BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a diagrammatic, side sectional view of a multiple-color sheet-fed printing press having a turner apparatus according to the invention;
FIG. 2 is a diagrammatic, plan view of a gear mechanism for driving a storage drum and a turner drum;
FIGS. 3-5 are diagrammatic illustrations for showing a setting of a phase between a storage drum and a turner drum;
FIG. 6 is a diagrammatic illustration of a gearwheel mechanism for precision setting of the phase;
FIG. 7 is a diagrammatic illustration of a cam mechanism for precision setting of the phase; and
FIG. 8 is a diagrammatic illustration of a coupler which is divided in two for disengaging intermediate gears.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the figures of the drawing in detail and first, particularly, to FIG. 1 thereof, there is shown a perfector printing press having eight printing units 1-8 and a varnishing unit 9 for printing on sheets 10. A feeder 12 having a suction head 13, a creeper table 14 and swinging grippers 15 is provided for separating sheets 10 from a stack 11 and for conveying them to the first printing unit 1. Transfer drums 16-49 are provided for conveying the sheets 10 through the printing press. The transfer drums 17, 21, 25, 29, 33, 37, 41, 45, 49 are configured as impression cylinders and interact with transfer cylinders 50-57. The transfer cylinders 50-57 interact with form cylinders 58-65. In the varnishing unit, the transfer drum 49 interacts directly with a form cylinder 66. During passage through a press nip between a transfer cylinder 50 to 57 and an impression cylinder 17, 21, 25, 29, 37, 41, 45, 49, the sheets 10 are printed with color separation. The color separation of a color separation image is transferred from the respective form cylinder 58-65 onto a transfer cylinder 50-57. The color separation image is transferred from the respective transfer cylinder 50-57 to a surface of the sheet 10. In the varnishing unit, the sheets 10 are given in each case a final varnish coat on that side of the sheet 10 which was printed last. All transfer drums 16-49 which guide sheets 10 have gripper configurations 67 for gripping a leading edge of the sheets 10. The transfer drum 31 has additional gripper configurations 68 for holding a trailing edge of the sheet 10. The transfer drums 16-49, the transfer cylinders 50-57 and the form cylinders 58-66 are coupled to one another in a gearwheel mechanism. In order to drive the printing press, a motor 69 is provided which feeds a torque to a shaft of the transfer drum 38 via a gear mechanism 70. The completely printed sheets 10 are conveyed onto a stack 73 in a deliverer 71 having a chain gripper system 72.
The printing press can be changed over from printing on only one side of the sheets 10 to printing on both sides. In perfecter operation, the printing units 1-4 serve for printing on the front side and the printing units 5-8 and the varnishing unit 9 serve for printing on the rear side of the sheets 10. The transfer drums 31, 32 are configured between the printing units 4 and 5 as a storage drum and a turner drum. During printing on both sides, the phase positions of the gripper configurations 67, 68 are set in such a way that the edge which trails in the printing units 1 to 4 is conveyed further as the leading edge from the printing unit 5.
There is no direct drive connection between the drive gearwheel of the storage drum 31 and the turner drum 32, but rather via intermediate gears 74, 75 which are kept at a spacing by way of a coupler 76. The intermediate gears 74, 75 are assigned a coupling configuration 77 which disengages or closes the coupler 76 in order to set the phase position of the gripper configurations 67, 68 and brings the intermediate gears 74, 75 out of or into engagement. The intermediate gear 74 and the intermediate gear 75 are kept at a spacing with respect to the storage drum 31 and with respect to the turner drum 32 by swinging arms 78 and 79. The remote-controlled coupling configuration 77 is connected to a control device 80. Setting of the phase is carried out by way of the motor 69 or an additional adjusting motor and is monitored on the shaft of the transfer drum 46 by way of a rotary encoder 81. The rotary encoder 81 and the motor 69 are likewise connected to the control device 80.
In printing operation, the coupling configuration 77 is closed, with the result that, starting from the motor 69 via the coupling configuration 77, a torque is transmitted to the elements which are to be driven in the printing units 1 to 4.
In the following text, the method of operation of the intermediate gears 74, 75 and the coupling configuration 77 is to be described using FIGS. 2 to 6. If designations which have already been introduced are used in the following description, they are elements with an equivalent function.
As shown in plan view in FIG. 2, the storage drum 31, the turner drum 32 and the impression cylinder 33 having shaft journals 82 to 87 are mounted rotatably in side walls 88, 89 of the printing press. Helically toothed gearwheels 90 to 92 are disposed fixedly in terms of rotation on the shaft journals 83, 85, 87. The gearwheels 90, 92 are connected to further gearwheels 93, 94 of the main drive gear train. The gearwheels 90, 91 lie in different planes and are not in engagement with one another. The gearwheel 90 is in engagement with an intermediate gear 95, which is shown symbolically by a dashed line. The intermediate gear 95 has the diameter of the intermediate gear 91. The intermediate gear 95 is mounted on an axle pin 96. The shaft journal 83 and the axle pin 96 are kept at a spacing by way of the swinging arm 78. The gearwheel 91 is in engagement with an intermediate gear 97 and is mounted on an axle pin 98. The shaft journal 85 and the axle pin 98 are kept at a spacing by way of a swinging arm 79. The axle pins 96, 98 are kept at a spacing by way of the coupler 76. The coupler 76 is assigned the coupling configuration 77. The axle pin 98 is coupled to a hydraulic actuator 99 which is connected to the control device 80.
During printing, the torque flow leads from the gearwheel 90 of the storage drum 31 to the intermediate gear 95, from the intermediate gear 95 to the intermediate gear 97 and from the intermediate gear 97 to the gearwheel 91 of the turner drum 32. The gearwheel 91 is the first gearwheel in the gearwheel train of that part of the printing press which lies behind the turner apparatus. In order that the torque can be transmitted in the gearwheel train from the plane of the gearwheel 90 into the plane of the gearwheel 91, one of the intermediate gears 95, 97 has double the width. During printing, the coupler 76 is fixed on the side wall 89. The connection of the coupler 76 to the side wall 89 can be released for a phase adjustment between the gearwheels 90 and 91.
FIGS. 3 and 4 show two different positions of the swinging arms 78, 79 and of the coupler 76. The phase positions of the gearwheels 90, 91 and the intermediate gears 95, 97 are identified in each case with a phase arrow 100. In FIG. 3, the phase positions are in an initial position. If the swinging arms 78, 79 and the coupler 76 are pivoted or pushed into the positions which are shown in FIG. 4 by the actuator 99, the phase positions of the gearwheel 91 and the intermediate gears 95, 97 are changed by an angle α with respect to the initial position. The phase position can also be set in an infinitely variable manner during printing.
If the printing press is changed over from printing on one side to printing on both sides of the sheets, the phase position of the gearwheels after the turner drum 38 has to be adjusted with respect to the phase position of the gearwheels before the turner drum 32 by a relatively great amount. This relatively great amount cannot be achieved solely by pivoting of the swinging arms 78, 79 and by displacement of the coupler 76. A mechanism, in particular a threaded spindle 101, with which the length 1 of the coupler 76 can be increased, is situated on the coupler 76. If, as shown in FIG. 5, the coupler 76 is extended to such an extent that the intermediate gears 95, 97 are out of engagement, the main drive gear train is disconnected and the phase position can be adjusted by the abovementioned relatively great amount. After the adjustment of the phase position, the length l of the coupler 76 is again reduced by way of the threaded spindle 101 to such an extent that the intermediate gears 95, 97 are in engagement again. In order that the intermediate gears 95, 97 can be brought into engagement again, the adjustment of the phase position is performed in such a way that the rotated intermediate gear 95 or 97 is rotated only by a multiple of the tooth pitch.
FIGS. 6 and 7 show variants of how a precision adjustment of the phase position of the gearwheels 90, 91 and the intermediate gears 95, 97 can be performed.
According to FIG. 6, a gearwheel mechanism is provided, containing a gearwheel 102 and a rack 103. The rack 103 is in engagement with the gearwheel 102. One end of the rack 103 is connected to the axle pin 98 in an articulated manner. If the gearwheel 102 is rotated, the positions of the swinging arms 78, 79 and the coupler 76 are changed.
In the variant which is shown in FIG. 7, a cam mechanism having a cam 104 and a cam roller 105 is used. The cam roller 105 is mounted on the swinging arm 98. If the cam 104 is rotated about an axle 106, the cam roller 105 then follows the profile of the cam 104 and the swinging arm 79 is deflected. As a result of the coupling to the axle pins 96, 98, the coupler 76 and the swinging arm 78 are also moved, so that a change in the rotational phase position of the intermediate gears 95, 96 and the gearwheels 90, 91 results.
FIG. 8 shows one variant of how the coupler 76 can be extended or shortened. The coupler 76 contains a first coupler rod 76.1 and a shorter second coupler rod 76.2, which are connected to a joint 107. In each case that end of a coupler rod 76.1, 76.2 which faces away from the joint 107 is connected to the axle pins 98, 96 in an articulated manner. In order to change the coupler length l, the coupler rod 76.2 is rotated about the axle pin 96. If the angle β between the coupler rods 76.1, 76.2 is 180°, this results in a maximum coupler length lmax, at which the intermediate gears 95, 97 are reliably out of engagement.
Patent Application
20070234913
