JPH02194953A - Vibrating printing press roller and operation method thereof - Google Patents

Abstract

PURPOSE: To easily arrange a printing press roller on a printing press by bringing about the axial operation of a roller covering in the relation to a roller shaft by the inflow and outflow of a pressure fluid from an axial variable vol. CONSTITUTION: The annular piston member 58 abutted to the outside of a ring clip 56 is provided on a fixed shaft 40 in a slidable manner and an annular cylinder member 64 also slides on the shaft 40 and, by introducing air into the axially variable vol. space constituted between the piston member 58 and the cylinder member 64, the cylinder member 64 is moved to the left. The axial motion of the cylinder member is transmitted to an annular sleeve 72. A roller covering 88 and a core 86 are attached in a rotatable manner by a ball bearing 76 and the axial motion is perfectly separated from rotary motion.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to rollers of printing presses, and more particularly to vibrated rollers for use in inking and dampening systems of printing presses.

PRIOR ART AND PROBLEM SOLVED BY THE INVENTION The use of an ink transfer roller (sometimes called a distribution or transfer roller) somewhere between a form roller that rests on a plate cylinder or roller and a source of ink or dampening fluid. It is already known to use an axial traverse motion on the rollers in the inking and dampening systems of lithographic printing presses. Generally, these ink transfer rollers are rotatably driven by a press and are made to vibrate mechanically in the axial direction.

Additionally, oscillating foam rollers have been developed which are axially frictionally driven by the oscillatory motion of adjacent transfer or ink transfer rollers. For a disclosure of such a transverse foam roller, see U.S. Patent No. 4.493.
．． No. 257 and No. 4,718,344. Similarly, pneumatically vibrated and mechanically rotated ink transfer rollers have been developed. For the disclosure of such a roller, see Japanese Patent No. 57-9.
See No. 3150. Another embodiment of a fluid motorized transverse roller for fluids in ink and dampening systems is disclosed in U.S. Pat. No. 2,242,2.14.
No. Methods of mechanically vibrating rollers in the axial direction are also known. U.S. Patent No. 3,625.14
8, 4,509,426 and 4,672,894 and British Patent Application No. 207B, 72A.

Furthermore, methods are known in which a mechanically rotated and mechanically axially vibrated form roller is used in conjunction with a horizontally oscillating ink transfer roller, with both rollers being vibrated at different frequencies. There is. US Patent No. 4
See No. 397.236.

However, while each of these prior art rollers solves some of the inking or dampening fluid distribution problems, they often create other problems or It was not a complete solution to the distribution problem. For example, in the case of a horizontally oscillating form roller driven axially by friction, when this form roller is being pulled in one direction by an adjacent axially moving ink transfer roller, the nip between these two rollers will normally There is a certain amount of time during which the two rollers move axially essentially simultaneously so that little or no axial inking occurs.

Fresh ink being fed to the foam roller by the ink transfer roller is therefore only transferred radially and is not redistributed axially onto the foam roller, increasing the possibility of "ghosting" occurring.

In most presses, if the form roller is originally made to be non-vibrating and the transversely oscillating form roller is retrofitted, due to the structure of the press,
The retrofitted form roller does not drive the entire axial distance of the ink transfer roller. Therefore, the axial oscillatory movement of this form roller is intentionally stopped so that, while the ink transfer roller oscillates throughout its axial stroke, this form roller comes into contact with the bearer on the form cylinder or with other parts of the press. There is another time when it seems like you won't move until you do something. This type of intermittent axial movement of the foam roll is such that most horizontally oscillating foam rollers driven axially by friction according to the prior art have a stop to prevent its contact with other parts of the press and its overtravel. It was widely used because it was equipped with a collar for use. When operated in this way, excellent transport from the ink transfer roller to the form roller is seen when the axial perforation action occurs, but the transport from the form roller to the plate cylinder/roller is different from that of these two. If the roller is now only rotating, which is less than ideal, no diagonal transfer to the form cylinder will occur while the form roller is stopped from axial vibration by the collar. These 2
As three different modes of operation occur during each axial stroke that makes up the complete cycle of the foam roller, each mode has a unique effect on print quality. Therefore, the form roller is supplied with varying amounts of ink by the form roller, while the form roller receives varying amounts of ink from the transfer roll, so that during a full cycle these two It is difficult to obtain the same print quality between two different modes.

Many attempts have been made to mechanically vibrate the rollers to achieve higher homogeneity, but the mechanical drive mechanisms are complex and themselves a source of problems. For this reason, most foam rollers on the press were not mechanically vibrated axially. Furthermore, the foam roll is generally not fixed in a single location, but is mounted from a swing hanger that is itself biased and can move toward both the plate cylinder and the adjacent ink transfer roller. This required flexibility poses additional problems in attempting to mechanically oscillate such rollers. Although it is possible to design new presses for mechanically axially vibrated form rollers, such presses would be expensive to manufacture and operate. While it can be difficult to design a good mechanical vibration mechanism for a new press, it is even more difficult to design one for an existing press. For this reason, many retrofitted vibrating form rollers have only been vibrated axially due to friction from the vibrating motion of adjacent ink transfer rollers. Additionally, because the form rollers in most presses were not mechanically driven, the press frame adjacent to the form rollers was usually solid, and such a construction is shown in U.S. Pat. No. 2.242.214. Prevents retrofitting of fluid drives extending outside of the press frame as shown.

Pneumatic pressure has been used to provide oscillatory motion for ink transfer, or transfer rollers, but previous designs have been inadequate and long It was not possible to adapt it to wide presses that required small diameter rollers. Also, some prior art air rollers used a fixed shaft and rotating roller body or core itself as the air cylinder.

As a result, sealing is difficult as the cylinder is rotated, and/or the seal between the stationary and rotating parts is forced by the air pressure on these parts, acting as a brake, and thus the rollers. Further rotation of the seal shortens the life of the seal and increases maintenance and downtime. Japanese Patent No. 5
Another drawback of the previous pneumatic horizontal ink sifting roller construction as shown in No. in that it is generally restricted to the press. This limitation makes rollers like the one shown in this Japanese patent unsuitable for wide presses, i.e., 36 inches wide or wider.
As such an air roller is pressed against an adjacent roller, due to its construction, the central shaft deflects away from this adjacent roller, and instead, due to the abutted central portion therein, the central shaft deflects away from this adjacent roller. This arises from the fact that the center similarly deflects away from adjacent rollers. thus,
The end journal of a roller is aligned with the adjacent roller.
The harder it is pressed, the worse the problem becomes, resulting in more (rather than less) deflection in the center and less homogeneous loading of the inking roller relative to the adjacent rolls. For roller lengths of 36 inches or more, the problem of center deflection becomes very significant, and even more so for longer roller lengths. As a matter of course,
This non-uniform roller loading causes changes in the ink or dampening fluid across the roller,
It tends to result in varying print quality across the roller.

Attempts have been made to vibrate both the foam roller and the ink roller, but these prior art devices could easily be retrofitted into existing presses that were originally fitted with non-vibrating foam rollers. No complex mechanical devices were used on both rollers. Furthermore, the axial movement of the foam roller during oscillation is only for a portion of its time or is not synchronized with the movement of the ink sifter roller; There was no relative axial movement between; or U.S. Pat. No. 4,397,
No. 236, the wiping action between the foam roller and the ink sifting roller is not homogeneous, as is the case when the foam roller and the oscillating roller vibrate at different frequencies, or the wiping action is not maximal. There was no way to optimize the wiping action of the rollers. U.S. Patent No. 4,397
Apparatus constructed as required by No. 236 also introduces another variable in the distribution of ink and/or dampening fluid. That is, for different parts of a complete cycle, different degrees of shearing occur between two rollers vibrating at different frequencies, which changes the ink delivery and thus the quality of the print. It becomes.

[Means for Solving Problem A] The horizontal oscillating roller according to the present invention can be used as a form roller in a press dampening system or an inking system, or as an ink sifting roller. It can also be used in other roller positions. The press may be of any type having an ink train or a dampening train, including lithographic offset presses, flexo offset presses, and the like. In a preferred embodiment, the transverse roller of the present invention includes an axially extending roller shaft that is adapted to be attached to a press frame. The roller shaft can be a dead shaft, i.e. not rotating, or a live shaft, i.e. a rotating shaft. The roller shaft has a piston element which is rotated axially on the shaft. Attached. The roller generally has a covering made of any suitable material used in ink or dampening trains, such as metal (chromed), rubber or plastic compounds, or ceramic materials. The piston interlocks with the cylinder element or structure and forms therewith an axially variable volume. The roller cover and cylinder structure are arranged in such a way that this variable volume expansion or contraction results in an axial movement or oscillation of the roller cover.

Of course, it is also possible to use the opposite arrangement, where the cylinder structure is positioned axially on the shaft, with the piston moving the roller covering.

The cylinder structure and piston are positioned within the roller between the roller shaft and the roller covering in a manner that does not interfere with the press frame to slow the rotation of the roller or cause deflection of the roller. In the dead shaft version, the piston and cylinder structure is independent of the roller shaft and roller covering and its core. In live shaft versions, the rotational motion is carried by bearings on the end of the roller shaft that attaches the shaft to the press frame, so that the piston and cylinder structure is connected to the outer surface of the shaft and the inner surface of the roller covering or The backup core can be used to create a variable volume. To minimize or eliminate roller deflection problems due to loading of the shaft journal relative to adjacent rollers, unlike the prior art, the piston and cylinder structure is located at the ends of the rollers rather than at or near the center of the rollers. It is located very close to the department. Therefore, rollers according to the invention include long rollers (e.g., paper or press widths of 36 inches or more) and fine rollers (large length-to-diameter ratios).
Particularly suitable for

In order to develop suitable vibrational forces in especially small diameter rollers, the piston and cylinder structure of the rollers is double,
Triples or stacks can be stacked as needed to develop sufficient force to vibrate the rollers against all forces resisting the vibration, such as from adjacent rollers vibrating in opposite directions. Naturally, the stacked piston-cylinder structure is spaced from the body or core of the roller and is kept at the ends of the roller and does not extend to the center to minimize sagging problems.

Furthermore, in order to minimize the problem of deflection and reduce manufacturing costs, we have developed a roller shaft.

The piston and cylinder structures are made to fit freely into each other without close tolerances. A "0" ring is used in place of a traditional interference compression fit when necessary to provide a tight seal or to prevent rotation of parts.

The oscillating roller according to the invention can also be used in conjunction with another adjacent oscillating roller; in such a case, the roller according to the invention can be used in combination with another adjacent oscillating roller with the same larger or smaller stroke. Same as roller
Or it can oscillate in the opposite direction at this same cycle rate or frequency.

If each print made must be of the same consistent high quality, it is necessary to dampen and ink the plates in exactly the same way. In order to maintain this consistency, 1. There should be no variation in the delivery of ink and dampening fluid. In order to achieve consistency with maximum redistribution of ink and/or dampening fluid, and also to reduce "ghosting", the oscillating roller according to the present invention, when used in the form position, It can be used with one adjacent ink feed or distribution roller in such a way that it vibrates at a frequency but moves in different directions along its axis. Such construction and operation ensures that the relationship between these two rollers and between the form roller and the plate cylinder is repeated in order to ensure that a precise and secure relationship is repeated each time the plate is inked and/or moistened. Provides consistent axial shear. Furthermore, the resulting transfer of fluid, whether ink or dampening moisture, between the ink sifting roller and the form roller, as well as between the form roller and the plate cylinder, occurs in a desirable diagonal pattern. That is, the relative axial and rotational movements of two respectively adjacent rollers always form a diagonal pattern.

The oscillation of the roller of the invention is achieved by sensing the oscillation of an adjacent roller, such as a change in direction of axial movement, and applying pressure from the piston-cylinder structure to cause the roller according to the invention to oscillate, preferably in the manner described above. control means for controlling the intake, degassing, or evacuation of compressed fluid or compressed air. The control system provides variable length strokes to the rollers of the present invention, allowing the rollers of the present invention to move at the same speed as adjacent rollers, or at a lower speed, or at a higher speed if desired. Can be moved axially with variable dwell time. Therefore, the wiping action between the transverse roller according to the invention and the adjacent transverse roller and with the form cylinder can be optimized. The motion of the oscillating rollers according to the invention provides compressed air at high air pressure regulated to the piston-cylinder structure on one side of the roller and discharges the piston-cylinder structure on the opposite side of the roller through variable area orifices;
Or it can be achieved by degassing. Changing the size of the discharge orifice changes the speed of the roller. Naturally, high or low supply pressure also changes the vibration speed. Adjustment of supply pressure and/or venting can also be used to provide, eliminate or adjust dwell time.

The length of the vibration, or stroke, is determined by its speed.

High speeds are used for long strokes and low speeds are used for short strokes.

The purpose of the transverse roller according to the invention is to provide a pneumatic mechanism that can be easily installed on a printing press to eliminate the "ghosting phenomenon".

Another object of the oscillating roller of the present invention is to provide a pneumatic piston-cylinder arrangement that produces axial movement without controlling rotational movement.

Yet another object of the oscillating roller and method of the present invention is to be isolated from the outside of the body or core of the roller and/or to be enclosed at the ends of the roller, thus eliminating and minimizing sagging of the roller. The objective is to provide a pneumatic piston-cylinder arrangement such as

Yet another object of the oscillating roller according to the invention is to enable it to be equipped with one or more piston-cylinder structures on each side of the roller, thus providing the desired vibration even in small radius rollers. The objective is to provide a structure that allows the development of sufficient power.

Yet another object of the oscillating rollers and methods of the present invention is to move in the same or opposite direction and in the same cycle at a speed and/or stroke that provides optimal wiping action for the printing job at hand. The object is to provide a roller that can be used in conjunction with another adjacent oscillating roller in such a way that both rollers are synchronized to operate at speed or frequency.

Yet another object of the oscillating rollers and methods of the present invention is to operate at the same cycle speed or frequency, moving in axially opposite directions to maximize fluid distribution to eliminate "ghosting". The object is to provide a foam roller that can be used in conjunction with adjacent ink transfer rollers in such a way that both rollers are synchronized.

Yet another object of the invention is to provide a structure for pneumatically vibrating rollers within an inking or dampening system of a press.

Another object of the invention is to provide a vibrating roller structure that is particularly suitable for retrofitting into presses in place of non-vibrating rollers.

These and other objects and advantages of the present invention include:
This will become clear from the attached drawings and the following description.

EXAMPLE Referring to FIG. 1, one type of printing press in which a transverse roller according to the present invention can be used is shown. Although the press shown here is a lithographic or offset printing press that has both an ink train and a dampening train, this press is of the type that combines these two systems, an ink system and a dampening system. It may also be a press of a different type, such as a gravure printing press or a flexo printing press. In the double-sided press shown in Figure 1, the web (9) is placed between two offset or blanket cylinders or rollers (10) each running against its own plate cylinder or roller (ii). pass through. Each plate cylinder receives a supply of ink fluid from a liquid reservoir (12), a supply of dampening fluid from a tray (13), and a roller (14), which in some presses may be an ink fountain roller. ), a distribution roller (15), an axially oscillating ink transfer roller (17) and a form roller (18) which rests against the form cylinder. In addition, rider rollers (2
0) is shown on the foam roller (18).

According to the invention the transverse roller has the reference number 17.18
and/or the rollers can also be used in the positions indicated at 20.

Referring to FIG. 2, the transverse roller according to the present invention (
A first embodiment of 30) is illustrated. Although this figure actually shows only one end (left side) of the roller (30), the other end is generally of the same construction and the differences that exist therebetween are described below or From Figure 6.

As shown, the roller (30) is mounted in a press hanger or frame (32), which is only partially shown. For convenience of reference, it is assumed that this roller is used in the position numbered 20 in FIG. In this example, roller (30) was retrofitted to replace the live shaft. Therefore, the press frame (32) is equipped with dummy bearings (36) to perform the conversion in this example.
A bearing cavity (34) is provided. This dummy bearing (36) is positioned or clamped within the press frame (32) by conventional means (not shown) to prevent its rotation. The small diameter pilot end (3) of the roller shaft (40)
8) extends into the dummy bearing and is held by the roll bin (42). The other end of the shaft (40) (
(not shown) are similarly attached to the press frame. The roller shaft (40) is a dead shaft, ie a shaft that does not rotate.

As can be seen in Figure 2, the roller shaft is enlarged to a larger diameter from the pilot end (38). A shaft (40) extends completely across the press to the opposite tongue or frame. The diameter of the roller shaft is increased to better withstand the bending loads imposed on the shaft by contact with the adjacent roller or rollers. (See Figure 1) In order to supply pressurized fluid or compressed air to the operating mechanism of the transverse roller according to the invention, the center of the roller shaft (40) is partially disposed as shown in (44). A through hole is drilled. In some cases, the outer end of the opening (44) could also be used to connect to an air supply/vent, but in this example this is not possible due to the rigid press frame (32). The outer end of (44) is closed by a pipe plug (46) or the like. A shaft (40) for admitting and discharging pressurized fluid to and from the passageway (44).
Therein is a short radial passageway (48), with suitable fittings (50) and hoses or tubes (52) attached to this passageway and connecting it to the control system. A suitable control system is shown in FIG. 6 or FIG. 7. Similarly, a radial passageway (54) is provided for supplying or discharging air from the passageway (44), which passageway (54) is provided for supplying or discharging air through the hose (52). They are supposed to be in fluid communication.

The construction of a vibratory roller according to the invention for producing and receiving a sliding or axial vibratory motion will now be described. A few inches from each end,
The shaft (40) is provided with a groove for a ring clip (56), which groove is positioned towards the inside of the radial passageway (54).

Slidingly mounted on the shaft is an annular piston member (58) abutting against the outside of the ring clip (56). The piston (58) has its inner diameter,
and a groove on the outer diameter to receive a sealing "0" ring (60 and 62) to seal the piston (58) to an adjacent surface. An annular cylinder member (64) also slides on the roller shaft (40) and has a connected cylinder wall portion (68) and cylinder head portion (66) into which the piston (58) can slide.
). The inner surface of the cylinder head (66) adjacent to the roller shaft is also grooved for sealing purposes.
0'' ring (70) can be inserted. In addition, the piston member (58) and the cylinder member (6
In order to take in air into the axially variable volume space formed between 4), the piston member is pushed to the right, the annular ring (56) is brought into contact with the cylinder member (64), and the cylinder member (64) is moved to the left. Become. Naturally, the intake of air into the axially variable volume chamber between the piston and cylinder member (not shown) on the other side of the roller causes this cylinder member to move to the right. This side-to-side axial vibration can be caused by pressurization and/or venting of the variable volume chamber on the left or right side of the roller.

The axial movement of the cylinder member is caused by a roller shaft (40
) annular sleeve made of oil-impregnated bronze (7
2).

As shown in FIG. 2, the right end of this sleeve abuts the left end of the cylinder member (64) for this purpose.

In this example, the axial sleeve includes a rolling bearing (76
) has an inner lace (74). Both the inner and outer surfaces of the annular sleeve are grooved to provide a secure fit for the sleeve on the shaft, and the inner race (
74) to rotate on the annular sleeve or the annular sleeve to rotate on the shaft (40).
Rings (78, 80 and 82) can be stored. Therefore, the annular sleeve (72) and the inner race (74
) undergoes only axial motion and does not undergo rotational motion.

The rolling bearing (76) is a roller covering (B,)
It has an outer race (84) that engages the roller body or core (86) that supports the roller body. Therefore, the roller covering (B,) and the core (86) are connected to the rolling bearing (76).
It is rotatably mounted and can be rotated freely. Again, the core (86) lends itself to an interference fit with the outer race (84) without the need for extremely tight tolerances, and a "0" ring (0) that allows the outer race and core to rotate together. The outer race and core are both grooved to accommodate the roller shaft (4).
0).

The illustrated rolling bearing does not incorporate axial thrust, so the radial roller (94), inner race (94),
6), and a thrust bearing (9) consisting of an outer race (98).
2) butts against the annular sleeve (72).

The end of the annular sleeve is stepped in this example to accommodate the inner race (96). The outer race (98) rests on an end ring (100) which is held in place by an outer annular ring (102) in a groove on the end of the roller core (86). Again, the "0" ring (103) is the end ring (100
), the end ring (100) and the roller core (
86) can prevent relative rotation between the two.

To position the outer race (98) within the core (86), the end ring (100) is fitted against the outer race (84) of the rolling bearing (76) and the keeper (104) of the "L" shaped cross section. are stacked on top of each other, all of which are formed within the outer end of the core (86) and have an enlarged diameter portion (105).
). The keeper (104) has an annular sleeve (
The thrust bearing roller (94) and the inner race (96) are always held together by the annular sleeve (72) and the inner race (74).
72) Provided to ensure that it remains supported above. The end ring (100) and shaft (40) close the rollers and keep lubrication in place for the thrust bearing (92) and rolling bearing (76).
) is provided with a seal (106). In order to lubricate the rolling bearing (76) and thrust bearing (92), a grease fitting (tOa) is installed inside the end ring (100).
and a grease passage (110) may also be provided.

With the construction described above, the axial movement is completely separated from the rotational movement, and there is no possibility that the seal, which is subjected to air pressure, is also subjected to rotational movement. Therefore, there is no tendency for the rotating seal to act as a brake or otherwise provide additional resistance to rotation, as was the case in the prior art.

Preferably, the axial vibration of the roller of the invention can be controlled by the control system shown in FIG. 6 or FIG. 7. First, the system shown in FIG. 6 will be described here. In this figure, the inventive roller (30) is in contact with an ink sifter roller (120) which is mechanically axially vibrated by a plate cylinder (not shown in Figure 6) and a press drive. and is assumed to be in the form position (see number 18 in FIG. 1). As shown, the vibration of the adjacent oscillating ink sifting roller (120) is triggered by a proximity switch (122 or 124) that detects the change of direction of the roller at the end of its axial motion (trigger point). (proximity sinch such as the cylindrical AC or DC type manufactured by Furnas). Of course, proximity switches such as microswitches or pneumatic logic devices (122 and 1
24) could be used, or the timing signal could also be taken from somewhere on the press drive or inking roller drive. If desired, instead of sensing the roller (120) itself, it is also possible to sense one of two adjustable collars (125) mounted on opposite sides of the shaft of the roller (120). . Adjustable collars allow these trigger points to be easily changed. Similarly, the position of the proximity switch can be changed to adjust the trigger point. (providing the trigger point) roller (120
), or when the end of the axial stroke of the collar (125) is detected, the solenoid-type four-way control valve (126) (Schra
der Bellows, Parksr Hamn
Directair 2 valve manufactured by ifin division,
A single signal is sent to the direct pipe 0.4-way dual solenoid spool (such as pulp), which causes the valve to pressurize an axially variable volume on one side of the roller (30). On the other side, the axially variable volume is made to vent.

As shown, the slidable body (121) within the valve (126) is arranged such that one variable volume is pressurized and the other volume is degassed.
23). As shown in FIG. 6, the variable volume on the left is indicated by solid arrow 125.
The right side is pressurized while being degassed, as represented by A, and thus the roller (3o) and its covering (86) are in contact with each other when the right side variable volume piston and cylinder head are in contact with each other. and will move to the left until further restriction of movement or until a subsequent reversal of direction of the roller (120) occurs.

When the right end of the roller (120) reaches the right end of its travel, it trips the proximity switch (124), which is itself partially shown in dotted lines at the right end of the body (121). Activate the right side coil (123) to move valve W4 (121) from its leftmost position shown to the right, so that the dotted arrow (127)
As shown, the right variable volume is pressurized and the left side is vented. When the above happens, the roller (
The core (86) and covering (B,) of 30) begin to move and move to the right until the left variable volume piston and cylinder head come into contact or a subsequent redirection of the roller (120) occurs. continue.

During this time, the roller (120) is moving to the left, and when it reaches the leftmost point of its stroke, it trips the switch (122) and then begins to move back to the right.

When the switch (122) is pulled out, the left side coil (1
23) is activated, inverting the valve body (121) again and removing the core (86) and covering (B, ) of the roller (30).
Move to the left again. The operations described above are repeated continuously as necessary to vibrate the roller (30). Therefore, the control system of FIG.
The direction of the ink sifting roller (120) is changed almost simultaneously with the direction change of the adjacent horizontal ink sifting roller (120).

Here, the oscillating roller according to the invention as described above moved in the opposite direction to the adjacent oscillating roller, but if desired, this may be the case on which side of the oscillating roller according to the invention the oscillating roller according to the invention is pressurized. Depending on whether it is degassed or not, it can also move in the same direction as the adjacent horizontal swinging roller. The speed of vibration of the roller of the present invention may be higher, lower, or equal to the speed of vibration of an adjacent ink sifting roller. Of course, if the speed is higher, there may be a dwell time at the end of the stroke. Similarly, the length of vibration can also be controlled. For example, if the inventive roller moves slowly and does not complete a full stroke before a change of direction occurs, the axial velocity of the adjacent oscillating roller (which decouples the inventive roller from oscillating) Assuming constant, it will have shorter oscillations than if it were moving at a faster speed. The axial speed of the transverse roller according to the invention can be adjusted using conventional adjustment devices (
by increasing the supply pressure via 128) and/or
Alternatively, it can be increased by reducing the restriction of the valve (130) controlling the venting. Of course, the velocity can be reduced by reducing the supply pressure and/or by increasing the restriction of the valve (130) (reducing the flow area).

Also, if desired, the rollers (30) can be made non-oscillating or simply biased towards either side of the brace. For example, one of the solenoid coils (123) is kept activated and the sixth solenoid coil (123) is kept activated.
It is also possible to keep the valve body in the position shown, with the roller covering (B,) biased to the left.

Alternatively, such biasing can be accomplished pneumatically, such as by supplying pressure to only the left variable volume. Another variant embodiment provides a different type of valve (12
6). In any case, whether biased to either side or centered, because the ink transfer roller (120) is longer, the roller (30) of the present invention never leaves this ink transfer roller; There is no problem at all since the edge a of the form on the form cylinder never separates since the form is inside the end of the covering (B,) of the roller (30).

Referring to FIG. 7, a second aspect of the control system is shown; unlike the system shown in FIG. 6, which synchronized vibrations to adjacent rollers, the system of FIG. It is a self-help vibration type. A system such as that shown in FIG. 7 can be used to vibrate the roller according to the invention, as is the case with the roller shown in the position designated by the number 15 in FIG. Ideal where there is no need or desire to synchronize the vibration of one roller to the vibration of another roller. It is also possible to use the system of Figure 7 to self-oscillate one roller and the system of Figure 6 to vibrate adjacent rollers such as foam rollers and ink transfer rollers for dampening or inking systems. I can do it. This arrangement is extremely effective in retrofitting two adjacent oscillating rollers to a press that had non-oscillating rollers.

As can be seen in Figure 6, in this example the roller (30) has at its end the same left and right air supply/vent lines (52L and 52R) for variable left and right volumes. )have. These air lines are equipped with two functional valves (14) that detect the presence or absence of pressure in the lines (52L and 52R), respectively, to allow the rollers to vibrate on their own.
0 and 141) (model no. made under the trademark LegrLs.

7B, 8-5420).

As shown, after leaving the function valve, the line (5
2L and 52R) each have a variable area throttle valve (142
or 143) (such as the valve (130) shown in Figure 6) and the flow only occurs when the ball leaves its valve seat in the direction of its respective variable volume. a second one with a one-way valve (144 or 145) that allows
branch into parts. For convenience, one-way valves (142 and 143
) and the throttle valve (144 or 145) are both Hum
These lines can then be integrated into a single valve body, such as in the SCI sold by Phrey, Inc.
4-way valve (146) with a slidable segmented valve body (147) similar to that of valve (126) with valve (121) but differing in that the valve body is pneumatic rather than electric;
) and enter this. As shown, each end of the valve body (147) has a piston-cylinder arrangement (14
8 and 149) (34 manufactured by Humphrey)
A type A-like air operator for valve (146) is provided, which is connected back to either of the two function valves. The functional valves (140 and 141) and the four-way valve (146) are all connected to a high pressure source, such as a pressure regulator (128).

According to the control system as shown in place in FIG. 7, from the regulator to the four-way valve as indicated by the left arrow, to the left variable volume between the left piston cylinder of the roller, and both. function valves (140 and 141
), high air pressure is applied. Left side line (52L
) is pressurized, the left-hand function valve (140) is closed due to its configuration, allowing the passage of pressurized air from the regulator through the line to the right-hand piston cylinder (148) on the valve body (147). deter. However, the right piston cylinder in the roller has a functional valve (141), a variable area throttle valve (143), as indicated by the right arrow.
) and a four-way valve (146).

As the pressure in the right-hand variable volume decreases, the right-hand function valve (141) opens due to its configuration and the flow of air through the right-hand function valve from the regulating device to the left-hand piston cylinder (149) of the valve body (147) occurs. Allow the flow to move to the right. At the same time, the increase in pressure in the line (52L) causes the left-hand function valve (140) to shut off pressure to the piston cylinder (148) on the right side of the valve body. As a result, approximately at the same time that the roller core (86) and the covering (B,) have moved to their fully leftmost position on the shaft, the valve JP (147) slides to the right, partially shown in dotted lines on the right side. pressurize the right variable volume of the roller (as shown) and degas the left variable volume of the roller (6th
The roller core (86) and covering are then moved back to the right to the position shown in FIG. 6) (as noted in the description of the operation shown in the figure). Here again, the subsequent pressure rise in the left-hand function valve (140) and pressure drop in the right-hand function valve are again explained (147).
This causes another stroke. This procedure is repeated as many times as desired to cause the rollers to vibrate on their own. It should be understood that any suitable roller biasing or centering arrangement, such as that described in connection with FIG. 6, may also be adapted to the self-help vibration control system of FIG.

Just as any control system is shown used with roller (30), any one may be used with the subsequently described embodiments of the roller of the invention, depending on the field of application. is possible.

Referring to FIG. 3, a second embodiment of a roller (150) according to the present invention is shown. This roller is generally similar to the roller shown in FIG. 2 and, to the extent that it is similar, has been given the same numbering as that shown in FIG. The main difference between the rollers shown in FIGS. 2 and 3 is that the roller (150) in FIG. 3 includes stacked pistons that develop additional axial forces to vibrate the rollers. and has a cylinder structure. As previously mentioned, this configuration is particularly advantageous when the rollers are of small diameter, especially when large It is difficult to provide volumes with variable cross-sectional areas.

Instead of having a single piston on each side of the roller shaft (151) as shown, each side is equipped with a second identical inner piston (152). This second piston has an outer annular ring (56) and a second annular ring (154) mounted in a second annular ring groove on the roller shaft (151) inwardly of the outer annular ring (56) and its groove.
Linked with. The second piston (152) and second cylinder (156) both have the same "0" ring as the first piston and first cylinder. The second cylinder (156) simply butts the first cylinder (64). The supply or venting of air for the second piston and cylinder is provided by a passageway (44) designated with the number 158 and communicating therewith and for the second cylinder (15
6) and the second piston (152).
A radial passage (is
This is just a continuation of o).

The force generated in the second piston-cylinder adds to the force generated by the first piston-cylinder, doubling its output. Of course, if additional force is required, additional piston-cylinder configurations can be stacked on each side of the roller.Referring to FIG. A third embodiment of iao) is shown and described, which is particularly suitable for small diameter rollers. In this example, the second
Instead of rolling a rolling bearing on an inner race on an inner annular sleeve as shown in FIGS.
) is rotating directly on top. The roller shaft can be hardened or heat treated in the area below the roller, if necessary. As a result, this structure can be adapted to rollers of significantly smaller diameter. As shown, this type of configuration is used for the stacked piston-cylinder structure described above. That is, there are multiple pistons (186 and 18) and cylinders (190) at each end of the roller to provide sufficient axial force.
and 192), a plurality of axially variable volumes are configured. This configuration is particularly suitable for small diameter rollers (small area between roller core (192) and shaft (184)).

Another difference between the third embodiment (180) and the previously described embodiments is the positioning of the thrust bearing. In a third embodiment, hitherto a roller (7
The thrust bearing (194), which was on the outside of 6), is now on the inside of the roller (182). Either position is acceptable and works well as long as the rotating parts are separated from the non-rotating parts by thrust bearings.

For both embodiments shown, the axial load capacity of the combination of the radial load carrying capacity of the rolling bearing and the rolling thrust bearing is similar to that of a tapered rolling bearing, a thrust angular contact ball bearing, or even a sliding ball bearing. It should be understood that it can be fulfilled in another way. However, the use of rolling bearings in conjunction with other thrust bearings provides greater radial load capacity with a more compact diameter. Although rolling or ball bearings are preferred, it is also possible to use suitable sliding bearings, such as oil-impregnated types.

Referring to FIG. 5, an axially vibrating roller (19
A fourth embodiment of 8) is shown. Unlike the previous embodiment, which had a dead or non-rotating shaft, this fourth embodiment has a live or rotating shaft. As shown, the shaft (200) is mounted by a pair of ball or rolling bearings (202) held in a press hanger or frame (204). The entire shaft (Zoo) is thus free to rotate by the adjacent rollers, whether they are plate cylinders or other adjacent rotating rollers. Of course, with this configuration, the shaft (200) can easily be adapted to be rotated mechanically, such as by a gear (not shown) on one end being driven by a press drive.

As shown, the roller shaft (Zoo) communicates with a first radial connecting passageway (206) originating from an air coupling (2i0) and a second radial connecting passageway (206) with a variable volume piston and cylinder structure. It has an air passageway (206) therein having a radial passageway (211) of , which will be described below. The air coupling (210) is itself stationary and can supply air to or vent air from the rotating roller shaft (200) and its passageway (208). As shown, the coupling includes a body (212) having an opening (214) for rotatably receiving a shaft (200). Since no separate bearing for the air coupling is provided, the body (210) itself can act as a bearing and may be made of a suitable bearing material, such as oil-impregnated bronze. The body has two parts (216) that engage the shaft like bearings. Immediately inside portion (216), an annular collector chamber (218) is formed within the body to maintain constant communication with rotating passageway (208). This annular chamber (218), in turn, is connected to an air supply/vent line (224) from the control system via a passageway (220) and a fitting (222). A pair of seals (226) are provided on the ends of the body that seal against the shaft (200) to reduce leakage. This seal (22B) is held in place by two washer rings (228),
These rings, on the other hand, can be attached to two ring clips positioned in the grooves on the shirt)-(200), or to the ring (200).
30) is fixed by C. Alternatively, these seals (226) may be omitted and the shaft (20
In order to allow the body to function as an air bearing with a small air flow around the air coupling body (210), it is possible to provide a shaft bore with close tolerances in the air coupling body (210). can. The body (210) itself is preferably connected to the body (210) by an air line (224).
Rotation is prevented by a torque strap (not shown) that connects the press frame to the press frame.

As shown, the second radial passageway (211)
are in communication with an axially variable volume at each end of the roller which causes the outer surface of the roller to vibrate axially. As shown, and similar to the previously described embodiments, each of the axially variable volume chambers is provided with a piston and cylinder structure. The piston (232) is connected to the shaft (200
) is an annular member slidably attached to the top. Again, the piston (232) is used to seal the piston with both the shaft (200) and the cylinder (238), respectively.
) has an inner "0" ring (234) and an outer "0" ring (236), so no interference fit is required. In this example the cylinder itself is designed to form a shoulder (244) to limit the stroke of the piston.
It is formed by one end of a roller core (240) which is stepped as shown at (242). The stroke of the piston relative to the shaft in one direction inwardly is thus limited by the annular ring (246) which engages a groove in the roller shaft (200).

The other end of the annular, axially variable volume cylinder structure is closed by another annular ring (250) or cylinder head which is slidable on the roller shaft (200). In this way, the annular ring (25
0) is sealed to both the shaft (200) and the cylinder wall (238) by a pair of "0" rings (252 and 254). The annular ring (250) can slide on the roller shaft (200), but the annular ring (250) is kept in a groove formed in the outer end of the core (240).
56), making it impossible to move further outward relative to the roller core (240).

The core (240) itself is covered with a roller covering (258) suitable for the location where the rollers are operated. "0" rings (234 and 23) on member (232)
6) and the use of "0" rings (252 and 254) on member (250) to connect these two members and shaft (
200) will be rotated together with the core (240) and covering (258). All relative rotation therefore occurs within the bearing (202).

The above structure is preferably replicated on the other side of the roller and two air supply/venting lines are connected to the control system as shown in FIGS. 6 and 7. ing. This pressurized air is supplied to the roller core (2
40) and its covering (25B) vibrate or shift to the left, air under pressure is released or degassed from a variable volume at the other end of the roller (not shown). 5 to the end shown in FIG. 5 to axially expand the variable volume on that side. At the desired point, the end shown in FIG. 5 is then vented and the end not shown is pressurized to move the core and covering to the right.
The air connections are reversed to end the cycle. This operation can be repeated and changes can be made as described above.

To give a rough idea of the size of the rollers described, the roller shaft diameter would be from 3/4 inch to 3 inches, and the outer diameter of the roller covering would be from 2 inches to 8 inches. Of course, smaller sizes are particularly applicable to the embodiment shown in FIG.

Although the construction according to the invention is particularly advantageous in rollers having a length of 36 inches or more, it can also be used with rollers as small as 12 inches long or in larger lengths, such as 80 inches or more.

The control system is shown using a 4-way valve;
A dialect can also be used instead. Thus, assuming appropriate timing devices such as multi-contact relays, multiple single solenoid valves can alternatively be used to perform various functions.

Although FIG. 1 shows a web printing press having a dampening and inking system such that the ink and dampening fluids are applied to at least one common foam roller, the present invention All types of dampening and/or inking can be applied to the system, such as having many rolls, no rolls at all, or even just one inking system. It will be appreciated that the invention may be integrated into only one or both of these systems, and may be integrated into just one, several or many rollers on a web printing press. Of course, all of the above should be considered as falling within the scope of the claims.

As noted, the oscillation speed of the roller can be controlled by pressurizing a variable volume at one end and degassing a variable volume at the other end of the roller, and more specifically by reducing the constriction in the line being degassed. caused by being able to adjust the This method provides smoother operation and prevents the jerky operation that often occurs when speed is controlled only by adjusting high voltage inputs.

Having shown and described several preferred embodiments of the oscillating roller device according to the invention and the method of oscillating the rollers according to the invention, it will be apparent from the foregoing that variations, modified embodiments and equivalent constructions thereof are possible. , and steps are also to be understood as falling within the scope of the claims herein.

[Brief explanation of the drawing]

The drawings illustrate an embodiment of the invention, and FIG. 1 is a cross-sectional view of one type of press in which a transverse roller according to the invention can be used. FIG. 2 is a cross-sectional view of one end of a first embodiment of the oscillating roller of the present invention using a dead or non-rotating shaft. Figure 3 is somewhat similar to that shown in Figure 2, but differs in that it has two stacked piston-cylinder configurations instead of one;
FIG. 3 is a cross-sectional view of one end of a second embodiment of the oscillating roller according to the invention; FIG. 4 shows a transverse roller according to the invention, which is somewhat similar to that shown in FIG. 2, but differs in that it is particularly suitable for rollers of small diameter. FIG. 7 is a cross-sectional view of one end of the third embodiment. FIG. 5 is a cross-sectional view of a fourth embodiment of a transverse roller according to the invention using a live or rotating shaft. FIG. 6 is a schematic diagram of one embodiment of a control system for a transverse roller according to the present invention. FIG. 7 is a schematic diagram of a second embodiment of a control system for a transverse roller according to the invention. (14) - Rolling paper... Blanket cylinder... Plate cylinder - Liquid storage container - Tray - Ink dispenser roller - Distribution roller - Axial horizontal ink sifting roller - Form roller - Rider roller - Lateral l Dragon roller press hanger (frame) ・Bearing cavity ・Dummy bearing ・Pilot end ・Roller shaft ・Roll pin ・Opening (passage) ・Vibe plug ・Radial passage ・Mounting hardware ・Hose ・Passage ・Ring clip・Annular piston (62) r□, ring...Annular cylinder member ・Cylinder head section...Cylinder wall section (70)...-"0" ring (72)...Annular sleeve (74)... ... Inner race (76) ... Rolling bearing (78) (80) (82) rOJ ring (84) ...
・Outer race (86)... Core (B,)... Roller covering (90)... "0" ring (92)... Thrust bearing (94)... Radial roller ( 96) ... Inner race (98) ... Outer race (100) ... End ring (102) ... Outer ring ring (103) ... "0" ring (104) ... Keeper (106) Seal (108) Grease installation tool (110)
...Fleece passage (120) ...Ink sifting roller (121)
... Valve body (122) l 24) Proximity switch (123) ... Coil (125) ... Collar (126) ... Valve (128) ... Adjustment device (130) ... Valve (140) (141) Functional valves (142) (143) Throttle valves (144) (145) to one-way valve (146)...Four-way valve (147)...Valve body (14B)...Right piston cylinder (149)・・・
・Left side piston cylinder (150) ・Roller (151) ・Roller shaft (152) ・
...Second piston (154) ...Ring (156) ...Second cylinder, radial passage, lateral swing roller, roller, roller shaft (1B,) Piston (192) Cylinder...core - Thrust bearing - Roller - Shaft - Rolling bearing - Press hanger - First radial connection passage - Passage - Air shaft joint (212) Main body - Opening - Two parts - Collector Chamber/passage patent application/installation equipment/air supply/gas vent line/pair of seals/washer ring/ring clip/piston (236) rOJ ring...cylinder wall...core/ring ring...ring Ring (254) rQ” Ring...Covering Person Advanced Graphics Chikunoroses Incorporated

Claims (1)

Claims: 1. In a transverse roller for one of the ink and dampening fluid systems of a printing press, an axially extending roller adapted to be mounted across the width of the printing press. a roller shaft, a cylinder head concentric with and axially positioned above the roller shaft, mounted relatively non-rotatably on the roller shaft and relatively slidable thereon; a concentric piston, a cylinder wall between said cylinder head and said piston (wherein said cylinder head, piston and cylinder wall constitute an axially variable volume), in relation to said cylinder head; control means for inflowing and outflowing pressurized fluid from the variable axial volume to cause axial movement in at least one of the cylinder wall and the piston; a roller covering; and a roller covering; with at least one of the wall and the piston;
Means are included for axially moving said roller covering so that inflow and outflow of pressurized fluid from said axially variable volume causes axial movement of said roller covering in relation to said roller shaft. A horizontal swinging roller that is characterized by 2. said oscillating roller has on each side thereof one of said piston, cylinder head and cylinder wall, providing an axially variable volume on each side thereof; and said control means; The oscillating roller according to claim 1, further comprising means for alternately pressurizing and degassing the axially variable volume for oscillating the oscillating roller. 3. The control means further includes means for determining the traversing motion of the immediately adjacent roller, wherein the roller covering of the oscillating roller is free to rotate and is controlled by the rotation of the immediately adjacent roller. being adapted to be rotated, the control means causes the oscillating roller to oscillate with the same oscillation as the oscillation of the immediately adjacent roller, but in a direction substantially opposite to this, thus causing rotational and axial 2. The oscillating roller of claim 1, wherein a combination of directional oscillating motions causes one of the ink and dampening fluid to be transferred to the oscillating roller in a substantially diagonal pattern. 4. further comprising bearing means for rotatably mounting said roller covering, said bearing means comprising an inner portion slidable on said roller shaft and axially movable by said axially variable volume; The horizontal swinging roller according to claim 1, characterized in that it has: 5. In a oscillating roller for one of the ink and dampening fluid systems of a printing press with an ink transfer roller vibrating at a predetermined cycle rate,
a roller shaft adapted to be mounted on a printing press; a roller covering mounted on said roller shaft to rotate freely and at the same time slide axially; and in relation to said roller shaft at the same cycle speed as an ink transfer roller. A oscillating roller characterized in that it includes means on the oscillating roller for vibrating said roller covering. 6. The means for vibrating the roller covering in relation to the roller shaft further comprises: 2.
an axially variable volume having two parts, one of which is axially supported by said roller shaft and the other part for rotatably mounting said roller covering; axially supported by said means of) and control means for directing pressurized fluid into and out of said variable volume for axially moving said roller covering in relation to said roller shaft. The oscillating roller according to claim 5, further comprising: . 7. Said control means for inflowing and outflowing pressurized fluid further comprises means for determining the axial vibration of the ink transfer roller and valve means for pressurizing and then degassing this variable volume. (wherein this valve means for pressurizing and then degassing is operated by said means for determining the axial vibrations of the ink transfer roller). The horizontal swing roller described in 6. 8. An axial variable volume is provided on each side of the oscillating roller, the means for inflowing and outflowing pressurized fluid is connected to both of the variable volumes, and the valve means is connected to one of the variable volumes. The oscillating roller according to claim 7, characterized in that while degassing the volume, the other variable volume is simultaneously pressurized. 9. In an oscillating roller for one of the ink and dampening fluid systems of a printing press having an oscillating ink transfer roller moving at a predetermined cycle speed, a roller shaft adapted to be mounted on the printing press, rotating and a roller covering mounted on the roller shaft for both axial vibration;
and a transverse roller comprising pneumatic means for vibrating the roller covering in relation to the roller shaft. 10. The oscillating roller according to claim 9, wherein the oscillating roller vibrates at the same speed as the ink transfer roller. 11. The oscillating roller according to claim 10, wherein the oscillating roller vibrates in a direction opposite to that of the ink transfer roller. 12. The oscillating roller according to claim 11, wherein the oscillating roller is a foam roller. 13. The oscillating roller according to claim 1, wherein the oscillating roller is a distributor roller. 14. The horizontal swing roller according to claim 1, wherein the horizontal swing roller is a rider roller. 15. The horizontal shaking roller according to claim 1, wherein the horizontal shaking roller is a foam roller. 16. A method of vibrating rollers in a printing press having one transverse roller and at least one other vibrated roller, comprising the steps of: A. detecting the vibration of the other vibrated roller; and B. the other vibrated roller. A method comprising the step of vibrating the first transverse roller at the same frequency as the roller. 17. The method of vibrating a roller according to claim 16, further comprising the step of vibrating the first roller in a direction opposite to the direction in which the other vibrated rollers are moving. 18. A method of vibrating a pneumatic axially variable volume air roller for vibrating a roller, comprising the steps of: A. pressurizing the variable volume to move in one axial direction; and B. then degassing the variable volume to move it in another axial direction, thus allowing the roller to vibrate. 19. A method of vibrating an air roller having a pneumatic axially variable volume at each end to vibrate the roller, comprising: A. degassing one axially variable volume while simultaneously degassing the other axially variable volume; B. pressurizing the axially variable volumes, and then simultaneously degassing one axially variable volume while simultaneously pressurizing the other axially variable volume, such that the two axially variable volumes A method characterized in that the variable volume vibrates the roller in the axial direction. 20. A method for controlling the application of at least one of ink and dampening fluid in a lithographic printing press having a lateral ink transfer roller, a foam roller and a plate cylinder, comprising: rotating the ink transfer roller at a predetermined frequency in an axial direction; and rotating the foam roller at the same frequency as the ink transfer roller, but in the opposite direction, and vibrating axially, so that the one fluid is oscillated in a diagonal pattern from the ink transfer roller to the foam roller. a control method, characterized in that said one fluid is transported in a diagonal pattern from a foam roller to a plate cylinder. 21. The oscillating roller of claim 5, wherein the oscillating roller is a foam roller within the dampening system and the ink transfer roller is within the dampening system. 22. The oscillating roller according to claim 21, wherein the ink transfer roller is in contact with the fall roller. 23. A method of vibrating rollers in a printing press having a first oscillating roller and a second oscillating roller in contact with each other, in which one of the first and second oscillating rollers is vibrated against the other roller. A method characterized by comprising the step of vibrating in the opposite direction. 24. The method of claim 23, wherein the first roller is an ink transfer roller and the second roller is a foam roller. 25. Claim 24, wherein the foam roller and the ink transfer roller are coated with ink fluid.
The method described in. 26. The method of claim 24, wherein the foam roller and ink transfer roller are provided with a dampening fluid. 27. Claim 26, wherein the foam roller is coated with both ink and dampening fluid.
The method described in.