connecting the center of the second opposing gear and the center of the second driven gear, and is 30 degrees or less.

[0015] The transmission gear device according to the fifth aspect of the present disclosure is the transmission gear device according to any one of the first to fourth aspects, wherein the angle formed by the line segment connecting the center of the first transmission gear and the center of the first opposing gear and the line segment connecting the center of the first driven gear and the center of the first opposing gear is the same as the angle formed by the line segment connecting the center of the second transmission gear and the center of the second opposing gear and the line segment connecting the center of the second driven gear and the center of the second opposing gear, and is 40 degrees or more.

[0016] The transmission gear device according to the sixth aspect of the present disclosure is the transmission gear device according to any one of the first to fifth aspects, wherein the first opposing gear and the second opposing gear are arranged such that a part of the first opposing gear and a part of the second opposing gear overlap when viewed from the axial direction of the drive shaft.

[0017] The twin-screw extruder according to the seventh aspect of the present disclosure includes the transmission gear device according to any one of the first to sixth aspects, a barrel, and a first screw shaft and a second screw shaft, which are two screw shafts arranged in the barrel, and is a device for performing an extrusion process on a material supplied into the barrel.

[0018] The twin-screw kneader according to the eighth aspect of the present disclosure includes the transmission gear device according to any one of the first to sixth aspects, a barrel, and a first screw shaft and a second screw shaft, which are two screw shafts arranged in the barrel, and is a device for performing a kneading process on a material supplied into the barrel.

[0019] Hereinafter, embodiments according to the present disclosure will be described in detail based on the drawings.

[0020] (Embodiment 1) Fig. 1 shows a schematic configuration of a two - shaft kneader 50 provided with a transmission gear device 1 according to Embodiment 1 of the present disclosure. Fig. 2 shows a perspective view showing a schematic arrangement configuration of each gear and shaft included in the transmission gear device 1 shown in Fig. 1, and Fig. 3 shows a schematic arrangement configuration of the gears and shafts viewed from the axial direction of the screw shaft. This transmission gear device 1 is, for example, a transmission gear device used in a two - shaft kneader that rotationally drives two screw shafts by one drive device. In Fig. 1, a part of a plurality of gears included in the transmission gear device 1 is omitted, and in Figs. 2 and 3, components such as bearings are omitted. Also, the display of teeth on each gear is omitted.

[0021] As shown in Fig. 1, the two - shaft kneader 50 includes a barrel 53, a first screw shaft 51 and a second screw shaft 52 which are two screw shafts arranged side by side in the barrel 53, and a transmission gear device 1.

[0022] The barrel 53 is a cylindrical hollow container extending in the axial direction of the screw shafts 51, 52, and a material to be kneaded is supplied therein.

[0023] The first screw shaft 51 and the second screw shaft 52 are arranged side by side in the barrel 53 such that their respective axial directions are parallel. The material supplied into the barrel 53 is kneaded between each screw shaft 51, 52 and the inner surface of the barrel 53, and between each screw shaft 51, 52, and is discharged from a discharge port 54 provided at the tip of the barrel 53.

[0024] The transmission gear device 1 includes a drive shaft 3 connected to a drive motor 2 which is a rotational drive device, and a plurality of gears for transmitting the rotational drive of the drive shaft 3, and rotationally drives the first screw shaft 51 and the second screw shaft 52.

[0025] Details of the transmission gear device 1 of the present Embodiment 1 will be described using Figs. 1, 2, and 3. The transmission gear device 1 includes a drive shaft 3, a first driven shaft 11, a second driven shaft 12, a first opposed gear 4, a second opposed gear 5, a first transmission gear 6, and a second transmission gear 7.

[0026] The drive shaft 3 comprises a first drive gear 8 and a second drive gear 9 positioned axially apart from the first drive gear 8. The drive shaft 3 is rotatably supported by a plurality of bearings (not shown).

[0027] One end of the first driven shaft 11 is connected to the end of the first screw shaft 51, and the first driven shaft 11 and the first screw shaft 51 are rotated integrally with their respective rotational axes coaxially positioned. Similarly, one end of the second driven shaft 12 is connected to the end of the second screw shaft 52, and the second driven shaft 12 and the second screw shaft 52 are rotated integrally with their respective rotational axes coaxially positioned. The first driven shaft 11 and the second driven shaft 12 are rotatably supported by a plurality of bearings 15.

[0028] The first driven shaft 11 is provided with a first driven gear 13 that engages with the first drive gear 8, and the second driven shaft 12 is provided with a second driven gear 14 that engages with the second drive gear 9. Since the first drive gear 8 and the second drive gear 9 are positioned at different axial positions on the drive shaft 3, the position of the first driven gear 13 on the first driven shaft 11 and the position of the second driven gear 14 on the second driven shaft 12 are also at different axial positions. Furthermore, the gear sizes and the distance between the first driven shaft 11 and the second driven shaft 12 (axis-center distance) CP (see Figure 1) are set so that the first driven gear 13 and the second driven shaft 12 do not interfere with each other, and the second driven gear 14 and the first driven shaft 11 do not interfere with each other.

[0029] The first opposing gear 4 is positioned opposite the first drive gear 8 with the first driven gear 13 in between, and the first opposing gear 4 is engaged with the first driven gear 13 (see Figure 3). The first transmission gear 6 is engaged with the first drive gear 8 and the first opposing gear 4, and the first transmission gear 6 transmits the rotational drive of the first drive gear 8 to the first opposing gear 4.

[0030] Similarly, the second opposing gear 5 is positioned opposite the second drive gear 9 with the second driven gear 14 in between, and the second opposing gear 5 is engaged with the second driven gear 14 (see Figure 3). The second transmission gear 7 is engaged with the second drive gear 9 and the second opposing gear 5, and the second transmission gear 7 transmits the rotational drive of the second drive gear 9 to the second opposing gear 5.

[0031] As shown in Figure 3, in the transmission gear device 1 of this embodiment 1, the first drive gear 8, the second drive gear 9, the first opposing gear 4, and the second opposing gear 5 have the same reference circle diameter and number of teeth. Also, the first driven gear 13 and the second driven gear 14 have the same reference circle diameter and number of teeth.

[0032] As shown in Figure 3, the reference circle diameters of the first drive gear 8, the second drive gear 9, the first opposing gear 4, and the second opposing gear 5 are larger than the reference circle diameters of the first driven gear 13 and the second driven gear 14, and smaller than the reference circle diameters of the first transmission gear 6 and the second transmission gear 7. Furthermore, the first transmission gear 6 and the second transmission gear 7 have the same reference circle diameter and number of teeth.

[0033] As shown in Figure 3, the angle θ1 formed by the line segment connecting the center A1 of the first drive gear 8 and the center B1 of the first driven gear 13, and the line segment connecting the center A2 of the second drive gear 9 and the center B2 of the second driven gear 14, when viewed from the axial direction of the drive shaft 3, is set to 60 degrees or less.

[0034] As shown in Figure 3, the acute angle θ2 is formed by the line connecting the center A1 of the first drive gear 8 and the center B1 of the first driven gear 13, and the line segment connecting the center C1 of the first opposing gear 4 and the center B1 of the first driven gear 13. The acute angle θ3 is formed by the line connecting the center A2 of the second drive gear 9 and the center B2 of the second driven gear 14, and the line segment connecting the center C2 of the second opposing gear 5 and the center B2 of the second driven gear 14. The acute angles θ2 and θ3 are the same angle and are set to 30 degrees or less. In the transmission gear device 1 of this embodiment 1, the acute angles θ2 and θ3 are set to 0 degrees. Furthermore, the case where the acute angles θ2 and θ3 are not 0 degrees but are set to 30 degrees or less is shown in Figure 4 (Embodiment 2) described later.

[0035] As shown in Figure 3, angle θ4 is formed by the line segment connecting the center D1 of the first transmission gear 6 and the center C1 of the first opposing gear 4, and the line segment connecting the center B1 of the first driven gear 13 and the center C1 of the first opposing gear 4. Angles θ5 are formed by the line segment connecting the center D2 of the second transmission gear 7 and the center C2 of the second opposing gear 5, and the line segment connecting the center B2 of the second driven gear 13 and the center C2 of the second opposing gear 5. Angles θ4 and θ5 are the same and are set to be 40 degrees or greater.

[0036] As shown in Figure 3, the first opposing gear 4 and the second opposing gear 5 are arranged such that, when viewed from the axial direction of the drive shaft 3, a portion of the first opposing gear 4 and a portion of the second opposing gear 5 overlap.

[0037] In the twin-shaft kneader 50 equipped with the transmission gear device 1 of this embodiment 1, a driving gear and an opposing gear are positioned approximately 180 degrees opposite each other, with one driven gear placed between them, and the driving gear and the opposing gear transmit driving force to one driven gear.

[0038] Specifically, the first opposing gear 4, positioned opposite the first drive gear 8 with respect to the first driven gear 13, and the first drive gear 8 engage with the first driven gear 13, allowing the first driven gear 13 to receive driving force from the first opposing gear 4 and the first drive gear 8. Furthermore, the first drive gear 8 and the first opposing gear 4 engage with the first transmission gear 6, allowing the driving force from the first drive gear 8 to be transmitted to the first opposing gear 4 via the first transmission gear 6.

[0039] Similarly, the second opposing gear 5, positioned opposite the second drive gear 9 with respect to the second driven gear 14, and the second drive gear 9 engage with the second driven gear 14, allowing the second driven gear 14 to receive driving force from the second opposing gear 5 and the second drive gear 9. Furthermore, the second drive gear 9 and the second opposing gear 5 engage with the second transmission gear 7, allowing the driving force from the second drive gear 9 to be transmitted to the second opposing gear 5 via the second transmission gear 7.

[0040] The first drive gear 8 and the second drive gear 9 are fixed to a common drive shaft 3. Therefore, by rotating the drive shaft 3 with the drive motor 2, the driving force of the drive shaft 3 can be transmitted to the first driven shaft 11 through the first driven gear 13, and to the second driven shaft 12 through the second driven gear 14.

[0041] When this rotational drive is performed, the driving force is transmitted to the first driven shaft 11 by two gears positioned approximately 180 degrees opposite each other, so the radial load generated on the first driven shaft 11 becomes a couple. Therefore, the radial load can be significantly reduced compared to the case where the driving force is transmitted to the first driven shaft 11 by a single gear. Similarly, the radial load on the second driven shaft 12 can also be significantly reduced.

[0042] Because the radial load generated when the first driven shaft 11 and the second driven shaft 12 are rotationally driven can be significantly reduced, the bearing capacity (bearing diameter) of the bearing 15 can be reduced. The amount saved by reducing the bearing capacity can be used to increase the diameter of the first driven shaft 11 and the second driven shaft 12. Therefore, in the transmission gear system 1 of a twin-shaft kneader, it is possible to provide a transmission gear system 1 that can transmit a greater driving force without changing the distance between the centers of the two screw shafts 51 and 52.

[0043] In particular, in the twin-shaft kneader 50, the distance (axis-center distance) CP between the first screw shaft 51 and the second screw shaft 52, which are located inside the barrel 53, is determined based on the specifications of the material to be kneaded and the specifications of the screw shafts. Therefore, increasing the shaft diameter of the first driven shaft 11 and the second driven shaft 12, as well as the diameter of the bearings, solely to transmit greater driving force would necessitate a redesign of the entire device. However, by adopting the configuration of the transmission gear device 1 of this embodiment 1 in the twin-shaft kneader 50, it becomes possible to transmit greater driving force without changing the screw shaft distance CP.

[0044] Furthermore, since driving force is transmitted from two gears to a single driven gear, the tooth width (axial dimension) of the gears can be shortened compared to when driving force is transmitted by only one gear.

[0045] In the transmission gear device 1 of this embodiment 1, acute angles θ2 and θ3 are set to 0 degrees, and the first drive gear 8 and the first opposing gear 4 are positioned 180 degrees opposite each other with respect to the first driven gear 11. Similarly, the second drive gear 9 and the second opposing gear 5 are positioned 180 degrees opposite each other with respect to the second driven gear 12. By adopting this arrangement, the radial loads generated on the first driven shaft 11 and the second driven shaft 12 become a couple, and the radial loads can be significantly reduced. Note that if acute angles θ2 and θ3 are the same angle and set to 30 degrees or less, substantially similar effects can be obtained.

[0046] Furthermore, the reference circle diameters of the first drive gear 8, the second drive gear 9, the first opposing gear 4, and the second opposing gear 5 are set to be larger than the reference circle diameters of the first driven gear 13 and the second driven gear 14, and smaller than the reference circle diameters of the first transmission gear 6 and the second transmission gear 7. By adopting this configuration, the angle θ1 formed by the line segment connecting the center A1 of the first drive gear 8 and the center B1 of the first driven gear 13, and the line segment connecting the center A2 of the second drive gear 9 and the center B2 of the second driven gear 14 can be reduced. The angle θ1 can be set to, for example, 60 degrees or less. As a result, the transmission gear device 1 of this embodiment 1 can be applied to a twin-shaft kneader 50 even when the distance between the centers of the first screw shaft 51 and the second screw shaft 52 is short.

[0047] The angle θ4 formed by the line segment connecting the center D1 of the first transmission gear 6 and the center C1 of the first opposing gear 4, and the line segment connecting the center B1 of the first driven gear 13 and the center C1 of the first opposing gear 4, and the angle θ5 formed by the line segment connecting the center D2 of the second transmission gear 7 and the center C2 of the second opposing gear 5, and the line segment connecting the center B2 of the second driven gear 13 and the center C2 of the second opposing gear 5, are the same angle and are set to 40 degrees or more. These angles θ4 and θ5 may be set in the range of, for example, 40 to 70 degrees. For example, the diameter of the first transmission gear 6 can be increased while preventing interference between the first transmission gear 6 and the first driven gear 13 which are arranged in the same plane, and the rotational driving force of the first drive gear 8 can be stably transmitted to the first opposing gear 4 via the first transmission gear 6. Similarly, the diameter of the second transmission gear 7 can be increased while preventing interference with the second transmission gear 7 and the second driven gear 14, which are arranged in the same plane on the other side, and the rotational driving force of the second drive gear 9 can be stably transmitted to the second opposing gear 5 via the second transmission gear 7.

[0048] The first opposing gear 4 and the second opposing gear 5 are arranged such that, when viewed from the axial direction of the drive shaft 3, a portion of the first opposing gear 4 and a portion of the second opposing gear 5 overlap. This makes it possible to suppress an increase in the widthwise dimension (the direction in which the driven shafts are aligned) of the transmission gear device 1 while employing a configuration using opposing gears 4 and 5.

[0049] The first drive gear 8, the second drive gear 9, the first opposing gear 4, and the second opposing gear 5 each have the same reference circle diameter and number of teeth, and the first driven gear 13 and the second driven gear 14 each have the same reference circle diameter and number of teeth. By adopting this configuration, a symmetrical structure can be achieved in a mechanism that transmits driving force from one drive shaft 3 to two shafts, enabling well-balanced power transmission.

[0050] (Embodiment 2) Next, Figure 4 shows a schematic configuration of the gears and shafts in the transmission gear device 61 according to Embodiment 2 of this disclosure, as viewed from the axial direction of the screw shaft. Note that Figure 4, which shows the configuration of Embodiment 2, corresponds to Figure 3 of Embodiment 1. In the transmission gear device 61 of Embodiment 2, configurations that are substantially the same as those of the transmission gear device 1 of Embodiment 1 are given the same reference numerals, and their descriptions are omitted. The main differences will be explained below.

[0051] As shown in Figure 4, in the gear transmission 61, the driving force from the first drive gear 8 is transmitted to the first driven gear 13, and is also transmitted from the first opposing gear 64 to the first driven gear 13 via the first transmission gear 66. In addition, the driving force from the second drive gear 9 is transmitted to the second driven gear 14, and is also transmitted from the second opposing gear 65 to the second driven gear 14 via the second transmission gear 67. Thus, the driving force transmission system in the gear transmission 61 is the same as that in the gear transmission 1.

[0052] On the other hand, the first opposing gear 64 and the second opposing gear 65 are arranged such that, when viewed from the axial direction of the drive shaft 3, they do not overlap each other.

[0053] Furthermore, the acute angle θ2 formed by the line connecting the center A1 of the first drive gear 8 and the center B1 of the first driven gear 13, and the line segment connecting the center C1 of the first opposing gear 64 and the center B1 of the first driven gear 13, is not zero, but is set to, for example, 25 degrees. The acute angle θ3 formed by the line connecting the center A2 of the second drive gear 9 and the center B2 of the second driven gear 14, and the line segment connecting the center C2 of the second opposing gear 65 and the center B2 of the second driven gear 14, is also not zero, but is set to, for example, 25 degrees. The line segment C1-B1 is located to the left of the line A1-B1 shown in Figure 4, and the line segment C2-B2 is located to the right of the line A2-B2 shown in Figure 4.

[0054] By adopting this configuration, the reference circle diameters of the first transmission gear 66 and the second transmission gear 67 can be made smaller compared to the transmission gear device 1 of Embodiment 1, and the widthwise dimension W of the transmission gear device 1 can be reduced.

[0055] In the above-described embodiment, the transmission gears 1 and 61 were shown as being applied to a twin-screw kneader 50 as an example. However, instead of this case, they may also be applied to a twin-screw extruder that extrudes material supplied into a barrel using two screw shafts.

[0056] Furthermore, by appropriately combining any of the above various embodiments, the effects of each can be achieved. [Industrial applicability]

[0057] The transmission gear system of this disclosure is applicable to a twin-screw extruder or twin-screw kneader that rotates two screw shafts arranged in a barrel with a single drive unit to extrude material supplied into the barrel by the two screw shafts or kneading process. [Explanation of Symbols]

[0058] 1. Transmission gear system 2 Drive motor 3 drive shafts 4. First opposing gear 5. Second opposing gear 6. First transmission gear 7. Second transmission gear 8. First drive gear 9. Second drive gear 11 1st driven axis 12 2nd driven shaft 13. First driven gear 14. Second driven gear 50 Twin-shaft mixer 51 First screw shaft 52. Second screw shaft 53 barrels 54 outlet CP interval W width dimension

Claims

1. A transmission gear system for a twin-screw extruder or twin-screw kneader, which has two screw shafts positioned inside a barrel and performs extrusion or kneading on a material supplied to the barrel, A drive shaft having a first drive gear and a second drive gear arranged axially apart from the first drive gear, A first driven shaft is provided with a first driven gear that is axially connected to the first screw shaft and engages with the first drive gear, A second driven shaft is provided with a second driven gear that is axially connected to the second screw shaft and engages with the second drive gear, With respect to the first driven gear, a first opposing gear is positioned opposite to the first drive gear and engages with the first driven gear, With respect to the second driven gear, a second opposing gear is positioned opposite to the second drive gear and engages with the second driven gear, A first transmission gear that engages with the first drive gear and the first opposing gear and transmits the rotational drive of the first drive gear to the first opposing gear, The system comprises a second drive gear and a second transmission gear that engages with the second drive gear and transmits the rotational drive of the second drive gear to the second transmission gear, The first drive gear, the second drive gear, the first opposing gear, and the second opposing gear have the same reference circle diameter and number of teeth, and the first driven gear and the second driven gear have the same reference circle diameter and number of teeth. A transmission gear system for a twin-screw extruder or twin-screw kneader.

2. The gear transmission device according to claim 1, wherein the reference circle diameters of the first drive gear, the second drive gear, the first opposing gear, and the second opposing gear are larger than the reference circle diameters of the first driven gear and the second driven gear, and smaller than the reference circle diameters of the first transmission gear and the second transmission gear.

3. The transmission gear device according to claim 2, wherein, viewed from the axial direction of the drive shaft, the angle formed by the line segment connecting the center of the first drive gear and the center of the first driven gear and the line segment connecting the center of the second drive gear and the center of the second driven gear is 60 degrees or less.

4. The transmission gear device according to claim 3, wherein the acute angle formed by the straight line connecting the center of the first drive gear and the center of the first driven gear and the line segment connecting the center of the first opposing gear and the center of the first driven gear is the same angle as the acute angle formed by the straight line connecting the center of the second drive gear and the center of the second driven gear and the line segment connecting the center of the second opposing gear and the center of the second driven gear, and is 30 degrees or less.

5. The transmission gear device according to claim 4, wherein the angle formed by the line segment connecting the center of the first transmission gear and the center of the first opposing gear and the line segment connecting the center of the first driven gear and the center of the first opposing gear is the same as the angle formed by the line segment connecting the center of the second transmission gear and the center of the second opposing gear and the line segment connecting the center of the second driven gear and the center of the second opposing gear, and is 40 degrees or more.

6. The transmission gear device according to claim 4, wherein the first opposing gear and the second opposing gear are arranged such that, when viewed from the axial direction of the drive shaft, a part of the first opposing gear and a part of the second opposing gear overlap.

7. A transmission gear device according to any one of claims 1 to 6, The barrel and, The barrel comprises two screw shafts, the first screw shaft and the second screw shaft, which are two screw shafts arranged within the barrel. A twin-screw extruder that performs an extrusion process on a material supplied into the barrel.

8. A transmission gear device according to any one of claims 1 to 6, The barrel and, The barrel comprises two screw shafts, the first screw shaft and the second screw shaft, which are two screw shafts arranged within the barrel. A twin-shaft kneader that performs kneading on the material supplied into the barrel.

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