US2886973A

US2886973A - Cylinder printing machine

Info

Publication number: US2886973A
Application number: US544268A
Authority: US
Inventors: Schunemann Hans-Bernhard
Original assignee: Schnellpressenfabrik Koenig and Bauer AG
Current assignee: Schnellpressenfabrik Koenig and Bauer AG
Priority date: 1955-06-10
Filing date: 1955-11-01
Publication date: 1959-05-19
Anticipated expiration: 1976-05-19

Description

May 19, 1959 CYLINDER PRINTING MACHINE Fil ed Nov. 1, 1955 4 Sheets-Sheet 1 H. I g mm" Gn-aIIIIIIIIIIU-P-III---I---=j== I May 19, 1959 HANS-BERNHARD S CHUNEMANN CYLINDER PRINTING MACHINE 4 Sheets-SheetZ Filed Nov. 1, 1955 HANS-BERN HARD SCHUNEMANN I May 19,1959

CYLINDER PRINTING MACHINE 4 Sheets-Sheet 3 Filed Nov. 1, 1955 May 19, 1959 HANS-BERNHARD SCHUNEMANN 2,385,973

CYLINDER PRINTING MACHINE Filed Nov. 1, 1955 4 Sheets-Sheet 4 United States Patent i CYLINDER PRINTING MACHINE Hans-Bernhard Schiinemann, Wurzburg, Germany, assignor to Schnellpressenfabrik Koenig 8: Bauer Aktiengesellschaft, Wurzburg, Germany, a corporation of Germany Application November 1, 1955, Serial No. 544,268 1 Claims priority, application Germany June 10, 1955 11 Claims. (Cl. 74-27) The invention relates to a cylinder printing machine with a uniformly rotating impression cylinder and a carriage whose return movement is faster than its forward,

stroke and the stationary fixed driving-wheel of which engages continuously with a spur-rack on the carriage.

Attempts have already been made to drive the carriagedriving shaft with two counter running toothed segments in alternating directions, and braking and accelerating was to be done by a spur-rack that was to be controlled in a form-locked fashion by curved-disks. Experience has shown that obtaining shock-free engagement with a uniformly rotating toothed drive by means of curve-disks is very difficult, especially when great forces have to be controlled as they do occur in the case of braking the carof a cylinder printing machine with uniformly rotating impr ession cylinder and a carriage whose return movement is faster than its forward stroke is effected by means of two differing and always alternatingly acting gears that are similar to Maltese crosses. Suitable for the purpose,

according to location, are true Maltese crosses, open Mal-Q tese cross flank pairs with enclosed toothed segment, and similar gears. Crosses with differing divisions are especiallyused in order to provide the main driving shaft with ample time for accelerating and retarding at the higher return speed. Obtaining approximately equally high accelerating values for forward running and return move ment is thus made possible in an advantageous way. Furthermore, the entire carriage path is kept short.

Figures 1, 2 and 3 show by way of example three different versions of the invention for two-revolution presses. Figure 4shows a press according to Figure 3 in cross section. The invention, however, allows alsofor combinations of these arrangements and further versions.

. With an arrangement according to Figure 1, a shaft 18 with gears thereon drives uniformly rotating single-revolution wheels respectively on shafts 2 and 11. Single. revolution shaft 2 is connected with impression cylinder by an intermediate wheel which can be seen to the right and above the carriage driving wheel 1. This single-, revolution shaft 2 provides for the movement of the carriage through the printing motion pushers and rollers 3 and 4 at each arcuate end and within the pitch circle of toothed segment 5 attached to the single revolution wheel on shaft 2. These pushers cooperate as pushing and braking rolls with open Maltese cross straight flanks 6 and wheel 34 of carriage driving shaft 27 and acts as a re- Patented May 19, 1959 flank and driving flank 6 attached to the carriage driving shaft 7 sets the carriage moving and after a turning of 45 degrees brings the toothed segment 5 into bump-free driving engagement with the driving wheel 8 afl'lxed to shaft 7. As this occurs the forward motion of the carriage S is in synchronized running with the impression cylinder 20. At the end of segment 5 the other pusher 4 contacts the braking flank portion 9 of the open Maltese cross flank and brakes the carriage driving shaft 7 down to speed 0, so that the pusher 4 subsequently leaves its braking flank 9 in a tangential fashion. At this moment, a second uniformly driven single-revolution shaft 11 takes over the return movement of the carriage at the same swinging angle of the carriage driving shaft 7 as that of the forward running movement. Toothed segment 14 of the single-revolution shaft 11 also has a pusher roll and a braking roll 17 at the ends thereof. The turn-table mounting the respective straight flanks 12 and 16 is affixed on shaft 19 of a reduction gear segment or speed change drive 13. The pusher roll 10 runs into its pushing flank 12 and starts the reverse turning of the carriage driving shaft 7. Pusher 10 with shaft 11 travels an even 60 degrees before its toothed segment 14 meshes with the toothed segment 15 of the counter shaft 19 and reduction gear segment 13 meshes with wheel 8 of the carriage driving shaft 7 so as to uniformly move the carriage.

Subsequently, the other flank 16 brakes with its roll 17 the quick return motion. Braking roll 17 leaves its flank 16 in a tangential fashion at the moment of dead center position of the carriage at the same time, pusher 4, as shown at the right in Figure l enters tangentially against its pusher flank 6. Both main driving shafts 2 and 11 rotate together with pushers in the same direction and' which work together with the straight flanks 28 and 29 respectively of a Maltese cross gear turn-table which is wedged onto the carriage driving shaft 27. The toothed segment 22 carries furthermore at a corresponding radius distance a further pusher 25. Pusher 25 causes the accelerated return motion of the carriage. Pusher 25 cooperates with a balancer 26 of toothed segment 32 on auxiliary shaft 33 which meshes continuously with the driving ancer 26 and pusher 23 causes the forward movement of the carriage via the pushing flank 28 of carriage driving shaft 27.. After this, toothed segment 22 in mesh with 1 driving wheel 34 of shaft 27 takes over the uniform printing action until braking roll 24 with its braking flank 29 of carriage driving shaft 27 effects the retarding until standstill of the carriage before reversal. The toothed segment of the balancer 26 always remains in mesh with the driving wheel 34 of shaft 27 and is, therefore, upon =tangentially leaves its braking flank 29. For driving the I At the moment of reversal carriage the toothed wheel 30 wedged on shaft 27 cooperates with spur-rack 31 of the carriage.

In a further version of the invention, Figure 3 shows two uniformly rotating single-revolution main driving shafts 43, 44 which are countercurrently driven in a more or less known fashion by means of their meshing,

toothed wheels

41, 42. Each shaft carries one of the toothed segments 45, 46 differing in length and diameter, which cooperate with the toothed segments 47, 48 of carriage driving shaft 49 and which within the pitch circle are at both ends flanked by a pusher and braking pair of

rolls

50, 52 or 51, 53 respectively. Here, too, the pusher roll 50 and braking roll 52 cooperate respectively with pusher flank 54 and braking flank 56 to cause smooth acceleration and retardation of the carriage to speed 0. So also the pusher roll 51 and braking roll 53 cooperate respectively with the pusher flank 55 and braking flank57 at each end of segment 47. Both turn-tables of all braking and pushing flanks are stationary wedged on carriage driving shaft 49. in contrast to Figure 1, the differing Maltese crosses are not adjusted to the same turning angle of the carriage driving shaft at forward and return motion by means of a reduction-gear, but by means of the curved shape of pushing and braking flanks 55, 57' which actas speed change drive coupling. Thus, it can be obtainedv that the main driving shaft allows for more time, i.e., greater rotation angles, for accelerating and retarding the high return speed than for the smaller forward motion speed. Here again it is possible to make accelerating movements at forward and return motion practically equal, which results in the smallest possible accelerating in the entire machine. The curves of the flanks 55 and 57 may be shaped more or less at will, however, exact circular cylinder pieces are especially advantageous from a manufacturing point ofview. Should in the known fashion cycloidally shaped forms be chosen, the flank curves may then be shaped as locked guiding-slots by means of which auxiliary curves are no longer required. With carriage driving shaft 49 there is a toothed segment connected within the machine, which continuously meshes with spurrack 59 of carriage 60. Impression cylinder 61 is driven by single-revolution shaft 43 via an intermediate wheel 62. Intermediate wheel 62 is thereby situated almost horizontally to the cylinder, so that lifting the cylinder practically does not cause any increase in teeth back-lash. Driving the cylinder can also be effected by driving shaft 44 via toothed wheel 42. In addition to the open pushing and braking'flanks, all gears shown possess guidings which at slow running of the machine hold the pushing and braking rolls at the flanks, i.e., guide these in a form-locked manner. These guidings act as auxiliary curves which do not absorb the dynamic forces and are correspondingly less heavy in construction. For the sake of illustrating them well, they have only been indicated in Figure 2 under 34 and 35, without being limited tothis arrangement.

It may be mentioned that these Maltese cross-type gears may be shaped for external switching, internal switching or as. straight guidingswith spur-racks. In the latter case there are by way of example four-third revolution shafts switching with alternatingly acting pushers.

The gears according to the invention can be housed in a more or less closed-up gear-box in the known manner. Figure 4 shows a cross-section through a press, according to Figure 3. side frame II, there is running in an oil bath the reversing gear, from which the carriage driving shaft 49 leads into the machine, carryingthe carriage driving wheel 58. This meshes continuously with spur-rack 5 of the carriagefitl which is led in the conventional manner. The deep'level of shaft 49 has in the low level of the carriage a favorable effect. By means of a reduction gear, it is possible to increase the rotating angle of shaft 49 andto locate the carriage on a deeper level.

example, would receive its drive from the single-revolu- Outward to the left, in front of machine.

Impression cylinder 61, for

4 tion main driving shaft via an intermediate wheel 62 within gear-box 63.

Main driving shafts of the multi-revolution type may be envisaged for all cases, however, these gears are unable to work on the same level. Couplings would then have to be provided or lateral shifting of the driving wheels would become necessary. Against this, the examples given of gears with single-revolution main driving shafts distinguish themselves by their simple design, their small. highest accelerations and their small depth in construction.

What I claim is:

1. In mechanism for transmitting alternating forward and rearward rotation to a reverse motion shaft, gear means fixedly mounted on said shaft, a first Maltesecross type drive means meshing with said gear means and having a driving angle for rotating said shaft in one direction representing advance travel, a second Maltesecross type drive means meshing with said gear means and having a driving angle of a larger size as compared with the driving angle of said first Maltese-cross type drive means for rotating said shaft in a reverse direction representing return travel faster than in the advance travel, said first and second Maltese-cross type drive means having pusher and braking flanks, pusher and braking rolls corresponding to the flanks and associated toothed segments for meshing engagement with said gear means, and synchronizing and speed change drive means interposed between said gear means on the reverse motion shaft and one of said Maltese-cross type drive means for synchronizing corresponding rotating angles at the end of one direction of rotation of the reverse motion shaft and the gear thereon and the beginning of the reverse direction of rotation of said reverse motion shaft' and the gear thereon and between such synchronizing accelerating, changing the speed of drive and decelerating the drive of said reverse motion shaft.

2. In mechanism for transmitting alternating forward and rearward rotation to a reverse motion shaft, gear means fixedly mounted on said shaft, 2. first constantly rotating shaft spaced from said reverse motion shaft, a first gear segment mounted on the first shaft, a pusher and a braking roll mounted respectively at the ends of said segment, an intermediate shaft mounted intermedi-- ate said reverse motion shaft and said first shaft, a first Maltese-cross like gear means having a segment, a pusher flank means and a braking flank means mounted on said" intermediate shaft for driving and braking engagement by said segment and rolls on the first shaft, a reduction gear segment fixed to the intermediate shaft and meshing with said gear means on the reverse motion shaft, a. second constantly rotating shaft rotating at the same speed as the first shaft and in the same direction, a second Maltese-cross type drive means including a gear seg:' ment on the second shaft for meshing with said gear means on the reverse motion shaft, a pusher roll and'a braking roll at each end of said last named gear SE8?- ment and a pusher flank and a braking flank fixed tosaid reverse motion shaft and for cooperative driving action with said respectively last named pusher and braking rolls for driving the reverse motion shaft in a reverse direction of rotation and at a higher angular speed of rotation than said first shaft, said reduction gear segment and said means mounted on the intermediate shaft acting as speed change drive means and synchronizing,

means for synchronizing the speed of rotation of said,

reverse motion shaft at the end of one direction of rotation with the speed of rotation at the beginning of the reverse rotation of the reverse motion shaft and changing the speed of dri e of the reverse motion shaft.

3. A mechanism according to claim 1 wherein said intermediate shaft is positioned intermediate said second.

shaft and said reverse motion shaft, said first Maltesecross type gear means on the intermediate shaft having;

engagement with the gear segment, pusher braking rolls assaors on the second shaft respectively and said gear segment, pusher and braking rolls on the first shaft having cooperative engagement with said flanks and gear means of the reverse motion shaft.

4. In mechanism for transmitting alternating forward and" rearward rotation to a reverse motion shaft, gear means fixedly mounted on said shaft, a constantly rotating shaft, a first Maltese-cross type drive means for drivsaid gear means and reverse motion shaft in one direction, including pusher and braking flanks fixed to said reverse motion shaft, a gear segment fixed to said constantly rotating shaft for meshing and driving engagement with said gear means on the reverse motion shaft, a pusher roll and a braking roll at the ends of said gear Segment and for driving and braking action with said flanks, an auxiliary shaft, an arcuate gear segment pivoted on said auxiliary shaft and meshing with said gear means to drive said reverse motion shaft at a different rate of rotation than said first Maltese-cross type drive means and in part of its arcuate travel causing a rotation in a synchronizing manner of the reverse motion shaft at one end of its arcuate travel in one direction with the beginning of its arcuate travel in the reverse direction, said arcuate gear segment mounted on the auxiliary shaft having a balancer drive affixed thereto of a true Maltese-cross, said constantly rotating shaft having a pusher arm means fixed thereto with a pusher thereon forldriving engagement with said balancer drive thereby driving said arcuate gear segment in one direction when not being driven in the reverse direction by said first Maltese-cross type drive means.

5. In mechanism for transmitting alternating forward and rearward rotation to a reverse motion shaft, said reverse motion shaft having a high speed gear segment and -a low speed gear segment thereon, a first constantly rotating shaft, a second constantly rotating shaft rotat ing at the same speed but in a reverse direction from said first constantly rotating shaft, a Maltese-cross type drive means drivingly disposed between the first constantly rotating shaft and the low speed gear segment and including a gear segment, a pusher and a braking flank and pusher and braking rolls for respective cooperation with said flanks, a Maltese-cross type drive means drivingly disposed between the second constantly rotating shaft and the high speed gear segment on the reverse motion shaft and including a gear segment, pushor and braking flanks and pusher and braking rolls respectively for cooperation with the last named flanks, said last named flanks being shaped for cooperation with their respective pusher and braking rolls to drive the reverse motion shaft at a rotation rate at the beginning of its high speed reverse motion that is equal to the rotation rate at the end of its just prior direction of rotation thereby synchronizing the deacceleration speed of prior direction of rotation with the acceleration speed at the beginning of said reverse rotation.

6. In a mechanism according to claim 5 wherein the flanks of the first Maltese-cross type drive means are straight flanks and the flanks of the second Maltese-cross type drive means are exact circular arcs.

7. In combination in a cylinder printing press with uniformly rotating impression cylinder, a carriage having a spur-rack thereon, a driving wheel continuously meshing with the spur-rack, a forward and rearward rotation shaft having fixedly mounted thereon said driving wheel, a reversely driven gear fixed on said shaft, a first Maltesecross type drive means meshing with said reversely driven gear having a driving angle size for moving the carriage in the advance travel, a second Maltese-cross type drive means meshing with said reversely driven gear having a driving angle of a larger size as compared with the driving angle of said first Maltese-cross type drive means for moving the carriage in the return travel faster than in the advance travel, said first and second Maltese-cross type drive means having pusher and braking flanks and pusher and braking rolls corresponding to the pusher and braking flanks and associated toothed segments for driving engagement with said reversely driven gear, said braking means of one Maltese-cross type drive means being synchronized with the pusher means on the second Maltese-cross type drive means for synchronizing the swivel angles of the reversely driven gear and said braking pusher means on the second Maltese-cross type driving means being synchronized with the pusher flank means on the first Maltese-cross type drive means for synchronizing the swivel angles of the reversely driven gear.

8. In a mechanism for transmitting alternating forward and rearward rotation to a reverse motion shaft; gear means fixedly mounted on said shaft; a first Maltese-cross type gear means for driving said gear means and having a driving angle for rotating said shaft in one direction representing forward travel; a second Maltese-cross type drive means for driving said gear means and having a driving angle of a larger size as compared with the driving angle of said first Maltese-cross type drive means for rotating said shaft in a rearward direction representing rearward travel faster than in the forward travel; said second Maltese-cross type drive means having speed change drive means interposed between the second Maltese-cross type drive means and the gear means fixed to the reverse motion shaft; said speed change drive means having synchronizing means portion causing synchronism of angle of drive with the first Maltese-cross drive means at the beginning of the rearward drive motion of the reverse motion shaft, means portion accelerating the rearward motion of the reverse motion shaft through a greater drive angle portion than the comparable acceleration drive for the forward drive motion of the reverse motion shaft, means portion driving said reverse motion shaft in the rearward direction at a fixed speed greater than the comparable drive speed in the forward motion of said shaft by the first Maltese-cross type drive means, means portions decelerating the rearward motion of the reverse motion shaft through a greater deceleration drive for the forward drive motion of the reverse motion shaft and synchronizing means causing synchronism of angle of drive with the first Maltese-cross drive means at the beginning of the forward drive motion of the reverse shaft.

9. In a mechanism for transmitting alternating forward and rearward rotation to a reverse motion shaft, gear means fixedly mounted on said shaft, a first constantly rotating shaft spaced from said reverse motion shaft, a first gear segment mounted on the first shaft, a pusher and a braking roll mounted respectively at the ends of said segment, and intermediate shaft mounted intermediate said reverse motion shaft and said first shaft, a first Maltese-cross like gear means having a segment, a pusher flank means and a braking flank means mounted on said intermediate shaft for driving and braking engagement by said segment and rolls on the first shaft, a reduction gear segment fixed to the intermediate shaft and meshing with said gear means on the reverse motion shaft, a second constantly rotating shaft rotating at the same speed as the first shaft and in the same direction, a second Maltese-cross type drive means including a gear segment on the second shaft for meshing with said gear means on the reverse motion shaft, a pusher roll and a braking roll at each end of said last named gear segment and a pusher flank and a braking flank fixed to said reverse motion shaft and for cooperative driving action with said respectively last named pusher and braking rolls for driving the reverse motion shaft in a reverse direction of rotation and at a higher angular speed of rotation than said first shaft, said reduction gear segment and said means mounted on the intermediate shaft acting as speed change drive means and synchronizing means for synchronizing the speed of rotation of said reverse motion shaft at the end of one direction of rotation with the speed of rotation at the beginning of the reverse rotation of the reverse motion shaft and changing the speed of drive of the reverse motion shaft.

7 1.0. In a mechanism for transmitting alternating for- Ward and rearward rotation to a reverse motion shaft, gear means fixedly mounted on said shaft, a constantly rotating shaft, a first Maltese-cross type drive means for driving said gear means and reverse motion shaft in one direction, including pusher and braking flanks fixed to said reverse motion shaft, a gear segment fixed to said constantly rotating shaft for meshing and driving engagement with said gear means on the reverse motion shaft, a pusher roll and a braking roll at the ends of said gear segment and for driving and braking action with said flanks,.an auxiliary shaft, an arcuate gear segment pivoted on said auxiliary shaft and meshing with said gear means to drive said reverse motion shaft at a different rate of rotation than said first Maltese-cross type drive means and in part of its arcuate travel causing a rotation in a synchronizing manner of the reverse motion shaft at one end of its arcuate travel in one direction With the beginning of its arcuate travel in the reverse direction, said arcuate gear segment mounted on the auxiliary shaft having a balancer drive affixed thereto of a true Maltesecross, said constantly rotating shaft having a pusher arm means fixed thereto With a pusher thereon for driving engagement with said balaneer drive thereby driving said arcuate gear segment in one direction when not being driven in. the reverse direction by said first Maltese-cross type drive means.

11. In a mechanism for transmitting alternating for ward and rearward rotation to a reverse motion shaft, said reverse motion shaft having a high speed gear segment and a low speed gear segment thereon, a first constantly rotating shaft, a second constantly rotating shaft} rotating at the same speedbut in a reverse direction froth! said first constantly rotating shaft, a Malte'se-cros'stype drive means drivingly disposed between the first constantly rotating shaft and the high speed gear segment andineluding a gear segment, a pusher and a braking .flank and pusher and braking rolls for respective cooperation with said flanks, a Maltese-cross type drive means drivingly disposed between the second constantly rotatingshaft and the low speed gear segment on the reverse mo tion shaft and including a gear segment, pusher and-1 braking flanks and pusher and braking rolls respectively for cooperation with the last named flanks, said last I named flanks being shaped for cooperation with their re-;:

\ spective pusher and braking rolls to drive the reverse motion shaft at a rotation rate at the beginning: of its} low speed reverse motion that is equal totherotation rate at the end of its just prior direction ofrotation thereby synchronizing the deceleration speed of prior direction of i rotation with the acceleration speed at the beginning of said reverse rotation.

References Cited in the file of this patent UNITED STATES PATENTS Yeider May'S, 193=1-'