Inking systems

An inker for a lithographic printing press in which ink and dampening fluid are applied to the printing plate by a resilient applicator roller. A resilient ink metering member having a flat metering surface is mounted on a support member which is movable to adjust the angle of intersection of the metering surface relative to a plane tangent to the roller surface. A doctor blade is mounted to remove dampening fluid from the roller surface and is actuated to an operative position upon actuation of the dampener to apply dampening fluid to the applicator roller.

BACKGROUND OF INVENTION 
All activities involved in the preparation of negatives, positives, 
half-tones, linework and solids in the preparation of metal plates is a 
photo-mechanical process. A metal printing plate is a photo contact print, 
exposed to light, developed and processed for the lithographic printing 
press. 
No ghosting effect, influence, crossover influence, front-to-back color 
variation or across the sheet color variations are ever established by the 
making of a printing plate. Conventional printing presses equipped with 
conventional inkers introduce inherent ghosting effects and other 
inaccurate printing of the printing plate onto the printed sheet. It is 
the effect of a particular form or printed format with its ghosting 
potential, front and back influence, and crossover, which is transmitted 
to the conventional inking system and is continuously transmitted back and 
forth from the printing plate to the inking system and from the inking 
system back to the printing plate. This continues throughout the run, 
making color control very difficult and color variation the norm for 
conventional printing presses. Heretofore color variations have been 
established and perpetuated throughout a printing run by conventional 
inking systems. 
Structural components of inking systems heretofore devised have been 
eliminated from the improved inking systems disclosed herein while 
providing a new structure capable of forming a smooth continuous film of 
ink on a resilient applicator roller surface for application to a printing 
plate to provide photo-mechanical reproduction of the printing plate onto 
a blanket cylinder and to the paper. No ink keys are employed and no 
job-to-job adjustments are necessary. To change from one job to another, 
one merely changes the printing plate. No inker adjustments are made to 
match the new job. Solids, half-tones, line work and process, all are 
printed at the same time and at the same ink setting. Gear streaks, 
hickeys, and improper water balance are problems which constantly plague 
printers using conventional inking systems. 
The improved inking system disclosed herein offers a solution to the 
technical problem of providing an inking system which will faithfully 
reproduce an image on a printing plate by a photo-mechanical process while 
eliminating gear streaks, ghosting, and color variation resulting from the 
inability of the printing press to offer a fresh continuous uniform film 
on each revolution of the printing plate. 
SUMMARY OF INVENTION 
The improved inking system disclosed herein incorporates several improved 
features in structure mounted about a resilient surfaced applicator roller 
to form a continuous uniform film of ink so that every point on a printing 
plate is offered the same ink film upon every revolution of the plate to 
permit faithful photo-mechanical reproduction of the printing plate. 
The improved structure includes an improved oscillator roller drive 
mechanism wherein a pair of ink smoothing rollers of substantially equal 
mass are urged in opposite directions by cam rollers on opposite ends of a 
rocker arm adjacent opposite sides of the inker. The smoothing rollers of 
approximately equal mass move in opposite directions and the kinetic 
energy which would normally be transmitted to the press drive train for 
decelerating a smoothing roller is transmitted to another smoothing roller 
moving in the opposite direction to minimize application of oscillatory 
loading into the printing press drive which could cause undesirable 
vibration of the structure. In addition, the oscillator roller drive 
mechanism is employed in combination with an applicator roller which is 
significantly larger and of greater mass than conventional inking form 
rollers. The applicator roller has significant mass and the oscillator 
roller drive is driven by a gear train on the drive shaft of the massive 
applicator roller such that any oscillatory loading resulting from 
movement of the vibrator rollers will be damped and its influence 
substantially eliminated by the inertia of the applicator roller. 
An improved positive variable speed drive is provided for the applicator 
roller so that a precise speed relationship between the applicator roller 
and the printing plate can be established. 
A set of improved metering members which are particularly adapted for 
forming a thin film of uniform thickness on an applicator roller, is 
provided and is adjustable by an improved blade holder assembly for 
establishing and maintaining a precisely controlled film of ink on an 
applicator roller surface. The improved holder for the metering members 
includes spring locking elements to facilitate replacement of one metering 
member with another for establishing different ranges of thickness of the 
film of ink formed on the applicator roller to permit use of a variety of 
inks of different viscosity. An improved end dam construction is employed 
in combination with the metering member and the metering member support to 
form a reservoir of ink on the applicator roller surface. 
To prevent undesirable marking of the applicator roller when the press is 
stopped, an improved air circuit is employed for actuating the metering 
member to reduce pressure between the metering member and the applicator 
roller when the press is stopped. Night latches are provided on vibrator 
rollers and dampener rollers to permit reduction of pressure at the nip 
between the various rollers if the press is to be stopped for a 
significant time period. 
A primary object of the invention is to provide an improved inking system 
which is capable of metering a film of ink of a precisely controlled 
thickness to permit photo-mechanical reproduction of a printing plate in a 
rotary printing press. 
A further object of the invention is to provide an improved inking system 
comprising a single applicator roller having a substantial mass in 
combination with a vibrator roller drive mechanism and a positive variable 
speed drive for the applicator roller which can be driven by the press 
drive without introducing shock loading which causes gear streaks to be 
printed on the printed page. 
A still further object of the invention is to provide an improved inking 
system for a lithographic printing press wherein dampening fluid is 
applied to a single applicator roller prior to inking the printing plate 
and removed from the applicator roller after inking the printing plate to 
maintain a reservoir of ink which is substantially free of dampening 
fluid. 
Other and further objects of the invention will become apparent upon 
referring to the detailed description hereinafter following and to the 
drawings annexed hereto.

DESCRIPTION OF A PREFERRED EMBODIMENT 
Referring to FIGS. 1, 6, 14 and 17 of the drawings, the numeral 30 
generally designates an inker having spaced sideframes 32 and 33 movably 
secured to adaptor frames 32' and 33' secured to sideframes 32A and 32B of 
a printing press having a conventional plate cylinder 34, blanket cylinder 
35, and impression cylinder 36 mounted therein for printing on a web 37 or 
a sheet of paper. An inker of this type is disclosed in our copending 
application Ser. No. 06/282,294 filed Jul. 13, 1981 and entitled "Ink 
Metering Apparatus With Obtuse Metering Member," the disclosure of which 
is incorporated herein by reference in its entirety for all purposes. 
Sideframes 32 and 33 pivot about pins 38a and 38b, as best illustrated in 
FIGS. 1, 3, 5, 14, 16 and 18, upon actuation of cylinders 38 which are 
connected between the adaptor frames 32' and 33' and inker sideframes 32 
and 33. As will be hereinafter more fully explained, this axis of rotation 
is aligned with the axis of the dampener transfer roller 300. 
Metering member support means 50, best illustrated in FIGS. 6, 9 and 10, is 
provided to adjustably secure metering member 40 between sideframes 32 and 
33 and to position metering member 40 in relation to a resilient covered 
applicator roller 80. Opposite ends of applicator roller 80 are rotatably 
secured to sideframes 32 and 33 in suitable bearings, as illustrated in 
FIGS. 5, 16 and 18, and applicator roller 80 is driven by a positive 
infinitely variable speed drive 90 as illustrated in FIGS. 14 and 18. The 
surface speed of applicator roller 80 is preferably substantially equal to 
the surface speed of plate cylinder 34. 
End dams 160 are in sealing relation with support means 50 and are urged 
into sealing relation with the periphery of and at opposite ends of 
applicator roller 80 and member 40 forming a reservoir R from which ink is 
metered onto the surface of applicator roller 80. One or more ink storage 
vibrator rollers 124 and 126 are positioned in rolling engagement with ink 
on the surface of applicator roller 80 for smoothing any surface 
irregularities which may appear in the ink film before the ink film is 
carried by the surface of roller 80 to the dampener 225 and to the surface 
of a printing plate P on plate cylinder 34. Ink storage rollers 124 and 
126, having outer covers which are resilient, are in rolling engagement 
with ink on the surface of applicator roller 40 and not only smooth 
surface irregularities, but also change a slick metered finish to a smooth 
matte-like finish for conditioning the ink film for proper dampening and 
application to an image on a printing plate. 
It will be appreciated that as the surface of applicator roller 80 moves 
away from the surface of the printing plate, the surface is again smoothed 
and conditioned by ink and dampening fluid storage vibrator rollers 120 
and 122 prior to being submerged in ink where an excess of ink is applied 
thereto at the reservoir R. Ink vibrator roller 120, like rollers 124 and 
126, is resilient covered. 
As the inking system is employed for lithographic printing, dampening fluid 
is applied first to the ink on the surface of the applicator roller 80 and 
thence to the printing plate P on plate cylinder 34. Dampening fluid 
removal means 200, best illustrated in FIGS. 6 and 12, are provided for 
removing dampening fluid from the surface of roller 80 to prevent 
accumulation of excessive dampening fluid in reservoir R. 
Also, the dampening solution could contain more than the normal 5 to 25% 
alcohol to insure rapid evaporation of the dampening solution from the 
applicator roller as it travels between the plate and the ink metering 
member. The alcohol, rollers 120 and 122 and dampening fluid removal 
device 200, all contribute to the removal and redistribution of excess 
dampening fluid after printing. 
INK METERING MEMBER 
Referring particularly to FIG. 22, the ink metering member 40 has a smooth, 
polished, highly developed, precision metering edge 45 which is formed at 
the juncture of metering surface 44 and support surface 46. Polished 
surfaces 44 and 46 meet at an obtuse angle to form a wedge having an 
included edge bevel angle which is approximately 120.degree. or greater. 
The edge 45 is preferably formed on relatively hard metallic material 
having a hardness of about Rockwell C48-50 or higher. It is important that 
the polished edge 45, metering surface 44, support surface 46, trailing 
surface 48 and edge 47 be smooth and wear resistant since they are 
indented into the resilient surface 85 of form roller 80 during normal 
operating conditions. 
Metering member 40 is preferably a resilient, i.e., flexible, metallic, 
material having a modulus of elasticity of approximately 30.times.10.sup.6 
psi, or less, to provide what might be termed a "stylus effect" to the 
metering edge 45 as the applicator roller 80 rotates. 
Metering member 40 has been formed with good results from a strip of 
Hardened and tempered stainless steel with sheared edges which is 
commercially available from Sandvik Steel, Inc., Benton Harbor, Mich. and 
distributed as Sandvik 7C27Mo2. The strip of stainless steel was selected 
for its hardness, flatness, resilience, grain structure and fine surface 
finish to provide high wear resistance and good fatigue properties. The 
stainless steel strip has a thickness of 0.070 inches and a width of 
approximately 4.0 inches. 
The edge 45 must be quite flexible in a lengthwise direction so that when 
urged into pressure indented relation with the resilient surface of 
applicator roller 80, the edge 45 will be flexed, yielding to the 
influence of the surface of roller 80, to conform the edge 45 and the 
surface of roller 80 to form a substantially uniform indented area along 
the length of roller 80. As will be hereinafter more fully explained, the 
resilient cover 85 on roller 80 has a thickness in the range of 
approximately 3/8 to 5/8 inches, preferably 1/2 inch, and a resilience of 
about 40 to 80 Shore A durometer, preferably 60 durometer, Shore A. This 
loading of edge 45 to obtain conformation with the surface of roller 80 
should be possible without excessively indenting the surface of the roller 
when in a dynamic, running condition. 
The edge 45 on metering member 40 should be mounted so that it is 
resiliently urged toward the surface of the applicator roller 80 and is 
free for movement along its entire length in a direction radial to the 
applicator roller as the applicator roller 80 rotates. Also, the edge 45 
must be rigidly supported in a direction substantially tangent to the 
applicator roller surface. 
The ideal support for the edge 45 is a flexible cantilever beam which 
supports the edge 45 and provides the required bias and rigidity. Although 
the edge 45 may be a part of a separate trapezoidal like element, which is 
functionally associated with a cantilever beam, it is preferable to form 
the edge 45 of the trapezoidal portion 10 on the beam so that the two are 
an integral unit. To accomplish this, the beam must be flexible in two 
directions; namely, along the length of the edge 45 and also along the 
width of the strip, i.e., the length of the cantilever beam. 
Metering member 40 has a groove or relieved area 42 formed in the lower 
surface 41 of the strip of material from which metering member 40 is 
formed. 
The portion of the strip of material which will be polished to form 
polished edge 45 is masked and the metallic material adjacent thereto is 
removed by chemically milling or by grinding to remove a portion of the 
metal without creating stresses that would cause the strip of material to 
warp. 
Surfaces 44, 46 and surface 48 adjacent the support surface 46 is smoothed 
by finish grinding to remove approximately 0.003 inch of rough surface 
material. These surfaces may then be sanded with 600 grit paper to provide 
a very smooth surface finish. Edges 45 and 47 are therefore formed on 
trapezoidal position 10. 
If the thickness, the distance between upper and lower surfaces, of the 
strip of material is 0.070 inches, the depth of the relieved area 42 is 
preferably greater than 0.020 inches, for example, 0.035 inches, such that 
the thickness of the material remaining after relieved area 42 is formed 
is approximately 0.035 inches. Surface 48 intersects the polished support 
surface 46 at an angle in a range between 30.degree. and 90.degree. as 
shown. 
Upon finishing of the member 40, the member may be further treated to 
provide extremely good wear resistance by cryogenic (low temperature) 
treatment which rearranges the molecular structure of the material 
throughout the material and without warping or altering the hardness of 
the material. 
I have found that included angles of 110.degree. to 160.degree. adequately 
cover the range of inks encountered in lithographic printing, the smaller 
angles used for more viscous sheet-fed inks and the larger angles for less 
viscous web-inks. 
METERING MEMBER SUPPORT 
Support means for metering member 40 is illustrated in FIGS. 6, 9 and 10 of 
the drawings. Metering member 40 is secured to a rigid support bar 50 
having a ground and true face 51 on one side thereof and having journals 
52 and 54 extending outwardly from opposite ends thereof. As best 
illustrated in FIG. 9 of the drawing, each of the journals 52 and 54 is 
formed from the square shaped end of support bar 50. 
The journals 52 and 54 are rotatably secured in self-aligning bushings 56 
in guide blocks 58 and 60 which are slidably disposed in slots 59 in 
sideframes 32 and 33, respectively. 
As best illustrated in FIGS. 6, 9 and 17 of the drawings, rails 62 have 
opposite ends bolted or otherwise secured adjacent opposite sides of slot 
59 in sideframes 32 and 33 and pressure adjustment screws 63, restrained 
against vertical movement by lock rings 63a in openings in rails 62, have 
a lower threaded end extending into a threaded openings in one of the 
guide blocks 58 or 60. Thus, rotation of pressure adjustment screws 63 
imparts vertical motion to guide block 58 or 60 for moving support bar 50 
and metering member 40 relative to the surface 85 of cover 84 of 
applicator roller 80. Lock-down screws 61 and 61' serve as maximum limits 
of the position of ends of holder 50, screws 61 and 61' being threaded 
through rails 62 and inker sideframes, respectively, and engage the upper 
and lower surfaces of guide blocks 58 or 60. Lock screw 61' is preferably 
a socket setscrew positioned to engage the lower surface of the guide 
block 58 or 60 to limit movement of the blocks. 
The center line of guide blocks 58 and 60, in which opposite ends of 
support bar 50 are rotatably disposed, is positioned such that the point 
of contact of the metering edge 45 on metering member 40 engages the 
surface 85 of applicator roller 80 at a point which is a few degrees, 
measured in a counterclockwise direction as viewed in FIGS. 10 and 22, 
from a line tangent to the roller surface at a point where edge 45 
intersects the roller surface. Thus, rotation of adjustment screw 63 
changes the angle between the metering surface on the end of metering 
member 40 relative to a tangential line which results in a change in ink 
film thickness. 
As best illustrated in FIG. 6, each guide block 58 and 60 has a position 
indicator arm 57 bolted or otherwise secured thereto. The outer end of 
each position indicator arm is engaged by a dial indicator 64 supported by 
inker sideframes 32 and 33. Thus, the dial indicator 64 at each side of 
the printing press can be observed and set to determine when guide blocks 
58 and 60 are properly individually adjusted such that the blade edge 45 
is precisely parallel to surface 85 of applicator roller 80 and moved 
together to change the angular relation of the member 40 to roller 80. 
In a test to determine the change in color density on a sheet resulting 
from adjustment of adjustment screws 63, the following results were 
observed: 
______________________________________ 
Support Bar Position (In.) 
Color Density 
______________________________________ 
0.150 1.21 
0.200 1.37 
0.250 1.57 
0.300 1.73 
0.350 1.80 
0.400 1.87 
______________________________________ 
The support bar position was read from dial indicators 64 while the color 
density of ink printed upon a sheet was measured using a "SOS- 40" digital 
reflection densitometer, commercially available from Cosar Corporation of 
Garland, Tex. The support surface on the metering member was substantially 
tangent to the roller surface and adjustment of screws 63, from a reading 
of 0.150 inches to 0.400 inches on the dial indicator, changed the angle 
between the metering surface on the end of the metering member and a line 
extending radially of the roller passing through the metering edge 45 of 
member 40. 
Adjustment screws 63 are a coarse or rough adjustment of color density 
while rotation of metering member support bar 50 provides a fine 
adjustment of color density by changing indentation of the metering edge 
45 on the metering member into the resilient surface 85 of applicator 
roller 80. 
As best illustrated in FIGS. 9, 10 and 22 of the drawing, a clamp bar 70, 
having a flange 71 positioned to engage the lower surface 41 of metering 
member 40 and to urge the upper surface of metering member 40 into 
engagement with the ground and true surface 51, is provided for mounting 
metering member 40 on support bar 50. 
Member 40 is accurately located by two pins 51' for parallel alignment 
prior to being clamped to support surface 51 by clamp bar 70. Axial 
alignment of metering member 40 relative to roller 80 is provided by an 
end locator tab 51a, as illustrated in FIG. 9, and is secured to one end 
of support bar 50, the holder 50 being cut back from each end of roller 
80. 
As best illustrated in FIGS. 9 and 22 of the drawing, clamp bar 70 is 
movably secured to support bar 50 by spaced pins 72 which are urged by 
springs 73 into engagement with metering member 40. A pin collar 77 is 
rigidly secured to shaft 75 to permit rotation of collar 77 and shaft 75 
for moving cam elements 74 spaced along the length of shaft 75 into 
engagement with upper ends of pins 72 to permit downward movement of clamp 
bar 70 to release metering member 40 from support bar 50. Support bar 50 
is preferably provided with four or more of the cam assembly elements 
spaced along the length thereof. The flange 71 on clamp bar 70 extends 
slightly above the upper surface of the mid clamping section of clamp bar 
70 so that flange 71 will deflect slightly under the force of springs 73 
to assure that the upper surface of metering member 40 is maintained in 
engagement with the true surface 51 on support bar 50. The relief of the 
opposite end of clamp bar 70 from end 71 is 0.070 inches. 
Referring to FIGS. 1 and 7 of the drawing, the journal 54 on the operator 
side of the inker has a crank arm 64 keyed or otherwise secured thereto. 
An air cylinder 65 is pivotally secured by a pin 65a to the sideframe 32 
on the operator side of the inker and has a rod end pivotally secured by a 
pin 65b to bell-crank arm 65c. Arm 65c is rotatably secured to sideframe 
32 by pin 65c and has a cam groove 65d formed therein to engage cam 
follower 64a on crank arm 64 for rotating crank arm 64 and support bar 50 
relative to sideframes 32 and 33 for adjusting indentation of metering 
edge 45 into the resilient surface 85 on cover 84 of applicator roller 80. 
The bell-crank arm 65c and crank arm 64 are formed to provide a variable 
mechanical advantage upon actuation of metering member 40. 
As best illustrated in FIGS. 1 and 7 of the drawings, a position screw 66 
is threadedly secured to a support member 66a bolted or otherwise secured 
to the operator sideframe 32 in close alignment with metering member edge 
45 such that when screws 63 are rotated, only the angle between the 
surface 44 of member 40 and surface 85 of roller 80 is altered, without a 
significant change in the indentation of edge 45 into surface 44. Screw 66 
has a gear 67 secured to the lower end thereof which is driven by a gear 
67a on the drive shaft of a motor 68 which is also secured to support 
member 66a. Thus, when motor 68 is energized, position adjustment screw 66 
will be rotated thereby limiting movement of crank arm 64 for establishing 
indentation of metering edge 45 on metering member 40 into the surface 85 
of applicator roller 80. 
From the foregoing it should be readily apparent that in the embodiment of 
the invention illustrated in FIGS. 1 and 7 of the drawing, position 
adjustment screw 66 is remotely controlled by the direct current 
electrically driven motor 68. Gears 67 and 67a form a gear reducer to 
reduce the speed or rotation of adjustment screw 66. Motor 66 is 
commercially available from Globe Industrials Division of TRW, Inc., of 
Dayton, Ohio. 
Conductors 68a and 68b extend between motor 68, and a motor position 
control unit 69, which comprises essentially a source of direct current 
electricity and a three position switch including an off (neutral) 
position and two positions for rotating motor 68 in opposite directions to 
move screw 66 up or down. 
The motor position control unit 69 preferably has a digital readout 
indicator (not shown) associated therewith to indicate the position of a 
rotary potentiometer 69c secured to the end of position adjustment screw 
66 with a slotted arm 69d engaged with pin 69e secured to support member 
66a to provide a visual indication of the position of crank arm 64 and, 
consequently, the position of support member 50 and metering edge 45 on 
metering member 40. The output terminals of the potentiometer are 
connected to the digital readout device calibrated to indicate the 
position of metering edge 45 and consequently the thickness of the film of 
ink applied to the sheet or web 37. Motor 68 may be manually or 
automatically energized to change the thickness of the ink applied to the 
sheet or web 37. 
APPLICATOR ROLLER 
The applicator roller 80 comprises a hollow, rigid, tubular metallic core 
82 having a resilient non-absorbent cover 84 secured thereto, the cover 
having a uniformly smooth, uniformly textured, and resilient outer surface 
85. The cover 84 on applicator roller 80, while being resilient, is 
relatively firm, for example, in a range between 40 and 80 Shore A 
durometer. 
As illustrated in FIG. 6 of the drawing, applicator roller 80 is 
substantially the same diameter as plate cylinder 34. Conventional inking 
systems generally employ four form rollers which are approximately 
one-fourth the diameter of the printing plate. Applicator roller 80 
preferably has a diameter of approximately 101/4 inches and a thickness of 
about 5/8 inches and the metallic steel core 82 preferably has a thickness 
of, for example, one-half inch to provide form roller 80 with sufficient 
mass and weight to provide a "dampening effect" as a result of the mass 
and inertia of the roller. As will hereinafter be more fully explained, 
streaks on printed sheets which have been heretofore referred to as "gear 
streaks" have been eliminated in presses upon which the inking system 
disclosure has been tested. As will hereinafter be more fully explained, 
several features of the present invention contribute to the elimination of 
"gear streaks." However, the mass of applicator roller 80 offers a 
significant contribution. 
The cover 84 on applicator roller 80 is preferably formed of a resilent 
polyurethane or rubber-like material attached to a metallic core 82. The 
cover can be made from Buna Nitrile rubber which provides a natural 
surface having microscropic pores to receive and hold ink therein to 
enable metering a thin ink film suitable for lithographic printing 
applications. 
The cover 84 on applicator roller 80 should have high tensile strength, 
excellent tear and abrasion resistance, and resistance to oils, solvents 
and chemicals. The cover should, furthermore, have low compression set, 
good recovery, and uniform ink receptivity. A suitable cover can be formed 
using polyurethane or rubber to form a resilient cover preferably of about 
60 Shore A durometer. 
A suitable polyurethane cover may be made from a blocked, pre-catalized, 
strained and pure material, having a 2% filler added, which is 
commercially available from Arnco in South Gale, Calif., under the 
trademark "Catapol". The material is pre-heated at 160.degree. F. for five 
hours, poured into a mold around the roller core, and then heated to 
280.degree. F. for 81/2 hours, and allowed to cool prior to grinding and 
polishing. 
If no filler is in the material, ink will not readily attach itself to the 
roll surface and if a high filler content is used ink will not be readily 
metered from the roll surface. Tear strength is also lost will a high 
filler percentage. Clay is normally used as a filler material. 
A suitable rubber cover may be obtained from Mid-America Roller Company, 
Arlington, Tex., and specified as Buna-Nitrile which is conventionally 
attached and formed over the core and ground with a high-speed grinder 
prior to polishing. 
After a resilient cover 84 of either polyurethane or rubber has been 
formed, the roller may have a slick glazed outer skin or film over the 
surface thereof which is removed by grinding. After grinding with a 120 
grit rock, the surface of resilient cover 84, if constructed of 
polyurethane, is sanded by using 180 grit sandpaper to form a surface of 
uniform smoothness over the surface 85 of the resilient cover 84. However, 
after grinding with a 120 grit rock, the surface of resilient cover 84, if 
constructed of rubber, is sanded with 800 grit sandpaper to insure a 
velvet smooth, uniformly textured surface, free of "orange peel" or other 
surface irregularities. 
Microscopic reservoirs into which ink is attached help to assure that a 
continuous unbroken film of ink is maintained on the surface 85 of 
applicator roller 80. 
Surface scratches, grind lines, and other surface irregularities should be 
removed so that the surface roughness of the surface of either 
polyurethane or rubber after sanding does not exceed 30 RMS. As will be 
hereinafter more fully explained, adhesive force between molecules of ink 
and molecules of the surface 85 of cover 84 must exceed cohesive force 
between ink molecules to permit shearing the ink to form a controlled, 
continuous, unbroken film of ink on the surface 85 of applicator roller 
80. 
It will be appreciated that it is physically impractical, if not 
impossible, to construct and maintain roller 80 such that surface 85 is 
perfectly round in a circumferential direction, perfectly straight in a 
longitudinal direction, and precisely concentric to the axis of core 82. 
The straightness or waviness of surface 85 on roller 80 can be 
economically manufactured within a tolerance of about 0.002 inches along 
the length of roller 80 and the radial eccentricity can be economically 
manufactured within a tolerance of about 0.0015 inches. Abrupt changes in 
physical properties of the material, in the roller surface, in the 
durometer, or, in the thickness of the cover 84, can adversely affect ink 
metering and therefore color. 
In FIG. 5, ends of roller 80 are shown bevelled to provide support at the 
ends such that pressure between edge 45 of member 40 and roller surface 85 
of roller 80 is uniform along the entire length of edge 45. It is 
advantageous, as shown in FIG. 5 for the ends of the member 40 to extend 
beyond the ends of plate P on cylinder 34, a distance shown as "X," i.e., 
at least, 1/8 inches. A small bead of ink has been known to form at the 
intersection of the metering member and the end dam. 
A Shore A durometer test is generally used to indicate the hardness of a 
resilient roller cover by measuring resistance to penetration at a 
constant temperature of about 76.degree. F. while the resilient cover is 
stationary. The apparent hardness of a resilient surface under dynamic 
conditions deviates radically from the hardness indicated by the durometer 
test under static conditions. The spring constant of a resilient material 
so increases slightly as deformation increases. 
As the frequency of loading of a resilient member increases, the dynamic 
modulus or apparent modulus of elasticity increases causing the cover to 
appear as a harder, stiffer material. However, cyclic loading of a 
resilient member results in generation of internal heat which increases 
temperature and results in a decrease in the durometer and therefore the 
modulus of elasticity of the resilient cover. 
Further, since the surface 85 of cover 84 on roller 80 is preferfably in 
pressure indented relation with the surface of a plate cylinder, the plate 
cylinder having a gap extending longitudinally thereof, this cyclic 
loading will result in generation of heat at an irregular rate 
circumferentially of the surface 85. Such temperature differences over 
surface 85 may cause an appreciable variation in the radial distance from 
the axis of the roller 80 to points over the surface 85, because the 
co-efficient of thermal expansion of elastomeric materials employed for 
forming resilient roller covers is several times the co-efficient of 
thermal expansion, of e.g. steel. 
Also, as temperatures change, thermal expansion changes pressures between 
adjacent surfaces and therefore nip widths and relative surface speeds 
also change between the adjacent members in pressure indented relation. 
As shown, roller 80 can be and is desirably different in diameter than the 
plate cylinder 34 without adversely affecting printing of the film 400 to 
the web 37, or sheet, since metering member 40 produces a smooth, 
continuous ribbon of ink on the applicator roller surface regardless of 
influences of the prior impression and regardless of normal dynamics in 
printing operations. 
The applicator roller 80 should not be exactly the same diameter as the 
plate cylinder 34, because even the slightest defect, hole, or flaw in the 
surface of the applicator roller 80, would be repeated in the same place 
on the plate when the two are driven at the same surface speed and are the 
exactly same diameter. This repeat, especially when printing to a 
lithographic plate, eventually causes sensitizing of the non-image area. 
The flaw will then appear as ink on the printed sheet in the non-image 
area. If the flaw occurs in the image area, eventually a light spot in the 
ink will appear in this area. Therefore, it is imperative that the surface 
of the applicator roller 80 not repeat with the surface of the plate on 
the plate cylinder. It has been observed that with the absence of a 
repeat, the flaw, even when considered excessive, will not sensitize a 
lithographic plate in the non-image area. 
APPLICATOR ROLLER DRIVE 
Applicator roller 80 is positively driven by a speed control device 90 of 
the type disclosed in copending application Ser. No. 06/314,043, filed 
Oct. 22, 1981, entitled "Inker Form Roller Drive," the disclosure of which 
is incorporated herein by reference in its entirety for all purposes. 
FIGS. 14 and 15 illustrate a lithographic printing press drive wherein a 
blanket cylinder 35 and plate cylinder 34 are conventionally driven by a 
printing press drive gear (not shown) which is conventionally driven by a 
motor (not shown) which imparts rotation to blanket cylinder gear 35a 
which is disposed in meshing relation with plate cylinder gear 34a. 
Blanket cylinder gear 35a and plate cylinder gear 34a are drivingly 
secured to blanket cylinder 35 and to plate cylinder 34, respectively. 
Plate cylinder gear 34 is mounted on journalled shaft ends of the plate 
cylinder which is axially aligned with and supports plate cylinder 34. 
Journal shaft ends of cylinder 34 are rotatably supported by bearings in 
openings in the press sideframes. A conventional plate and blanket are 
attached to the plate and blanket cylinders. 
A positive, infinitely variable, speed control device (PIV) generally 
designated by the numeral 90 is mounted for transmitting power from the 
press drive, for example, from the plate cylinder shaft to applicator 
roller 80, as will be hereinafter more fully explained. In the particular 
embodiment of the invention illustrated in FIG. 18 of the drawing, the 
positive, infinitely variable, speed control device 90 is a harmonic 
drive, which incorporates pancake gearing, which is available from U.S.M. 
Corporation, Harmonic Drive Products, Icon Division, of Wobum, Mass., USA. 
Speed control device 90 comprises a dynamic spline (not shown) within the 
harmonic drive bolted or otherwise secured to a sleeve drivingly secured 
to the plate cylinder shaft. The dynamic spline comprises a circular ring 
having teeth on its inner surface to form an internal gear and is 
positioned adjacent to a circular spline bolted to a connector hub 92 
which is bolted or otherwise secured to a sprocket 95. Sprocket 95 has a 
central opening and is supported by bearings which are positioned about 
the outer surface of the sleeve secured to plate cylinder shaft. 
The circular spline, connector hub 92 and sprocket 95 are rotatable 
relative to the dynamic spline and the plate cylinder shaft. 
An elastic steel ring having external spline teeth on the outer surface 
thereof is rotatably mounted on an elliptical bearing or wave generator 
and a rotating input element keyed or otherwise connected to input shaft 
94. The elliptical bearing has an elliptical shaped outer surface which 
engages the inner surface of the elastic steel ring. Rotation of the input 
element and the elliptical bearing causes the elastic steel ring disposed 
about the outer periphery thereof to be deformed in a wave-like manner. 
The elastic steel ring extends into the dynamic spline and the circular 
spline such that teeth on a portion of the periphery of the ring engage 
internal teeth on the dynamic spline and on the circular spline along 
diametrically opposed portions of the dynamic and circular splines. 
Thus, when assembled, rotation of the elliptical bearing and the input 
element imparts a rotating elliptical shape to the elastic steel ring 
causing progressive engagement of these external teeth with the internal 
teeth of the dynamic spline and the circular spline. 
The circular spline has two more teeth than the elastic steel ring, thereby 
imparting relative rotation to the elastic steel ring at a reduction ratio 
corresponding to the number of teeth. The dynamic spline has the same 
number of teeth as the elastic steel ring, therefore it rotates with and 
at the same speed as the elastic steel ring. Thus, the circular spline 
establishes the positive transmission reduction ratio equal to one-half 
the number of teeth on the elastic steel ring. 
A flexible coupling 93 is connected between input shaft 94 and output shaft 
96 of a right-angle gear reducer 98 which is driven by a variable speed, 
direct current, electric motor 100, the speed of which is controlled by a 
tachometer-generator circuit (not shown), which causes the speed of motor 
100 to be maintained in a selected speed ratio relative to the speed of 
the printing plate 34. 
DC motor 100 is connected through suitable circuitry (not shown) for 
maintaining a desired speed relationship between the press drive and motor 
100 and ultimately between form roller 80 and plate cylinder 34. 
A silent chain 102 extends about a portion of the periphery of sprocket 95 
and engages teeth on sprocket 110 which is bolted or otherwise secured by 
an air clutch 112 to a drive shaft 115 which is drivingly connected to 
journalled end of 86 applicator roller 80. Air clutch 112 comprises an 
input segment 114 and an output segment 115 for permitting rotation of 
drive shaft 115 in one direction only. 
As illustrated in FIG. 14 of the drawing, the tension in silent chain 102 
is maintained by a pair of idler sprockets 116 and 117. Idler sprocket 116 
is spring urged away from the axis of plate cylinder 34 so that sprocket 
116 may move inwardly toward the axis of plate cylinder 34 when surfaces 
of applicator roller 80 and the plate cylinder 34 are separated, for 
example, when the inker is moved to an "off impression" position. 
The output segment 115 of clutch 112 has a drive shaft supported by 
bearings and connected through a coupling 118 to the applicator roller 
journal 86 which is rotatably supported by bearings 119. 
It has been observed that when a roller having a resilient surface is urged 
into pressure indented relation with a hard surfaced roller, and the 
rollers are frictionally driven with a dry nip therebetween, the surface 
speed of the resilient roller will be less than the surface speed of the 
hard surfaced roller. Further, it has been observed that when the 
indentation between the resilient roller and the hard roller is adjusted, 
the relative speeds of the rollers will change, the surface speed of the 
resilient roller decreasing relative to the surface speed of the hard 
surfaced roller as the indentation is increased. 
It should be readily apparent that speed control device 90 permits 
adjustment of the surface speed of applicator roller 80 relative to the 
surface speed of plate 34 for causing applicator roller 80 to be driven at 
a desired surface speed even though the diameters of cylinders 80 and 34 
may change as a result of thermal expansion or if it is necessary, under 
certain operating conditions, to adjust pressure at the nip N between the 
applicator roller 80 and printing plate 34. This is sometimes necessary 
under normal operating conditions for applying different inks to different 
printing plates to prevent scumming and slurring, to maintain a proper dot 
size, shape and dimension. 
It is contemplated that speed control device 90 will normally be employed 
for making very slight changes in the relative surface speed of the 
applicator roller 80 relative to printing plate cylinder 34, for example, 
the surface speed of the surface 85 on applicator roller 80 might only be 
changed a maximum of about two or three percent of the surface speed of 
plate P on plate cylinder 34 for establishing the desired speed 
relationship between the roller surfaces. 
As noted herein before, the primary function of speed control device 90 is 
to drive applicator roller 80 in a true rolling relationship relative to 
the plate cylinder 34 to prevent undesirable deformation and, skidding, of 
the resilient surface of applicator roller 80 at the nip N between the 
rollers. 
We have observed that when the applicator roller drive 90 is adjusted to 
assure that the surfaces of the applicator roller 80 and plate cylinder 34 
are in true rolling relation, the terminology generally referred to as 
"gear streaks" is not observed on printed sheets. This is believed to 
result from the fact that applicator roller 80 has sufficient size and 
mass to provide a substantial inertia, which when combined with a smooth 
and true rolling relationship between the applicator roller 80 and plate 
cylinder 34, minimizes disturbance to the rotation of the cylinders and 
results in a smooth even printed ink film on the sheet or web 37. 
VIBRATOR ROLLER DRIVE 
A prime safety consideration in the design of the vibrator drive is to have 
all major drive components, which oscillate and/or rotate the vibrators, 
to be located on the outside of the inker sideframes and to enable quick 
removal of the vibrators from the inker. 
The mechanism for oscillating vibrator rollers 120 and 122 and vibrator 
rollers 124 and 126 is best illustrated in FIGS. 1, 4, 5, 14, 15 and 16. 
As best illustrated in FIGS. 5 and 16, the journal 86 of applicator roller 
80 is rotatably mounted in bearings 119 to the gear side sideframe 33 of 
the inker. As hereinbefore described, journal 86 is connected through a 
coupling 118 to the output of shaft 115 of clutch 112. Shaft 115 has a 
pair of gears 130 and 132 mounted thereon, as best illustrated in FIGS. 16 
and 18. Gear 130 is disposed in meshing relation with an idler gear 131 
mounted on a stub shaft 131a on the gear side sideframe 33 of the inker. 
Idler gear 131 imparts rotation to a gear 133 on a cross shaft 135 having 
opposite ends rotatably journaled in sideframes 32 and 33 of the inker. 
The end of cross shaft 135 which is rotatably journaled in the operator 
side sideframe 32 has a gear 136 mounted thereon in meshing relation with 
a gear 138 rotatably supported by a stub shaft 138a on operator side 
sideframe 32. Gear 138 has a crank plate 140 adjustably secured to the 
surface thereof as best illustrated in FIG. 1 of the drawing. Crank plate 
140 supports an eccentrically located crank pin 142 which is pivotally 
connected to one end of a link 144, the other end of which is pivotally 
connected to a crank arm 145 which is keyed or otherwise secured to a 
rocker shaft 146 mounted in bearings in bearing blocks 147. Rocker arms 
148 and 150 are mounted on opposite ends of rocker shaft 146 and have 
eccentric shaft cam follower rollers 152 rotatably secured thereto. 
As best illustrated in FIGS. 1 and 4 of the drawing, rollers 152 having 
shafts eccentric to the roller portion alternately push vibrator rollers 
120 and 122 to the gear side as viewed in FIG. 4 of the drawing. Eccentric 
shaft cam follower rollers 152 may be adjusted in rocker arms 148 and 150 
to take up manufacturing tolerances to eliminate looseness in the 
engagement with the ends of vibrator rollers 124 and 126. The rollers 152 
on rocker arm 150 similarly operate vibrator rollers 124 and 126. 
From the foregoing it should be readily apparent that rotation of shaft 115 
imparts rotation to journal 86 of roller 80 and gear 130 that imparts 
motion to idler gear 131 which in turn imparts rotation through gear 133, 
cross shaft 135 and gear 136 to gear 138 which in turn rotates crank plate 
140. Rotation of adjustable crank plate 140 imparts sinusoidal 
reciprocating motion through pin 142 to link 144 to the crank arm 145 for 
imparting rotary oscillation to rocker shaft 146. Rotation of rocker shaft 
146 in a clockwise direction that is viewed in FIG. 4 of the drawing urges 
the end of vibrator roller 120 to the right as viewed in FIG. 4. 
Referring now to FIG. 15 of the drawing, movement of vibrator roller 120 to 
the right causes force to be exerted by the end of vibrator roller 120, 
through roller 152 on rocker arm 149 mounted on a stub shaft 147 rotatably 
secured between bearings in bearing blocks 147a and 147b on the gear side 
sideframe 33. 
As rocker arm 149 rotates in a clockwise direction as illustrated in FIG. 
15 of the drawing, force is exerted through roller 152 on the lower end of 
rocker arm 149 for urging vibrator roller 126 to the left as viewed in 
FIG. 15. 
As will be hereinafter more fully explained, vibrator roller 122 is used as 
a washup roller and therefore is preferably positively rotatably driven 
while the other vibrator rollers 120, 124 and 126 are idler rollers 
rotatably driven through friction contact with roller 80. As best 
illustrated in FIGS. 15 and 16 of the drawing, the gear 132 on output 
shaft 115 of the clutch 112 which drives applicator roller 80 is 
positioned with meshing relation with idler gears 134 in meshing relation 
with a gear 137 keyed or otherwise secured to the end of vibrator roller 
126. Thus, vibrator roller 126 is positively driven and will rotate even 
when lightly striped in to the surface of applicator roller 80, when 
engagable with a washup blade, or when the surfaces of applicator roller 
80 and vibrator roller 126 are covered with a relatively slick, thin 
washup solution. 
From the foregoing it should be readily apparent that vibrator rollers 120 
and 122 oscillate in opposite directions and when reversing direction will 
apply a substantially balanced load to rollers 152 on rocker arms 148 and 
149. Similarly, vibrator rollers 124 and 126 move in opposite directions 
and exert substantially uniform loading to vibrator roller ends through 
rocker arms 150 and 151 adjacent opposite sides of the inker. 
The vibrator roller drive hereinbefore described, because of the movement 
of the various rollers in opposite direction simultaneously, does not 
apply an oscillatory loading on the form roller either circumferentially 
or axially thereof. Thus, the vibrator roller drive mechanism contributes 
to elimination of any gear and virtually all other streaks which have 
heretofore been observed in virtually all rotary printing presses. 
As hereinbefore noted, vibrator roller 122 is positively driven to 
facilitate use of that roller as a washup roller for removing ink from the 
inked rollers. As best illustrated in FIGS. 1 and 6 of the drawings, a 
washup tray 155 is positionable for positioning a doctor blade in 
engagement with the surface of roller 122 for scraping ink and a washup 
solution from the surface of roller 122 for removing all of the ink from 
the inked rollers 80, 120, 122, 124 and 126 when applicator roller 80 is 
thrown off impression and out of engagement with the plate cylinder 34 and 
separated from dampener D. 
As best illustrated in FIGS. 4, 6 and 17 of the drawings, opposite ends of 
vibrator rollers 120, 122, 124 and 126 are rotatably secured in 
self-aligning sleeve bearings 172 mounted in slide blocks 174 which slide 
in grooves formed in the inker sideframes 32 and 33, respectively, and are 
captured in position by retainer plates 176. Each slide block 174 is urged 
in a direction away from the surface of applicator roller 80 by a spring 
178. A pressure adjustment screw 180 is threadedly secured in a support 
bar 182 which engages the upper surface of the slide block 184. Thus, a 
stripe between applicator roller 80 and each of the vibrator rollers 
120-124 is adjustable by the rotation of the pressure adjustment screw 
180. 
As best illustrated in FIG. 17 of the drawing, each support bar 182 is 
mounted to provide a "night latch" to facilitate reducing pressure between 
vibrator rollers 120-124 and applicator roller 80 when the press is to be 
stopped for any substantial period of time. One end of support bar 182 is 
pivotally connected by a pin 184 to the inker sideframe. The opposite end 
of support bar 182 is urged inwardly by an end surface 186 on a latch 
member 188 pivotally connected by a pin 189 to the inker sideframe. When 
latch member 188 is in the position illustrated in FIG. 17, pressure 
adjustment screw 180 carried by support bar 182 will urge slide block 184 
to a position wherein the vibrator roller carried thereby is urged into 
engagement with the applicator roller 80 to establish a predetermined 
pressure. Latch member 188 has a second surface 190 on a side, surface 190 
being spaced radially closer to the axis of pin 189 than is the end 
surface 186. Thus, when latch member is rotated 45.degree. as viewed in 
FIG. 17 of the drawing, end surface 186 will be disengaged from support 
bar 182 so that spring 178 will urge slide block 174, pressure adjustment 
screw 180 and support bar 182 away from the surface of applicator roller 
80 into engagement with the second surface 190. This reduces pressure 
between the surfaces of applicator roller 80 and vibrator rollers 120-124 
to prevent the formation of a stripe (permanent set) on the curved 
surfaces of the rollers which may result when the rollers are left urged 
into pressure indented relation for a significant period of time while the 
rollers are not rotating. 
Each latch member 188 has a pin wrench socket formed in the end thereof to 
facilitate actuation of the latch mechanism between the "on impression" 
and "off impression" positions. The pressman need only insert the wrench 
in the pin wrench socket and rotate latch member 188 through an angle of 
45.degree. to establish or relieve pressure between surfaces of the 
vibrator rollers and the applicator roller 80. 
END DAMS 
End dams 160 illustrated in FIGS. 6, 13 and 17 comprise a pair of plates 
secured together by a transversely extending member 162 which forms the 
rear wall of the reservoir R defined between end dams 160 and bounded on 
the front side by metering member 40 and holder 50. 
Each end dam 160 and transverse member 162 is supported by a lug 164 
pivotally secured to arm 166 by pin 165. Pin 165 is supported in arm 166 
that has one end pivotally secured by a pin 167 to the inker sideframes. 
The opposite end of the arm 166 has a pointer formed thereon which moves 
adjacent indicia plates 168 to facilitate aligning transverse extending 
member 162 parallel to the surface of the roller 80 and for establishing 
the optimum sealing relationship between end dams 160 and the ends of 
applicator roller 80, as will be more fully explained. End dam alignment 
screw 169 are threadedly secured to arms 166 adjacent each side of the 
printing press and engage locking screws 170 inside frames to permit 
movement of each of the arms 166 adjacent opposite sides so that they will 
be positioned precisely parallel. Locking screws 170 secure each arm 166 
in position after the optimum parallel relationship has been established. 
Each end dam 160 has a curved and ground lower surface which has a radius 
of curvature equal to the radius of curvature of the outer surface of 
applicator roller 80 and is urged into sealing relation with opposite ends 
of applicator roller 80 by force of gravity or by an adjustable spring 
biased means for the dams 160 and member 162 about pivot pin 165. 
DAMPENING FLUID REMOVAL DEVICE 
Referring to FIGS. 6 and 12 of drawing, the numeral 200 generally 
designates a dampening fluid removal device of the type disclosed in 
International Application Ser. No. PCT/US81/01213, filed Sept. 8, 1981, 
entitled "Dampening Fluid Removal Device," the disclosure of which is 
incorporated herein by reference in its entirety comprising a doctor blade 
202 secured to a support bar 204 having cylindrical openings 205 formed in 
opposite ends thereof. A piston 206 extends into each of the cylindrical 
openings 205 and is limited in travel by stop lug 104a secured to support 
bar 204 which engage adjustment screws 208 extending through lugs 210a on 
U-shaped mounting brackets 210 to adjust the position of the support bar 
when the cylindrical openings 205 are pressurized. Springs 211 in support 
bar 204 engage a second lug 210b on the U-shaped mounting bracket for 
urging support bar 204 to a position separating doctor blade 202 from the 
surface of applicator roller 80 when the cylinders are depressurized. 
Mounting brackets 210 are pivotally connected by pins 214 to Haner 212 
secured to sideframes 32 and 33 by screws 212a. Hangers 212 can be rotated 
about screws 212a by loosening lock screws 212b which extend through an 
arcuate slot in hanger 212 to adjust the angle of engagement of doctor 
blade 202 relative to applicator roller 80. 
Dampening fluid removal device 200 may be removed from its mounted position 
and rotated for cleaning by disengaging locking pins 216 from hangers 212 
allowing pivot pins 214 to slide down stepped slots 212c and engage lugs 
212d. 
As will be hereinafter more fully explained, pressurized air is delivered 
into chamber 205 when the dampening system is thrown "on-impression" for 
moving doctor blade 202 into engagement with the surface of applicator 
roller 80. When the dampener is thrown off impression, pressurized air is 
exhausted from chamber 205 and spring 211 moves doctor blade 202 out of 
engagement with surface of applicator roller 80. 
PNEUMATIC CONTROL SYSTEM 
The pneumatic control circuit 240 as illustrated in FIGS. 1, 14, 18, 19, 
and 20 delivers pressurized air to cylinder 38 which moves applicator 
roller 80 into pressure indented relation with the plate cylinder 34; the 
cylinder 65 which urges the metering member 40 into indented relation with 
the resilient surface 85 of the applicator roller 80; the cylinders 300 
which moves the hyrdophilic dampening fluid transfer roller into pressure 
indented relation with the applicator roller 80; the cylinder 205 which 
urges the doctor blade 202 into pressure indented relation with the 
applicator roller 80 to remove dampening fluid; and the air clutch 112 
which transmits torque to rotate applicator roller 80. In FIGS. 14 and 19 
of the drawing, solonoids 242 and 244 control the indentation of metering 
member 40 into the resilient surface 85 of applicator roller 80. 
Solonoid 246 controls the flow of pressurized fluid through lines 246a and 
246b to cylinders 38 adjacent opposite sides of inker for moving 
applicator roller 80 into and out of pressure indented relation with the 
printing plate 34. 
Solonoid 248 is connected to actuate clutch 112 through line 248a. 
Solonoid 250 actuates cylinders 300 through lines 250a and 250b which move 
the hydrophilic dampening fluid transfer roll 226 "on" or "off" and also 
controls the single acting cylinders 205 through line 250c which moves the 
dampening fluid removal blade into and out of engagement with a surface of 
the applicator roller 80. It will be noted that a single solonoid 250 
causes cylinders 205 and 300 to be actuated simultaneously. Thus, when the 
dampener is thrown on for delivering dampening fluid to the applicator 
roller 80, the cylinder 205 will be actuated simultaneously for removing 
said dampening fluid from the applicator roller 80. 
The pneumatic control circuit 240 comprises a source of pressurized fluid 
252, such as an air compressor which delivers pressurized fluid through a 
pressure regulator 254 for establishing a line pressure of, for example, 
80 pounds per square inch to high pressure line 255. 
Each of the solonoid actuated valves 244-250 is of identical construction 
and are illustrated in an energized position. As illustrated in FIG. 19 of 
the drawing, high pressure line 255 is connected to a central inlet port 
of each of the solonoid actuated valves. 
In the energized position as illustrated in FIG. 19 of the drawing, each of 
the cylinders 38, 65, 205 and 300 is actuated to extend rods in the 
cylinders by pressure from high pressure 255 while the rod end of each of 
the cylinders is connected through an exhaust port of valves 242, 246, 248 
and 250 to a low pressure or exhaust line 257. Further, high pressure line 
255 is connected through solonoid actuated valve 248 to energize clutch 
112. 
When the solonoid actuated valves 246, 248, and 250 are de-energized, high 
pressure line 255 will be connected to the rod end of each of the 
cylinders while the base of each of the cylinders is connected to a low 
pressure or exhaust line 259. 
Each exhaust line 257 and 259 is provided with a muffler 260 and 261. 
To assure that the edge of metering member 40 is not excessively indented 
into resilient roller surface, a pressure regulator 245 is positioned in 
the line 242a leading to the base of cylinder 65. Regulator 245 has an 
adjustable output pressure and is employed for reducing pressure from high 
pressure line 255 which may be at, for example, 80 pounds per square inch 
to a control pressure of, for example, 60 pounds per square inch. This 
safety device or control pressure is preferably established by adjusting 
regulator 245 while the inker is running. 
Solonoid actuated valve 244 is connected to a low pressure line 265, 
carrying compressed air at a pressure of, for example, 10 pounds per 
square inch, the pressure being regulated by a vent pressure regulator 
266. 
When the inker is initially energized by closing an electrical circuit to 
turn the unit on, solonoid actuated valve 248 will be energized for 
delivering pressurized air through line 248a to clutch 112 for engaging 
the clutch to enable clutch 112 to transmit torque to the applicator 
roller 80 when the press drive is energized. 
Also when the press is started, solonoid 244 will be shifted to deliver 
high pressure air to double acting solonoid valve 242 for moving the 
metering edge on metering member 40 from a very lightly indented position 
to the indentation which is required for metering a film of ink onto the 
applicator roller. High pressure air is supplied through line 255b to 
valve 244 and low pressure air is supplied through line 265b. Valve 242 is 
shown in the energized normal running position. When valve 242 is 
energized to the cleaning position, pressurized fluid is delivered through 
the line 242b to lift the metering member. 
When the "print on" button is pushed on the control, solonoid actuated 
valve 250 is immediately actuated for moving the hydrophilic roller on the 
dampener into engagement with the applicator roller 80 for delivering 
dampening fluid to applicator roller 80. Simultaneously, cylinder 205 is 
actuated for removing excess dampening fluid from the surface of 
applicator roller 80. When the "print on" circuit is closed, the signal is 
delivered through a time delay device for energizing solonoid actuated 
valve 248 after a predetermined period of time for delivering pressurized 
fluid to cylinders 38 for moving applicator roller 80 into engagement with 
the printing plate. 
DAMPENING SYSTEM 
The dampener 225 comprises a hydrophilic transfer roller 226 and a 
resilient covered metering roller 228 rotatably secured to hangers 230. 
Dampeners of this general configuration are well known to persons skilled 
in the art and further description thereof is not deemed necessary. 
However, such dampener is of the type disclosed in Dahlgren U.S. Pat. No. 
3,343,484, dated Sept. 26, 1967, entitled "Lithographic Dampener With 
Skewed Metering Roller," the disclosure of which is incorporated herein by 
reference. 
As best illustrated in FIGS. 1, 2, 17 and 17A, throw-off cylinder 300 has a 
lower end pivotally connected to the frame member 32' by a lug 232 and a 
rod pivotally connected to a bell-crank 234. Bell-crank 234 is secured by 
a pin 235 and angle bracket 236 to frame member 32'. 
The dampening fluid metering roller 228 is provided with a night latch 
mechanism similar to that hereinbefore described for the vibrator rollers 
102-124. As best illustrated in FIG. 17 of the drawing, latch member 194 
is pivotally connected by a pin 198 to a slide bar 199 wherein is located 
pressure adjustment screw 197. Latch member 194 is also pivotally secured 
by a pin 193 to one end of a link (not shown) the other end of which is 
pivotally secured by a pin 196 to hangers 230. Pin 198 pivotally connects 
latch member 194 to a slide bar 199 which supports pressure adjustment 
screw 197. 
As viewed in FIG. 17, latch member 194 is in the on impression position 
wherein slide bar 199 and pressure adjustment screw 197 are urged to the 
innermost position. When latch member 194 is rotated 45.degree. in a 
counterclockwise direction, as viewed in FIG. 17, pin 193 will be elevated 
allowing movement of pin 198 and slide bar 199 outwardly for reducing 
pressure between the metering roller and transfer roller of the dampening 
system.