EP0726868B1 - Device for conveying flat floppy products - Google Patents

Device for conveying flat floppy products Download PDF

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Publication number
EP0726868B1
EP0726868B1 EP95900100A EP95900100A EP0726868B1 EP 0726868 B1 EP0726868 B1 EP 0726868B1 EP 95900100 A EP95900100 A EP 95900100A EP 95900100 A EP95900100 A EP 95900100A EP 0726868 B1 EP0726868 B1 EP 0726868B1
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EP
European Patent Office
Prior art keywords
band conveyor
pulleys
radius
intermediate band
speed
Prior art date
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
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EP95900100A
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German (de)
French (fr)
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EP0726868A1 (en
Inventor
Heido Brokate
Ralph Jakob
Friedrich Jarchow
Rudolf Stäb
Klaus-Jürgen TAUBERT
Ming Liu
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Gruner and Jahr GmbH and Co KG
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Gruner and Jahr GmbH and Co KG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H5/00—Feeding articles separated from piles; Feeding articles to machines
    • B65H5/02—Feeding articles separated from piles; Feeding articles to machines by belts or chains, e.g. between belts or chains
    • B65H5/021—Feeding articles separated from piles; Feeding articles to machines by belts or chains, e.g. between belts or chains by belts
    • B65H5/023—Feeding articles separated from piles; Feeding articles to machines by belts or chains, e.g. between belts or chains by belts between a pair of belts forming a transport nip
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H29/00—Delivering or advancing articles from machines; Advancing articles to or into piles
    • B65H29/68—Reducing the speed of articles as they advance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/20—Belts
    • B65H2404/26—Particular arrangement of belt, or belts
    • B65H2404/261—Arrangement of belts, or belt(s) / roller(s) facing each other for forming a transport nip
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2513/00—Dynamic entities; Timing aspects
    • B65H2513/20—Acceleration or deceleration

Definitions

  • the invention relates to a device which is intended to bring flat, pliable products, such as sheets or sheet packs of paper or plastic, from one constant input speed v E to another constant output speed v A.
  • flat, pliable products such as sheets or sheet packs of paper or plastic
  • An example is the transport of printed sheet packets which have to be decelerated from a high input speed to a low output speed in order to adapt to the processing speed of a folder.
  • the center distance a of the deflection pulleys of the intermediate conveyor belt is made up of the length L and the deceleration length L V in the case of a product deceleration and the length L and the acceleration length L in the case of product acceleration B together.
  • the invention is based, for one in the cycle time the task T predetermined movement sequence the relationship between Center distance a of the deflection sheaves and radius of the traction sheave r of the intermediate conveyor belt to show the mass forces as possible to keep small and a slip-free transport of the To ensure products.
  • the gearwheels with the ratio i have the result that the mass moment of inertia of traction sheaves with radius r compared to traction sheaves with radius R by factor i 5 and reduced to the drive shaft of the periodic gear by factor i 3 , if one assumes that the ratio of width to radius of the disks remains constant.
  • the Invention provided that the conveyor belts each at a distance have straps arranged in parallel, with between the Distances of the deflection pulleys at the ends of the intermediate conveyor belt on the one hand deflection pulleys of the input conveyor belt and on the other hand, store the deflection pulleys of the outgoing conveyor belt.
  • Toothed belts are used, the teeth of which engage with toothed belt pulleys stand, with the driving toothed belt pulleys of the intermediate conveyor belt have partial circles with the radius r.
  • the intermediate conveyor belt can convey the intermediate conveyor belt from a lower and parallel to it consist of an upper conveyor belt, the working strands facing each other are in the same direction and synchronous move, with spring-loaded discs friction between the work strands and the products.
  • 1 to 9 illustrate the invention using the example of an intermediate conveyor belt for delaying sheet packets in a printing plant.
  • Fig. 1 shows schematically the intermediate conveyor belt, in which the center distance a of the deflection disks is made up of the product length L and the deceleration distance L v for decelerating the product.
  • Fig. 3 shows schematically a side view of the intermediate conveyor belt and pitch circles of gear wheels. It means 1 lower conveyor belt, 2 upper conveyor belt, 3 gear on the output shaft B of the periodic gear, 4 and 5 gears on the shaft C, 6 gear on the shaft D, 7 intermediate gear and 8 gear on the shaft E.
  • the shaft D stands with the driving toothed belt pulleys 9 of the lower and the shaft E with the driving toothed belt pulleys 10 of the upper conveyor belt via gears in connection.
  • the driving toothed belt pulleys have the pitch circle r.
  • the toothed belt pulleys 11 and 12 serve to deflect the toothed belt.
  • a denotes the center distance between shaft D of toothed belt pulley 9 and shaft of toothed belt pulley 11 or between shaft E of toothed belt pulley 10 and toothed belt pulley 12 of the intermediate conveyor belts.
  • ⁇ D and ⁇ E denote the opposite angular velocities of the shafts D and E.
  • the adjustable toothed belt pulleys 13 and 14 generate the necessary pretensioning of the conveyor belts.
  • Springs 15 press the toothed belt pulleys 17, which are mounted in beams 16, over the toothed belts against the sheet packets, which are conveyed in a non-positive manner in this way.
  • the vector v E denotes the speed of the input conveyor belt and the vector v A the speed of the output conveyor belt.
  • Fig. 4 shows the meshing of the toothed belt 18 of the lower one Conveyor belt with the toothed belt 19 of the input conveyor belt and with the toothed belt 20 of the output conveyor belt each at the transfer points of the sheet packs.
  • the driving toothed belt pulleys 9 support the deflection toothed belt pulleys 21 of the input conveyor belt and between the deflection toothed belt pulleys 11 the deflection toothed belt pulleys 22 of the Output conveyor belt.
  • Fig. 5 shows schematically an axial section of the intermediate conveyor belt, the gears with constant translation i and the periodic gear with the drive shaft A.
  • the shafts A, B, C, D and E have the angular velocities ⁇ A , ⁇ B , ⁇ C , ⁇ D and ⁇ E.
  • the gear wheels 23, 24 and 23 ', 24' with the clutch K 1 the gear wheels 3, 4 and 3 ', 4' with the clutch K 2
  • the coupling K 5 serves to connect the shaft D and the coupling K 6 to connect the shaft E of the intermediate conveyor belt.
  • the predetermined angular deceleration or angular acceleration e, the angular velocity ⁇ and the angle of rotation ⁇ of time t for one period, i.e. for the cycle time T ⁇ follows from the integration of ⁇ and ⁇ from the integration of ⁇ .
  • the periodic gear consists of non-circular gears that fulfill the sequence of movements according to FIG. 6.
  • FIG. 7 shows the rolling curve of the gearwheel seated on shaft A with the center 0 A and the minimum rolling curve radius r WAmin and the maximum rolling curve radius r WAmax .
  • the shaft A rotates at a constant angular velocity.
  • 8 shows, analogously to FIG. 7, the rolling curve of the gearwheel located on the shaft B with the center 0 B with r WBmin as the minimum and r WBmax as the maximum rolling curve radius.
  • E 'de notes the angular ranges for the constant speed v E , V' the angular ranges for the deceleration phase, A 'the angular ranges for the constant speed v A and B' the angular ranges for the acceleration phase of the intermediate conveyor belt.
  • the pitch curves of the non-circular wheels roll on each other without sliding. The arc lengths of the pitch curves belonging to the respective angular ranges are therefore of the same length.
  • the pitch curves can be described by the coordinates X A , Y A or X B , Y B.
  • FIG. 9 shows, analogously to FIG. 5, the axial section of the intermediate conveyor belt with a gear, in which, instead of the periodic gear with non-circular gears, a likewise known periodic gear with round gears in the arrangement of a planetary gear with the planetary gear carrier 25, the planetary gears 26 and 26 'and the sun gears 27 and 27 'is provided.
  • the wheels 26, 27 and 26 ', 27' can be preloaded with the clutch K 7 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Structure Of Belt Conveyors (AREA)
  • Separation, Sorting, Adjustment, Or Bending Of Sheets To Be Conveyed (AREA)

Description

Die Erfindung betrifft eine Vorrichtung, die flächige, biegeschlaffe Produkte, wie Blätter oder Blattpakete aus Papier oder Kunststoff, von einer konstanten Eingangsgeschwindigkeit vE auf eine andere konstante Ausgangsgeschwindigkeit vA bringen soll. Als Beispiel sei der Transport von bedruckten Blattpaketen angeführt, die von einer großen Eingangsgeschwindigkeit auf eine kleine Ausgangsgeschwindigkeit zu verzögern sind, um eine Anpassung an die Verarbeitungsgeschwindigkeit eines Falzapparates zu bewirken.The invention relates to a device which is intended to bring flat, pliable products, such as sheets or sheet packs of paper or plastic, from one constant input speed v E to another constant output speed v A. An example is the transport of printed sheet packets which have to be decelerated from a high input speed to a low output speed in order to adapt to the processing speed of a folder.

Die DE 1 189 919 A beschreibt bereits eine Vorrichtung, die aus einem Eingangstransportband mit konstanter Geschwindigkeit, einem Zwischentransportband mit periodisch sich verändernder Geschwindigkeit und einem Ausgangstransportband besteht. Die Übergabe des zu transportierenden Produktes von einem Band auf das nächste Band erfolgt jeweils bei gleichen Geschwindigkeiten der betroffenen Bänder. Das Zwischentransportband bewirkt eine Beschleunigung des Produktes auf eine höhere Geschwindigkeit. Sein Antrieb erfolgt durch ein periodisch übersetzendes Getriebe. Periodengetriebe sind bekannt. Als Beispiel sei das in der DE 646 002 A gezeigte Getriebe mit unrunden Rädern angeführt.DE 1 189 919 A already describes a device that consists of an input conveyor belt at constant speed, an intermediate conveyor belt with periodically changing Speed and an exit conveyor belt exists. The Transfer of the product to be transported from a conveyor the next belt takes place at the same speeds of the affected tapes. The intermediate conveyor belt causes one Accelerating the product to a higher speed. It is driven by a periodically translating gear. Period gearboxes are known. As an example, see the DE 646 002 A shown gear with non-circular wheels.

Für Produkte mit der Länge L, die in der Taktzeit T aufeinander folgen, setzt sich der Achsabstand a der Umlenkscheiben des Zwischentransportbandes im Fall einer Produktverzögerung aus der Länge L und der Verzögerungslänge LV und im Fall einer Produktbechleunigung aus der Länge L und der Beschleunigungslänge LB zusammen.For products with the length L, which follow each other in the cycle time T, the center distance a of the deflection pulleys of the intermediate conveyor belt is made up of the length L and the deceleration length L V in the case of a product deceleration and the length L and the acceleration length L in the case of product acceleration B together.

Relativ kurze Taktzeiten T erfordern verhältnismäßig große Beschleunigungen und Verzögerungen des Zwischentransportbandes. Dadurch entstehen relativ hohe Massenkräfte, die zum Ausfall von Triebwerksteilen führen können. Außerdem besteht die Gefahr, daß die Produkte rutschen, ihre Abstände verändern und dadurch den Taktbetrieb stören.Relatively short cycle times T require relatively large accelerations and delays in the intermediate conveyor belt. This creates relatively high mass forces that lead to the failure of Engine parts can lead. There is also a risk that the products slip, change their distances and thereby the Disrupt cycle operation.

Der Erfindung liegt die Aufgabe zugrunde, für einen in der Taktzeit T vorgegebenen Bewegungsablauf den Zusammenhang zwischen Achsabstand a der Umlenkscheiben und Radius der Treibscheibe r des Zwischentransportbandes aufzuzeigen, die Massenkräfte möglichst klein zu halten und einen schlupffreien Transport der Produkte zu gewährleisten.The invention is based, for one in the cycle time the task T predetermined movement sequence the relationship between Center distance a of the deflection sheaves and radius of the traction sheave r of the intermediate conveyor belt to show the mass forces as possible to keep small and a slip-free transport of the To ensure products.

Erfindungsgemäß betrachtet man den Achsabstand a als einen Teil des Umfanges einer Ersatzscheibe mit dem Radius R, zu der die Winkelbereiche ϕE für die konstante Eingangsgeschwindigkeit vE, ϕV für den Verzögerungsbereich, ϕA für die konstante Ausgangsgeschwindigkeit vA und ϕB für den Beschleunigungsbereich gehören und die in der Taktzeit T eine Umdrehung ausführt, so daß die Beziehungen a = L + R ϕV für den Fall der Produktverzögerung oder a = L + R ϕB für den Fall der Produktbeschleunigung gelten.According to the invention, the center distance a is considered to be part of the circumference of a replacement disk with the radius R, to which the angular ranges ϕ E for the constant input speed v E , ϕ V for the deceleration range, ϕ A for the constant output speed v A and ϕ B for the Acceleration range belong and which makes one revolution in the cycle time T, so that the relationships a = L + R ϕ V apply in the case of product deceleration or a = L + R ϕ B apply in the case of product acceleration.

Treibscheiben mit einem Radius R würden zu groß bauen und daher zu hohe Massenträgheitsmomente haben. Um bei einem vorgegebenen periodischen Bewegungsablauf und Achsabstand a der Umlenkscheiben des Zwischentransportbandes die Verzögerungs- und Beschleunigungsdrehmomente möglichst klein zu halten, sieht die Erfindung einen wesentlich kleineren Radius r der Treibscheibe des Zwischentransportbandes als den Radius R der Ersatzscheibe vor. Dies wird dadurch erreicht, daß zwischen dem Periodengetriebe und der Treibscheibe ins Schnelle übersetzende Zahnradstufen angeordnet werden, die insgesamt betragsmäßig die konstante Übersetzung i < 1 haben. Der Radius der Treibscheibe wird dann ohne Veränderung der Geschwindigkeiten des Zwischentransportbandes zu r = iR.Traction sheaves with a radius R would build too large and therefore have too high moments of inertia. To at a given periodic motion sequence and center distance a of the deflection disks of the intermediate conveyor belt the deceleration and acceleration torques The invention sees keeping it as small as possible a much smaller radius r of the traction sheave Intermediate conveyor belt as the radius R of the replacement disc. This is achieved in that between the periodic gear and the traction sheave gear ratios be arranged, the total amount of the constant Have translation i <1. The radius of the traction sheave will then without changing the speeds of the intermediate conveyor belt to r = iR.

Die Zahnräder mit der Übersetzung i haben zur Folge, daß das Massenträgheitsmoment von Treibscheiben mit dem Radius r im Vergleich zu Treibscheiben mit dem Radius R um den Faktor i5 und reduziert auf die Antriebswelle des Periodengetriebes um den Faktor i3 kleiner wird, wenn man voraussetzt, daß das Verhältnis Breite zu Radius der Scheiben konstant bleibt.The gearwheels with the ratio i have the result that the mass moment of inertia of traction sheaves with radius r compared to traction sheaves with radius R by factor i 5 and reduced to the drive shaft of the periodic gear by factor i 3 , if one assumes that the ratio of width to radius of the disks remains constant.

Da nun für eine vorgegebene Beanspruchung Treibscheiben für Transportbänder erheblich größer als Zahnräder bauen, erhält das auf die Antriebswelle des Periodengetriebes reduzierte Massenträgheitsmoment auch unter Berücksichtigung der zusätzlichen Zahnräder einen beachtlich kleineren Wert. Dadurch entstehen geringere Drehmomente für die Verzögerung und Beschleunigung des Transportbandes.Since traction sheaves for That gets conveyor belts that are considerably larger than gears Mass moment of inertia reduced to the drive shaft of the periodic gear also taking into account the additional Gears a considerably smaller value. This creates lower torques for decelerating and accelerating the Conveyor belt.

Insbesondere führen bei Produkten mit relativ kleinen Massen gleich große Winkelbereiche ϕV und ϕB und symmetrische zeitabhängige Verläufe der Verzögerung und Beschleunigung der Abtriebswelle des Periodengetriebes zu gleichen Beträgen der Extremwerte von Verzögerung und Beschleunigung und damit zu einem Minimum des sonst größten Betrages der Extremwerte. Der Achsabstand der Umlenkscheiben des Zwischentransportbandes hat in einem solchen Fall der Beziehung a = π r/i zu genügen.In particular, for products with relatively small masses, equally large angle ranges ϕ V and ϕ B and symmetrical time-dependent courses of the deceleration and acceleration of the output shaft of the periodic gear lead to the same amounts of the extreme values of deceleration and acceleration and thus to a minimum of the otherwise largest amount of the extreme values. In such a case, the center distance of the deflection pulleys of the intermediate conveyor belt must satisfy the relationship a = π r / i.

Um die Produkte am Anfang und Ende des Zwischentransportbandes ohne Querspalt übergeben zu können, wird in Ausgestaltung der Erfindung vorgesehen, daß die Transportbänder jeweils mit Abstand parallel angeordnete Riemen aufweisen, wobei zwischen den Abständen der Umlenkscheiben an den Enden des Zwischentransportbandes einerseits Umlenkscheiben des Eingangstransportbandes und andererseits Umlenkscheiben des Ausgangstransportbandes lagern.To the products at the beginning and end of the intermediate conveyor belt without being able to hand over the transverse gap, the Invention provided that the conveyor belts each at a distance have straps arranged in parallel, with between the Distances of the deflection pulleys at the ends of the intermediate conveyor belt on the one hand deflection pulleys of the input conveyor belt and on the other hand, store the deflection pulleys of the outgoing conveyor belt.

Zur Vermeidung gegenseitiger Verschiebungen der zu transportierenden Produkte infolge des Schlupfes der Transportbänder können Zahnriemen verwendet werden, deren Zähne im Eingriff mit Zahnriemenscheiben stehen, wobei die treibenden Zahnriemenscheiben des Zwischentransportbandes Teilkreise mit dem Radius r haben.To avoid mutual displacement of the goods to be transported Products due to the slippage of the conveyor belts can Toothed belts are used, the teeth of which engage with toothed belt pulleys stand, with the driving toothed belt pulleys of the intermediate conveyor belt have partial circles with the radius r.

Um ferner die Produkte während einer Beschleunigungs- oder Verzögerungsphase relativ zum Zwischentransportband schlupffrei zu befördern, kann das Zwischentransportband aus einem unteren und parallel dazu aus einem oberen Transportband bestehen, deren einander zugewandte Arbeitstrums sich gleichsinnig und synchron bewegen, wobei federnd angestellte Scheiben Kraftschluß zwischen den Arbeitstrums und den Produkten erzeugen.To further the products during an acceleration or deceleration phase slippage-free relative to the intermediate conveyor belt can convey the intermediate conveyor belt from a lower and parallel to it consist of an upper conveyor belt, the working strands facing each other are in the same direction and synchronous move, with spring-loaded discs friction between the work strands and the products.

Zur Vermeidung von Stößen in den Verzahnungen infolge des Flankenwechsels der Zähne durch den Wechsel zwischen Beschleunigungs- und Verzögerungsphasen und der dadurch bedingten Tragfähigkeitsminderung sind in weiterer Ausgestaltung der Erfindung zwei gleich ausgebildete, parallele Zahnrad-Getriebezüge vorgesehen, die sich mit Kupplungen so drehmomentmäßig vorspannen lassen, daß kein Anlagewechsel der Zahnflanken geschieht. Untersuchungen zeigen, daß die dadurch bedingten zusätzlichen Massen den Vorteil von kleinen Treibscheiben des Zwischentransportbandes im. Hinblick auf das reduzierte Massenträgheitsmoment an der Antriebswelle des Periodengetriebes nicht beseitigen.To avoid shocks in the gears as a result of the flank change of teeth by alternating between acceleration and delay phases and the resulting reduction in load capacity are in a further embodiment of the invention two identically designed, parallel gear-gear trains are provided, that torque with couplings leave that there is no change of contact of the tooth flanks. Investigations show that the resulting additional masses the advantage of small traction sheaves on the intermediate conveyor belt in the. With regard to the reduced moment of inertia at the Do not remove the drive shaft of the periodic gear.

Die Fig. 1 bis 9 erläutern die Erfindung am Beispiel eines Zwischentransportbandes für die Verzögerung von Blattpaketen in einer Druckereianlage.1 to 9 illustrate the invention using the example of an intermediate conveyor belt for delaying sheet packets in a printing plant.

Fig. 1 zeigt schematisch das Zwischentransportband, bei dem der Achsabstand a der Umlenkscheiben sich aus der Produktlänge L und der Verzögerungsstrecke Lv für die Verzögerung des Produktes zusammensetzt. Fig. 1 shows schematically the intermediate conveyor belt, in which the center distance a of the deflection disks is made up of the product length L and the deceleration distance L v for decelerating the product.

In Fig. 2 ist die Ersatzwalze mit dem Radius R dargestellt. Zum Kreisbogen mit der Länge L gehört der Winkelbereich ϕE für die konstante Eingangsgeschwindigkeit vE, zum Kreisbogen mit der Länge Lv der Winkelbereich ϕV für den Verzögerungsbereich, zum Kreisbogen mit der Länge L der Winkelbereich ϕA = ϕE für die konstante Ausgangsgeschwindigkeit vA und zum Kreisbogen mit der Länge LB der Winkelbereich ϕB für den Beschleunigungsbereich. Außerdem zeigt Fig. 2 den Kreisbogen mit der Länge a des Achsabstandes der Umlenkscheiben des Zwischentransportbandes.In Fig. 2 the replacement roller with the radius R is shown. The circular arc with the length L includes the angular range ϕ E for the constant input speed v E , the circular arc with the length L v the angular range ϕ V for the deceleration range, the circular arc with the length L the angular range ϕ A = ϕ E for the constant output speed vA and to the circular arc with length L B the angular range ϕ B for the acceleration range. 2 also shows the circular arc with the length a of the center distance of the deflection disks of the intermediate conveyor belt.

Fig. 3 zeigt schematisch eine Seitenansicht des Zwischentransportbandes und Wälzkreise von Zahnrädern. Es bedeuten 1 unteres Transportband, 2 oberes Transportband, 3 Zahnrad auf der Abtriebswelle B des Periodengetriebes, 4 und 5 Zahnräder auf der Welle C, 6 Zahnrad auf der Welle D, 7 Zwischenzahnrad und 8 Zahnrad auf der Welle E. Die Welle D steht mit den treibenden Zahnriemenscheiben 9 des unteren und die Welle E mit den treibenden Zahnriemenscheiben 10 des oberen Transportbandes über Zahnräder in Verbindung. Die treibenden Zahnriemenscheiben haben den Teilkreisradius r. Die Zahnriemenscheiben 11 und 12 dienen zur Umlenkung der Zahnriemen. a kennzeichnet den Achsabstand zwischen Welle D der Zahnriemenscheibe 9 und Welle der Zahnriemenscheibe 11 bzw. zwischen Welle E der Zahnriemenscheibe 10 und der Zahnriemenscheibe 12 der Zwischentransportbänder. ωD und ωE bezeichnen die gleich großen gegenläufigen Winkelgeschwindigkeiten der Wellen D und E. Die verstellbaren Zahnriemenscheiben 13 und 14 erzeugen die notwendige Vorspannung der Transportbänder. Federn 15 drücken die in Balken 16 gelagerten Zahnriemenscheiben 17 über die Zahnriemen gegen die Blattpakete, die auf diese Weise kraftschlüssig befördert werden. Der Vektor vE bezeichnet die Geschwindigkeit des Eingangstransportbandes und der Vektor vA die Geschwindigkeit des Ausgangstransportbandes.Fig. 3 shows schematically a side view of the intermediate conveyor belt and pitch circles of gear wheels. It means 1 lower conveyor belt, 2 upper conveyor belt, 3 gear on the output shaft B of the periodic gear, 4 and 5 gears on the shaft C, 6 gear on the shaft D, 7 intermediate gear and 8 gear on the shaft E. The shaft D stands with the driving toothed belt pulleys 9 of the lower and the shaft E with the driving toothed belt pulleys 10 of the upper conveyor belt via gears in connection. The driving toothed belt pulleys have the pitch circle r. The toothed belt pulleys 11 and 12 serve to deflect the toothed belt. a denotes the center distance between shaft D of toothed belt pulley 9 and shaft of toothed belt pulley 11 or between shaft E of toothed belt pulley 10 and toothed belt pulley 12 of the intermediate conveyor belts. ω D and ω E denote the opposite angular velocities of the shafts D and E. The adjustable toothed belt pulleys 13 and 14 generate the necessary pretensioning of the conveyor belts. Springs 15 press the toothed belt pulleys 17, which are mounted in beams 16, over the toothed belts against the sheet packets, which are conveyed in a non-positive manner in this way. The vector v E denotes the speed of the input conveyor belt and the vector v A the speed of the output conveyor belt.

Fig. 4 stellt das Ineinandergreifen der Zahnriemen 18 des unteren Transportbandes mit den Zahnriemen 19 des Eingangstransportbandes und mit den Zahnriemen 20 des Ausgangstransportbandes jeweils an den Übergabestellen der Blattpakete dar. Zwischen den treibenden Zahnriemenscheiben 9 lagern die Umlenk-Zahnriemenscheiben 21 des Eingangstransportbandes und zwischen den Umlenk-Zahnriemenscheiben 11 die Umlenk-Zahnriemenscheiben 22 des Ausgangstransportbandes.Fig. 4 shows the meshing of the toothed belt 18 of the lower one Conveyor belt with the toothed belt 19 of the input conveyor belt and with the toothed belt 20 of the output conveyor belt each at the transfer points of the sheet packs. Between the driving toothed belt pulleys 9 support the deflection toothed belt pulleys 21 of the input conveyor belt and between the deflection toothed belt pulleys 11 the deflection toothed belt pulleys 22 of the Output conveyor belt.

Fig. 5 zeigt schematisch einen Achsschnitt des Zwischentransportbandes, der Zahnräder mit konstanter Übersetzung i und des Periodengetriebes mit der Antriebswelle A. Die Wellen A, B, C, D und E haben die Winkelgeschwindigkeiten ωA, ωB, ωC, ωD und ωE. In jeder Getriebestufe sind zwei gleiche parallel angeordnete Radsätze vorhanden, wobei sich die Zahnräder 23, 24 und 23', 24' mit der Kupplung K1, die Zahnräder 3, 4 und 3', 4' mit der Kupplung K2, die Zahnräder 5, 6 und 5', 6' mit der Kupplung K3 und die Zahnräder 5, 7, 8 und 5', 7', 8' mit der Kupplung K4 drehmomentmäßig vorspannen lassen. Die Kupplung K5 dient zum Anschluß der Welle D und die Kupplung K6 zum Anschluß der Welle E des Zwischentransportbandes.Fig. 5 shows schematically an axial section of the intermediate conveyor belt, the gears with constant translation i and the periodic gear with the drive shaft A. The shafts A, B, C, D and E have the angular velocities ω A , ω B , ω C , ω D and ω E. In each gear stage there are two identical gear sets arranged in parallel, the gear wheels 23, 24 and 23 ', 24' with the clutch K 1 , the gear wheels 3, 4 and 3 ', 4' with the clutch K 2 , the gear wheels 5 , 6 and 5 ', 6' with the clutch K 3 and the gears 5, 7, 8 and 5 ', 7', 8 'with the clutch K 4 torque. The coupling K 5 serves to connect the shaft D and the coupling K 6 to connect the shaft E of the intermediate conveyor belt.

Für den geforderten Bewegungsablauf des Zwischentransportbandes stellt Fig. 6 die vom Periodengetriebe zu realisierenden Verläufe der vorgegebenen Winkelverzögerung bzw. Winkelbeschleunigung e, der Winkelgeschwindigkeit ω und des Drehwinkels ϕ abhängig von der Zeit t für eine Periode, d.h. für die Taktzeit T dar. ω folgt aus der Integration von ε und ϕ aus der Integration von ω.For the required movement of the intermediate conveyor belt 6 shows the courses to be realized by the periodic gear the predetermined angular deceleration or angular acceleration e, the angular velocity ω and the angle of rotation ϕ of time t for one period, i.e. for the cycle time T ω follows from the integration of ε and ϕ from the integration of ω.

In diesem Beispiel besteht das Periodengetriebe aus unrunden Zahnrädern, die den Bewegungsablauf nach Fig. 6 erfüllen. Fig. 7 zeigt die Wälzkurve des auf der Welle A mit dem Mittelpunkt 0A sitzenden Zahnrades und den minimalen Wälzkurvenradius rWAmin sowie den maximalen Wälzkurvenradius rWAmax. Die Welle A dreht mit konstanter Winkelgeschwindigkeit. Fig. 8 zeigt analog zu Fig. 7 die Wälzkurve des sich auf der Welle B mit dem Mittelpunkt 0B befindenden Zahnrades mit rWBmin als minimalem und rWBmax als maximalem Wälzkurvenradius. In den Fig. 7 und 8 bezeichnen E' die Winkelbereiche für die konstante Geschwindigkeit vE, V' die Winkelbereiche für die Verzögerungsphase, A' die Winkelbereiche für die konstante Geschwindigkeit vA und B' die Winkelbereiche für die Beschleunigungsphase des Zwischentransportbandes. Die Wälzkurven der Unrundräder rollen ohne Gleiten aufeinander ab. Die zu den jeweiligen Winkelbereichen gehörenden Bogenlängen der Wälzkurven sind also gleich lang. Die Wälzkurven lassen sich durch die Koordinaten XA, YA bzw. XB, YB beschreiben.In this example, the periodic gear consists of non-circular gears that fulfill the sequence of movements according to FIG. 6. FIG. 7 shows the rolling curve of the gearwheel seated on shaft A with the center 0 A and the minimum rolling curve radius r WAmin and the maximum rolling curve radius r WAmax . The shaft A rotates at a constant angular velocity. 8 shows, analogously to FIG. 7, the rolling curve of the gearwheel located on the shaft B with the center 0 B with r WBmin as the minimum and r WBmax as the maximum rolling curve radius. 7 and 8, E 'denotes the angular ranges for the constant speed v E , V' the angular ranges for the deceleration phase, A 'the angular ranges for the constant speed v A and B' the angular ranges for the acceleration phase of the intermediate conveyor belt. The pitch curves of the non-circular wheels roll on each other without sliding. The arc lengths of the pitch curves belonging to the respective angular ranges are therefore of the same length. The pitch curves can be described by the coordinates X A , Y A or X B , Y B.

Fig. 9 zeigt analog Fig. 5 den Achsschnitt des Zwischentransportbandes mit einem Getriebe, bei dem anstelle des Periodengetriebes mit unrunden Zahnrädern ein ebenfalls bekanntes Periodengetriebe mit runden Zahnrädern in der Anordnung eines Planetengetriebes mit dem Planetenradträger 25, den Planetenzahnrädern 26 und 26' sowie den Sonnenzahnrädern 27 und 27' vorgesehen ist. Die Räder 26, 27 und 26', 27' lassen sich mit der Kupplung K7 drehmomentmäßig vorspannen. Die im Planetenrad 26' exzentrisch gelagerte Rolle 28 wälzt auf der Kurvenscheibe 29 ab, stützt das Drehmoment der Planetenräder ab und überlagert den Planetenrädern den periodischen Bewegungsablauf nach Fig. 6, die anstelle der Welle B nach Fig. 5 die Bewegung auf die Welle C übertragen. Das Zahnräder-Planetengetriebe wirkt bereits im Sinne der Erfindung als eine Stufe der Zahnräder, die die konstante Übersetzung i = r/R zu realisieren haben.FIG. 9 shows, analogously to FIG. 5, the axial section of the intermediate conveyor belt with a gear, in which, instead of the periodic gear with non-circular gears, a likewise known periodic gear with round gears in the arrangement of a planetary gear with the planetary gear carrier 25, the planetary gears 26 and 26 'and the sun gears 27 and 27 'is provided. The wheels 26, 27 and 26 ', 27' can be preloaded with the clutch K 7 . The roller 28 mounted eccentrically in the planet gear 26 'rolls on the cam plate 29, supports the torque of the planet gears and superimposes the periodic movement sequence according to FIG. 6 on the planet gears, which transmit the movement to the shaft C instead of the shaft B according to FIG. 5 . In the sense of the invention, the planetary gearwheel gear already acts as a stage of the gearwheels which have to implement the constant ratio i = r / R.

Claims (6)

  1. Device for varying the speed of flat, flexible products of length L and cycle time T, in particular of sheets and sheet stacks of paper or plastics, which has an incoming band conveyor with a constant speed vE, an intermediate band conveyor with a periodically varying speed and an outgoing band conveyor with a constant speed vA, there being provided for the drive of the intermediate band conveyor a gearing which transforms the speed periodically and at the cycle time T generates the angle-of-rotation regions E for the constant speed vE, v for the deceleration region, A for the constant speed vA and E for the acceleration region, characterised in that the circumference of a replacement pulley of radius R is composed of the circular arcs L = R E, Lv = R v, L = R A = R R and LB = R B, in that, for the centre distance a of the deflection pulleys of the intermediate band conveyor, the relation a = L + R v holds for the case of the product deceleration and the relation a = L + R B holds for the case of the product acceleration, and in that the radius r of the driving pulleys (9; 10) of the intermediate band conveyor results from the equation r = iR, where in terms of amount i < 1 denotes the constant stepping up of gearwheels which are located between the periodic gearing and the driving pulleys (9; 10) of the intermediate band conveyor.
  2. Device according to Claim 1, characterised in that the angle-of-rotation regions v and B are of equal size and the deceleration and acceleration courses as a function of time are symmetrical, and in that the relation a = π r/i exists between the radius r of the driving pulleys (9; 10) and the centre distance a of the deflection pulleys of the intermediate transport [sic].
  3. Device according to Claim 1 or 2, characterised in that the band conveyors each have belts (18; 19; 20) arranged spaced apart and parallel, deflection pulleys of the incoming band conveyor (21) being mounted between the spacings of the driving pulleys (9; 10) of the intermediate band conveyor, and deflection pulleys of the outgoing band conveyor (22) being mounted between the deflection pulleys of the intermediate band conveyor (11; 12).
  4. Device according to one of Claims 1 to 3, characterised in that the belts (18; 19; 20) are toothed belts whose teeth mesh with toothed-belt pulleys, and in that the driving toothed-belt pulleys (9; 10) of the intermediate band conveyor have pitch circles of radius r.
  5. Device according to one of Claims 1 to 4, characterised in that the intermediate band conveyor comprises a lower band conveyor (1) and an upper band conveyor (2) parallel thereto, the mutually facing working strands of which are driven in the same direction and synchronously, and in that resiliently set-against pulleys (17) produce a frictional connection between the band conveyors (1, 2) and the products.
  6. Device according to Claim 5, characterised in that two identically constructed, parallel gear trains from the drive shaft (A) of the periodic gearing as far as the driving shafts (D; E) of the lower and upper band conveyor (1; 2) of the intermediate band conveyor are provided, it being possible to prestress the gear trains in terms of torque by means of clutches (K1 to K7).
EP95900100A 1993-11-02 1994-11-01 Device for conveying flat floppy products Expired - Lifetime EP0726868B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4337410 1993-11-02
DE4337410 1993-11-02
PCT/EP1994/003579 WO1995012540A1 (en) 1993-11-02 1994-11-01 Device for conveying flat floppy products

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EP0726868A1 EP0726868A1 (en) 1996-08-21
EP0726868B1 true EP0726868B1 (en) 1998-03-18

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US (1) US5803450A (en)
EP (1) EP0726868B1 (en)
JP (1) JPH09504260A (en)
DE (1) DE59405493D1 (en)
WO (1) WO1995012540A1 (en)

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JP4948711B2 (en) * 2001-02-16 2012-06-06 株式会社イシダ Article supply equipment
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US8025291B2 (en) * 2006-01-10 2011-09-27 Goss International America, Inc. Signature velocity reduction device and method
JP6431773B2 (en) * 2015-01-13 2018-11-28 富士機械工業株式会社 Printing device that performs multicolor printing on metal sheets
JP6424093B2 (en) * 2015-01-13 2018-11-14 富士機械工業株式会社 Printing device that performs multicolor printing on metal sheets
CN104843514A (en) * 2015-04-17 2015-08-19 杭州登新科技有限公司 PCB transmission device
CN104843516A (en) * 2015-04-29 2015-08-19 浙江好时加卫生用品有限公司 Sanitary towel conveying device
JP6722067B2 (en) * 2016-08-31 2020-07-15 株式会社沖データ Medium transport device, medium supply device, and image forming system
CN117347837B (en) * 2023-12-04 2024-02-13 四川弘仁财电科技有限公司 Double-sided testing device and testing method for integrated circuit element

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DE102005054270A1 (en) * 2005-11-11 2007-05-16 Eastman Kodak Co Transport assembly for photo-sensitive printing paper has two parallel endless belts one or both of which are toothed belts

Also Published As

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WO1995012540A1 (en) 1995-05-11
DE59405493D1 (en) 1998-04-23
JPH09504260A (en) 1997-04-28
EP0726868A1 (en) 1996-08-21
US5803450A (en) 1998-09-08

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