JP6794236B2 - Drive device for twin-screw extruder - Google Patents

Description

The present invention relates to a drive device for a twin-screw extruder.

FIG. 1 is a diagram showing a structure of a drive device for a twin-screw extruder known in principle from Patent Document 1. Of the two-screw extruders, screw shafts 2 and 4 arranged parallel to each other are shown, and both screw shafts are driven in the same rotation direction 6. The drive device has a planetary gear arrangement 8 and a power split transmission device 10 rearranged in the planetary gear arrangement 8. The planetary gear arrangement 8 preferably has two planetary gear stages 12 and 14 arranged side by side in the axial direction. The main electric motor 16 preferably has a torque safety clutch 18 assigned to the shaft 17, a one-stage spur gear having both gears 19 and 20, and a gear joint 21 in this order of the first planetary gear stage. It is drive-coupled to the sun gear 22. According to the modified embodiment, the motor 16 is arranged axially with respect to the sun gear 22 as shown by the broken line in FIG. 1 and also indicated by the reference numeral 16', and the one-stage spur gears 19 and 20 are arranged. It can be drive-coupled to the sun gear 22 without. The sun gear 22 can be blocked by a brake 24 located at the outer free end of the shaft 25 of the second gear. Alternatively, the motor 16'can also be coupled to the sun gear 22 via additional planetary gear stages. The additional electric motor 30 is mounted on the outer teeth of the rotatably arranged internal gear 40 of the first planetary gear 12 via a torque safety clutch 32 and a one-stage spur gear with gears 34, 35 and 36. Can be drive-coupled to row 38, the additional electric motor 30 can be steplessly adjustable with respect to its output and thereby its output rotation speed and can have a smaller power capacity than the main motor 16. ..

A rotatably arranged planetary carrier 42 of the first planetary gear stage 12 supports the planetary gear 43, which meshes with the outer dentition of the sun gear 22 on the one hand and inside the internal gear 40 on the other. It meshes with the dentition 44. The planetary carrier 42 of the first planetary gear stage 12 is coupled to the sun gear 50 of the second planetary gear stage 14 arranged adjacent to the planet carrier 42 in the axial direction via a gear joint 46. The second planetary gear stage 14 has an internal gear 52 arranged so as not to rotate and a planetary carrier 54 arranged so as to be rotatable. The planetary carrier 54 supports the planetary gear 56, and the planetary gear 56 is supported by the planetary gear 56. On the one hand, it meshes with the outer dentition of the sun gear 50, and on the other hand, it meshes with the inner dentition of the internal gear 52. The internal gear 40 of the first planetary gear stage 12 can be blocked by a brake 33, that is, a reverse rotation prevention device, which is preferably between the internal gear 40 and the additional motor 30 in the drive train. , Arranged at the outer free end of the shaft 37 of the first gear 34 driven by the adder motor 30. The planetary gear output shaft 60 is arranged axially with respect to the sun gears and planetary carriers of both planetary gear stages 12 and 14, and also axially with respect to the screw shaft 2. The planetary gear output shaft 60 can be configured from a plurality of parts, or preferably integrally, and at its drive end, it is stationary on one screw shaft 2 via a joint 86, in a rotational direction, and in an axial direction. Is combined with. The planetary gear output shaft 60 can also be driven directly by the first planetary gear stage 12. In this case, the planetary gear arrangement 8 is formed by only one planetary gear stage. The power split transmission device 10 has at least two branch shafts 62 and 64 arranged parallel to the planetary gear output shaft 60, near the planetary gear arrangement 8 of these branch shafts 62 and 64. The positioned end compartments are connected to one gear 63 or 65 in a stationary orientation, respectively, and these gears 63, 65 have the same diameter and the same number of teeth, the oblique tooth row 66 or The central gear 70 is provided with 67 and meshes with the corresponding oblique tooth row 68 of the central gear 70, and the central gear 70 is arranged on the planetary gear output shaft 60 in a stationary direction of rotation. The central gear 70, together with the gears 63 and 65, forms an output branch portion from the planetary gear output shaft 60 to the branch shafts 62 and 64.

The end compartments of the branch shafts 62 and 64, farther away from the planetary gear arrangement 8, are separately coupled to the gears 73 and 75 in a rotationally stationary manner, with the gears 73 and 75 having the same diameter. However, preferably, the outer gear rims 76 and 77 having the same number of oblique teeth are separately provided. These gears 73 and 75 mesh with the gear 80, which has a corresponding outer dentition 78 with oblique teeth and is coupled to the second output shaft 84 in a rotational orientation. .. The gears 73, 75 and 80 form a total output portion from both branch shafts 62 and 64 to the second output shaft 84 of the drive device at the distal ends of the branch shafts 62 and 64. The second output shaft 84 is arranged parallel to the planetary gear output shaft 60 and at an axial offset with respect to the second screw shaft 4, and at an end farther away from the second planetary gear stage 14. It is coupled to the second screw shaft 4 in a rotational direction and in an axial position via a joint 86.

In order to illustrate both branch shafts 62 and 64 and their gears in FIG. 1, they are shown in a folded form in a common plane in FIG. 1, but in reality they are planetary gear output shafts. It is not located in a common plane with 60, which is indicated by the arrow 82 in FIG. 1 and in fact correctly in FIG. 2 of Patent Document 1, in which the gears 73 and 75 are branched. This is to engage the common gear 80 at the distal ends of the shafts 62 and 64. As a result, the rotation direction 6 of the screw shafts 2 and 4 also corresponds to the rotation direction 6 of both output shafts 60 and 84.

According to Patent Document 1, the shaft bearing 101 receives a force in the radial direction and, if necessary, also undertakes an axial guidance function, and is implemented as a sliding bearing. The sliding bearing of the slowly rotating shaft can be hydrostatically supported. However, this does not apply to the bearing of the drive device, which absorbs the axial thrust force as in Patent Document 1.

The axial thrust force of one screw shaft 2 is transmitted to the axial bearing 88 via the planetary gear output shaft 60, and is transmitted from the axial bearing 88 to the gear housing portion 90. The axial bearing 88 exists between the drive gear 70 of the output branch portions 63, 65, and 70 and the planet carrier 54 of the second planetary gear stage 14. The axial thrust force of the second screw shaft 4 is transmitted to the second axial bearing 92 via the second output shaft 84, and is also transmitted from the second axial bearing 92 to the gear housing portion 94. The second axial bearing 92 is located next to the shafts 60, 62 and 64 and is intermediate between the output branch gears 63, 65 and 70 and the output total output gears 73, 75 and 80 of the branch shafts 62 and 64. Exists in space.

The two axial bearings 88 and 92 are also called axial main bearings, and according to Patent Document 1, they are implemented as conventional axial rolling bearings or axial cylindrical roller bearings.

German Patent Application Publication No. 102004051306

In view of the above, an object of the present invention is to provide a new drive device for a twin-screw extruder having an improved output shaft bearing.

This problem is solved by the drive device for a twin-screw extruder according to claim 1. According to the present invention, the axial main bearing of the output shaft is configured as a hydrostatically supported axial plain bearing.

For the first time in the drive device for a twin-screw extruder of the present invention, the axial main bearings of both output shafts are implemented as hydrostatically supported axial plain bearings. As a result, on the one hand, the overall length of the axial main bearing can be surely shortened, and the life of the axial main bearing can be extended.

According to a preferred evolution, the hydraulically supported axial plain bearings have multiple plain bearing planes, each of which has a shaft-side thrust washer and a stator-side thrust washer. The sliding surfaces are hydrostatically separated via a lubricant, and the thrust washer on the stator side and / or the thrust washer on the shaft side each has at least one lubricating pocket. Provided, the lubricant can be supplied to the lubrication pocket via the hydraulic system. This makes it possible to implement the axial main bearing particularly preferably. Through the lubrication pockets, the lubricant can be fed into each axial main bearing in a defined form, thereby ensuring hydrostatically dynamic each axial main bearing configured as an axial plain bearing. Can be supported by.

Desirably, each plain bearing plane and / or each lubrication pocket can be individually supplied with a defined amount of lubricant. This ensures that the amount of lubricant is evenly distributed on the various plain bearing planes, thereby ensuring a uniform load on the plain bearing planes, and thus uniform wear. It is possible to prevent some of the plain bearing planes from being worn prematurely, which can further extend the life of the axial main bearing.

A desirable development of the present invention can be understood from the dependent claims and the following description. Examples of the present invention will be described with reference to the drawings, but the present invention is not limited thereto.

It is a figure of the drive device for a twin-screw extruder known from the prior art. It is a long-axis sectional view of the axial slide bearing of the drive device of this invention. It is sectional drawing which cut | cut the axial plain bearing of FIG. 2 in the cutting direction III-III.

The present invention relates to a drive device for a twin-screw extruder. The structure of the drive device for a twin-screw extruder is well known to those skilled in the art, and is also known from Patent Document 1. The drive unit for a twin-screw extruder has at least one motor 16, 16', 30, and each motor operates on a drive shaft or an input shaft 17, 25, 37. The drive device of the twin-screw extruder further has a plurality of output shafts 60 and 84, and the screw shafts 2 and 4 of the twin-screw extruder are connected to the output shafts 60 and 84, respectively.

A planetary gear arrangement 8 having at least one planetary gear stage and a gear configured as a power split transmission device 10 between one or each drive shaft, that is, input shafts 17, 25, 37 and output shafts 60, 84. Arrangement and are connected.

The present invention relates to the details of a drive device for a twin-screw extruder, and the details can reliably support both output shafts 60 and 84 of the drive device in the axial direction.

As already mentioned in connection with FIG. 1, each of the output shafts 60, 84 of the drive unit is supported by the radial bearing 101 on the one hand and separately by the axial bearings 88 and 92 on the other hand. , Axial bearings 88 and 92 are also referred to as axial main bearings.

In the present invention, the axial main bearings 88 and 92 of the output shafts 60 and 84 are implemented as hydrostatically supported axial plain bearings. This allows, on the one hand, to reduce the overall length of the axial main bearing and, on the other hand, to extend its life.

Each of the axial main bearings 88 and 92 has one or more plain bearing planes 91, and in the axial main bearing shown in FIG. 2, four plain bearing planes 91 are arranged in the front-rear direction in the axial direction. positioned. Each of the slide bearing flat surfaces 91 has a thrust washer 93 on the shaft side and a thrust washer 95 on the stator side or the housing side. During operation, an axial thrust force is applied, so that in the region of each slide bearing plane 91, the assembled thrust washers 93 and 95 are pressed in the direction toward the sliding surfaces facing each other.

As described above, the axial main bearings 88 and 92 are implemented as hydrostatically supported axial slide bearings, and the shaft side thrust washer 93 and the stator side thrust washer 95 of each slide bearing flat surface 91 are used. A lubricant can be fed between the thrust washers 93 and 95 in order to hydrostatically separate the sliding surfaces facing each other.

In the examples of the axial main bearings 88 and 92 shown in FIGS. 2 and 3, at least one lubrication pocket 96 is provided in each of the stator side thrust washer 95, and each of the lubrication pockets 96 is lubricated. The agent can be supplied, thereby ensuring the hydrostatic separation of the slide surfaces in the region of the respective plain bearing plane 91, thereby ensuring the hydrostatic support of the respective axial main bearings 88, 92. Being. At that time, a lubricant, which is preferably a lubricating oil, can be supplied to the lubricating pocket 96 from a hydraulic system (not shown).

Alternatively or additionally, the shaft-side thrust washer 92 may also be provided with such a lubrication pocket, unlike the illustrated embodiment. At this time, the lubrication pockets 96 are provided on the respective thrust washers so that the respective lubrication pockets can lubricate the cooperating sliding surfaces of the respective slide bearing planes 91 with high reliability.

The axial main bearings 88 and 92 of the drive device of the present invention have one or more plain bearing planes 91. The axial force to be supported is introduced into the axial main bearings 88 and 92 by the output shafts 60 and 84, respectively. This axial thrust force is transmitted to the thrust washer 95 on the stator side or the housing side via the shaft side thrust washer 93, whereby the axial thrust force is finally transmitted to the respective housings 90 and 94, respectively. Adjacent or facing sliding surfaces are lubricated with lubricating oil, preferably in each region of the plain bearing plane 91, whereby the sliding surfaces are hydrostatically separated from each other. For that purpose, in the region of each plain bearing plane 91, at least one of the thrust washers 93 and 95 is provided with at least one lubricating pocket 96 on at least one of the cooperating sliding surfaces, and lubricating oil is fed into the lubricating pocket 96. be able to. At the corresponding lubricating oil pressure, the axial thrust force is supported by the lubricating oil pressure, whereby the sliding surfaces of the cooperating thrust washers 93 and 95 of each plain bearing surface 91 are hydrostatically separated from each other. It is decided.

At that time, the lubricating oil can be individually supplied to the sliding bearing flat surface 91, that is, the lubricating pocket 96 of the sliding bearing flat surface 91, whereby the lubricating oil can be uniformly distributed in the region of the sliding bearing flat surface 91. .. The amount of lubricating oil to be supplied to the individual plain bearing planes 91, on the one hand, is such that, on the one hand, a sufficiently large lubricating film thickness is adjusted in the region of each plain bearing plane 91, on the other hand, at intervals of thrust washers 93, 95. The quantity is determined so that differences in manufacturing origin can be compensated.

It is desirable that the lubrication pocket 96 be provided on the stator side thrust washer 95, because the oil supply of the lubrication pocket 96 can be performed in the stator side system.

2 screw shaft, 4 screw shaft, 6 rotation direction, 8 planetary gear arrangement, 10 power split transmission device, 12 planetary gear stage, 14 planetary gear stage, 16 motor, 16'motor, 17 input shaft, 18 torque safety clutch, 19 Gears, 20 gears, 21 gear joints, 22 sun gears, 24 brakes, 25 input shafts, 30 additional electric motors, 32 torque safety clutches, 33 brakes, 34 gears, 35 gears, 36 gears, 37 input shafts, 38 outer dentition , 40 internal gear, 42 planetary carrier, 43 planetary gear, 44 inner gear row, 46 gear joint, 50 sun gear, 52 internal gear, 54 planetary carrier, 56 planetary gear, 60 output shaft, 62 branch shaft, 63 gear, 64 Branch shaft, 65 gears, 66 oblique gears, 67 oblique gears, 68 oblique gears, 70 central gears, 73 gears, 75 gears, 76 outer gear rims, 77 outer gear rims, 78 outer gears, 80 Gears, 82 Arrows, 84 Output Shafts, 86 Joints, 88 Axial Main Bearings, 90 Gear Housings, 91 Sliding Bearing Planes, 92 Axial Main Bearings, 93 Thrust Washers, 94 Gear Housings, 95 Thrust Washers, 96 Lubricating Pockets , 101 radial gear

Claims (4)

A drive device for a twin-screw extruder
With at least one input shaft (17, 25) to which the motor (16, 16') can be connected,
The first output shaft (60) to which the first screw shaft of the two-screw extruder can be connected and
A second output shaft (84) that can be connected to the second screw shaft of the twin-screw extruder.
Planetary gear arrangement (8) and
Power split transmission device (10) and
Is equipped with
The first output shaft (60 ) and the second output shaft (84) are, on the one hand, in the radial bearing (101) and on the other hand, in the axial main bearings (88, 92) that receive the axial thrust force. In the drive unit supported by
The axial main bearings (88, 92) of the first output shaft (60 ) and the second output shaft (84) are configured as hydrostatically supported axial plain bearings .
The hydrostatically supported axial plain bearing has one or more plain bearing planes (91).
Each of the slide bearing planes (91) has a shaft side thrust washer (93) and a stator side thrust washer (95).
The sliding surfaces of the shaft-side thrust washer (93) and the stator-side thrust washer (95) are hydrostatically separated via a lubricant.
The drive device is characterized in that each of the shaft-side thrust washers (93) is provided with at least one lubricating pocket, and the lubricating pocket can be supplied with a lubricant via a hydraulic system . Each of the stator-side thrust washers (95) is provided with at least one lubricating pocket (96), and the lubricating pocket (96) can be supplied with a lubricant via a hydraulic system. The drive device according to claim 1 . The drive device according to claim 1 or 2 , wherein a predetermined amount of lubricant can be individually supplied to each slide bearing plane (91). The drive device according to any one of claims 1 to 3 , wherein a predetermined amount of lubricant can be individually supplied to each lubrication pocket (96).

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