DE102015016065A1 - Drive device for a twin-screw extruder - Google Patents

Abstract

Drive device for a twin-screw extruder, with at least one input shaft (17, 25) to which a motor (16, 16 ') can be coupled, with a first output shaft (60), to which a first screw shaft of the twin-screw extruder can be coupled, with a second output shaft (84), to which a second worm shaft of the twin-screw extruder is couplable, with a planetary gear arrangement (8) and with a power dividing gear (10), wherein the output shafts (60, 84) on the one hand in radial bearings (101) and on the other hand in axial main bearings (88, 92 ), which serve to receive axial thrust forces, are mounted, and wherein the axial main bearings (88, 92) of the output shafts (60, 84) are designed as hydrostatically supported thrust bearings.

Description

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

1 shows that from the DE 10 2004 051 306 B4 basically known construction of a drive device for a twin-screw extruder. From the twin-screw extruder are arranged parallel to each other screw shafts 2 and 4 represented, which both in the same direction of rotation 6 are driven. The drive device includes a planetary gear arrangement 8th and a subordinate power division transmission 10 , The planetary gear arrangement 8th preferably includes two axially successively arranged planetary gear stages 12 and 14 , An electric main engine 16 is preferably via a torque safety clutch 18 that a wave 17 is assigned, a single-stage spur gear with the two gears 19 and 20 and a gear coupling 21 in this order, with a sun wheel 22 the first planetary gear stage 12 drivingly connected. According to an alternative embodiment, the engine 16 , as in 1 shown in dashed lines and with the reference number 16 ' provided, axially to the sun gear 22 arranged and with him without the single-stage helical gear 19 . 20 be drivingly connected. The sun wheel 22 can through a brake 24 be blocked, which at the free outer end of a shaft 25 of the second gear is arranged. The motor 16 ' could alternatively also have another planetary gear with the sun gear 22 be connected. An electric auxiliary motor 30 , which is infinitely variable in terms of its performance and thus also with respect to its output speed and a smaller power capacity than the main engine 16 can have, via a torque-safety clutch 32 and a single-stage spur gear with gears 34 . 35 and 36 , with external teeth 38 a rotatably arranged ring gear 40 the first planetary gear stage 12 be drivingly connected.

A rotatably arranged planet carrier 42 the first planetary gear stage 12 carries planet wheels 43 , on the one hand with an external toothing of the sun gear 22 and on the other hand with an internal toothing 44 of the ring gear 40 are engaged. The planet carrier 42 the first planetary gear stage 12 is via a gear coupling 46 with a sun gear arranged axially next to it 50 the second planetary gear stage 14 connected. The second planetary gear stage 14 has a non-rotatably mounted ring gear 52 and a rotatably mounted planet carrier 54 , which planetary gears 56 carries, on the one hand with an external toothing of the sun wheel 50 and on the other hand with an internal toothing of the ring gear 52 are engaged. The ring gear 40 the first planetary gear stage 12 is through a brake 33 or a backstop lockable in the drive train between it and the auxiliary engine 30 is arranged, preferably at the free outer end of a shaft 37 the first of the auxiliary engine 30 driven gear 34 , A planetary gear output shaft 60 is axial to the sun gears and planetary carriers of the two planetary gear stages 12 and 14 and also axially to a worm shaft 2 arranged. This planetary gear output shaft 60 may be formed in several parts or preferably in one piece and is at its drive end via a coupling 62 rotatably and axially fixed with a worm shaft 2 connected. The planetary gear output shaft 60 can also directly through the first planetary gear stage 12 are driven. The planetary gear arrangement 8th then only consists of a planetary gear stage. The power dividing gearbox 10 contains at least two to the planetary gear output shaft 60 parallel branch waves 62 and 64 , of which the planetary gear arrangement 8th nearby end sections each with a gear 63 respectively. 65 are rotatably connected, which have the same diameter and with a helical toothing 66 respectively. 67 are provided with the same number of teeth and with a corresponding helical toothing 68 a central gear 70 are engaged, which rotatably on the planetary gear output shaft 60 is arranged. The central gear 70 forms with the gears 63 and 65 a power split from the planetary gear output shaft 60 on the branch waves 62 and 64 ,

The from the planetary gear arrangement 8th further away end portions of the branch shafts 62 and 64 are ever with a gear 73 respectively. 75 rotatably connected, which ever equal diameter and preferably a helical external ring gear 76 respectively. 77 having an equal number of teeth. These gears 73 and 75 are with a gear 80 in engagement, which has a corresponding helical external toothing 78 has and with a second output shaft 84 rotatably connected. The gears 73 . 75 and 80 form at the far end of the branch waves 62 and 64 a power summation from the two branch waves 62 and 64 on the second output shaft 84 the drive device. This second output shaft 84 is parallel to the planetary gear output shaft 60 and axially offset to the second worm shaft 4 arranged and at its from the second planetary gear stage 14 further away via a coupling 86 with the second worm shaft 4 rotatably and axially connected.

So that both branch waves 62 and 64 and her gears in 1 are apparent, they are shown folded into a common plane, while in reality they are not in a common plane with the planetary gear output shaft 60 lie, so that both gears 73 and 75 at the far end of the branch shaft 62 and 64 with the common gear 80 are engaged, as in 1 through an arrow 82 indicated and in 2 the practice is shown correctly. This corresponds to the direction of rotation 6 the worm shafts 2 and 4 also the direction of rotation 6 the two output shafts 60 and 84 ,

After DE 10 2004 051 306 B4 are shaft bearings 101 , which absorb radial forces and possibly take an axial leadership function, designed as a sliding bearing. Bearings of slow running shafts can be hydrostatically supported. However, this is true after the DE 10 2004 051 306 B4 not for the bearings of the drive device that absorb axial thrust forces.

Axial thrust forces of a worm shaft 2 be about the planetary gear output shaft 60 on a thrust bearing 88 and from this to a transmission housing part 90 transfer. The thrust bearing 88 is located between the driving gear 70 the power split 63 . 65 . 70 and the planet carrier 54 the second planetary gear stage 14 , Axial thrust forces of the second worm shaft 4 be over the second output shaft 84 on a second thrust bearing 92 and of this also on a gear housing part 94 transfer. The second thrust bearing 92 is located next to the waves 60 . 62 and 64 in a space between the gears 63 . 65 . 70 the power split and the gears 73 . 75 . 80 the power summation of the branch waves 62 and 64 ,

The two thrust bearings 88 . 92 are also referred to as Axialhauptlager and are after the DE 10 2004 051 306 B4 designed as conventional axial roller bearings and axial cylindrical roller bearings.

On this basis, the present invention seeks to provide a novel drive device for a twin-screw extruder with improved storage of the output shafts.

This object is achieved by a drive device for a twin-screw extruder according to claim 1. According to the invention, the axial main bearings of the output shafts are designed as hydrostatically supported axial plain bearings.

In the drive device for a twin-screw extruder according to the invention, the axial main bearings of the two output shafts are designed as hydrostatically supported axial plain bearings for the first time. Hereby, on the one hand, a shorter overall length of the Axialhauptlager be guaranteed, also the life of the same can be increased.

According to an advantageous development, the hydrostatically supported thrust bearings on several slide bearing layers, each of the slide bearing layers comprises a shaft-side pressure plate and a stator pressure plate whose sliding surfaces are separated hydrostatically via a lubricant, and wherein in the stator-side pressure plates and / or in the shaft-side pressure plates respectively at least a lubricating pocket are introduced, to which the lubricant can be supplied via a hydraulic system. This makes a particularly advantageous embodiment of the axial main bearing possible. About the lubrication pockets, the lubricant can be defined in the respective axial main bearing introduced so as to ensure the hydrostatic support of the respective formed as a thrust bearing Axiallagerlagers.

Preferably, each sliding bearing plane and / or each lubrication pocket, a defined amount of lubricant can be fed individually. In this way, a uniform distribution of the amount of lubricant can be ensured on the various bearing layers, whereby a uniform load and thus a uniform wear of the bearing layers can be guaranteed. Premature wear of some of the plain bearing levels can be prevented, which can further increase the life of the axial main bearings.

Preferred embodiments of the invention will become apparent from the dependent claims and the description below. Embodiments of the invention will be described, without being limited thereto, with reference to the drawings. Showing:

1 a drive device known from the prior art for a twin-screw extruder;

2 an axial sliding bearing of a drive device according to the invention in longitudinal section; and

3 a cross section through the thrust bearing of the 2 in cutting direction III-III.

The invention relates to a drive device for a twin-screw extruder. The structure of a drive device for a twin-screw extruder is familiar to those skilled in the art and from the DE 10 2004 051 306 B4 known. Thus, a drive device for a twin-screw extruder comprises at least one motor 16 . 16 ' . 30 wherein each motor on a drive shaft or input shaft 17 . 25 . 37 attacks. Furthermore, the drive device of a twin-screw extruder comprises a plurality of output shafts 60 . 84 , to each output shaft 60 . 84 a worm shaft 2 . 4 coupled to the twin-screw extruder.

Between the or each drive shaft or input shaft 17 . 25 . 37 and the output waves 60 . 84 is a planetary gear arrangement 8th with at least one planetary gear and one as a power dividing gear 10 switched gear arrangement switched.

The present invention relates to such details of a drive device for a twin-screw extruder, with which an advantageous axial support of the two output shafts 60 . 84 the drive device can be guaranteed.

As already related to 1 executed, is each of the output shafts 60 . 84 the drive device on the one hand in radial bearings 101 and on the other hand in thrust bearings 88 respectively. 92 supported, wherein the thrust bearing 88 . 92 Also referred to as Axialhauptlager.

For the purposes of the present invention, the Axialhauptlager 88 . 92 the output shafts 60 . 84 designed as hydrostatically supported thrust bearings. As a result, on the one hand reduces the length of the Axialhauptlager and on the other hand their life can be increased.

Each of the axial bearing 88 . 92 has one or more plain bearing levels 91 , in which in 2 axial bearing shown four bearing layers 91 are positioned one behind the other in the axial direction. Each of the plain bearing levels 91 includes a shaft-side thrust washer 93 and a stator-side or housing-side pressure disk 95 , In operation, due to acting axial thrust forces, in the area of each plain bearing plane 91 the associated pressure discs 93 . 95 pressed in the direction of the opposite sliding surfaces.

As already stated, the axial main bearings 88 . 92 designed as a hydrostatically supported thrust bearing, wherein between the shaft-side thrust washer 93 and the stator side thrust washer 95 each slide bearing plane 91 a lubricant can be introduced to the opposing sliding surfaces of the associated pressure discs 93 . 95 hydrostatically separated from each other.

In the in 2 and 3 shown embodiment of the axial bearing 88 . 92 are in the stator-side pressure plates 95 at least one lubrication pocket 96 introduced, with each of the lubrication pockets 96 can be supplied with lubricant to the hydrostatic separation of the sliding surfaces in the region of the respective plain bearing plane 91 and thus the hydrostatic support of the respective axial main bearing 88 . 92 to ensure. The lubricant, which is preferably lubricating oil, is the lubrication pockets of a hydraulic system, not shown 96 fed.

In contrast to the embodiment shown may alternatively or additionally also in the shaft side pressure discs 92 be introduced such a lubricating pocket. The lubrication pockets 96 are in such a manner introduced into the respective thrust washer, that the respective lubricating pocket the cooperating sliding surfaces of the respective plain bearing plane 91 can lubricate reliably.

The axial main bearings 88 . 92 the drive device according to the invention therefore have one or more plain bearing levels 91 , To be supported axial forces are through the respective output shaft 60 . 84 in the respective axial main bearing 88 . 92 initiated. About the shaft-side pressure discs 93 These axial thrust forces are applied to the stator-side or housing-side pressure disks 95 transferred so as ultimately the axial thrust forces into the respective housing 90 . 94 transferred to. Adjacent sliding surfaces are in the region of each of the plain bearing planes 91 lubricated, preferably with lubricating oil so as to hydrostatically separate the sliding surfaces from each other. This is in the range of each plain bearing level 91 in at least one of the pressure discs 93 . 95 at least one lubrication pocket on at least one of the cooperating sliding surfaces 96 introduced, in which the lubricating oil can be introduced. The corresponding lubricating oil pressure is designed so that it carries the axial thrust forces and thus the sliding surfaces of the cooperating thrust washers 93 . 95 each slide bearing plane 91 hydrostatically separated from each other.

The plain bearing levels 91 So, the lubrication pockets 96 the same, while the lubricating oil is fed individually, so a uniform distribution of the lubricating oil in the region of the plain bearing levels 91 to enable. The amount of the individual bearing layers 91 supplied lubricating oil is so dimensioned that on the one hand in the region of each plain bearing plane 91 a sufficiently large lubricating film thickness is set, and on the other hand, production-related differences in the distances of the pressure disks 93 . 95 can be compensated.

The introduction of the lubrication pockets 96 in the stator-side pressure plates 95 is preferred because then the oil supply of the lubrication pockets 96 Can be done in the stator system.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102004051306 B4 [0002, 0006, 0006, 0008, 0018]

Claims (6)

Drive device for a twin-screw extruder, with at least one input shaft ( 17 . 25 ) to which an engine ( 16 . 16 ' ) is coupled, with a first output shaft ( 60 ), to which a first worm shaft of the twin-screw extruder can be coupled, with a second output shaft ( 84 ), to which a second worm shaft of the twin-screw extruder can be coupled, with a planetary gear arrangement ( 8th ) and with a power dividing transmission ( 10 ), the output waves ( 60 . 84 ) on the one hand in radial bearings ( 101 ) and on the other hand in axial stock bearings ( 88 . 92 ), which serve to receive axial thrust forces, are mounted, characterized in that the axial main bearings ( 88 . 92 ) of the output shafts ( 60 . 84 ) are designed as hydrostatically supported thrust bearings. Drive device according to claim 1, characterized in that the hydrostatically supported thrust bearings one or more bearing layers ( 91 ), wherein each of the plain bearing layers ( 91 ) a shaft-side thrust washer ( 93 ) and a stator-side thrust washer ( 95 ), whose sliding surfaces are hydrostatically separated via a lubricant. Drive device according to claim 2, characterized in that in the stator-side pressure discs ( 95 ) at least one lubrication pocket ( 96 ) are introduced, where the lubricant is supplied via a hydraulic system. Drive device according to claim 2 or 3, characterized in that in the shaft-side pressure discs ( 93 ) at least one lubricating pocket are introduced, to which the lubricant can be supplied via a hydraulic system. Drive device according to one of claims 2 to 4, characterized in that each sliding bearing plane ( 91 ) A defined amount of lubricant can be fed individually. Drive device according to one of claims 3 to 5, characterized in that each lubricating pocket ( 96 ) A defined amount of lubricant can be fed individually.

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