US3889940A

US3889940A - Device for adjustment of oscillation amplitude on zigzag folding apparatus

Info

Publication number: US3889940A
Application number: US378009A
Authority: US
Inventors: Hans Jakob
Original assignee: Maschinenfabrik Goebel GmbH
Current assignee: Maschinenfabrik Goebel GmbH
Priority date: 1972-07-10
Filing date: 1973-07-10
Publication date: 1975-06-17
Anticipated expiration: 1992-06-17
Also published as: CH548934A; DE2233879B2; DE2233879C3; GB1417600A; NL176770B; DE2233879A1; NL7309472A; NL176770C; JPS5545465B2; JPS4952021A; FR2192545A5; IT989486B

Abstract

The reciprocating guide channels of zigzag folding apparatus for folding webs of paper or other material, provided outwardly of the opposite side edges of the web, are operatively interconnected so as to be driven together. Both guide channels may be quickly and positively adjusted together as a unit to accommodate varying form widths. The cams provided for the guide channels at both sides of the web are shifted together upon a loosening thereof from their respective drive shafts. A positive adjusted position is assured by means of cooperating roughened surfaces at the joint between each cam and their respective drive shafts.

Description

United States Patent 11 1 Jakob June 17, 1975 54] DEVICE FOR ADJUSTMENT OF 3,143,895 8/1964 Robie 74/214 OSCILLATION AMPLITUDE ON ZIGZAG FOREIGN PATENTS OR APPLICATIONS FOLDING APPARATUS 894.791 4/1962 United Kingdom 270/79 Inventor:

Germany Assignee: Maschinenfabrik Goebel GmbH, Darmstadt, Germany Filed: July 10, 1973 Appl. No.: 378,009

Foreign Application Priority Data July 10, 1972 References Cited UNITED STATES PATENTS Hans Jakob, Darmstadt-Eberstadt,

Germany 2233879 Truslow et a1. 270/79 Primary ExaminerRobert Michell Assistant Examiner--A. Heinz Attorney, Agent, or Firm-Watson, Cole, Grindle & Watson [57] ABSTRACT The reciprocating guide channels of zigzag folding apparatus for folding webs of paper or other material, provided outwardly of the opposite side edges of the web, are operatively interconnected so as to be driven together. Both guide channels may be quickly and positively adjusted together as a unit to accommodate varying form widths. The cams provided for the guide channels at both sides of the web are shifted together upon a loosening thereof from their respective drive shafts. A positive adjusted position is assured by means of cooperating roughened surfaces at the joint between each cam and their respective drive shafts.

4 Claims, 4 Drawing Figures PATENTEDJUN17 197s 3.889.940

SHEET DEVICE FOR ADJUSTMENT F OSCILLATION AMPLITUDE 0N ZIGZAG FOLDING APPARATUS The invention relates to a device for adjusting the oscillation amplitude of reciprocating guide channels on zigzag folding apparatus for webs of paper or other material.

Known folding apparatus for zigzag folding of webs of paper or other materials are normally connected directly to a printing machine, i.e., a printer for the production of forms from webs of indeterminant length. These folding apparatus fold a printed web of paper or other material so that the web can be bent along lines of perforations, disposed crosswise to the direction of travel. In this way a zigzag stack can be formed so that the individual parts of the web between the perforations are superimposed.

The perforations which extend crosswise to the direction of travel of the Web are generally applied in such a way that the imprint made on the web during the printing operation is located between two transverse lines of perforations. If imprints of different sizes are made, the transverse lines of perforations are arranged at a different prescribed distance from one another. Consequently, the stack formed at the output of the zigzag folding apparatus likewise presents different external dimensions. It is therefore necessary to correspondingly adapt the zigzag folding apparatus to the particular spacing of the transverse perforation lines or to the particular imprint size. The folding apparatus must therefore be adjustable according to the format desired during a particular operation.

Such a prior art adjustable folding apparatus is disclosed in German Pat. No. 1,070,010 commonly owned herewith. Disclosed therein is a folding apparatus in which a web of paper or the like to be folded is delivered by means of a movable pocket-like hopper, or a plurality of such hoppers, to the actual folding station. Movement of the hopper is effected by means of cams which may be shifted to adapt to different formats to be folded. Such known device, however, suffers from the drawback of permitting only one specific working speed. If such speed is exceeded, the web to be folded may deviate, for example, from its predetermined path, or there may be other undesired occurrences, so that a regular stack cannot effectively be formed.

With the high performances normally expected today, and therewith the high speeds of machines that produce forms of indeterminant length, it is necessary to adapt the folding apparatus for zigzag folding so as to be connected to follow the printers which also operate at high speeds. In devices known thus far, the printing apparatus can be driven at a relatively high speed, although such speed cannot be fully exploited since the following folding apparatus does not permit it. Accordingly, this requires the printer to be run at speeds producing a lower output.

It should be noted that the reason for the lower performance of the zigzag folding apparatus as compared to that of the printer is due to inaccurate guiding of the web of paper or the like to be folded since the elements utilized in the guidance of the web are not sufficiently sensitive to permit adjustment.

The present invention is therefore addressed to the problem of avoiding the drawbacks of prior art machines known in this field. A device is therefore provided making it possible to adjust the elements used in guiding the paper web with much greater accuracy and sensitivity than was heretofore made possible. The invention solves this problem in that the cams corresponding to the number of reciprocating elements of the guide channel that control such elements and are displaceable with reference to their drive shafts, are disposed at either edge of the web to be folded and are interconnected in a form-locking manner to their drive shafts, in one or more predetermined positions. It is advantageous that the cams that control the various elements of the paper guide channel be provided with noses which extend into corresponding grooves provided on their drive shafts.

In accordance with another aspect of the invention it is possible that the cams controlling the various elements of the paper guide channel be joined to one structural member on one side of the web. Also, the surfaces opposing one another in the displacement of the cams with reference to their drive shafts may be corrugated. It is also possible, however, to provide such opposed areas with a roughened surface. In accordance with a further aspect of the invention, the displacement of the cam with reference to the drive shaft may be made adjustable by means of one or more side plates, each controlled by an additional cam.

The invention makes it possible to precisely guide the web to be folded, and to render the cams, that move the machine elements in a reciprocating motion and guide the web to be folded, adjustable on both sides of the web to the same desired degree during the particular operation. According to the invention there is the assurance that this eccentricity once set will be sustained exactly during the entire operation of the machine. Thus, high operating speed is made possible for the entire folding apparatus, an'd the printer connected upstream can therefore be run at' high speeds. Because of the present invention, it is'not necessary to run the printer at a reduced outputJ-The folding apparatus can be speeded up, so that the rate of the printer or its output is no longer limited. In addition, the present invention offers a simple opportunity for regulation of the cams, i.e., to convert the folding apparatus from one format to another. This regulation requires only a brief adjustment time and thereby involves only short stoppages for changeover of the entire machine from one format to another. This advantage of the invention allows a further increase in output of both printer and folder.

An embodiment of the present invention is shown in the drawings wherein:

FIG. 1 is a side elevational view, partly in section, of a device in a folding apparatus according to the invention, taken along line l] of FIG. 2;

FIG. 2 is a sectional view of the device according to the invention taken along line 2-2 of FIG. 1 and rotated FIG. 3 is a view of the adjustment means taken along line 3-3 of FIG. 2; and

FIG. 4 is an enlarged view at location 4 of FIG. 2.

A web 1 of paper or the like, having spaced lines of perforations thereon extending transversely to its direction of travel, and comprising one or more layers, is moved downwardly from the web conveying device into the folding apparatus for folding in a manner similar to that described in the aforementioned German patent. Web 1 is generally shown in phantom lines in FIG. 1, and is bent in the area of one of its transverse perforations, e.g., at points 2, by means of a beater 3, to thereby form a zigzag stack 4. For this purpose web 1 passes through one or more pocket-like hoppers or guide channel devices 5 or 5'. The motion of these hoppers is produced by drive rods 6, 6' or 7, 7, in turn moved by

cams

8, 8 and 9, 9'. The tilting of hoppers 5 and 5' occurs because hopper 5 is pivoted about a stationary point 10 on the machine frame by means of drive rods 6 and 6', whereas hopper 5' is pivoted about a pin 11 located on hopper 5 by means of drive rods 7.

and 7' opposite hopper 5. To adjust for different formats,

carns

8, 8 and 9, 9 are displaceable in

slots

12, 12 and can be fixed in position by bolts 13, 13'.

The drive of

cams

8 and 9 is effected by means of a shaft l4located in the machine, the shaft having gear teeth thereon. Shaft 14 rotates at an rpm that corresponds to the rpm of the printer.-Gear 15 engages a gear 16 fixed on a shaft 17. Shaft 17 is mounted for rotation on machine frame 18 and has an intermediate strip 19 mounted thereon along with

cams

8 and 9 by means of a bolt 13.

The drive of cams 8 and 9' also is effected by shaft 17, a gear 20 being fixedly mounted thereon and cooperating with a gear 21 mounted on a shaft 22. Shaft 22 is mounted for rotation on

machine frame

18 or 18 and has a gear 23 fixedly mounted on its opposite end. Gear 23 cooperates with a gear 24 fixedly mounted on a shaft 25 which is mounted for rotation on machine frame 18'. Shaft 25 is similar to shaft 17 in that it also has an intermediate strip 19 mounted thereon along with cams 8' and 9' by means of a bolt 13'.

The setting of

cams

8, 9 and 8', 9' is the same so that, for the sake of simplicity, only the setting of

cams

8 and 9 will be described.

For adjustment, shaft 17 has a flange 27 in which a I groove is provided having surfaces 28 and 29 (see FIG.

3). Strip 19 is located in-the groove for sliding movement in a lengthwise direction, and is fixed therein by means of

bolts

30 and 31 engaging with flange 27. The side of strip 19 facing toward cam 8 is provided with corrugations 32 extending perpendicular to

walls

28, 29 of the groove.

A nose 33 (see FIGS. 2 and 4) of cam 8 extends into the groove of flange 27 and has teeth 34 thereon corresponding to teeth 32 of strip 19. Upon loosening of bolt 13 it is possible to move

cams

8 and 9 away from shaft 17 in the direction indicated by arrow A in FIG. 1, to such an extent that

teeth

32 and 34 will be moved out of engagement. Nose 33 of cam 8 can then be shifted (in the direction indicated by arrow D in FIG. 1) in the groove defined by

surfaces

28 and 29 until the desired setting of

cam

8 or 9 is reached. Thereafter, bolt 13 is again tightened, whereby

teeth

32 and 34 come into engagement in another relative position than before the adjustment. Obviously, the distribution of

teeth

32 and 34 can be finer than that illustrated in FIG. 4.

For precise adjustment, the number of teeth per inch on both cam 8 and strip 19 is exactly the same as the number of teeth per inch on cam 8' and strip 19'. This ensures that both cam 8 and cam 8 can be reset 'by exactly the same amount. There is likewise assurance that the adjusted measure will then be retained if

cams

8 and 9 or 8' and 9' are not applied with exactly the same pressure against their respective shafts as a consequence of slight irregularities in the tightening bolts 13 and 13'. Any slight irregularity is thus prevented in the setting of

cams

8 and 9 which would cause slantwise guidance, for example, of web 1, to yield a stack which would later be unusable.

In the same way, a movement between the cams and the'shafts that drive them is prevented, so that the selected setting will not be changed by inertial forces act ing on

cams

8, 9, 8' and 9' in a different and undesirable manner. Further, the torque transferred from

shafts

17 or 25 to

cams

8, 8 and 9, 9 is transferred not only in a force-locking manner but also form-locking by means of

noses

33, 33 and the grooves formed by

surfaces

28 and 29 or 28 and 29'. This arrangement likewise'provides that, with the high inertial forces occurring at high running speeds on

hoppers

5 and 5, changes in the selected setting are avoided. The necessary torque for movement of the hoppers is therefore acceptably transferred.

For rapid and uniform setting of

cams

8 and 9 or 8' and 9' a hollow shaft 35 is provided on which additional earns 36 and 36' are guided so as to be axially displaceable in the direction of arrows A and B. Aside plate 37 is rotatably mounted on cam 36 which, in the end setting to theleft of cam 36 as in FIG. 2, engages a circular recess 38 of a'plate 39 mounted on cam 9. In addition, in theleft end settingof cam 36, an end switch 40 is actuated which, during engagement of plate 37 in recess 38, stops the main drive of the machine.

A handle 41 on shaft 35 permits it and cam 36 to be pivoted. As shown in FIG. 1, movement of handle 41 in the direction of arrow C causes a movement of side plate 37 in the direction of

arrow D. Cams

8 and 9 may therefore be shifted with respect to strip 19 after bolt 13 is loosened.

Similarly, movement of handle 41 turns cam 36' so as to move side plate 37 andshift plate 39' and earns 8, 9 with respect to strip 19' after bolt 13' is loosened. An end switch 40 similar to switch 40 is actuated in the right end position of cam 36' to also stop the main drive of the machine.

Since feather keys 42 and 42' which transmit the torque from shaft 35 to

cams

36 and 36 are mutually aligned in their

respective grooves

43 and 43, it is as sured that with actuation of handle 41,

cams

36 and 36 and therewith side plates 37 and 37' and earns 8, 9 and 8' 9' respectively will be quickly adjusted by exactly the same amount. When

cams

8, 9 and 8', 9' are set and bolts 13 and 13' respectively are again tightened, cam 36 shown in FIG. 2 will be shifted to the right in the direction of arrow A, and cam 36 will be shifted to the left in the direction of arrow B, in their respective inoperative positions.

Cams

8, 9 and 8', 9, as driven by their

respective shafts

17 and 25, can therefore rotate while the end switch 40 or 40' restarts the main drive of the machine along with that of shaft 14. During the running of the machine earns 36 and 36 are in an inoperative position.

Obviously, many modifications and variations of the present invention are made possible in the light of the above teachings. For example, cams 9 and 9' which control hopper 5 can be disposed on another side of the machine with respect to the entrance of web 1 into the folding apparatus as compared to cams 8 and 8' which control hopper 5'. It is also possible to dispose

rods

6 and 7 or 6 and 7 on

cams

8 and 9 or 8 and 9' which, during assembly of the folding apparatus, may be interconnected for example by bolts.

Cams

8 and 9 or 8' and 9 can, however, as shown in the described embodiment, consist of a single structural part. It is also within the scope of the invention to provide a rough surface rather than

teeth

32, 34 for the contacting surfaces of strips 19, 19' and cams 8, 8'. If

cams

8, 8 and cams 9, 9' are on different sides with reference to web 1, obviously

cams

9 and 9 must also be provided with noses which have ridges or a rough surface and which extend into grooves provided on the shafts which drive them.

It is likewise possible that a folding apparatus with the device of the invention may be utilized without upstream connection of a'printer that prints the forms, e.g., for folding a web of paper or the like, rolling off from a roll.

It is also within the scope of the invention to provide one, three or more hoppers instead of the two shown in the drawings, namely, the reciprocating and swinging guide channel for the web constituted by hoppers S and 5'. In such instance, each hopper would be moved by a cam associated with it or by a pair on either side of the edges of the web to be folded. Also, because of the present invention, there would be an advantageous possibility for adjustment of the reciprocating and swinging guide channel or channels and an exact adjustment and retention of the amplitude or amplitudes of their oscillation.

It is therefore to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described.

What is claimed is:

1. In a folding apparatus for printing machines including reciprocating guide channel devices for delivering a web of paper or other material downwardly from a web conveyor device in Zigzag folds, driving means for each guide channel device being provided at opposite side edges of the web, said driving means including rotatable cams supporting each said guide channel device for reciprocating same upon rotation of the cams, each cam being mounted on a drive shaft, gear means operatively interconnecting the drive shafts to effect synchronous rotation of the cams; drive means in operative engagement with at least one of said drive shafts; means connected with said guide channel devices for quickly and positively adjusting the oscillation amplitude thereof, each of said cams having an elongated opening extending therethrough, fastening means extending through said openings for mounting said cams to their respective drive shafts, a surface of each said cam adjoining a surface of its respective shaft when mounted thereto, the adjoining surfaces between said respective cams and said drive shafts being roughened, said surface of each of said drive shafts being provided with a groove extending parallel to said elongated openings, and each of said cams having nose portions extending into respective ones of said grooves, whereby each said cam may be shifted by actuation of said adjustment means with respect to its respective drive shaft upon a loosening of said fastening means and, upon tightening said fastening means, said roughened surfaces serve to positively maintain the adjusted position of said drive channel devices.

2. The folding apparatus of claim 1 wherein each said guide channel devices comprise at least two guide channels, and each said cam comprising at least two cam elements integrally connected together, each said channel of each said guide channel device being independently connected to a respective one of said cam elements.

3. In the folding apparatus of claim 1 wherein said roughened adjoining surfaces are each corrugated in mating engagement with one another.

4. In the folding apparatus of claim 1 wherein said adjustment means includes rotatable cam members and side plates mounted thereon said plates being engaged with each said cam, respectively, said cam members being operatively interconnected by means of a movable shaft for sliding movement therealong and for rotational movement together therewith to effect synchronous adjustment of said cams with respect to their drive shafts.