US2990770A - Ink feed mechanism - Google Patents

Description

4 Sheets-Sheet 1 July 4, 1961 R. E. LINDEMANN INK FEED MECHANISM Filed Dec. 22, 1958 IN VEN TOR. R0861? r5. L INDEMA NN 5 4 ArroezvEys July 4, 1961 R. E. LINDEMANN INK FEED MECHANISM 4 Sheets-Sheet 2 Filed Dec. 22, 1958 INVEN TOR. xsoemrfl/weMA/wv fiahm July 4, 1961 R. E. LINDEMANN 2,990,770

INK FEED MECHANISM Filed Dec. 22, 1958 4 Sheets-Sheet 3 IN VEN TOR. ROBERT E. L INOEMflN/Y Arron/v5 vs July 4, 1961 R; E. LINDEMANN INK FEED MECHANISM 4 Sheets-Sheet 4 Filed Dec. 22, 1958 I N KER co NTRO LS INVENTOR. fioseprf-l/Na'MAfi v WM Arr-o RNE ya fie. 6

United States Patent 2,990,770 INK FEED MECHANISM Robert E. Lindemann, Medina, Ohio, assignor to Harris- Intertype Corporation, Cleveland, Ohio, a corporation of Delaware Filed Dec. 22, 1958, Ser. No. 782,094 11 Claims. (Cl. 101-364) improvements in the feeding of ink to a printing press. Usually the inking mechanism includes a fountain roll that is rotatable in a bath of ink, and a ductor roll which swings back and forth from a position in contactwith the fountain roll to a position in contact with a driven roller forming part of the printing press, whereby ink in desirable amounts is deposited upon the last named roll. The present invention has to do with the operation of the fountain roll. That roll turns forward a small increment at a time, that is its driving mechanism may be said to oscillate, imparting driving motion to the fountain roll in one direction only, its movement in the opposite directionbeing an idling movement.

Ink fountain rolls of this general type are normally intermittently driven by a pawl and ratchet. The ratchet is fastened to the roll and the pawl is moved through a fixed angle during every other revolution of the press. A masking means is interposed between the pawl and the ratchet teeth for the purpose of varying the extent of movement of the roll for each oscillation of the pawl. The masking means is arcuately adjustable about the axis of the fountain roll, and the extent of adjustment of the mask may be great enough so that the pawl is prevented from engaging any of the ratchet teeth whatsoever during oscillation. When so adjusted the fountain roll will remain stationary.

There are two main difficulties with the pawl and ratchet type of drive for a fountain roll. The first is that the extent of adjustment is limited by the angle between the teeth of the ratchet and therefore the drive is not infinitely adjustable. The second objection is that the pawl and ratchet type of drive is not suitable for high speed machines where the impact of the pawl against a tooth may be severe upon contact since the pawl is moving at the time of engagement. Both of these disadvantages can be overcome by using an overrunning clutch of the indexing type connected to a variable stroke drive, instead of using a fixed stroke drive and its cooperating means for masking out a portion of the drive as is customary with the pawl and ratchet type of mechanism. The indexing clutch permits an infinite adjustment of the drive mechanism, and also enables driving of an ink fountain roll at high speeds without breakage or wear of parts due to impact.

With a pawl and ratchet it is a simple matter to move the mask to a position to prevent rotation of the fountain roll. This is not possible with an indexing clutch however, because the parts are enclosed. It was therefore necessary to provide another form of means for disconnecting the fountain roll from the drive during operation of the drive. It was also desirable to have a drive which was simple in construction, easy and cheap to manufacture, and easy to operate. These objectives I have attained by taking the adjusting mechanism for the drive and bodily moving it rapidly to a position corresponding to an adjustment position which would give no rotation of the roll when the drive was in operation. By so doing, the adjustment itself is moved but not destroyed, and can be restored.

While the present invention was designed primarily to enable use of an overrunning clutch, its simplicity makes it desirable also for use with a pawl and ratchet type mechanism which does not have a masking member.

This invention relates to ice The pawl of such a device would back over the ratchet teeth on the return stroke and drop into the last tooth prior to being driven forward the next time. This in itself would be an advantage over present pawl and ratchet drives using a mask, because the pawl would always engage before it started forward, and not during the forward movement as in the case where a pawl drops off its mask at high speed.

One of the objects of the invention is to enable a press operator to prevent actuation of the fountain roll whenever the press is running with the fountain blade in operative position, but without ink in the fountain. Under such conditions the blade can wear against the rotating roll, and either the roll or the blade may be scored to such an extent that the future accuracy of metering may be seriously impaired.

Another object is to provide means for disconnecting an ink fountain drive when using an infinitely variable indexing clutch.

A further object is the provision of means for bodily moving the adjusting means to rapidly disconnect the fountain roll drive while the printing press is running.

Another object is to provide a novel worm and worm wheel rotary adjustment for an ink fountain roll drive, wherein the worm is mounted in such a way as to be axially movable to cooperate rapidly with the worm wheel in the manner of a rack and pinion.

Still another object is to provide a linkage drive with adjusting means and rapid throwoif of the adjustment, the linkage being arranged so that the resultant forces exerted thereby will urge the adjusting means in the direction of throwoif.

Other objects and features of novelty will appear as I proceed with the description of that embodiment of the invention which, for the purposes of the present application, I have illustrated in the accompanying drawings, wherein- FIG. 1 is a side elevation of the intermittent driving means for the fountain roll, with latch means for holding the mechanism in adjusted position, the latch means and drive means being capable of rapid actuation to disconnect the driving mechanism from the overrunning clutch;

FIG. 2 is an elevational side view with the parts in zero position, that is to say the position in which no actuation is imparted to the fountain roll;

FIG. 3 is a similar view with the parts in the maximum drive position, that is to say the position in which the active stroke of the oscillation imparted to the fountain roll is at its maximum;

FIG. 4 is an end view taken at right angles to FIGS. 1 and 2 and inside the machine casing, as indicated by the line 4-4, FIG. 2;

FIG. 5 is an elevational view externally of the casing, showing the control means;

FIG. 6 is a fragmental sectional view taken substantially on the line 6-6 of FIG. 1; and

FIG. 7 is a fragmental sectional view taken substantially on the line 7-7 of FIG. 1.

In FIG. 2 the ink fountain roll is indicated at20. The driving and driven parts of the overrunning clutch are carried in closed housings shown at 2-1 and 22 respectively. The bottom of the ink fountain is constituted by a blade 23 which bears against the roll 20, the supply of ink being contained in the fountain between the blade 23 and the periphery of the roll 20. The roll 20 turns an increment at a time in the direction of the arrow of FIG. 2. The oscillation of the roll driving mechanism is effected by a link or arm 24, which is oscillated back and forth through a variable stroke by mechanism described hereinafter.

Worm wheel 25 is mounted on shaft 26, which turns through a limited are about a fixed axis. It carries a radially disposed arm or link 27 which may be adjusted along with the worm wheel 25 from the position of FIG. 2 to that of FIG. 3, and vice versa. The outer end of link 27 carries a pivot 28 by which it is connected to link 29 in the shape of a three-cornered plate. When the link 27 is in the position of FIG. 2 the parts are disposed to impart zero drive to the link 24. In other words, the link 24 has no motion. On the other hand when the link 27 is in the position of FIG. 3 the parts are disposed to impart maximum drive to the link 24. During normal operation of the press the link 27 will occupy some position intermediate its positions in FIGS. 2 and 3, such that ink is supplied to the press at the desired rate.

A worm 30 meshes with worm wheel 25. It is mounted on shaft 31 that is journalled in bearings carried by a longitudinally movable slide 32 that is guided by top and bottom tracks 33 and 34 which are secured by suitable fastenings onto the casing. Shaft 31 projects outwardly of the casing where a wheel 40 is fastened thereto. By turning the wheel 40 the worm 30 is rotated in one direction or the other and the rotation of the worm is communicated to the worm wheel 25, by which means link 27 is adjusted to move link 27 bodily and provide the desired speed of operation to the inking mechanism, this speed being dependent upon the rotational position of the worm, which in turn controls the linkage that actuates the link 24 through a greater or lesser stroke. A stop 48 limits the movement of the link 27 in a counterclockwise direction and therefore constitutes the maximum ink feed setting.

In the event that it is desired to suddenly stop the feeding of ink while the operation of the press continues, the operator grasps the knob 35 on the end of a lever 36 which is pivoted at 37, and moves it downwardly from the full line position of FIG. 1 to the dotted line position of that figure. This depresses latch 38 down below a notch 39 in the slide 32. Ordinarily, the forces applied to the linkage will tend to move the side 32 leftwardly. The operator may assist these forces by grasping the wheel 40 and pulling it outwardly to the full line position shown in FIG. 2. The worm 30 and the slide 32 in which it is mounted are thereby moved over to the left as in FIG. 2 as far as they will go, that is until a link is encountered by a stop 6 carr'- d by a link 6. The rectilinear movement of worm 30 over to the left causes clockwise rotation of worm wheel 25 and the link 27 carried thereby to move the link 29 and other portions of the drive to the FIG. 2 position. When the drive is subsequently restored to its original operating setting, the wheel 40 is moved to the right to return the parts toward the FIG. 3 position, this movement being terminated by a stop 58 engaged by the slide 32. Link 5 has a fixed pivot 49 and a movable pivot 50 that is pivotally connected with the upper extremity of a link 51 and the lower end of the link 6. Link 51 is reciprocated continuously by a crank wheel 53 rotated in a clockwise direction. Link 51 connected to crank wheel 53 at 54 moves upwardly toward the left and downwardly toward the right. From the FIG. 3 position, link 51 next moves upwardly and swings links 5 and 6 upwardly, link 5 swinging about its fixed pivot 49, and link 6 moving substantially linearly with its pivot 55 moving about pivot 28 of the link 29.

Links 5 and 6 are of identically the same length between pivots. When it is desired to eliminate any motion of roll 20, the pivot 55 of link 6 is caused to lie directly in line with and behind the fixed pivot 49, so that when link 5 swings about its fixed pivot 49 link 6 will swing back and forth about the same axis from the dotted line position in FIG. 2 to a position directly behind the full line position of link 5 in that figure. The links 5 and 6 then swing idly about fixed center 49 without communicating any motion to links 29 and 24. This is the zero position.

On the other hand when ink is being fed normally the upper end of link 6 is not in line with the fixed pivot 49 and the pivotal connection 55 between link 6 and triangular link 29 will swing up and down, communicating motion to pivot 56 at the base end of link 24. Such motion will, of course, be communicated to the driving part of the overrunning clutch.

When worm 30 is manually drawn suddenly to the left the worm will act as a rack, turning the worm wheel 25 clockwise to the FIG. 2 position, shifting triangular link 29 to the zero position of FIG. 2 and interrupting the rotation of the ink fountain roll. The latch 38 in the meantime rides on the bottom surface of slide 32. When it is desired to resume feed, the operator pushes the worm and slide back to the right until latch 38 snaps back into the notch 39 due to the effect of the coil spring "s, whereby the adjustment of the ink feed is returned to precisely the same point as obtained previously.

In order that the operator may be apprised of the setting of the ink feed at any particular time, a bar 41 is locked to shaft 26 by a setscrew 42, FIG. 1. Bar 41 therefore is moved up or down as the adjustment is varied. The outer end of bar 41 carries a depending arm 43 which supports a pointer 44 that travels over a scale 45 on the outside of a plate 47. See FIG. 5. This scale indicates the different rates of relative ink feed effected by the adjustment. Arrows 46 indicates the direction of rotation of the wheel 40 that is required to increase or decrease the rate of feed. Below the scale 45, the plate 47 is provided with a slot therethrough to receive the lever 36.

With the knob 35 in its upper position the latch 38 may rise under the effect of spring s and engage the notch 39 whenever the slide 32 comes into position to permit such engagement. At the same time the slide will encounter stop 58 Which is preferably adjustable. The fine adjustment of the feed is effected by rotating the shaft 31 and the worm 30, the endwise adjustment of the worm being employed merely for quickly throwing off the ink feed or throwing it back to the previous rate of feed. Both adjustments can be effected while the press is in operation.

The linkage referred to above has one position, not used in the ordinary feeding of ink, called the zero position, in which the constant rotation of the crank wheel 53 causes link 51 to reciprocate up and down and links 5 and 6 to swing idly about a center through the axis of fixed pivot 49, but without communicating any motion to link 24. That position is shown in FIG. 2.

The linkage also has variable positions for feeding ink at different rates. In these positions the link 27 will rest anywhere between the position of FIG. 2 and that of FIG. 3, in other words between the position of zero ink feed and the position of maximum feed. Whenever ink is being fed the reciprocating link 51, instead of merely swinging link 6 idly back and forth, communicates substantially endwise motion to link 6, which motion is transmitted through triangular link 29, which may then be in a position somewhat like that of FIG. 3, to link 24. The position of the parts for maximum drive is illustrated in FIG. 3.

Having thus described my invention, what I claim is:

1. In an ink fountain, a fountain roll, a one-way drive clutch having a driving portion and a driven portion the latter of which is mounted to drive the roll, a first link having one end mounted in a fixed pivot, a second link pivoted to the other end of said first link, means pivotally connected to the end of said second link remote from its connection to the first link and operatively connected to the driving portion of the clutch, said first and second links being of identical length between their respective pivots, means for oscillating the first link through a predetermined angle about its axis, adjusting means connected to the second link for varying the relative angular relationship of the first and second links about a center located at the point of connection of said links, said first and second links being adjustable between a first position wherein the fixed pivot of the first link and the point of connection of the second link to the clutch coincide and a second position wherein said pivot and point are spaced apart duringoscillation of the first link, and means for rapidly moving the adjusting means bodily to move the second link to said first position.

2. An ink fountain as defined in claim 1 wherein the rapid moving means is constructed to maintain the adjustment between said links during rapid movement thereof.

3. An ink fountain as defined in claim 2 including means for limiting the movement of said second link beyond the first position when the adjusting means is rapidly moved to said first position.

4. An ink fountain comprising a frame, a fountain roll rotatable in said frame, a one-way drive clutch having an output connection connected to drive said roll and an input connection, and a Variable throw oscillating mechanism connected to oscillate the input connection of said clutch and including means for adjusting the throw of the mechanism between a maximum and Zero, the last said means comprising a first member movable in first and second directions to respectively vary the stroke to a maximum and to zero, said mechanism being inefiective to oscillate said input connection when the stroke is zero, a second member having a first position relative to said frame, means supporting said second member for movement in one direction relative to said frame from said first position and for return to said first position, means connecting said first member to said second member to move said first member in its said first and second directions respectively on movement of said second member in its said one direction and return respectively and for adjustment of said first member in either its said first or second directions respectively with said second member in its said first position, said second member having sufficient movement in said one direction from its said first position to actuate said first member in its said second direction from a maximum throw position to a zero throw position, and means for selectively holding said second member in its said first position.

5. An ink fountain as defined in claim 4 wherein means is provided for limiting the return of said second member to its said first position.

6. An ink fountain as defined in claim 4 wherein said first member is a rotatable member and is rotated in opposite directions to respectively increase and decrease the throw of the mechanism and wherein said second member comprises rotatable means for efiecting rotation of said first member and wherein said second member including said rotatable means is translatable from its said first position and return to effectively disconnect and reconnect said drive mechanism to said fountain roll.

7. An ink fountain as defined in claim 6 wherein means is provided for limiting the return of said second member to its said first position.

8. An ink fountain comprising a frame, a fountain roll located in said frame, a one-way drive clutch having an output connection connected to drive said roll and an input connection, and a variable throw oscillating mechanism connected to oscillate the input connection of said clutch and including a member angularly adjustable about an axis to adjust the throw of the mechanism between a maximum and zero to effectively disconnect the drive mechanism from said clutch, a rotatable worm wheel connected to rotate said member about said axis, a worm enmeshed with said worm wheel, means supporting said worm for rotation and for axial movement relative to said frame while in mesh with said wheel, said worm having a first position relative to said frame and being axially movable from said first position in one direction to rotate said worm wheel in a direction to vary said throw to zero, and means for selectively holding said worm in said position and against movement therefrom.

9. An ink fountain as defined in claim 8 wherein said ink fountain includes adjustable means preventing axial movement of said worm from its said first position in a direction opposite to its said one direction.

10. An ink fountain as defined in claim 8 wherein said drive mechanism urges said worm in its said one direction during normal operation of said drive mechanism.

11. An ink fountain as defined in claim 8 wherein said worm is limited in its axial movement in a direction opposite to said one direct-ion by an adjustable stop which engages said worm when said worm is in its said predetermined position.

References Cited in the file of this patent UNITED STATES PATENTS 408,392 Tucker Aug. 6, 1889 967,906 Haliwell Aug. 23, 1910 1,540,357 Matteson June 2, 1925 1,868,383 Greenwood July 19, 1932 2,539,383 Davidson Jan. 30, 1951 2,583,639 Faeber et al. Jan. 29, 1952 2,798,425 George et al. July 9, 1957 2,891,473 Faeber et al. June 23, 1959 2,915,970 Mestre Dec. 8, 1959

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