referring now to fig1 the dampening and inking device of the present invention is comprised by a pair of spaced frame members 10 , only one of which s shown in fig1 the frame members 10 being arranged in spaced parallel relation , and secured in any convenient manner against movement relative to each other . the frame members 10 provides end supports , respectively , for a printing cylinder 12 adapted to carry a printing plate [ not shown ], a form roll 14 and a metering roll 16 . the metering roll 16 , in use of the device , extends into a trough 18 to which a metered quantity of water and printing ink is supplied , as is well known in the art . alternatively , the metered supply of water and printing ink can be fed to the nip between the form roll 14 and the metering roll 16 . thus , upon rotation of the printing cylinder 12 , the form roll 14 is rotated at a peripheral speed corresponding with the peripheral speed of the printing cylinder 12 and in turn , the metering roll 16 is rotated at a peripheral speed corresponding with the peripheral speed of the form roll 14 . rotation of the metering roll 16 will cause it to pick up on its surface a film of water and printing ink , which is then carried into the nip between the form roll 14 and the metering roll 16 . the pressure between the form roll 14 and the metering roll 16 is then adjusted in order that only a metered quantity of water and printing ink can pass through the nip and remain on the surface of the form roll 14 as a metered film of water and printing ink . to further equalize and distribute the water and ink film on the surface of the form roll 14 , optionally , according to the present invention , an axially oscillating form assist roll 20 is provided in pressure contact with the surface of the form roll 14 , the assist roll 20 acting to distribute and emulsify the film of water and printing ink on the surface of the form roll 14 during axial oscillation of the form assist roll 20 . any convenient mechanism can be provided for oscillating the form assist roll 20 , such mechanisms being well known in the art . the metered film of water and printing ink in emulsified or partially emulsified form is then carried by the form roll to the nip between the form roll 14 and the printing cylinder 12 , at which point the metered film of water and printing ink is deposited on the printing plate carried by the printing cylinder 12 . printing then proceeds from the printing plate carried by the printing cylinder 12 in an entirely usual manner as well known in the art . as will be readily apparent , adjustment of the relative positions of the form roll 14 relative to the printing cylinder 12 and the position of the metering roll 16 relative to the form roll 14 now become extremely critical . specifically , the pressure exerted between metering roll 16 and the form roll 14 must be only sufficient to permit the required metered quantity of water and ink to pass through the nip between those rolls , otherwise , an excessive amount of water and ink would be fed to the printing plate carried by the printing cylinder 12 with disastrous consequences . further , the pressure between the form roll 14 and the printing cylinder 12 must be adjusted with extreme accuracy , otherwise , an excessive quantity of water and printing ink would be built up at the nip between the printing cylinder 12 and the form roll 14 if the pressure is too great , with consequential under - inking of the printing plate , or , in the event that the pressure between the printing cylinder and the form roll 14 is too low , then , flooding of the printing plate will occur . these considerations are ones which are well known in the art and which are common to most forms of rotary printing . however , it is at this point that a major problem emerges , that problem now being discussed with reference to the diagrammatic illustration of the prior art mechanism of fig2 . in order to secure rotation of the metering roll 16 in timed relation with the printing cylinder 12 , this being one of the essential parameters , some form of drive must be provided between the printing cylinder 12 and the metering roll 16 . this is accomplished by providing a spur gear 12a which is fixed to and rotatable in unison with the printing cylinder 12 , the spur gear 12a in turn driving an idler gear 14a , which , according to the prior art teachings , is fast with the form roll 14 . the idler gear 14a , in turn meshes with a driven gear 16a , fast with the metering roll 16 . thus , upon rotational movement of the printing cylinder 12 , a corresponding rotational movement is produced in both the form roll 14 and the metering roll 16 to maintain their circumferential velocity in correspondence with the circumferential velocity of the printing cylinder 12 . any lack of identity between the peripheral velocities of the printing cylinder 12 , the form roll 14 and the metering roll 16 will result in &# 34 ; scuffing &# 34 ; of the printing plate , i . e ., will result in the emulsion of water and printing ink carried by the form roll 14 being smeared onto the printing plate , with consequential disastrous effects on the printed image , and wearing of the printing plate . while the maintenance of identical peripheral speeds is one essential parameter , further parameters are involved , namely , the extent of compression between the printing cylinder 12 and the form roll 14 , and the extent of compression between the metering roll 16 and the form roll 14 . as these variables cannot be accommodated within manufacturing tolerances of the device , some means must be provided for accommodating these variables . according to the prior art , and as illustrated in fig2 in order to provide for adjustment of the pressure between the printing cylinder 12 and the form roll 14 , the shaft on which the form roll 14 and its associated idler gear 14a are mounted is supported for adjustable movement towards or away from the axis of the shaft 12b on which the printing cylinder 12 and its associated drive gear 12a are mounted . however , movement of the shaft 14b towards the shaft 12b in order to increase the pressure at the nip between the printing cylinder 12 and the form roll 14 will have the effect of causing the teeth of the gears 12a and 14a to move towards or into bottoming relation with each other and will result in excessive noise and vibration produced in the gearing and which is transmitted to the form roll 14 . movement of the shaft 14b away from the shaft 12b , to the contrary , will cause the teeth of the gears 12a and 14a to move out of correct meshing engagment with each other and will result in free play and chatter in the teeth . free play and chatter in the teeth will have the effect of permitting unrestrained movement of the form roll 14 relative to the printing cylinder 12 both in forward and reverse directions , and will result in gear markings in the finished print . this is due to smearing in the forward circumferential direction of the printing cylinder in the event that the form roll overspeeds or reverse smearing of the printing cylinder in the event that the form roll underspeeds , this manifesting itself in the finished print as transverse lines of smearing in the finished print . a closely similar condition arises between the metering roll 16 and the form roll 14 in the event that the position of the shaft 14b of the form roll 14 is adjusted relative to the shaft 16b of the metering roll 16 . again , excessive noise can be produced in the gearing in the event that the gear teeth 14a and 16a bottom down on each other . in the event that free play exists between the gear teeth 14a and 16a , then chatter can occur between the gear teeth 14a and 16a , and the respective rolls can move within the extent of the free play in the gear teeth , with consequential disturbances in the film of water and printing ink metered onto the surface of the form roll 14 . referring now to the diagrammatic illustration of fig3 the device of the present invention overcomes this problem in its entirety in an extremely simple and entirely satisfactory manner , as is now fully described in detail . referring now to fig3 the respective gears 12a , 14a and 16a are each mounted on fixed and immovable axes , such that optimum meshing of the teeth of the respective gears is provided without regard to adjustments made in the position of the form roll 14 and the metering roll 16 . contrary to the proposals of the prior art , the form roll 14 , instead of being mounted for rotation about an axis coincident with the axis of the idler gear 14a , is mounted for movement of its longitudinal axis in an orbital path 22 relative to the fixed axis 14b of the idler gear 14a . similarly , and if desired , the metering roll 16 can be supported in an identical manner to the form roll 14 for movement of the longitudinal axis of the metering roll 16 in an orbital path about the fixed axis 16b of the driven gear 16a . the manner in which this orbital movement of the axis of the form roll 14 , and if required , that of the metering roll 16 , can be accomplished will now be described with reference to fig4 and 5 . referring firstly to fig4 one end of the respective printing cylinder and rolls is shown in association with one of the frame members 10 . the printing cylinder 12 is illustrated as carrying a spur gear 12a which is pinned thereto at 30 for rotation in unison therewith . the spur gear 12a is driven from a main drive of the printing press in any convenient manner , thus causing rotation of the printing cylinder about the fixed shaft 32 . the spur gear 12a in turn meshes with the teeth 14a of an idler gear 34 which is journaled for rotation on a fixed bearing 36 . the teeth 14a of the idler gear 34 in turn mesh with the teeth 16a of the driven gear of the metering roll 16 , which conveniently is pinned at 36 to the metering roll 16 for rotation in unison therewith , the metering roll 16 being journaled for rotation on a fixed shaft 38 . as has been previously explained , the form roll 14 is not mounted for rotation in unison with the idler gear 34 . instead , the form roll 14 is rotatable relative to the idler gear 34 , and in addition , the axis of rotation of the form roll 14 is displaceable on an orbital path relative to the idler gear 34 . thus , without regard to the position of the form roll 14 and its longitudinal axis , each of the gears 12a , 14a , 16a , remain journaled about a fixed axis , the respective axes being immovable one relative to the other . referring now to fig5 which shows the mounting of the form roll 14 in enlarged detail , the form roll 14 is shown as extending between the opposed end frames 10 , 10 . the bearing 36 is fixedly held in one of the end frames 10 , conveniently , by means of a threaded bolt 50 extending through a washer 52 , the bolt 50 being threaded into an axial extension 54 of the bearing 36 . the extension 54 can be cylindrical in cross - section , or of any other cross - sectional shape , the sole requirement being that the bearing 36 be immovable and that it provide a support for the idler gear 14a . extending within the form roll 14 is an anti - friction sleeve 56 which conveniently is a tubular sleeve of brass having a low coefficient of friction . the form roll itself is formed from a relatively hard resilient but compressible rubber or rubber like material , and conveniently can be formed from an elastomer . extending within the anti - friction sleeve 56 is a shaft 58 having an eccentric 60 - 62 at each of its opposite ends . while the eccentric 60 and 62 can be of different diameter , the essential condition is that the longitudinal axis of the respective eccentrics be coincident with each other along the central longitudinal axis 64 . the longitudinal axis 66 of the shaft 58 is located in staggered relationship relative to the longitudinal axis 64 . thus , rotation of the shaft 58 and its associated eccentrics 60 and 62 will cause the longitudinal axis of the shaft 58 to move in an orbital path about the longitudinal axis of the eccentrics 60 and 62 , i . e ., to move in the orbital path described with reference to fig3 . any convenient means is provided for rotating the shaft 58 about the longitudinal axis 64 . as illustrated , this can be accomplished by means of a handle 72 pinned to the eccentric 62 at 70 . the handle 72 can be manually actuated , or , as will be well understood , it can be actuated under the control of a micrometer screw arrangement diagrammatically indicated at 74 . while the structure for adjusting the form roll 14 has been described with particular reference to fig5 it will be appreciated that the metering roll 16 can be adjustably mounted in an identical manner to that described with reference to fig5 in order to ensure correct meshing of the teeth of the respective gears 12a , 14a and 16a , without reference to the position of adjustment of either the form roll 14 or the metering roll 16 . as will be appreciated , various modifications may be made in the preferred embodiment described above without departing from the scope of the invention as defined by the appended claims . for example , the idler gear 14a could be journaled for rotation directly on the adjacent end frame 10 , and , the eccentric 60 journaled for rotation directly in the associated end frame 10 , this being in accordance with the specific requirement of the present invention that the idler gear 34 be mounted for rotation about a fixed axis , whereas the axis of rotation for the shaft 58 is adjustable on an orbitable path relative to that fixed axis .