Extruder having a bevel gear transmission

Abstract

The invention relates to an extrusion device (1) and a transmission (2) for driving extruder screws (3, 4) of the extrusion device (1). The transmission (2) comprising a first drive shaft (10) with a first drive spur gear (11), a distributor shaft (13) with a distributor drive spur gear (15) and a distributor output gearwheel (16), wherein the distributor drive spur gear (15) is meshingly coupled with the first drive spur gear (11), a first output shaft (5) with a first output gearwheel (21) and a second output shaft (6) rotating in the same direction as the first output shaft (5) with a second output gearwheel (22), wherein the first output gearwheel (21) and the second output gearwheel (22) are each meshingly coupled with the distributor output gearwheel (16). The first output gearwheel (21) is designed as a beveloid or hypoloid gearwheel, wherein a first axis of rotation (25) of the first output shaft (5) and a second axis of rotation (26) of the second output shaft (6) are arranged in an intersecting axial position or intersecting with an axis-crossing angle (27) and in a common first axial plane (28).

Description

[0001] EXTRUDER WITH BEVEL GEAR

[0002] The invention relates to a gear unit for driving extruder screws of a co-rotating twin-screw extruder with meshing or non-mesh extruder screws, or for driving a melt pump. Extrusion is a process in the industrial production of plastics and food. The main components of an extrusion system are the extruder and the extruder gear unit. The extruder gear unit or the gear unit for driving a twin-screw extruder serves to convert and transmit torque and speed between a drive, in particular at least one motor drive, and the extruder or extruder screws. Depending on the speed and torque to be provided to the extruder screws, the gear unit must be designed to ensure advantageous load distribution in the gear unit, so that the extruder screws always run synchronously with one another.This can be achieved, among other things, by a symmetrical load distribution regarding the individual components of the gearbox and thus an identical torsional deformation.

[0003] Extruder gears used to drive extruder screws of a twin-screw extruder are known from AT 525055 B 1 and EP 0995580 B 1. These extruder gears are designed as independent units, with independent units provided at their output shafts for coupling to the extruder screws. Due to the requirements for the conversion and transmission of torque using the known extruder gears, a multiple introduction of the torque to be transmitted is designed, acting on individual shafts of the extruder gears. This results in the known extruder gears having a large number of individual components.Particularly in the case of a twin-screw extruder in which one end section of the extruder screws is designed without bearings and thus with a free-running end section, additional coupling elements must be provided between the extruder gear and the extruder screws when using the known extruder gears. However, each additional individual component of an extrusion system increases the system's susceptibility to errors and makes it more difficult to take the mandatory synchronous operation of the extruder screws into account, which also has a negative impact on the economical manufacture of the extrusion system and its operation in terms of maintenance costs. The object of the present invention was to overcome the disadvantages of the prior art and to provide a gear for driving extruder screws or an extrusion device, in particular a co-rotating twin-screw extruder with a bearingless end section, in which orin which the entire structure is simplified by reducing the individual components, thereby improving economic manufacturability and economical operation, while at the same time improving load distribution with regard to torque and speed conversion and transmission.

[0004] This object is achieved by a gear according to the invention and an extrusion device according to the claims.

[0005] The gear according to the invention for driving extruder screws of an extrusion device, in particular a co-rotating twin-screw extruder with bearingless accommodation of an end region of the respective extruder screws in an extruder housing, the gear comprising

[0006] - at least one first drive shaft with a first drive spur gear, wherein the first drive shaft can be coupled to a first motor drive,

[0007] - a distributor shaft with a distributor rotation axis, a distributor drive spur gear and a distributor output gear, wherein the distributor drive spur gear is meshingly coupled to the first drive spur gear of the first drive shaft, so that the distributor shaft can be driven by means of the first drive shaft and thus also by the first motor drive,

[0008] - a first output shaft with a first output gear and a second output shaft rotating in the same direction as the first output shaft with a second output gear, wherein the first output gear and the second output gear are each meshingly coupled to the distributor output gear, so that the first output shaft and the second output shaft are each drivable or torque-transmitting and rotationally coupled by means of the distributor shaft.

[0009] Furthermore, the first output gear is designed as a conical gear, as a beveloid or hypoloid gear, but preferably as a beveloid gear. Furthermore, a first axis of rotation of the first output shaft and a second axis of rotation of the second output shaft are arranged in an intersecting axial position or intersecting with an axis crossing angle and in a common first axial plane, wherein the axis crossing angle is selected from a range comprising 0.2° to 10°, in particular 1° to 2°. It would be conceivable that such an axis crossing angle between the first axis of rotation and the second axis of rotation could also be made possible by providing a corresponding play between the respective pairing of output gear and distributor output gear.However, since the gear according to the invention is intended for driving extruder screws, it must be ensured, on the one hand, that the required torque can be transmitted by the gear and, on the other hand, that slippage between the rotary movements of the two extruder screws as well as any relative movement in the axial and radial directions is minimized or avoided as far as possible. Therefore, the invention provides that at least the first output gear is preferably designed as a beveloid gear. This achieves a compact design of the gear, and furthermore, the required torque can be transmitted due to the advantageously formed mutual meshing of the first output gear with the distributor output gear.Synergistically, the improved meshing compared to conventional helical gearing with the necessary clearance for the required axis cross angle improves power transmission, which subsequently reduces the gear's tendency to wear. A further advantage is an increase in load capacity and reduced noise generation.

[0010] The intersection point of the first axis of rotation with the second axis of rotation is positioned, starting from the respective output gears in the direction of the extruder screws, along the axes of rotation of the output shafts, so that the drive shafts are positioned converging. The extruder screws of the twin-screw extruder for which the gear according to the invention can be used preferably have converging extruder screws with an end region of the extruder screws accommodated in the extruder housing without bearings. By means of the gear according to the invention, a direct drive of the extruder screws with intersecting axes is thus possible. No further coupling elements are necessary, and the direct drive of both extruder screws is possible simultaneously, so that no slippage occurs between the rotational movements of the extruder screws.

[0011] Furthermore, it can be expedient if the second output gear is designed as a beveloid gear. This allows the two drive axes to be arranged at an angle to one another, so that the gearbox as a whole is constructed symmetrically. The intersection point of the two axes of rotation of the drive shafts thus lies in a common plane with the distributor axis of rotation. This common plane is also the plane of symmetry of the gearbox. This achieves symmetrical and therefore improved bearing loading of the bearings of all gearbox shafts. This in turn leads to a simplified and therefore more economical design of the gearbox and also to reduced wear on the gearbox components, such as the output gears and the distributor output gear.

[0012] Furthermore, it can be provided that a first gear stage comprising the first drive spur gear and the distributor drive spur gear has a first gear ratio in the low range. This achieves improved meshing of the gears or spur gears of the first gear stage and thus improved engagement of the gear teeth and an increased service life thereof. Furthermore, this enables a higher motor speed of the motor drive(s) with reduced torque and the same drive power of the motor drive(s). This allows for synchronization, i.e., minimizing fluctuating speed, with high drive power of the extruder screws in a simple and improved manner.

[0013] Furthermore, a second gear stage comprising the distributor drive spur gear and the distributor output gear can be provided with a second gear ratio for the higher speed. This eliminates the need for a double introduction of torque to the extruder screws due to the high drive power required for the extruder screws. This further minimizes or eliminates slippage between the extruder screws. This minimizes gaps between the extruder screws or the output swollen screws and the extruder housing.

[0014] Another advantageous embodiment is one in which the distributor output gear is designed as a conical gear or a beveloid gear, so that the distributor rotational axis of the distributor shaft is aligned parallel to the first axial plane. Thus, all rotational axes of the transmission shafts are aligned parallel, enabling symmetry and thus a simple design of the transmission. This improves the longevity of the transmission, also due to the improved meshing of the second gear stage. Furthermore, the parallel arrangement of all rotational axes of the transmission shafts minimizes the axial play of the shafts, which leads to simplified transmission manufacturing and improved cost-effectiveness.According to a further development, it is possible for the gear unit to further comprise a second drive shaft with a second drive spur gear, wherein the second drive shaft is coupleable to a second motor drive, wherein the second drive spur gear is meshingly coupled to the distributor drive spur gear, and wherein the first drive shaft and the second drive shaft, or the first drive spur gear and the second drive spur gear, are arranged at a first angle of 180° to one another relative to the distributor rotation axis. Preferably, the first drive shaft and the second drive shaft, as well as the first drive spur gear and the second drive spur gear, as well as the first motor drive and the second motor drive, can each be of identical construction, so that complete symmetry of the gear unit and, subsequently, complete symmetry of the extrusion device is achieved.This makes manufacturing easier and in turn has beneficial effects on the load distribution in the gearbox and the bearing load, and thus on the service life of the bearings by means of which the shafts of the gearbox or the extrusion device are mounted.

[0015] Furthermore, it may be expedient if the transmission further comprises a third drive shaft with a third drive spur gear and a fourth drive shaft with a fourth drive spur gear, wherein the third drive shaft can be coupled to a third motor drive and the fourth drive shaft to a fourth motor drive, wherein the third drive spur gear and the fourth drive spur gear are each meshingly coupled to the distributor drive spur gear and wherein the third drive shaft and the fourth drive shaft are arranged relative to the distributor rotation axis at a second angle of 180° to one another and respectively relative to the first drive shaft and the second drive shaft relative to the distributor rotation axis at a third angle of 90°.It can also be advantageous if the first drive shaft and the second drive shaft, as well as the first drive spur gear and the second drive spur gear, as well as the first motor drive and the second motor drive, are each of identical construction, and if the third drive shaft and the fourth drive shaft, as well as the third drive spur gear and the fourth drive spur gear, as well as the third motor drive and the fourth motor drive, are each of identical construction. This opens up the possibility of driving the transmission by means of two different pairs of motor drives, namely with a first pair comprising the first and second motor drives, and with a second pair comprising the third and fourth motor drives.This allows the gearbox to be operated at at least two different load points without any necessary modifications, with the respective driving pair of motor drives operating at the nominal operating point at each load point. This improves the usability of the gearbox while maintaining the symmetry of the gearbox and, consequently, of the entire extrusion device, thus achieving the aforementioned advantages. It is also conceivable for all four motor drives to be used simultaneously to drive the gearbox.

[0016] Alternatively, it can also be provided that the transmission, in addition to the first drive shaft, further comprises a second drive shaft with a second drive spur gear and a third drive shaft with a third drive spur gear, wherein the second drive shaft can be coupled to a second motor drive and the third drive shaft to a third motor drive, wherein the second drive spur gear and the third drive spur gear are each meshingly coupled to the distributor drive spur gear and wherein the drive shafts are arranged at a fourth angle of 120° to one another relative to the distributor axis of rotation. This makes it possible to achieve improved load distribution in the first gear stage. However, the third motor drive does not necessarily have to be identical in construction to the first and second motor drives, and this also applies to the third drive spur gear. This makes it possible to further improve the loading of the bearings of the three drive shafts orthe distributor shaft. Furthermore, it can be provided that the third motor drive can be decoupled if necessary, so that the third motor drive is not driving during normal operation of an extruder using the gear unit and is used, for example, only for starting the extrusion device or when the extrusion device has special performance requirements.

[0017] According to a further development, it is possible for the first output gear and the second output gear to each have flank lines and a cylindrical envelope surface with surface lines, which flank lines are each inclined at a respective angle of inclination relative to the surface lines, so that the distributor output gear can at least partially absorb axial forces of the first output shaft and the second output shaft in the direction of the distributor output gear. The output shafts or the extruder screws are expediently mounted by means of axial bearings in order to be able to absorb the axial forces occurring during the extrusion process in the direction of the gearbox or the drive motors.Since the angled position of the flank lines relative to the surface lines allows axial forces to be transmitted to the distributor shaft via the coupling of the output gears to the distributor output gear, the axial bearings of the output shafts can be designed for lower axial forces. This also allows axial forces resulting from the extrusion process and the nature of the extruder screws to be absorbed by the axial bearings of the distributor shaft. This distributes the load among the transmission components, allowing the components to be designed and procured more economically.

[0018] The invention further relates to an extrusion device comprising a gear mechanism as described above, wherein the first output shaft is designed in sections and in an extrusion region as a first extruder screw and the second output shaft is designed in sections and in the extrusion region as a second extruder screw, wherein the extruder screws are accommodated in an extruder housing without bearings in an end region opposite the first output gear or the second output gear along the rotational axes of the output shafts. As a result, the extruder screws are designed as an integral component of the gear mechanism and vice versa. Thus, no further coupling elements are required for coupling the gear mechanism to the extruder screws of an extruder, so that the number of individual components of the extrusion device according to the invention is reduced compared to conventional extrusion devices.This improves the economic manufacture and operation of the extrusion device, while at the same time improving the load distribution with regard to torque and speed conversion and transmission.

[0019] Also advantageous is a configuration according to which a respective drive shaft is coupled to the respective motor drive by means of a respective coupling element, wherein the extrusion device further comprises a control or regulating device, wherein the control or regulating device is designed to control or regulate the motor drives and the coupling elements. Preferably, the motor drives are synchronous motors, wherein the extruder screws or the torque required for extrusion or the speed required for extrusion can be controlled by means of the control or regulating device through feedback via the gearing by appropriately controlling the motor drives.

[0020] For a better understanding of the invention, it is explained in more detail with reference to the following figures. They show, in highly simplified, schematic representations:

[0021] Fig. 1 shows a possible embodiment of an extrusion device;

[0022] Fig. 2 shows a possible first arrangement of motor drives in an extrusion device;

[0023] Fig. 3 shows a possible second arrangement of motor drives in an extrusion device;

[0024] Fig. 4 shows a possible design of the output gears;

[0025] By way of introduction, it should be noted that in the variously described embodiments, identical parts are provided with identical reference symbols or component designations. The disclosures contained throughout the description can be applied analogously to identical parts with identical reference symbols or component designations. Furthermore, the positional information chosen in the description, such as top, bottom, side, etc., refers to the directly described and illustrated figure, and these positional information must be applied analogously to the new position in the event of a change in position.

[0026] Fig. 1 shows a possible embodiment of an extrusion device 1 in a highly simplified and schematic representation. The extrusion device 1 can be designed as a co-rotating twin-screw extruder. The extrusion device 1 can comprise a gear 2 for driving extruder screws 3 and 4, respectively. The gear 2 can comprise a first output shaft 5 and a second output shaft 6 rotating in the same direction as the first output shaft 5, wherein the first output shaft 5 is designed in sections and in an extrusion region 7 as a first extruder screw 3 and the second output shaft 6 is designed in sections and in the extrusion region 7 as a second extruder screw 4. It can be provided that the extruder screws 3 and 4 are received in an end region 8 in an extruder housing 9 without bearings.

[0027] The transmission 2 can further comprise a first drive shaft 10 with a first drive spur gear 11 coupled thereto. The first drive shaft 10 can be drivably coupled to a first motor drive 12. The transmission 2 can comprise a distributor shaft 13 with a distributor rotation axis 14, wherein a distributor drive spur gear 15 and a distributor output gear 16 can be coupled to the distributor shaft 13. The distributor drive spur gear 15 can further be meshingly coupled to the first drive spur gear 11 of the first drive shaft 10, so that the distributor shaft 13 is rotationally coupled at least by means of the first drive shaft 10 and thus at least to the first motor drive 12.

[0028] The transmission 2 can further comprise a second drive shaft 17 with a second drive spur gear 18 coupled thereto. The second drive shaft 17 can be drivably coupled to a second motor drive 19. The distributor drive spur gear 15 can be meshingly coupled to the second drive spur gear 18 of the second drive shaft 17, so that the distributor shaft 13 is rotationally coupled by means of the first drive shaft 10 and the second drive shaft 17 and thus to the first motor drive 12 and the second motor drive 19. The first drive shaft 10 and the second drive shaft 17 can be arranged relative to one another such that the axes of rotation of the drive shafts 10 and 17 are arranged at a first angle 20 of 180° to one another relative to the distributor rotation axis 14.

[0029] The first output shaft 5 of the transmission 2 can further be coupled to a first output gear 21 and the second output shaft 6 of the transmission 2 can be coupled to a second output gear 22, wherein the first output gear 21 and the second output gear 22 can each be meshingly coupled to the distributor output gear 16, so that the first output shaft 5 and the second output shaft 6 are each drivably coupled by means of the distributor shaft 13.

[0030] It can be provided that a first gear stage 23 comprising the first drive spur gear 11 and the distributor drive spur gear 15 or the second drive spur gear 18 and the distributor drive spur gear 15 has a first gear ratio for low speed. It can also be provided that a second gear stage 24 comprising the distributor drive spur gear 15 and the distributor output gear 16 has a second gear ratio for high speed.

[0031] Furthermore, it can be provided that at least the first output gear 21 is designed as a conical gear or as a beveloid or hypoloid gear. This has the effect that a first axis of rotation 25 of the first output shaft 5 and a second axis of rotation 26 of the second output shaft 6 are arranged in an intersecting axial position with respect to one another or intersecting with an axis crossing angle 27 and in a common first axial plane 28, wherein the axis crossing angle 27 can be selected from a range comprising 0.2° to 10°, in particular 1° to 2°. In particular, it can be advantageous if the first output gear 21 and the second output gear 22 are each designed as a beveloid gear, so that, due to the resulting inclination of the respective first axis of rotation 25 and the second axis of rotation 26 with respect to one another, a symmetrical arrangement of the transmission 2 is possible.

[0032] As a possible further development of the transmission 2, it can also be provided that the distributor output gear 16 is designed as a conical gear or a beveloid gear, wherein the distributor rotational axis 14 of the distributor shaft 13 is aligned parallel to the first axial plane 28. As a result, the distributor shaft 13 can be arranged in the transmission 2 such that the distributor rotational axis 14 is aligned parallel to the first axial plane 28. This improves the symmetry or parallelism of the transmission 2, which results in a more even load distribution and, in particular, a more even loading of the bearings of all shafts 5, 6, 13 and 10, 17.

[0033] Fig. 2 and Fig. 3 show a first possible and possibly independent arrangement and a second possible and possibly independent arrangement of motor drives in an extrusion device 1 or of drive shafts with coupled drive spur gears of the gear 2 of an extrusion device 1, wherein the same reference numerals or component designations as in the preceding Fig. 1 are used for the same parts. To avoid unnecessary repetition, reference is made to the detailed description in the preceding Fig. 1.

[0034] As shown in Fig. 2, it can be provided that the transmission 2 further comprises a third drive shaft 30 with a third drive spur gear 31 and a fourth drive shaft 32 with a fourth drive spur gear 33, wherein the third drive shaft 30 can be coupled to a third motor drive 34 and the fourth drive shaft 32 to a fourth motor drive 35, wherein the third drive spur gear 31 and the fourth drive spur gear 33 are each meshingly coupled to the distributor drive spur gear 15 and wherein the third drive shaft 30 and the fourth drive shaft 32 are arranged relative to the distributor rotation axis 14 at a second angle 36 of 180° to each other and respectively relative to the first drive shaft 10 and the second drive shaft 17 relative to the distributor rotation axis 14 at a third angle 37 of 90°. As shown in Fig. 3, alternatively to previously described embodiments of gearbox 2 orthe extrusion device 1 can be provided such that the gear 2, in addition to the first drive shaft 10, also comprises the second drive shaft 17 with the second drive spur gear 18 and the third drive shaft 30 with the third drive spur gear 31, wherein the second drive shaft 17 can be coupled to the second motor drive 19 and the third drive shaft 30 can be coupled to the third motor drive 34, wherein the second drive spur gear 18 and the third drive spur gear 31 are each meshingly coupled to the distributor drive spur gear 15 and wherein the drive shafts 10, 17, 30 are each arranged at a fourth angle 38 of 120° to one another relative to the distributor rotation axis 14.

[0035] With reference to all possible embodiments of the transmission 2 or the extrusion device 1, it can further be provided that a respective drive shaft 10 or 17, 30, 32 is coupled to the respective motor drive 12 or 19, 34, 35 by means of a respective coupling member (29), wherein the extrusion device 1 further comprises a control or regulation device, wherein the control or regulation device (not shown) is designed to control or regulate the motor drives 12 or 19, 34, 35 and the coupling members 29. Preferably, the motor drives 12 or 19, 34, 35 are synchronous motors, wherein the extruder screws 3, 4 or the torque required for the extrusion or the speed required for the extrusion can be controlled by means of the control or regulating device by feedback via the gear 2 by corresponding control of the motor drives 12 or 19, 34, 35.

[0036] 1 to 3 are used for identical parts. To avoid unnecessary repetition, reference is made to the detailed description in the previous FIGS. 1 to 3. A respective output gear 21 or 22 can have an imaginary cylindrical envelope surface 39, wherein such an envelope surface 39 is naturally constructed or formed from individual surface lines 40. A respective output gear 21 or 22 can have flank lines 41, which respective flank lines 41 define the course of the respective tooth flanks of the output gear 21 or 22 when the flanks intersect with the respective envelope surface 39. It can be provided that the flank lines 41 of a respective output gear 21 or22 are inclined at an angle 42 relative to the respective surface lines 40. As a result, axial forces which are introduced into the output shaft 5 or 6 as a result of the extrusion process can be at least partially transmitted to the distributor output gear 16 by means of the flank lines 41 arranged obliquely relative to the surface lines 40. As a result, the axial bearings of the output shafts 5, 6 experience reduced axial forces, whereby the axial bearings of the distributor shaft 13 must subsequently also absorb a portion of the axial forces caused by the extrusion process. Overall, the axial bearings of the gearbox 2 can thus be dimensioned smaller, since the axial forces are distributed among the individual components of the gearbox 2.

[0037] For the sake of clarity, it should finally be pointed out that, in order to better understand the structure, some elements have been shown out of scale and / or enlarged and / or reduced in size.

[0038] Reference symbol list

[0039] Extrusion device 32 Fourth drive shaft

[0040] Gear 33 Fourth drive spur gear

[0041] First extruder screw 34 Third motor drive

[0042] Second extruder screw 35 Fourth motor drive

[0043] First output shaft 36 Second angle

[0044] Second output shaft 37 Third angle

[0045] Extrusion area 38 Fourth angle

[0046] End area 39 Envelope area

[0047] Extruder housing 40 shell lines

[0048] First drive shaft 41 flank lines

[0049] First drive spur gear 42 inclination angle

[0050] First motor drive

[0051] distributor shaft

[0052] Distributor rotation axis

[0053] Distributor drive - spur gear

[0054] Distributor output gear

[0055] Second drive shaft

[0056] Second drive spur gear

[0057] Motor drive

[0058] First angle

[0059] First output gear

[0060] Second output gear

[0061] First gear stage

[0062] Second gear stage

[0063] First axis of rotation

[0064] Second axis of rotation

[0065] Axis crossing angle

[0066] First axis level

[0067] Coupling element

[0068] Third drive shaft

[0069] Third drive spur gear

Claims

Patent claims 1. Gear (2) for driving extruder screws (3, 4) of an extrusion device (1), in particular a co-rotating twin-screw extruder, the gear (2) comprising - a first drive shaft (10) with a first drive spur gear (11), wherein the first drive shaft (10) can be coupled to a first motor drive (12), - a distributor shaft (13) with a distributor rotation axis (14), a distributor drive spur gear (15) and a distributor output gear (16), wherein the distributor drive spur gear (15) is meshingly coupled to the first drive spur gear (11) of the first drive shaft (10), so that the distributor shaft (13) can be driven by means of the first drive shaft (10), - a first output shaft (5) with a first output gear (21) and a second output shaft (6) rotating in the same direction as the first output shaft (5) with a second output gear (22), wherein the first output gear (21) and the second output gear (22) are each meshingly coupled to the distributor output gear (16), so that the first output shaft (5) and the second output shaft (6) are each drivably coupled by means of the distributor shaft (13), characterized in that the first output gear (21) is designed as a beveloid or hypoloid gear, and in that a first axis of rotation (25) of the first output shaft (5) and a second axis of rotation (26) of the second output shaft (6) are in an intersecting axial position or intersecting with an axis cross angle (27) and are arranged in a common first axial plane (28), wherein the axis crossing angle (27) is selected from a range comprising 0.2° to 10°, in particular 1° to 2°.

2. Gearbox (2) according to claim 1, characterized in that the second output gear (22) is designed as a beveloid gear.

3. Transmission (2) according to one of the preceding claims, characterized in that a first gear stage (23) comprising the first drive spur gear (11) and the distributor drive spur gear (15) has a first gear ratio in the low range.

4. Transmission (2) according to claim 3, characterized in that a second gear stage (24) comprising the distributor drive gear (15) and the distributor output gear (16) has a second gear ratio in the fast.

5. Gearbox (2) according to one of claims 2 to 4, characterized in that the distributor output gear (16) is designed as a conical gear or as a beveloid gear, so that the distributor rotation axis (14) of the distributor shaft (13) is aligned parallel to the first axis plane (28).

6. Gearbox (2) according to one of the preceding claims, characterized in that the gearbox (2) further comprises a second drive shaft (17) with a second drive spur gear (18), wherein the second drive shaft (17) can be coupled to a second motor drive (19), wherein the second drive spur gear (18) is meshingly coupled to the distributor drive spur gear (15) and wherein the first drive shaft (10) and the second drive shaft (17) are arranged at a first angle (20) of 180° to one another relative to the distributor rotation axis (14).

7. Gearbox (2) according to claim 5, characterized in that the gearbox (2) further comprises a third drive shaft (30) with a third drive spur gear (31) and a fourth drive shaft (32) with a fourth drive spur gear (33), wherein the third drive shaft (30) is coupled to a third motor drive (34) and the fourth drive shaft (32) is coupled to a fourth motor drive (35), wherein the third drive spur gear (31) and the fourth drive spur gear (33) are each meshingly coupled to the distributor drive spur gear (15), and wherein the third drive shaft (30) and the fourth drive shaft (32) are arranged relative to the distributor rotational axis (14) at a second angle (36) of 180° to one another and respectively relative to the first drive shaft (10) and the second drive shaft (17) relative to the distributor rotational axis (14) at a third angle (37) of are arranged at 90°.

8. Gearbox (2) according to one of claims 1 to 5, characterized in that the gearbox (2) further comprises a second drive shaft (17) with a second drive spur gear (18) and a third drive shaft (30) with a third drive spur gear (31), wherein the second drive shaft (17) is connected to a second motor drive (19) and the third drive shaft (30) can be coupled to a third motor drive (34), wherein the second drive spur gear (18) and the third drive spur gear (31) are each meshingly coupled to the distributor drive spur gear (15) and wherein the drive shafts (10, 17, 30) are each arranged at a fourth angle (38) of 120° to one another relative to the distributor rotation axis (14).

9. Gearbox (2) according to one of the preceding claims, characterized in that the first output gear (21) and the second output gear (22) each have flank lines (41) and each have a cylindrical enveloping surface (39) with surface lines (40), which flank lines (41) are each inclined relative to the surface lines (40) at a respective angle of inclination (42), so that by means of the distributor output gear (16) at least partial axial forces of the first output shaft (5) and the second output shaft (6) in the direction of the distributor output gear (16) can be absorbed.

10. Extrusion device (1) comprising a gear (2) according to one of claims 1 to 9, characterized in that the first output shaft (5) is designed in sections and in an extrusion region (7) as a first extruder screw (3) and the second output shaft (6) is designed in sections and in the extrusion region (7) as a second extruder screw (4), wherein the extruder screws (3, 4) are accommodated in an extruder housing (9) without bearings in an end region (8) opposite the first output gear (21) or the second output gear (22) along the axes of rotation (25, 26).

11. Extrusion device (1) according to claim 10, characterized in that a respective drive shaft (10 or 17, 30, 32) is coupled to the respective motor drive (12 or 19, 34, 35) by means of a respective coupling member (29), wherein the extrusion device (1) further comprises a control or regulating device, wherein the control or regulating device is designed to control or regulating the motor drives (12 or 19, 34, 35) and the coupling members (29).

Images