EP0738585B1 - Transmission for driving the screws of a double-screw press - Google Patents

Transmission for driving the screws of a double-screw press Download PDF

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Publication number
EP0738585B1
EP0738585B1 EP96103491A EP96103491A EP0738585B1 EP 0738585 B1 EP0738585 B1 EP 0738585B1 EP 96103491 A EP96103491 A EP 96103491A EP 96103491 A EP96103491 A EP 96103491A EP 0738585 B1 EP0738585 B1 EP 0738585B1
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EP
European Patent Office
Prior art keywords
shaft
drive shaft
gearwheels
helical
coupled
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96103491A
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German (de)
French (fr)
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EP0738585A3 (en
EP0738585A2 (en
Inventor
Johannes Dr.-Ing. Weber
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Individual
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Publication of EP0738585A3 publication Critical patent/EP0738585A3/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
    • B30B11/22—Extrusion presses; Dies therefor
    • B30B11/24—Extrusion presses; Dies therefor using screws or worms
    • B30B11/241—Drive means therefor; screw bearings

Definitions

  • the invention relates to a gear arrangement for driving the two screws of a twin screw press according to the generic term of claim 1.
  • Such a gear arrangement is for example from US-A-3 766 797 known.
  • the gear arrangement described there are the second drive shaft and the intermediate shaft coupled via two gear pairs.
  • this gear arrangement has the advantage that the radial distance the output shafts of the reduction gear not the radial one The distance between the screws corresponds to the twin screw press got to. This allows gears with a larger diameter be used.
  • the transmissible torque limited by the load capacity of the two gear pairs.
  • DE-A-24 12 736 is a further development of that from the German patent 17 75 782 known gear arrangement known in which a shorter length is achieved in that on one side of the compensation point even number of pairs of wheels, on the other hand one odd number of pairs of wheels are provided, and that the Tooth slope of the odd-numbered pairs of wheels is selected so that the to associated displaceable gears the resulting axial forces from Compensate even-numbered pairs of axial forces.
  • the invention has for its object a transmission arrangement of the beginning mentioned type so that one with the same overall length compared to both known transmission arrangements higher torque can be transmitted or that the overall length of the Gear arrangement is less.
  • the gear arrangement according to the invention surprisingly combines the Advantages of the known gear arrangements.
  • By using at least another pair of gears while providing one Load balancing between the gear pairs can be the maximum transferable Torque by 50% compared to the solution known from US-A-3 766 797 be increased.
  • the maximum transferable torque can be achieved despite low Overall length can also be increased.
  • the special arrangement of the thrust bearings ensures that the gear arrangement itself remains free of axial forces during operation from the worm shafts be transmitted.
  • the load balancing device can be one of the axially in a conventional manner movable gears axially pressurized transmission device include.
  • the pressure transmission device can be at least one Compensation pillow, e.g. include an enclosed hydraulic compensation pad, the axially between two counter-rotating, helical teeth Gears 34 is arranged, and that the third gear 34th acts on the compensating cushion 44 via a piston 38, the one axial bore in the helical toothed with it in the same direction Gear 34 penetrates.
  • first drive shaft 14 mounted on its rear End with an output shaft 15 of a reduction gear, not shown can be coupled and at its front end a connecting shaft passing through an axial bearing unit 16 17 is coupled to a first worm shaft 18.
  • This Worm shaft 18 is thus over the reduction gear the first drive shaft 14 driven directly.
  • the second worm shaft 20 is another one Second connecting shaft 23 penetrating axial bearing unit 22 coupled to an intermediate shaft 24 which is in the transmission housing 10 is supported by means of bearings 26 and three helical teeth Gears or pinions 28 carries. Two of these sprockets 28 are helical in the same direction, while the third pinion 28 in the opposite direction with a helix angle is helical, which is one of the sum of the axial forces the amount of the first-mentioned pinion 28 is the same, but opposite axial force of the third pinion 28 causes.
  • This intermediate shaft 24 is a second drive shaft 30 ago driven by means of bearings 32 in the gear housing 10 is stored and at its rear end with a further output shaft 40 of the not shown Reduction gear is coupled.
  • the second drive shaft 30 includes 28 helical gears to match the pinions or pinions 34 which are axially movably mounted.
  • the middle one Pinion 34 has an axial bore 36 in which a piston 38 is axially displaceable with one of the two outer Pinion 34 is connected.
  • the other outer pinion 34 has an axial one on its side facing the central pinion Piston 42 which engages in the bore 36 and with the in this displaceable piston 38 via a compensating cushion 44 is coupled.
  • the bevel of the tooth adjacent to the reduction gear Gear pair 28, 34 is chosen so that the resulting Amount of axial force of the associated pinion 34 at least approximately equal to the sum of those of the two other opposite helical gears 34.
  • the area lying on the compensating cushion 44 is corresponding of the piston 42 is equal to the sum of that on the compensation cushion 44 adjacent surface of the piston 38 and an annular surface 46 (Figure 2) on the central gear 34.
  • the described embodiment includes a gear arrangement with three pairs of gears. It is understood that too more than three gear pairs can be provided.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Extrusion Moulding Of Plastics Or The Like (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
  • Friction Gearing (AREA)
  • Transmission Devices (AREA)

Abstract

The transmission has a first through drive shaft (14), able to be coupled on one side to the first output shaft of a reduction gear and on the other side to one of the screw conveyors. There is a second drive shaft (30) parallel to the first one, able to be coupled to the second output shaft of the reduction gear and to an intermediate shaft (24) to which it is parallel, via opposite-hand helical gear pairs (28,34). The second drive shaft and the intermediate shaft are engaged with each other by means of at least three of the helical gear pairs. The gears (34) for one of the two shafts can be moved axially. A load levelling device (38,44) is fitted between the gear wheels (34).

Description

Die Erfindung betrifft eine Getriebeanordnung zum Antrieb der beiden Schnecken einer Doppelschneckenpresse gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a gear arrangement for driving the two screws of a twin screw press according to the generic term of claim 1.

Eine solche Getriebeanordnung ist beispielsweise aus der US-A-3 766 797 bekannt. Bei der dort beschriebenen Getriebeanordnung sind die zweite Antriebswelle und die Zwischenwelle über zwei Zahnradpaare miteinander gekoppelt. Grundsätzlich hat diese Getriebeanordnung den Vorzug, daß der radiale Abstand der Ausgangswellen des Reduziergetriebes nicht dem radialen Abstand der Schnecken der Doppelschneckenpresse entsprechen muß. Dadurch können Zahnräder mit größerem Durchmesser verwendet werden. Allerdings wird das übertragbare Drehmoment durch die Belastbarkeit der beiden Zahnradpaare beschränkt.Such a gear arrangement is for example from US-A-3 766 797 known. With the gear arrangement described there are the second drive shaft and the intermediate shaft coupled via two gear pairs. Basically this gear arrangement has the advantage that the radial distance the output shafts of the reduction gear not the radial one The distance between the screws corresponds to the twin screw press got to. This allows gears with a larger diameter be used. However, the transmissible torque limited by the load capacity of the two gear pairs.

Aus dem deutschen Patent 1 757 782 ist ferner eine Getriebeanordnung zum Antrieb der beiden Schneckenwellen einer Doppelschneckenpresse bekannt, die zwei unmittelbar mit den beiden Schneckenwellen gekoppelte Antriebswellen umfaßt, von denen eine direkt angetrieben wird und mit der anderen über vier Zahnradpaare in Eingriff steht, wobei die Zahnräder der angetriebenen Welle axial beweglich sind und zwischen diesen axial beweglichen Zahnrädern jeweils eine Lastausgleichsvorrichtung vorgesehen ist. Diese Lösung hat den Nachteil, daß sie für gleichsinnig antreibbare Schneckenwellen nicht verwendbar ist, hat gegenüber der aus der US-A-3 766 797 bekannten Lösung aber den Vorteil, daß ein höheres Drehmoment übertragen werden kann, wenn auch diese Getriebeanordnung axial mehr Platz benötigt.From the German patent 1 757 782 there is also a gear arrangement to drive the two screw shafts of a twin screw press known the two immediately with includes the two worm shafts coupled drive shafts, one of which is driven directly and engages with the other via four gear pairs stands, wherein the gears of the driven shaft are axially movable and one between each of these axially movable gears Load balancing device is provided. This solution has the disadvantage that it cannot be used for worm shafts that can be driven in the same direction the solution known from US-A-3 766 797 but the advantage that a higher Torque can be transmitted if this gear arrangement is axial needs more space.

Aus der DE-A-24 12 736 ist eine Weiterentwicklung der aus dem deutschen Patent 17 75 782 bekannten Getriebeanordnung bekannt, bei der eine kürzere Baulänge dadurch erreicht wird, daß auf der einen Seite der Ausgleichsstelle eine geradzahlige Anzahl von Räderpaaren, auf der anderen Seite dagegen eine ungeradzahlige Anzahl von Räderpaaren vorgesehen sind, und daß die Zahnschräge der ungeradzahligen Räderpaare so gewählt ist, daß die an den zugehörigen verschieblichen Zahnrädern entstehenden Axialkräfte die von den geradzahligen Räderpaaren herrührenden Axialkräfte kompensieren.DE-A-24 12 736 is a further development of that from the German patent 17 75 782 known gear arrangement known in which a shorter length is achieved in that on one side of the compensation point even number of pairs of wheels, on the other hand one odd number of pairs of wheels are provided, and that the Tooth slope of the odd-numbered pairs of wheels is selected so that the to associated displaceable gears the resulting axial forces from Compensate even-numbered pairs of axial forces.

Der Erfindung liegt die Aufgabe zugrunde, eine Getriebeanordnung der eingangs genannten Art so auszubilden, daß bei gleicher Baulänge ein gegenüber beiden bekannten Getriebeanordnungen höheres Drehmoment übertragen werden kann oder daß bei gleichem übertragbaren maximalen Drehmoment die Baulänge der Getriebeanordnung geringer ist.The invention has for its object a transmission arrangement of the beginning mentioned type so that one with the same overall length compared to both known transmission arrangements higher torque can be transmitted or that the overall length of the Gear arrangement is less.

Diese Aufgabe wird erfindungsgemäß durch die im kennzeichnenden Teil des Anspruchs 1 angegebenen Merkmale gelöst.This object is achieved by the in the characterizing part of Features specified claim 1 solved.

Die erfindungsgemäße Getriebeanordnung vereinigt in überraschender Weise die Vorzüge der bekannten Getriebeanordnungen. Durch die Verwendung mindestens eines weiteren Zahnradpaares unter gleichzeitigem Vorsehen eines Lastausgleiches zwischen den Zahnradpaaren kann das maximal übertragbare Drehmoment gegenüber der aus der US-A-3 766 797 bekannten Lösung um 50% gesteigert werden. Gegenüber der aus dem deutschen Patent 17 75 782 bekannten Lösung kann das maximal übertragbare Drehmoment trotz geringer Baulänge ebenfalls erhöht werden. The gear arrangement according to the invention surprisingly combines the Advantages of the known gear arrangements. By using at least another pair of gears while providing one Load balancing between the gear pairs can be the maximum transferable Torque by 50% compared to the solution known from US-A-3 766 797 be increased. Compared to that from German patent 17 75 782 known solution, the maximum transferable torque can be achieved despite low Overall length can also be increased.

Die spezielle Anordnung der Axiallager stellt sicher, daß die Getriebeanordnung selbst frei von Axialkräften bleibt, die im Betrieb von den Schneckenwellen übertragen werden.The special arrangement of the thrust bearings ensures that the gear arrangement itself remains free of axial forces during operation from the worm shafts be transmitted.

Die Lastausgleichsvorrichtung kann in an sich bekannter Weise eine von den axial beweglichen Zahnrädern axial beaufschlagbare Druckübertragungseinrichtung umfassen. Dabei kann die Druckübertragungseinrichtung mindestens ein Ausgleichskissen, z.B. ein abgeschlossenes hydraulisches Ausgleichskissen umfassen, das axial zwischen zwei gegenläufig, schrägverzahnten Zahnrädern 34 angeordnet ist, und daß das dritte Zahnrad 34 auf das Ausgleichskissen 44 über einen Kolben 38 einwirkt, der eine axiale Bohrung in dem mit ihm gleichsinnig schrägverzahnten Zahnrad 34 durchsetzt.The load balancing device can be one of the axially in a conventional manner movable gears axially pressurized transmission device include. The pressure transmission device can be at least one Compensation pillow, e.g. include an enclosed hydraulic compensation pad, the axially between two counter-rotating, helical teeth Gears 34 is arranged, and that the third gear 34th acts on the compensating cushion 44 via a piston 38, the one axial bore in the helical toothed with it in the same direction Gear 34 penetrates.

Die folgende Beschreibung erläutert in Verbindung mit der beigefügten Zeichnung die Erfindung anhand eines Ausführungsbeispieles. Darin zeigt:

Figur 1
einen die Achsen der Wellen enthaltenden schematischen Schnitt durch die Getriebeanordnung und das ihr nachgeschaltete Axiallager, und
Figur 2
ein vergrößertes Detail aus Figur 1.
The following description explains the invention in conjunction with the accompanying drawing using an exemplary embodiment. It shows:
Figure 1
a schematic section containing the axes of the shafts through the gear arrangement and the axial bearing connected downstream thereof, and
Figure 2
an enlarged detail of Figure 1.

In einem Getriebegehäuse 10 ist mithilfe von Lagern 12 eine erste Antriebswelle 14 gelagert, die an ihrem rückwärtigen Ende mit einer Ausgangswelle 15 eines nicht dargestellten Reduziergetriebes koppelbar ist und an ihrem vorderen Ende über eine eine Axiallagereinheit 16 durchsetzende Verbindungswelle 17 mit einer ersten Schneckenwelle 18 gekoppelt ist. Diese Schneckenwelle 18 wird somit von dem Reduziergetriebe über die erste Antriebswelle 14 direkt angetrieben.In a gearbox housing 10 is with the help of bearings 12 first drive shaft 14 mounted on its rear End with an output shaft 15 of a reduction gear, not shown can be coupled and at its front end a connecting shaft passing through an axial bearing unit 16 17 is coupled to a first worm shaft 18. This Worm shaft 18 is thus over the reduction gear the first drive shaft 14 driven directly.

Die zweite Schneckenwelle 20 ist über eine eine weitere Axiallagereinheit 22 durchsetzende zweite Verbindungswelle 23 mit einer Zwischenwelle 24 gekoppelt, die in dem Getriebegehäuse 10 mithilfe von Lagern 26 gelagert ist und drei schrägverzahnte Zahnräder oder Ritzel 28 trägt. Zwei dieser Ritzel 28 sind gleichsinnig schrägverzahnt, während das dritte Ritzel 28 in der entgegengesetzten Richtung mit einem Schrägungswinkel schrägverzahnt ist, der eine der Summe der Axialkräfte der erstgenannten Ritzel 28 betragsmäßig gleiche, aber entgegengesetzt gerichtete Axialkraft des dritten Ritzels 28 bewirkt.The second worm shaft 20 is another one Second connecting shaft 23 penetrating axial bearing unit 22 coupled to an intermediate shaft 24 which is in the transmission housing 10 is supported by means of bearings 26 and three helical teeth Gears or pinions 28 carries. Two of these sprockets 28 are helical in the same direction, while the third pinion 28 in the opposite direction with a helix angle is helical, which is one of the sum of the axial forces the amount of the first-mentioned pinion 28 is the same, but opposite axial force of the third pinion 28 causes.

Diese Zwischenwelle 24 wird von einer zweiten Antriebswelle 30 her angetrieben, die mithilfe von Lagern 32 in dem Getriebgehäuse 10 gelagert ist und an ihrem rückwärtigen Ende mit einer weiteren Ausgangswelle 40 des nicht dargestellten Reduziergetriebes gekoppelt ist. Die zweite Antriebswelle 30 umfaßt zu den Ritzeln 28 passend schrägverzahnte Zahnräder oder Ritzel 34, die axial beweglich gelagert sind. Das mittlere Ritzel 34 hat eine axiale Bohrung 36, in der ein Kolben 38 axial verschiebbar ist, der mit dem einen der beiden äußeren Ritzel 34 verbunden ist. Das andere äußere Ritzel 34 hat auf seiner dem mittleren Ritzel zugewandten Seite einen axialen Kolben 42, der in die Bohrung 36 eingreift und mit dem in dieser verschiebbaren Kolben 38 über ein Ausgleichskissen 44 gekoppelt ist. Die Zahnschrägung des dem Reduziergetriebe benachbarten Zahnradpaares 28, 34 ist so gewählt, daß die resultierende Axialkraft des zugehörigen Ritzels 34 betragsmäßig mindestens annähernd gleich der Summe der von den beiden anderen entgegengesetzt schrägverzahnten Zahnrädern 34 ist. Entsprechend ist die am Ausgleichskissen 44 anliegende Fläche des Kolbens 42 gleich der Summe aus der am Ausgleichskissen 44 anliegenden Fläche des Kolbens 38 und einer Ringfläche 46 (Figur 2) an dem mittleren Zahnrad 34.This intermediate shaft 24 is a second drive shaft 30 ago driven by means of bearings 32 in the gear housing 10 is stored and at its rear end with a further output shaft 40 of the not shown Reduction gear is coupled. The second drive shaft 30 includes 28 helical gears to match the pinions or pinions 34 which are axially movably mounted. The middle one Pinion 34 has an axial bore 36 in which a piston 38 is axially displaceable with one of the two outer Pinion 34 is connected. The other outer pinion 34 has an axial one on its side facing the central pinion Piston 42 which engages in the bore 36 and with the in this displaceable piston 38 via a compensating cushion 44 is coupled. The bevel of the tooth adjacent to the reduction gear Gear pair 28, 34 is chosen so that the resulting Amount of axial force of the associated pinion 34 at least approximately equal to the sum of those of the two other opposite helical gears 34. The area lying on the compensating cushion 44 is corresponding of the piston 42 is equal to the sum of that on the compensation cushion 44 adjacent surface of the piston 38 and an annular surface 46 (Figure 2) on the central gear 34.

Mithilfe der aus dem Kolben 38 und dem Ausgleichskissen 44 bestehenden Lastausgleichsvorrichtung kann eine gleichförmige Belastung der drei Ritzelpaare und damit eine gleichmäßige Verteilung des zu übertragenden Drehmomentes auf drei Ritzelpaare erreicht werden. With the aid of the piston 38 and the equalization cushion 44 existing load balancer can be a uniform Loading of the three pairs of pinions and thus an even one Distribution of the torque to be transmitted over three pairs of pinions can be achieved.

Durch die Verwendung eines Dreiwellengetriebes und des dadurch möglichen relativ großen Achsabstandes der beiden Antriebswellen 14 und 30 kann auf jede der Antriebswellen ein relativ hohes Drehmoment übertragen werden, wobei die Antriebsrichtung der beiden Antriebswellen frei wählbar ist, so daß diese entweder gleichsinnig oder gegenläufig angetrieben werden. Durch die Verwendung von mehr als zwei Zahnradpaaren und mit Lastausgleich kann das maximal übertragbare Drehmoment noch erhöht werden. Damit kann bei relativ geringer Baulänge der Getriebeanordnung ein gegenüber den bekannten Lösungen größeres Drehmoment übertragen werden.By using a three-shaft gearbox and thereby possible relatively large center distance of the two drive shafts 14 and 30 can be on each of the drive shafts relatively high torque are transmitted, the drive direction of the two drive shafts is freely selectable, so that these are driven either in the same direction or in opposite directions become. By using more than two pairs of gears and with load balancing, the maximum transferable torque still be increased. This allows for a relatively short overall length the gear arrangement compared to the known solutions greater torque can be transmitted.

Das beschriebene Ausführungsbeispiel umfaßt eine Getriebeanordnung mit drei Zahnradpaaren. Es versteht sich, daß auch mehr als drei Zahnradpaare vorgesehen werden können.The described embodiment includes a gear arrangement with three pairs of gears. It is understood that too more than three gear pairs can be provided.

Claims (3)

  1. A transmission system for driving the two screws of a double screw extruder with a continuous first drive shaft (14) which is adapted to be coupled, on the one hand, to a first output shaft of a reduction gear and, on the other hand, to one of the screws, comprising a second drive shaft (30), which is parallel to the first drive shaft (14) and which is adapted to be coupled to a second output shaft of the reduction gear, and comprising an intermediate shaft (24) which, directed parallel to the second drive shaft (30) engages the latter via pairs of contradirectionally helical gearwheels (28, 34) and is adapted to be coupled to the second screw shaft, characterised in that the second drive shaft (30) and the intermediate shaft (24) are in engagement via at least three pairs of helical gearwheels (28, 34), in that at least the gearwheels (34) belonging to one of the two shafts (second drive shaft, intermediate shaft) are axially movable, in that a load balancing device (38,44) is disposed between the axially movable contradirectionally helical gearwheels (34), and in that an axial bearing unit (16, 22) which takes the axial reaction forces of the screw shaft (18, 20) is disposed between the first drive shaft (14) and the intermediate shaft (24) on the one hand, and the respective screw shaft (18, 20) on the other hand.
  2. A transmission system according to claim 1, characterised in that the load balancing device comprises a pressure transmission device which is axially loadable by the axially movable gearwheels (34).
  3. A transmission system according to claim 2, characterised in that the pressure transmission device comprises at least one balancing cushion (44) which is disposed axially between two contradirectionally helical gearwheels (34) and that the third gearwheel (34) acts on the balancing cushion (44) via a piston (38) which extends through an axial bore in the gearwheel (34) which is codirectionally helical therewith.
EP96103491A 1995-04-19 1996-03-06 Transmission for driving the screws of a double-screw press Expired - Lifetime EP0738585B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19514406 1995-04-19
DE19514406A DE19514406A1 (en) 1995-04-19 1995-04-19 Gear arrangement for driving the two screws of a twin screw press

Publications (3)

Publication Number Publication Date
EP0738585A2 EP0738585A2 (en) 1996-10-23
EP0738585A3 EP0738585A3 (en) 1997-02-26
EP0738585B1 true EP0738585B1 (en) 2001-01-17

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ID=7759877

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96103491A Expired - Lifetime EP0738585B1 (en) 1995-04-19 1996-03-06 Transmission for driving the screws of a double-screw press

Country Status (3)

Country Link
EP (1) EP0738585B1 (en)
AT (1) ATE198722T1 (en)
DE (2) DE19514406A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2342421B (en) * 1998-10-08 2003-03-19 Mmd Design & Consult A Conveyor
DE102006037509B4 (en) * 2006-08-10 2012-08-30 Johannes Weber Gear arrangement for driving the two screws of a twin-screw extruder

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1775782B1 (en) * 1968-09-23 1971-10-07 Weber Heinz Dipl Ing GEAR TRANSMISSION WITH ONE INPUT SHAFT AND TWO PARALLEL OUTPUT SHAFTS, CLOSELY ARRANGED, WITH LOAD BALANCING
US3766797A (en) * 1972-05-15 1973-10-23 Krauss Maffei Ag Power distributing transmission systems
DE2412736C3 (en) * 1974-03-16 1978-04-27 Heinz Dipl.-Ing. 8640 Kronach Weber Gear drive with an input shaft and two parallel, closely spaced output shafts
DE4313079A1 (en) * 1993-04-22 1994-10-27 Otto Michael Dr Ing Militzer Gear unit for twin screw extruders

Also Published As

Publication number Publication date
DE19514406A1 (en) 1996-10-24
EP0738585A3 (en) 1997-02-26
EP0738585A2 (en) 1996-10-23
DE59606326D1 (en) 2001-02-22
ATE198722T1 (en) 2001-02-15

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