EP1138622B1 - Device for decelerating signatures - Google Patents

Abstract

The device has an intake gap (40) to receive signatures (1) from a device with a first transportation speed, and decelerate these to a first reduced speed. Gap surfaces engaging on the signatures are formed by a pair of opposite non-circular rotating components (4), which define a draw-in gap (40) to decelerate the components, and an intermediate gap, accelerating them. The signatures are moved from the intake gap to an ejection gap (50), to be decelerated to a second reduced speed. The gap surfaces are formed by two non-circular rotating components (5), which similarly decelerate and accelerate the first components.

Description

The present invention relates to a device for slowing down signatures, in particular in a folder of a web-fed rotary printing press, according to the Preamble of claim 1 (see, e.g., EP-A-0 972 733).

The speed of conventional sword folding devices is constructional limited. Therefore, the speed of the printing press is around 55,000 copies limited per hour. There are usually two to achieve this speed Flap folder devices arranged in parallel are required, to which signatures are alternately fed become. To increase the speed to more than 55,000 copies per hour, must have a device to change the speed of the signatures from the Printing speed can be provided on the speed of the flap folder.

Combination folders are made using a series of successive Folding operations produce products of different sizes or formats based on same path through the folder. The different types of folds are funnel fold (first fold, first longitudinal fold), flap fold (second fold, first transverse fold), Digest and delta fold (third fold, second cross fold) and second sword fold (fourth fold, second longitudinal fold). The product length can be between 50% and 25% of the Section length if there is no protruding side and a little more, if a protruding page is provided. To process these products of varying lengths, the slowdown mechanism must be flexible to accommodate everyone Bring products to the same speed. If not, it would have to the folder in the section downstream of the decelerating mechanism via a variable translation, or the products of different lengths would have to be in different transport paths can be transported to the delivery.

In known slowdown devices are usually used to slow down the Signatures before entering a sword fold apparatus or Combination folder cylinder used.

No. 5,803,450 describes a device for transporting flat, flexible products (e.g. of signatures) that are running at a constant speed Infeed conveyor belt, a middle one running at a changing speed Conveyor belt and an exit conveyor belt running at a constant speed includes. The middle conveyor belt slows down or accelerates the promotional product. The transfer of the product from a conveyor belt to one other conveyor belt takes place if the corresponding conveyor belts are the same Running speed. The middle conveyor belt is driven by a periodically switching gear.

In US 4,506,873 is a system for performing a cross fold or Quarterfold operation described at high speed, along with High-speed conveyor belts for signatures in web presses can be used. The higher speed is said to be due to brake fluid for gradual, non-linear braking of the signature as it enters the Folders reached, allegedly damaging the product or erroneously Folding the product due to hitting the stationary stop in the folder is avoided at high speed. On a cyclically moving one Toothed belts are provided that slow down stops Catch paper product that is transported in at a higher speed by means of a conveyor belt the device is moved. This moving stop becomes synchronous in the way driven that the paper product intercepted at the highest transition speed and is moved non-linearly to the paper product at the lowest Decelerate speed before it hits the stationary stop to carry out the Folding process occurs. As a rule, the non-linear speed ratio becomes the Timing belt deceleration stops of 4: 1 through an arrangement of elliptical Timing belt causes. The system reduces the speed of impact of the signatures on stationary stop by at least 60% of the speed with which the signatures in break in the folder.

As already known, devices for slowing down signatures include cylinders, which are costly to manufacture and difficult to set up. In the US 5,803,450 and slowdown devices described in US 4,506,873 instead of cylinders used to slow down the signatures tapes. With these Devices, however, take longer to slow down than conventional ones Cylinders. They also require setup work by a machine operator as well a mechanism for phase adjustment, usually in a combination folder to be able to accommodate products of different lengths. Add to that the longer deceleration phase on the powertrain and the signature acts stronger forces, which can cause the tapes to slip.

It is therefore an object of the present invention to provide a device for To slow down signatures creating the aforementioned disadvantages of the prior art technology overcomes and a safe and precise slowdown of the signatures enables, whereby damage to the signatures are prevented. It is one Another object of the present invention is a device for slowing down To create signatures with which it is possible to create different signatures Section lengths from the same input speed to the same Brake output speed.

This object is achieved by the features of claim 1.

A device according to the invention for slowing down signatures comprises one Inlet gap for taking over a signature from an upstream device with a first transport speed and to slow down the transport speed of the Signature to a first reduced transport speed, the inlet gap being the Signature-contacting surfaces comprises that of a pair of opposing, non-circular, rotating components are formed, each one Draw gap between the components forming the first surface section and a a space between the components forming the second surface portion include and which are rotatable with a variable speed profile that at A slowdown in the formation of the pull gap and a slowdown in the formation of the intermediate space Provides acceleration of the components, as well as an exit gap to take over the Signature of the inlet gap and to further slow down the Transport speed of the signature reduced to a second Transport speed, with the exit gap surfaces contacting the signature includes that of a pair of opposed, non-circular, rotating Components are formed, each with a gap between the Components forming the first surface section and an intermediate space between the components forming the second surface section and the with a variable speed profile can be rotated, the one when the draft gap is formed Slowing down and accelerating the gap Components.

In particular, it can be provided according to one embodiment of the invention that the opposite, non-circular, rotating components of the Inlet gap comprise a pair of opposing cylinders, each one first peripheral portion with a to form a gap between the each other opposite cylinders suitable first radius and a second Circumferential section with at least one smaller than the first radius, for Formation of a space between the cylinders suitable second radius and that the opposite, non-circular, rotating Components of the exit gap comprise a pair of opposing cylinders, which each have a first circumferential section with a to form a tensile gap between the opposing cylinders suitable first radius and a second Circumferential section with at least one smaller than the first radius, for Formation of a space between the cylinders suitable second radius exhibit.

The cylinders of the inlet gap are preferably around from the cylinders of the outlet gap not more than a quarter of the section length of a signature in tabloid format spaced so that in the device signatures in delta format, in tabloid format and can be edited in digest format.

Furthermore, the first and second splitting mechanisms preferably have the same Speed profile.

Each of the cylinders may further comprise a plurality of axially spaced disks.

According to a second embodiment of the present invention, the Inlet gap mechanism an inlet gap cylinder and the outlet gap mechanism comprise an exit gap cylinder, each cylinder having a first Circumferential section with a first radius and a second circumferential section with comprises at least a second radius, the at least one second radius is smaller than the first radius. In particular, the first peripheral section is preferred with respect to the axis of rotation of the cylinder in the form of an arc and the second Circumferential section preferably with respect to the axis of rotation of the cylinder in the form of a Elliptical arch. "Formed in the form of an arc" means in this Context that every point on the peripheral portion of the cylinder in the same Distance to the axis of rotation is arranged while "in the form of an elliptical arc "means that the distance of the points on the peripheral portion of the Cylinder varies with respect to the axis of rotation of the cylinder, so that there is an elliptical shape with respect to the axis of rotation. However, it is also conceivable that certain Circumferential sections are formed in the shape of any arc, which means that the distance of the points on the peripheral portion of the cylinder with respect to the axis of rotation of the cylinder can vary in any way. It is preferably a continuous variation of the distance of the points with respect to the axis of rotation is selected.

Furthermore, the inlet gap can have an inlet gap cylinder and at least one belt leading first rotating element and the inlet gap cylinder include a first Circumferential section with a first radius and a second circumferential section with comprise at least a second radius. It can be provided that the at least one band carrying first rotating element having a first peripheral portion a pitch circle radius corresponding to the first radius and a second Circumferential section with at least one corresponding to the at least one radius has second pitch circle radius, the first radius to form a tensile gap between the inlet gap cylinder and the at least one band is suitable and the at least a second radius to form a gap between the Inlet gap cylinder and the rotating first element guiding at least one band suitable is. The opposite, non-circular, rotating Components of the exit gap can be one exit gap cylinder and one at least comprise a belt-guiding second rotating element, the outlet gap cylinder preferably a first peripheral section with the first radius and one comprises a second circumferential section with the at least one second radius. The at least one belt-guiding second rotating element preferably comprises one first circumferential section with a pitch circle radius corresponding to the first radius and a second peripheral section with at least one of the at least one smaller than the first radius formed second radius corresponding to the second pitch circle radius.

The inlet gap cylinder is preferably no more than one from the outlet gap cylinder Quarter section length of a signature in tabloid format arranged so that in the slowdown device signatures in delta format, tabloid format and Digest format can be edited.

Furthermore, the inlet gap cylinder and the outlet gap cylinder preferably have the same speed profile and the same phase position with respect to a fixed point, e.g. B. the floor.

The inlet gap cylinder and the outlet gap cylinder further preferably comprise each have a plurality of axially spaced disks. The rotating, tape-guiding element also preferably comprise a corresponding plurality of spaced elements, and the band preferably includes one as well corresponding plurality of axially spaced tapes.

According to a third embodiment of the invention, the inlet gap and Exit gap cylinder of the second embodiment by a second pair of rotating, band-leading elements replaced. In this embodiment the Slowdown device can use signatures in delta format, tabloid format and can be edited in digest format without changing the distance between the rotating ones Elements is a quarter of a section length.

The features of the present invention will become apparent in the following description preferred embodiments in connection with the attached, below listed drawings explained in more detail.

Fig. 1

eine Seitenansicht einer ersten Ausführungsform einer erfindungsgemäßen Spalt-zu-Spalt-Verlangsamungsvorrichtung;

Fig. 2

eine Reihe von an ihrer Hinterkante ausgerichteten Signaturen in der in Fig. 1 gezeigten Spalt-zu-Spalt-Verlangsamungsvorrichtung, die zur besseren Darstellung ohne die unteren Spaltscheiben gezeigt ist;

Fig. 3

eine Reihe von an ihrer Vorderkante ausgerichteten Signaturen in der in Fig. 1 gezeigten Spalt-zu-Spalt-Verlangsamungsvorrichtung, die zur besseren Darstellung ohne die unteren Spaltscheiben gezeigt ist;

Fig. 4

die in Fig. 1 gezeigte Spalt-zu-Spalt-Verlangsamungsvorrichtung mit einer Reihe von Signaturen, bei denen die Position des Klappenfalzes zu dem Greifer variiert und die Relativposition der drei Falze dargestellt ist;

Fig. 5

das Geschwindigkeitsprofil der in Fig. 1, 6 und 8 gezeigten Doppelspalt-Verlangsamungsvorrichtungen;

Fig. 6

eine Seitenansicht einer Ausführungsform einer Spalt-zu-Band-Verlangsamungsvorrichtung mit in einer Reihe angeordneten oberen Scheiben;

Fig. 7

eine Seitenansicht einer zweiten Ausführungsform einer Spalt-zu-Band-Verlangsamungsvorrichtung mit versetzt angeordneten oberen Scheiben;

Fig. 8a-h

eine Band-zu-Band-Verlangsamungsvorrichtung mit einer Reihe von an ihrer Vorderkante ausgerichteten Signaturen;

Fig. 9a

eine Draufsicht einer Antriebsanordnung der oberen Scheibenanordnung der in Fig. 7 gezeigten Spalt-zu-Band-Verlangsamungsvorrichtung;

Fig. 9b-d

eine perspektivische Darstellung der Antriebsanordnung von Fig. 9a;

Fig. 10

eine Seitenansicht einer Anordnung aus einer oberen und einer unteren Spalt-zu-Band-Verlangsamungsvorrichtung gemäß Fig. 7;

Fig. 11

eine Seitenansicht einer Band-zu-Band-Verlangsamungsvorrichtung gemäß Fig. 8a-h und eine verfahrbare Leitwalze gemäß einer weiteren Ausführungsform der vorliegenden Erfindung;

Fig. 12a

eine Draufsicht auf einen Abschnitt einer schwenkbaren Leitwalze gemäß einer weiteren Ausführungsform der Erfindung; und

Fig. 12b

eine Seitenansicht der schwenkbaren Leitwalze gemäß Fig. 12a.

Show it:

Fig. 1

a side view of a first embodiment of a gap-to-gap slowing device according to the invention;

Fig. 2

a series of signatures aligned at their trailing edge in the gap-to-gap slowdown device shown in Figure 1, shown without the lower split discs for better illustration;

Fig. 3

a series of signatures aligned at their leading edge in the gap-to-gap slowdown device shown in Figure 1, shown without the lower split discs for better illustration;

Fig. 4

the gap-to-gap slowdown device shown in Figure 1 with a series of signatures in which the position of the flap fold relative to the gripper varies and the relative position of the three folds is shown;

Fig. 5

the speed profile of the double gap decelerators shown in Figures 1, 6 and 8;

Fig. 6

a side view of an embodiment of a gap-to-band slowdown device with top disks arranged in a row;

Fig. 7

a side view of a second embodiment of a gap-to-band slowdown device with offset upper disks;

8a-h

a band-to-band decelerator with a series of signatures aligned on its leading edge;

Fig. 9a

a top view of a drive assembly of the upper disc assembly of the gap-to-tape slowdown device shown in FIG. 7;

9b-d

a perspective view of the drive assembly of Fig. 9a;

Fig. 10

a side view of an arrangement of an upper and a lower gap-to-band slowdown device according to FIG. 7;

Fig. 11

a side view of a belt-to-belt slowdown device according to FIG. 8a-h and a movable guide roller according to a further embodiment of the present invention;

Fig. 12a

a plan view of a portion of a pivotable guide roller according to a further embodiment of the invention; and

Fig. 12b

a side view of the pivotable guide roller according to FIG. 12a.

An inventive device for slowing down signatures by a High speed belt assembly to a downstream, lower one Speed-running belt arrangement to be passed includes one Double-slit arrangement that has a variable speed profile shown in FIG having. Below are three embodiments of a double slit slowdown device describe each essentially the same space take in. The three double-gap slowdown devices are 1) a gap-to-gap slowing device 100 as shown in Fig. 1, 2) around a gap-to-band slowing device 100 ', as shown in Fig. 2, and 3) around a band-to-band decelerator 100 "as shown in Figures 8a-h. In none of these embodiments, according to the invention, when the Length of the signatures transported Settings changes by a Machine operator required. In the case of the gap-to-band device and the band-to-band device are transported even when the thickness changes According to the invention, signatures do not require any changes to the settings.

According to a first embodiment of the present invention, a Slowdown device is provided in which products of any length from Tabloid format over the delta format up to the digest format can be slowed down can be changed without changing the phase setting or other settings have to. In this embodiment, all products are the same route from the Folding cylinders led to the quarter folder.

1 shows a gap-to-gap deceleration device 100 according to a first Embodiment of the invention comprising one of two groups of axially spaced to Axes 4.1 and 4.2 rotating brake discs 4 formed inlet gap 40 and one of two groups of axially spaced brake disks rotating about axes 5.1 and 5.2 5 formed outlet gap 50 comprises. The disks 4 are not of the disks 5 more than a quarter of a section away, d. H. the distance between the axes 4.1 and 5.1 (as well as between axes 4.2 and 5.2) is selected so that a Quarter turn of the disks 4 a predetermined section of a signature from Inlet gap 40 transported to the outlet gap 50. The disks 4 and 5 have the same Rotation frequency.

The brake discs 5, 6 have a "bell-shaped" profile, i. H. the one half of the circumference the disc has a larger radius than the other circumferential half, the second Forms surface section that can be shaped as desired. Accordingly, the column 40 arises and 50 when the opposite large radius sections meet.

FIG. 2 shows how the signatures 1, 2 and. In the gap-to-gap device 100 3 be slowed down, each of the signatures having a different length and the signatures are aligned at their rear edge. FIG. 3 shows how in device 100 the Signatures 1, 2 and 3 are slowed down, with each of the signatures having a different length and the signatures are aligned with the front edge. Fig. 4 shows how the device 100, the signatures 1, 2 and 3 are slowed down, the position of the Flap fold to the gripper varies. 2 to 4, the signature 1 corresponds to one Signature in tabloid format, signature 2 of a signature in delta format and the Signature 3 of a signature in digest format.

Fig. 5 shows the speed profile of the disks 4 and 5, with both simultaneously Brake discs 4 and 5 are rotated. According to this embodiment, the Disks 4, 5 in phase and at the same speed. When entering the Gap 40 or 50 the signature takes over the speed profile of the brake discs. The speed profile can be generated by any mechanism and can be any deceleration / acceleration profile that has a ratio of 1: 1 between the rotation frequency and the section length of a signature in tabloid format guaranteed. If the discs 4 (or 5) as circular discs with a Radius of section with larger radius of bell-shaped disks 4 (or 5) corresponding radius would be a signature in tabloid format during one revolution of the disk 4 (or 5) through the gap 40 (or 50) transported. An advantage of extending the slowdown phase with larger ones Discs and a gradual slowdown profile is that the on the System forces are significantly reduced.

A signature 1 runs at a speed corresponding to the speed of the printing press Initial speed in the first gap. The slowdown value is in the range selectable from 0.1% and 50%. At a printing speed of around 55 km / h (3,000 feet per minute) the speed of the signatures is at 50% Slow down to about 27.5 km / h (1,500 feet per minute) when the signature is reduced leaves the gap 50.

The speed profile of the disks 4, 5 shown in FIG. 5 comprises Acceleration phases 55 and deceleration phases 56. The rotation of the disks 4, 5 is matched in such a way that a signature during the slowdown of the opposite sections with larger radius of the disks 4 and 5 in the resulting gap 40, 50 is detected. Then the brake discs be accelerated again so their speed is the speed of the next corresponds to the incoming signature, there is a space between for this period the opposing disks so that the acceleration of the disks 4, 5 does not affect the speed of the signature.

2 and 3 it is clear that the signatures 1, 2 and 3 in the one shown in FIG. 2 Arrangement and the signatures 2 and 3 in the arrangement shown in Fig. 3 the front Leave gap 40 before the disks 4, 5 have been completely slowed down. thats why the speed of exit of these signatures when they exit the gap 40 is not equal to the speed of the exit belts (not shown). Only on in Gap 50 downstream of the product conveying direction becomes the slowdown process completed. In these embodiments, the distance between columns 40 and 50 should be chosen such that each of the signatures is captured by the gap 50 before it Gap 40 leaves. In this context, it is particularly advantageous if as a distance between the two columns 40, 50 a quarter of the section length of a product in Digest format, the smallest of the signature formats, is selected. The discs 4 can if necessary be axially offset with respect to the discs 5, so that the column can be arranged closer together.

In the arrangement shown in FIG. 2, the phase position of the disks 4, 5 must be relative of the signatures only for the longest of the signatures (here for the signature in tabloid format) can be set. As soon as the phase position for signatures in tabloid format is set, no further setting changes are necessary for other signature formats. Based 2, 3 and 4 it is clear that the device 100 functions independently of whether the signatures on the leading edge, the trailing edge or in the position of the fold break are aligned.

In Fig. 7 is a gap-to-band slowing device 100 'according to a second one Embodiment of the present invention shown using similar components with similar reference numerals as in Fig. 1 are designated. An advantage of this Device versus slit-to-slit slowing device 100 is that no settings are made for products of different thickness have to. As with device 100, there are none in device 100 ' Phase settings for products of different formats and different Folding combinations necessary.

7 is a side view of a gap-to-band device 100 '. A group in front Disks 4 'and a group of rear disks 5' are axially offset from one another arranged so that the two disc groups, as shown in Fig. 7, closer can be arranged together and overlapping. Timing belts 8 are provided, which rotate around gear wheels 9.1, 9.2, with the disks 4 'and 5' each forming a group made of timing belts and gears. The one shown in Fig. 5 Speed profile also applies to the pulleys 4 'and 5' and for the toothed belt 8 and the gears 9.1, 9.2. As with device 100 described above, this can Speed profile can be generated by any mechanism. Only one The prerequisite is that the ratio between the rotation frequency and the Section length is 1: 1.

The disk groups 4 'and 5' are no further than one in the signature transport direction Quarter of the section length apart. The gears 9.1, 9.2 are outside of the rotation range of the upper disks 4 'and 5' arranged such that the Toothed belt 8 partially wraps around the two disks 4 'and 5', while between the Sprockets 9.1, 9.2 and the two disks 4 ', 5' a distance is provided. The Pitch circle diameter of the gears 9.1, 9.2 essentially corresponds to the diameter the upper disks 4 ', 5'. A signature 40 runs in between the disks 4 ', 5' and the toothed belt 8 formed a gap. Through the S-shaped, looping leadership of the Toothed belt 8 against the disks 4 ', 5' creates a flexible gap, so that for signatures different thicknesses, no adjustment work is necessary.

Another advantage of the device 100 'is that the upper disks 4', 5 ' can be formed with a smaller diameter through the use of toothed belts 8, allowing slower deceleration than the gap-to-gap device 100th

In the device 100 'shown in FIG. 7, there is 4' for each disk and 5 'for each disk Toothed belt 8 (with assigned gears 9.1, 9.2) is provided because the pulleys 4 'and 5 'are arranged offset from one another. However, if smaller panes are used (which allow the disks 4 ', 5' to be arranged in a line) for each pair of disks 4 ', 5' arranged in a line, only a single toothed belt 8 is provided 6 as shown in FIG. The size of the disks 4 ', 5' is that for the Device 100 'predetermined desired rate of deceleration. Independent of Deceleration rate is the distance between the disks 4 'and 5' in Signature conveying direction not greater than a quarter of the section length.

The upper disks 4 ', 5' are preferably made to be lightweight To keep inertia as low as possible. In particular, the disks 4 ', 5' preferably made of aluminum, and the rear half of each disc is in Essentially elliptical. Similar to the smaller diameter sections of the Disks 4, 5 create the elliptical sections of the disks 4 ', 5' sufficiently Gap to move a signature to a position without being affected by accelerating the pulleys 4 ', 5' and the belt 8.

In addition, the elliptical section reduces or eliminates the occurrence of the Timing belt impulses acting on a less continuous surface such as B. would arise in the bell-shaped disks 4, 5. The discs 4, 5 of the Device 100 shown in FIG. 1 can of course also through the disks 4 ', 5 'to be replaced.

Control over the signatures entering the gap-to-band device 100 ' is by means of a guide roller 90 with associated belts or belts 91, 92 guaranteed. The belt 92 rotates freely about the axis 4.2 '. The guide roll 90 is related the gap between the discs 5 'and the belt 8 positioned so that the Leading edge of the signature in the open space between the band 91 and the Gap is moved. Immediately before the deceleration process is about 20 mm the signature 40 in the high-speed belts 91. A light one Difference in speed between the belts 91 and the gap can by a The signature 40 bulges on the intermediate space between the guide roller 90 and the nip be compensated.

The control over the signatures emerging from the device 100 'is carried out by means of a Guide roller 6 with associated belts 81, 82 guaranteed. The belt 82 rotates freely the axis 5.2 '. The guide roller 6 is positioned such that it the front edge of the Signature 40 captured when about 20 mm of signature 40 from brake disc 4 ' are recorded. The guide roller 6 is on a linearly movable carriage or a (not ) eccentric attached, so that their position on products of different lengths can be customized. Preferred embodiments for this Positioning mechanisms are explained in more detail below.

The gap-to-gap slowing device 100 can be used to control incoming and outgoing signatures similar procedures are used.

Figures 8a-h show a third embodiment of the present invention with a band-to-band slowdown device 100 ", with a complete in eight positions Transport cycle for products of different lengths through the device 100 " is shown. The band-to-band slowdown device 100 "is constructed similarly like the gap-to-band device 100 ', only the elliptical discs 4', 5 'were cut arranged in a line, toothed belt 81 leading elliptical gears 4 ", 5" replaced. Similar to the disks 4 ', 5', the elliptical section of the gear wheels 4 " and 5 "enough space so that the signature is unaffected by the Acceleration of the belts 8, 81 can be brought into position. Timing belts 81 and gears 4 ", 5" have the same pitch circle diameter as the lower gears 9.1, 9.2 and the timing belt 8. In this way the signature when slowing down captured between a number of timing belts so that they can advantageously during of slowing down. In this embodiment there is also none Need to maintain a quarter section spacing since the signatures between bands 8 and 81 remain recorded. The distance between the Gears 4 "and 5" can therefore be more than a quarter of the section length of the signatures be. In this embodiment, the gear wheel 4 ″ can be moved so that the belts 81 can be moved to a different position to break a signature into the Device 100 "without speed difference. As in Fig. 8a-h is shown, the guide roller 6 'depending on the format of the signature between two Positions movable, the guide roller 6 'in position 6.1 for signatures in digest format and in position 6.2 is suitable for signatures in tabloid and delta format. In the special embodiment shown in FIG. 8, the axes of the gear wheels 4 ", 5 "at a distance of 175 mm and the axes of the gears 9.1, 9.2 in one Distance of 275 mm to each other. As shown in Fig. 8d, the Guide roller 6 'after half a cycle in its front position 6.1 the first 20 mm of Front edge of a signature in digest format and in its rear position 6.2 the first 20 mm of the leading edge of a signature in delta format. As in Fig. 8h at the beginning of the Next cycle is shown, the guide roller 90 detects products that are on its rear edge are aligned, the last 20 mm of a trailing edge of a signature in digest, delta or tabloid format.

9a and 10 show a top view and side view of a drive for the upper one Gap. Figures 9b, 9c and 9d are perspective views of that shown in Figure 9a Drive. The gear train for the lower gear is similar to the upper gear train formed, however, the elliptical anti-gears and the elliptical driven gears are arranged in reverse order. In each of the Devices 100, 100 'and 100 "can use the same type of drive mechanism become. As shown in Fig. 9a, the brake discs 4 (or the discs 4 'or the gears 4 ") driven by a first drive mechanism 400, and the Brake discs 5 (or the discs 5 'or the gears 5 ") are replaced by a second Anti-secondary mechanism 500 driven, which in its construction essentially with the first drive mechanism 400 is identical. Each of those shown in Figures 9a-d Drive mechanisms 400 or 500 will change speed over one first elliptical gear pair 700, 800 and a second elliptical gear pair 109, 110 reached. A drive shaft 900 rotates at a constant speed, the elliptical drive gears 110, 800 a variable speed on the driven gears 109, 700 transmits. The driven gears 700, 109 rotate about a drive train 910. The brake disks 4, 5 (or the disks 4 ', 5' or the gears 4 ", 5") are to minimize the inertial forces directly with the Drive train 910 connected. Both the first elliptical gear pair 700, 800 and the second elliptical gear pair 109, 110 are connected to a torsion spring 120. The torsion spring 120 is on a gear axis 130 of the second elliptical gear 110 attached and wound on the element 140. The torsion spring 120 acts both gear pairs with a preload. The described idler gear arrangement prevents the meshing of the elliptical gear pairs during load reversal is interrupted. Each of the brake disc or gear groups is preferably from a respective gear mechanism driven to overload the elliptical Avoid gear pairs.

Figure 10 is a side view of an upper and a lower gap-to-belt decelerator 100 'with the associated drive mechanisms. The Disks 4 ', 5' and the toothed wheels 9.1, 9.2 of the toothed belt each require different pitch circle diameters for different section lengths. This Changing the pitch circle diameter requires repositioning the drive. Around to enable this, the two outer gears 510 and 516 can be moved laterally, so that a change in height between the upper and lower gear rows for the Disks 4 ', 5' and the gears 9.1, 9.2 is made possible. The lower one Slowdown device is driven via gear 507 '. The upper Slowdown device is driven via gear 513. An engine 1800 drives gears 507 ', 513 through a series of gears 502-506. Through the Position of the main drive gear 502 between the upper and lower Slowing down the forces caused by inertia on Drive input minimized. In Fig. 10 it is shown how a continuous product stream of of the deflection device 190 is deflected in such a way that the products alternate to the lower and upper decelerators 100, 100 '. The transport of the products in the upper deceleration device proceeds accordingly 180 ° out of phase for transporting the products in the lower one Slowdown device so that the forces caused by inertia cancel each other out.

Starting from the drive input 513, the gears 9.1, 9.2 and the disks 4 ', 5 'of the top decelerator via gears 507-512, 514-518 driven. Similarly, the gears 9.1, 9.2 and the disks 4 ', 5' of the lower deceleration device starting from the drive input 507 'over the Gear wheels 508'-518 'driven. Even if elliptical above with reference to FIGS. 9a and 9b Gears for generating the variable speed profile of the Slow mechanisms are described, other mechanisms for Generation of the variable speed profile can be used. Two interacting eccentric gears can e.g. B. a similar one Generate speed profile and the elliptical gear pair of Fig. 9a and 9b directly replace. This applies to elliptical gears with a gear ratio of 1.3 or less is. (This value corresponds to the preferred gear ratio for the in Fig. 1, 6 and 8.) However, other similarly acting devices can also be used Drive mechanisms are used.

11 shows a mechanism for transferring a signature from the Decelerator 100 "to those running at low speed Exit belts 93, 94. In this embodiment, a stationary exit guide roller 6 and belts 93 in conjunction with one at low speed running, movable conveyor belt 200 used. The conveyor belt 200 includes a Pair of elliptically shaped, movable drive gears 210. Fig. 11 shows the Mechanism at a time when signature 40 is slowing down has just ended. The shortest product (in digest format) is about 20 mm beyond the guide roller 6. All other products (in delta format and in tabloid format) are still far beyond the guide roller 6. In the position shown in FIG. 11 due to the position of the elliptical gears 210, the signatures are not Bands 200 captured. As the elliptical gears rotate, the bands become 200 raised so that they contact the exit guide roller 6. The gears 210 (and the movable belts 200) are at the same frequency as the gear wheels 9.1, 9.2, 4 ", 5 "of device 100" driven. However, the movable belt is turned by 180 ° out of phase with the device 100 ". The signatures are not thereby detected by the device 100 "when it is between the guide roller 6 and the belts 200 are detected, and on the other hand not between the guide roller 6 and the belts 200 if they are detected by the device 100 ″ movable belts 200 the speed of the signature during the Does not affect the slowdown process, on the other hand, device 100 "can Signatures speed does not affect if this controls the device through the belts 200 and the guide roller 6. Here too are products different page number or length, no setting changes necessary.

FIGS. 12a and 12b show a further device for transferring a signature from the Decelerator 100 "to the belts running at low speed 93, 94. FIG. 12a shows a top view and FIG. 12b shows a side view of a Transfer mechanism 300. In Fig. 12a it is shown how the exit guide roller 6 on a Eccentric 220 is pivotable. The eccentric 220 is designed in such a way that the Guide roller 6 can assume three predetermined positions. This is about a Reduction ratio of 2: 1 over gears 230, 240 achieved with a Three position air cylinder 250 and a connector 260 are connected. The upper conveyor belts 93, which run around the guide roller 6 at low speed, are brought into a different position when the guide roller 6 moves. The three positions of the guide roller 6 are the front position 6.3 (for signatures in the Digest format), the upper position 6.1 (for signatures in tabloid format) and the rear Position 6.2 (for signatures in delta format). The rear guide roller 7 and (not shown) assigned tapes are stationary and positioned in such a way that they have a signature in the Capture the tabloid format approximately 20 mm behind its front edge (while the tape 93 is lifted from the signature by the guide roller 6). This property enables one Automation of the exit guide roller 6.

Even if the embodiments shown in FIGS. 11 and 12 in connection with the Band-to-Band Slowdown Device 100 "have been described in in the same way in the gap-to-gap slowdown device 100 and the gap-to-band slowdown device 100 'can be used.

According to a further embodiment of the present invention, the double slit slowdown devices 100, 100 ', 100 "according to the invention in one arranged upstream of the deflection mechanism, which is the number of parts reduced per folder.

In a further embodiment of the present invention, the are movable Conveyor belts 270 and the guide rollers before and after the invention Double slit slowdown devices arranged to bulge the signatures by reducing speed differences.

List of reference numbers

1

signature

2

signature

3

signature

4,4 '

brake discs

4 '

gear

4.1

axis

4.2

axis

5.5 '

brake discs

5 '

gear

5.1

axis

5.2

axis

6.6 '

guide roll

6.1

Gear Position

6.2

Gear Position

8th

toothed belt

9.1

gear

9.2

gear

40

front gap / signature

50

rear gap

55

acceleration phase

56

deceleration phase

81

tape

82

tape

90

guide roll

91

tape

92

tape

93

tape

94

tape

100

Gap-to-gap decelerator / elliptical gear pair

100 '

Gap-to-band decelerator

100 '

Band-to-band decelerator

109

gear

110

gear

120

torsion spring

130

gear axis

140

element

190

deflecting mechanism

200

conveyor belt

220

eccentric

230, 240

gears

250

Air Cylinder

260

connecting element

300

Signatures boom

400

first drive mechanism

500

second drive mechanism

502-506

gears

507 '

gear

507-512

gears

508'-518 '

gears

514-518

gears

700

gear

800

gear

900

drive shaft

910

powertrain

1800

engine

Claims (23)

1. Device for decelerating signatures (1,2, 3), the device comprising an entrance nip (40) for receiving a signature (1, 2, 3) from an upstream device at a first transport speed and for decelerating the transport speed of the signatures (1, 2, 3) to a first reduced transport speed, the entrance nip (40) having surfaces contacting the signature (1, 2, 3) and formed by a pair of opposing non-circular rotating components (4, 4'), each of which comprises a first surface section forming a nip (40) between the components (4,4') and a second surface section forming a gap between the components (4, 4') and is rotatable at a variable velocity profile which provides deceleration of the components (4, 4') when the nip (40) is formed and acceleration of the components (4, 4') when the gap is formed, and an exit nip (50) for receiving the signature (1, 2, 3) from the entrance nip (40) and further decelerating the transport speed of the signature to a second reduced transport speed, the exit nip (50) having surfaces contacting the signature (1, 2, 3),
   characterized in that
   these surfaces are formed by a pair of opposing non-circular rotating components (5, 5'), each of which comprises a first surface section forming a nip (50) between the components (5, 5') and a second surface section forming a gap between the components (5, 5') and is rotatable at a variable velocity profile which provides deceleration (5, 5') when the nip (50) is formed and acceleration of the components (4, 4') when the gap is formed.
2. Device according to claim 1,
   characterized in that the opposing non-circular rotating components (4, 4') of the entrance nip (40) include a pair of opposing cylinders, and each cylinder includes a first circumferential section having a first radius suitable to form a nip (40) between the opposing cylinders and a second circumferential section having at least one second radius smaller than the first radius and suitable to form a gap between the cylinders, and that the opposing non-circular rotating components (5, 5') of the exit nip (50) include a pair of opposing cylinders, and each cylinder includes a first circumferential section having a first radius suitable to form a nip (50) between the opposing cylinders and a second circumferential section having at least one second radius smaller than the first radius and suitable to form a gap between the cylinders.
3. Device according to claim 2,
   characterized in that the first circumferential section is shaped like a circular arc and the second circumferential section is shaped like an elliptical arc.
4. Device according to claim 2 or 3,
   characterized in that at least one of the cylinders (4, 4') of the entrance nip (40) and at least one of the cylinders (5, 5') of the exit nip (50) comprises a plurality of disks that are axially spaced-apart.
5. Device according to one of claims 2 to 4,
   characterized in that the spacing between the pair of opposing cylinders (4, 4') of the entrance nip (40) and the pair of opposing cylinders (5, 5') of the exit nip (50) is one quarter of the cut-off of a tabloid signature.
6. Device according to one of claims 2 to 4,
   characterized in that the spacing between the pair of opposing cylinders (4, 4') of the entrance nip (40) and the pair of cylinders (5, 5') of the exit nip (50) is less than one quarter of the cut-off of a tabloid signature.
7. Device according to claim 1,
   characterized in that the opposing non-circular rotating components (4', 9.2) of the entrance nip (40) comprise an entrance nip cylinder (4') and at least one first rotating element (9.2) guiding at least one belt (8), that the entrance nip cylinder (4') has a first circumferential section having a first radius and a second circumferential section having at least one second radius,
   that the first rotating element (9.2) guiding at least one belt (8) has a first circumferential section with a pitch radius corresponding to the first radius and a second circumferential section with at least one second pitch radius corresponding to the at least one radius, the first radius suitable to form a nip between the entrance nip cylinder (4') and the at least one belt (8) and the at least one second radius suitable to form a gap between the entrance nip cylinder (4') and the rotating first element guiding at least one belt (8),
   that the opposing non-circular rotating components of the exit nip (50) comprise an exit nip cylinder (5') and at least one second rotating element (9.1) guiding a belt (8), that the exit nip cylinder (5') has a first circumferential section having the first radius and a second circumferential section having the at least one second radius,
   that the second rotating element (9.1) guiding at least one belt (8) has a first circumferential section with a pitch radius corresponding to the first radius and a first circumferential section with at least one second pitch radius corresponding to the at least one second radius that is smaller than the first radius.
8. Device according to claim 7,
   characterized in that the spacing between the entrance nip cylinder (4') and the exit nip cylinder (5') is one quarter of the cut-off of a tabloid signature.
9. Device according to claim 7,
   characterized in that the spacing between the entrance nip cylinder (4') and the exit nip cylinder (5') is less than one quarter of the cut-off of a tabloid signature.
10. Device according to one of claims 7 to 9,
    characterized in that the entrance nip cylinder (4') and the first rotating element (9.2) guiding at least one belt form a first S-shaped nip, and the exit nip cylinder (5') and the second rotating element (9.1) guiding at least one belt form a second S-shaped nip.
11. Device according to one of claims 7 to 10,
    characterized in that the at least one belt (8) is guided by both the first rotating belt-guiding element (9.2) and the second rotating belt-guiding element (9.1).
12. Device according to one of claims 7 to 11,
    characterized in that the first circumferential section of the entrance nip cylinder (4'), of the exit nip cylinder (5'), of the first rotating belt-guiding element (9.2), and of the second rotating belt-guiding element (9.1) is formed as a circular arc and that the second circumferential section of the entrance nip cylinder (4'), of the exit nip cylinder (5'), of the first rotating belt-guiding element (9.2), and of the second rotating belt-guiding element (9.1) is formed as an elliptical arc.
13. Device according to one of claims 7 to 12,
    characterized in that the first and the second rotating belt-guiding elements (9.1, 9.2) are sprockets.
14. Device according to one of claims 7 to 12,
    characterized in that the first and the second rotating belt-guiding elements (9.1, 9.2) are pulleys.
15. Device according to one of claims 7 to 14,
    characterized in that the first radius of the entrance nip cylinder (4') corresponds to the first radius of the exit nip cylinder (5').
16. Device according to claim 1,
    characterized in that the opposing non-circular rotating components of the entrance nip (40) comprise opposing first and second rotating belt-guiding elements (4", 9.2) with a first and at least one second belt (8, 81) respectively arranged thereon, each of the first and second rotating belt-guiding elements (4", 5", 9.1, 9.2) comprising a respective first circumferential section having a first pitch radius and a second circumferential section having at least one further pitch radius smaller than the first pitch radius, the first pitch radius suitable to form a nip between the first and the second rotating belt-guiding elements (4", 9.2) and the second pitch radius suitable to form a gap between the first and second rotating belt-guiding elements (4", 9.2) and
    that the opposing non-circular rotating components of the exit nip (50) comprise opposing third and forth rotating belt-guiding elements (5", 9.1) each guiding a respective one of the first and second belts (8, 81) and having a respective first circumferential section with the first pitch radius and a second circumferential section with the at least one second pitch radius.
17. Device according to claim 16,
    characterized in that the first circumferential sections of the first, second, third, and forth rotating belt-guiding elements (4", 5", 9.1, 9.2) are shaped like a circular arc and that the second circumferential sections of the first, second, third, and forth rotating belt-guiding elements are shaped like an elliptical arc.
18. Device according to claim 16 or 17,
    characterized in that the first, second, third, and forth rotating belt-guiding elements (4", 5", 9.1, 9.2) are sprockets.
19. Device according to claim 16 or 17,
    characterized in that the first, second, third, and forth rotating belt-guiding elements (4", 5", 9.1, 9.2) are pulleys.
20. Device according to one of claims 1, 4 to 11, 13 to 16, 18, or 19,
    characterized in that the first surface section is of circular shape and the second surface section is of any shape.
21. Device according to claim 15,
    characterized in that the spacing between the first belt-guiding element (9.2) and the second belt-guiding element (9.1) is more than one quarter of the cut-off of a tabloid signature.
22. Folder,
    characterized by
    a device according to one of the preceding claims.
23. Printing press, in particular web-fed rotary printing press,
    characterized by
    a device according to one of claims 1 to 21 or a folder according to claim 22.

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