DD297218A5

DD297218A5 - ROLLING GEAR WITH CHANGING AXLE DISTANCE BETWEEN DRIVE AND DISCONNECTING WHEEL

Info

Publication number: DD297218A5
Application number: DD34345290A
Authority: DD
Inventors: Wilfried Juhrs; Lothar Nowak; Steffen Poettrich
Original assignee: Gerfema Mbh,Dd; Heckert Gmbh,De
Priority date: 1990-08-15
Filing date: 1990-08-15
Publication date: 1992-01-02

Abstract

Die Erfindung betrifft einen Huelltrieb mit veraenderlichem Achsabstand zwischen Antriebs- und Abtriebsrad, auf dessen Kraftuebertragungsmittel eine verstellbare Spannrolle wirkt. Erfindungsgemaesz ist die Welle des Abtriebsrades in einer Verschiebebuchse gelagert, die zur Achsabstandsaenderung auf einer Geraden verschiebbar ist und auf der das eine Ende eines Steges drehbar angeordnet ist, dessen anderes Ende die Welle der Spannrolle aufnimmt. Die Wellenenden der Spannrolle sind in Nutkurven, die ineinander gegenueberliegende stationaere Gehaeuseteile eingearbeitet sind, zwangsgefuehrt. Bei Verschiebung des Abtriebsrades auf der Geraden wird durch die Ausgleichsbewegung der Spannrolle die Spannung des Kraftuebertragungsmittels selbsttaetig konstant gehalten. Fig. 2{Huelltrieb; Antriebsrad; Abtriebsrad; Achsabstand, veraenderbar; Kraftuebertragungsmittel; Spannrolle, verstellbar; Verschiebebuchse; Steg; Nutkurven; Gehaeuseteile, stationaer; Ausgleichsbewegung}The invention relates to a Huelltrieb with veraenderlichem center distance between the drive and driven gear on the Kraftuebertragungsmittel an adjustable tensioning roller acts. According to the invention, the shaft of the driven wheel is mounted in a sliding bush, which is displaceable on a straight line for the axle distance change and on which one end of a web is rotatably arranged, the other end of which receives the shaft of the tensioning roller. The shaft ends of the tensioning roller are positively guided in groove curves, which are incorporated into one another stationary stationary parts. Upon displacement of the output gear on the straight line, the voltage of the power transmission means is automatically kept constant by the compensating movement of the tensioning roller. Fig. 2 {Huelltrieb; Drive wheel; output gear; Axial distance, changeable; Kraftuebertragungsmittel; Tensioning pulley, adjustable; Sliding sleeve; Web; cam grooves; Housing parts, stationary; Compensating movement}

Description

Dabei ist es zweckmäßig, daß das Ende des Steges, welches die Wolle mit der Spannrolle aufnimmt, gabelförmig mit zwei Seitenteilen ausgebildet ist, wobei die Spannrolle zwischen den Seitenteilen liegt und die Enden der Welle durch die Seitenteile hindurch in die Nutkurven ragen.It is expedient that the end of the web, which receives the wool with the tension pulley, is fork-shaped with two side parts, wherein the tension roller is located between the side parts and the ends of the shaft project through the side parts into the groove curves.

Mit diesen Maßnahmen kann die Welle des Abtriebsrades entlang einer Geraden senkrecht oder unter einem anderen Winkel zur Verbindungslinie der Achsmittelpunkte von Antriebs- und Abtriebsrad bei konstant bleibender Spannung des Kraftübertragungemittels verschoben werden. Innerhalb des Verschiebebereiches kann die Welle des Abtriebsrades j jde beliebige Stellung einnehmen, wobei die Spannrolle dem Druck des Kraftübertragungsmittels infolge der Nutkurven nicht ausweichen kann.With these measures, the shaft of the output gear can be moved along a straight line perpendicular or at another angle to the connecting line of the axle centers of drive and driven at a constant voltage of the power transmission means. Within the displacement range, the shaft of the driven wheel j can take any position, wherein the tension roller can not escape the pressure of the power transmission means due to the Nutkurven.

Ausführungsbelsplel The invention will be explained in more detail with reference to the drawings. It shows Fro. 1: a top view of the envelope drive, 2 shows a sectional view according to arrow direction A in Fig. 1 and 3 shows a view of the sliding bush An envelope drive comprises according to FIG. 2 a drive wheel 1, an output gear 2 arranged axially parallel to the drive wheel 1 and a drive wheel 1 Timing belt 3. The drive wheel 1 is connected to a drive member, not shown, for. B. an electric motor with gear

verbunden. Das Abtriebsrad 2 ist auf einer Welle 4 befestigt, die mit dem einen Ende in einer Verschiebebuchse 5 (Fig. 1,3)gelagert ist und am anderen Ende eine nicht dargestellte Werkstückaufnahmerichtung trägt.connected. The output gear 2 is mounted on a shaft 4, which is mounted with one end in a sliding bush 5 (Fig. 1.3) and at the other end carries a workpiece receiving direction, not shown.

On the sliding bushing 5, a fork-shaped web β is rotatably mounted, which has a shaft 7 with its side parts 8 and 9

aufnimmt. Auf der Welle 7 ist zwischen den Seitenteilen 8 und 9 eine Spannrolle 10 drehbar angeordnet, die gegen den Leertrumdes Zahnriemens 3 drückt. Die Welle 7 ragt mit ihren Wellenenden 11,12 durch die Seitenteile 8,9 des Steges 6 hindurch, wobeidie Wellenenden 11,12 von Nutkurven 13,14 aufgenommen werden, die in Platten 15,16 eingearbeitet sind. Die Platten 15,16sind an stationären Gehäuseteilen 17 befestigt.receives. On the shaft 7, a tension roller 10 is rotatably disposed between the side parts 8 and 9, which presses against the empty belt 3 belt. The shaft 7 protrudes with its shaft ends 11,12 through the side parts 8,9 of the web 6, wherein the shaft ends 11,12 of Nutkurven 13,14 are taken, which are incorporated in plates 15,16. The plates 15, 16 are fastened to stationary housing parts 17.

The sliding bush 5 (FIG. 3) has two flats and is in the recess of the housing 17 by means of spindle 18 and Spindle nut 19 on a straight line or in a plane displaceable. The maximum displacement is marked with e. The Vorschiebebuchse 5 can occupy any position between the end points e 1 and e 2. The position, the curvature and the length Nutkurven 13,14 depends on the specific application and results after

bekannten mathematischen Beziehungen aus dem maximalen Verschiebeweg e, der Verschieberichtung, den Durchmessernder Spannrolle 10, des Antriebsrades 1 und des Abtriebsraries 2, dem mittleren Achsabstand zwischen dem Antriebsrad 1 unddem Abtriebsrad 2, dem Achsabstand zwischen dem Abtriebsrad 2 und der Spannrolle 10 sowie der Länge des Zahnriemens 3.known mathematical relationships of the maximum displacement e, the direction of displacement, the diameters of the tension roller 10, the drive wheel 1 and the Abtriebsraries 2, the center distance between the drive wheel 1 and the output gear 2, the center distance between the output gear 2 and the tension roller 10 and the length of the Timing belt 3.

For this purpose, the length of the toothed belt 3 in the tensioned state and in the Ausgangsiage the output gear 2 accordingly

seinem Verlauf in Kreisbögen und Tangenten unterteilt und daraus die Lage der Welle 7 ermittelt. Anschließend wird dasdivided its course in circular arcs and tangents and determines the location of the wave 7. Subsequently, the

Output gear 2 shifted point by point on the straight line and for each point the position of the shaft 7 with unchanged voltage

des Zahnriemens 3 berechnet. Aus den berechneten Punkten ergibt sich dann die Lage, Krümmung und Länge derof the toothed belt 3 is calculated. From the calculated points, the position, curvature and length of the

Nut curves 13,14. Each position of the shaft 4 of the output gear 2 on the displacement is a corresponding position of the Assigned shaft 7 of the tension roller 10 in the cam groove 13 and 14 respectively. Dio mode of action is the following: FIG. 2 shows the envelope drive according to the invention for two layers (end points e1 and e2) of the driven wheel 2. The output gear 2

soll vom Endpunkt e 1 nach Endpunkt e2 verschoben werden. Die Verschiebung kann z. B. manuell, pneumatisch oderhydraulisch erfolgen.should be moved from end point e 1 to end point e2. The shift can z. B. manually, pneumatically or hydraulically.

After the displacement of the output gear 2 to e vertically upwards results in the position shown in dashed lines of the individual Parts of the Hülltriebes, wherein the center distance between the drive wheel 1 and the output gear 2 has become smaller. In order to

die Spannung des Zahnriemens 3 trotzdem konstant bleibt, ist die Spannrolle 10 in den Nutkurven 13,14 zwangsgeführt. Diethe tension of the toothed belt 3 still remains constant, the tension roller 10 is forcibly guided in the groove curves 13,14. The

Position and curvature of the groove curves 13,14 and the constant center distance zwischon the driven gear 2 and the tension roller 10th

gewährleisten, daß die Spannrolle 10 infolge der Verschiebung des Abtriebsrades 2 selbständig eine Ausgleichsbev/egung zumensure that the tension roller 10 as a result of the displacement of the output gear 2 independently a Ausgleichsbev / egung for

Keeping the tension of the toothed belt 3 constant. In the present case, the impression amount of the tension roller 10

entsprechend größer. Nach Verstellung der Welle 4 des Abtriebsrades 2 wird die Vorrichtung mit bekannten Mitteln arretiert.correspondingly larger. After adjustment of the shaft 4 of the driven wheel 2, the device is locked by known means.

The displacement e can be arbitrarily selected between the end points el and e 2. The constancy of the tension of the toothed belt 3 is not only in the end points e 1, e2, but also during the Moving movement and regardless of the direction of displacement available. The tension roller 10 can in any phase of the Disengaging movement the pressure of the toothed belt 3, because the shaft 7 in the groove curves 13,14 positively

festgelegt ist.is fixed.

The space required for the actual clamping device is low because the web 6, the shaft 4 of the driven wheel 2 with the shaft. 7

der Spannrolle 10 direkt ohne oin äußeres ortsfestes Drehgelenk verbindet.the tension roller 10 connects directly without oin outer stationary pivot.

Claims

1. envelope drive with variable center distance between drive and driven gear, wherein a mounted on an adjustable shaft tensioning roller on the void of the power transmission means, in particular a toothed belt, acts, characterized in that the shaft (4) of the driven wheel (2) in a sliding bushing ( 5) is mounted, which is displaceable on a straight line and on which one end of the web (6) is rotatably arranged, the other end of the shaft (7) of the tension roller (10) receives and that the ends (11,12) of this Shaft (7) for keeping constant the toothed belt tension in Achsabstandsänderungen in groove curves (13,14) are forced, which lie in opposite stationary housing parts (17), wherein the position, the curvature and the length of the groove curves (13,14) according to known mathematical Relationships by the maximum displacement (e), the direction of displacement, the diameters of the tension roller (10), the drive wheel (1) and the driven wheel (2), d Em center distance between drive and driven gear (1,2), dom distance between the output gear (2) and the tension roller (10) and by the length of the toothed belt (3) is determined.

2. Hülltrieb according to claim 1, characterized in that the end of the web (6) which receives the shaft (7) with the tensioning roller (10), fork-shaped with two side parts (8,9) is formed, wherein the tension roller (10 ) lies between the side parts (8, 9) and the ends (11, 12) of the shaft (7) project through the side parts (8, 9) into the groove curves (13, 14).

For this 3 pages drawings
Field of application of the invention

The invention is suitable for Hülltriebe with functionally variable axis spacing between the drive and driven gear, the voltage of the power transmission means (belt, timing belt, chain o. Ä.) Before, during and after a change in the axle distance to be kept constant automatically.

Characteristic of the known state of the art

In the case of envelope drives with a variable center distance, the axial displacement in most cases serves to retighten the respective power transmission device. Additional tensioners are generally not required (DD 242856, DE 3006250). The corresponding adjustment paths are small depending on the elongation properties of the power transmission means. For envelopes with functionally dependent Achsabstandsänderungen the Achsverstell are relatively large. There is a requirement that the voltage be e.g. of the timing belt, regardless of the changing center distance should always be constant. Such a solution provides the V-belt transmission with drive and driven gear and idler according to the Auslegoschrift DE 17 52 386, F 16H-7/08. The output gear is in order to change the axle distance via a lever arm .im swiveled in a stationary hinge. The tension roller is mounted on a tensioning lever, which is also pivotable about the stationary pivot. The lever arm and the clamping lever are coupled to each other via a clamping element for adjusting the bias voltage, whereby the pivoting movement of the driven gear is transmitted to the tensioning roller. This Spam.einrichtung allows a displacement of the output shaft with constant belt tension in einsm relatively large area, the displacement movement is always circular arc because of the fixed hinge. A straight displacement is only approximately possible by correspondingly long lever. Such a solution is practically not feasible because of the very large space requirement.

Object of the invention

The aim of the invention is an envelope with variable center distance, which allows an axial displacement on a straight line boi constant voltage of the power transmission means and its space requirement is low.

Explanation of the essence of the invention

The invention has for its object to provide an envelope with variable center distance between the drive and driven, in which the length compensation movement of the tension roller for keeping constant the voltage of the power transmission means is derived from the rectilinear displacement movement of the driven wheel. According to the invention the object is achieved in that the shaft of the driven gear is mounted in a sliding bush which is displaceable on a straight line and on which one end of a web is rotatably arranged, whose other end receives the shaft of the tension roller, and that the shaft ends of Tensioner role for keeping constant the voltage of the power transmission means in Achsabstandsänderungen in Nutkurven are forced, which lie in opposite stationary housing parts, the position, the curvature and the length of the Nutkurven known mathematical relationships by the maximum displacement, the direction of displacement, the diameters of the tensioner, the drive wheel and the driven wheel, the average center distance between the drive and driven gear, the center distance between the driven gear and the tensioning roller and by the length of the power transmission means is determined.