JP3018081B2 - Roll roller - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to rollers for printing presses, and more particularly to roll rollers for use in inking and dampening systems of printing presses.

2. Description of the Related Art For ink transfer rollers (sometimes called dispensing or transfer rollers) somewhere between a form roller resting on a plate cylinder or roller and an ink or dampening fluid supply. It is already known to use an axial traversing motion on rollers in the inking and dampening system of a lithographic printing press. Generally, these ink transfer or transfer rollers are rotatably driven by a press and are made to mechanically vibrate axially.

In addition, traversing foam rollers have been developed that are frictionally driven axially by the oscillating motion of an adjacent transfer or ink transfer roller. No. 4,493,257 discloses such a traversing foam roller.
No. 4,718,344. Similarly, pneumatically oscillated and mechanically rotated ink transfer rollers have been previously developed. See Japanese Patent No. 57-93150 for the disclosure of such a roller. Another aspect of a motorized oscillating roller for fluid for ink and fluid in a dampening system is:
It is shown in U.S. Pat. No. 2,242,214. It is also known to mechanically vibrate the roller in the axial direction. See U.S. Patent Nos. 3,625,148, 4,509,426 and 4,672,894 and British Patent Application No. 2078172A. Furthermore, a method is known in which a foam roller that is mechanically rotated and mechanically oscillated in the axial direction is used in conjunction with a traversing ink transfer roller, and both rollers are oscillated at different frequencies. I have. U.S. Patent 4,397,
See 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 reduce the fluid distribution. It was not a complete solution to the problem. For example, in the case of a traversing foam roller driven axially by friction, when this foam roller is being pulled in one direction by an adjacent axially moving ink transfer roller,
In the nip of these two rollers there is a certain time during which the two rollers move axially essentially simultaneously so that little or no axial ink shearing occurs. Therefore, the new ink supplied to the foam roller by the ink transfer roller is transferred only in the radial direction and is not redistributed on the foam roller in the axial direction.
The possibility that "ghost phenomenon" occurs increases.

In most presses, where the foam roller is originally made non-vibrating and the traversing foam roller is retrofitted, the structure of the press causes the retrofitted foam roller to travel the full axial distance of the ink transfer roller do not do. Thus, the axial vibration movement of the foam roller is intentionally stopped, and the foam roller contacts the bearer on the plate cylinder or other parts of the press while the ink transfer roller is vibrating throughout its axial travel. There is another time that seems to be immobile. This kind of intermittent axial movement of the foam roll causes most oscillating foam rollers driven axially by friction according to the prior art to stop their contact with the rest of the press and to prevent excessive stroke. It has been widely used because it was equipped with a collar. When operated in this manner, excellent transfer from the ink transfer roller to the foam roller is seen when an axial shear action occurs, but transfer from the foam roller to the plate cylinder / roller requires that these two rollers Sometimes less than ideal when simply rotating, no diagonal transfer to the plate cylinder takes place while the foam roller is stopped axially by the collar.
Each of these modes has its own effect on print quality as these two different modes of operation occur during each axial stroke that makes up the entire cycle of the foam roller. Therefore, the plate has a foam roller,
Different amounts of ink are supplied, while the foam roller receives different amounts of ink from the transfer roll, the ink transfer roller, so that the same print quality is obtained during these two different modes of the full cycle. Hard to get.

Many attempts have been made to mechanically vibrate the rollers to achieve higher homogeneity, but the mechanical drive mechanism is complex and is itself a source of problems. For this reason most foam rollers on the press are
It was not mechanically vibrated in the axial direction. Further, the foam rolls are generally not fixed in a single location, but are biased themselves and are mounted from swing hangers that can move toward both within the plate cylinder and adjacent ink transfer rollers. This required flexibility imposes additional problems in attempting to mechanically oscillate such rollers. It is possible to design new presses for foam rollers that are mechanically axially vibrated, but such presses would be expensive to manufacture and operate. Designing a good mechanical vibration mechanism for a new press may be difficult, but designing for an existing press is even more difficult. For this reason, many of the retrofitted vibrated foam rollers have only been vibrated in the axial direction by friction from the oscillating motion of an adjacent ink transfer roller. Further, since the press roller was not mechanically driven in most presses, the press frame adjacent to the foam roller was usually rugged, and such a structure, as shown in U.S. Pat. Prevent retrofitting of the fluid drive extending outside the frame.

Pneumatic pressure has been used to provide oscillating motion for the ink transfer, i.e., the transfer roller, but previous designs have been inadequate and have long been found on presses in ink and dampening systems. It could not be adapted to a wide press requiring a small diameter roller. Also, some prior art air rollers used a fixed shaft and a rotating roller body or the core itself as an air cylinder.
As a result, the seal is difficult because the cylinder is rotated, and / or the seal between the fixed and rotating parts is forced by pneumatic pressure on these parts, acting as a brake and thus displacing the rollers. It also results in reduced rotation, reduced seal life, and increased maintenance and downtime. Japanese Patent No.
Another drawback of the previous pneumatic traversing ink transfer roller construction shown in No. 57-93150 is that it has a relatively short width, such as a small foam press, due to the deflection of the roller in the center. It is generally restricted to the press. Rollers such as those shown in this Japanese patent are not suitable for wide presses, i.e., presses having a width of 36 inches or more. This limitation is due to the structure of such a pneumatic roller as it is pressed against the adjacent roller, because of its structure, the central shaft flexes away from this adjacent roller, and instead, due to the abutting central portion therein. In addition, it comes from the fact that the center of a roller bends away from an adjacent roller as well. Thus, the more the end sinal of the roller is pressed against the adjacent roller, the worse the problem, the more (but not less) deflection in the center and the ink transfer roller to the adjacent roll. Results in a less homogeneous loading of For roller lengths greater than 36 inches, the problem of center deflection becomes very significant, and for rollers longer than this. Of course, this non-uniform roller loading tends to cause a change in ink or dampening fluid across the roller, resulting in a change in print quality across the entire roller.

Attempts have been made to vibrate both the foam roller and the ink transfer roller, but these prior art devices are not easily retrofitted to existing presses that are originally equipped with non-vibrating foam rollers. Various mechanical devices were used on both rollers. Furthermore, the axial movement during the vibration of the foam roller was only for a fraction of that time or was not synchronized with the movement of the ink transfer roller; the relative axis between the foam roller and the ink transfer roller There was no directional movement; or wiping between the foam roller and the ink transfer roller as if the foam roller and the oscillating roller were vibrating at different frequencies, as described in US Pat. No. 4,397,236. Because the action was not homogenous or maximized,
There was no way to optimize the wiping action of the rollers. Devices made as required by U.S. Pat. No. 4,397,236 further introduce another variable in the distribution of ink and / or dampening fluid. That is, for different parts of a complete cycle, different degrees of shearing action occur between the two rollers vibrating at different frequencies, which results in a change in the ink delivery and thus the quality of the print. It becomes.

[Means for Solving the Problems] The oscillating roller according to the present invention can be used as a foam roller in a dampening system of a press or an inking system, or at another roller position such as an ink transfer roller. But can be used. The press can be of any type with an ink train or a dampening train,
These include lithographic offset printing presses, flexo offset printing presses, and the like. In a preferred embodiment, the roll roller of the present invention includes an axially extending roller shaft adapted to be mounted on a press frame. The roller shaft may be a dead shaft, that is, a non-rotating one, or a live shaft, that is, a rotating shaft. The roller shaft has a piston element which is axially rotated on the shaft. The rollers generally have a covering made of metal (chrome plated), rubber or plastic compounds, or any suitable material used in the dampening train, such as a ceramic material. The piston is associated with a cylinder element, or structure, and with it forms an axially variable volume. The roller cover and cylinder structure are arranged such that expansion or contraction of this variable volume will cause the roller covering to move axially or oscillate. Of course, it is also possible to use the reverse arrangement, in which the cylinder structure is positioned axially on the shaft and the piston moves the roller covering. The cylinder structure and the piston are positioned within the roller between the roller shaft and roller covering without interfering with the press frame to slow down the rotation of the roller or cause the roller to deflect. In the dead shaft version, the piston and cylinder structure is independent of the roller shaft and roller covering and its core. In the live shaft version, the rotational movement is received by bearings on the ends of the roller shaft attaching the shaft to the press frame, so that the piston and cylinder structure has the outer surface of the shaft and the inner surface of the roller covering or its inner surface. A variable volume can be formed using the backup core. To minimize or eliminate roller deflection problems due to shaft journal loading on adjacent rollers, unlike the prior art, the piston and cylinder structure is such that the ends of the rollers are not at or near the center of the rollers. It is located very close to the department. The rollers according to the invention are therefore particularly suitable for long rollers (for example paper of 36 inches or more, or press width) and fine rollers (large length to diameter ratio).

In order to develop adequate vibratory forces, especially in small diameter rollers, the roller piston and cylinder structure must be capable of resisting all forces that resist vibration, such as from adjacent rollers that vibrate in double, triple or opposite directions. They can be stacked as needed to develop enough force to vibrate the roller in opposition. Of course, the stacked piston-cylinder structure is spaced from the body or core of the roller, held at the ends of the roller, and does not extend to the center to minimize deflection problems.

To further minimize deflection problems and reduce manufacturing costs, the roller shaft, piston and cylinder structures are made free to fit together without tight tolerances. If necessary to provide a tight seal or prevent rotation of the part, a "0" ring is used instead of a conventional tight compression fit.

The traversing roller according to the invention can also be used in conjunction with another adjacent traversing roller, in which case the roller according to the invention can be used with the same traversing, with a larger or smaller stroke. It can vibrate in the same or opposite direction as the roller at the same cycle speed or frequency.

If each of the prints performed must be of the same consistent high quality, it is necessary to dampen and inked the plate in exactly the same way. To maintain such consistency, the delivery of ink and dampening fluid must be consistent. In order to achieve consistency for maximum redistribution of the ink and / or dampening fluid, and also to reduce "ghosting", the swaying roller according to the invention has the same frequency when used in the foam position. Can be used with one adjacent ink feed or dispensing roller in such a way that it oscillates but moves in different directions along the axis. Such a structure and operation is achieved by inking the plate and / or
Or to provide a consistent axial step between these two rollers as well as between the form roller and the plate cylinder to ensure that the exact and confidential relationship is repeated each time the humidification takes place. Furthermore, the transfer of the resulting fluid, whether ink or dampening moisture, between the ink transfer roller and the foam roller and between the foam roller and the plate cylinder is performed in a desired diagonal pattern. That is, the relative axial and rotational movements of two respectively adjacent rollers always form a diagonal pattern.

The vibrations of the rollers of the present invention detect the vibrations of adjacent rollers, such as a change in axial movement, and pressurize the piston-cylinder structure to vibrate the rollers according to the present invention, preferably in the manner described above. Fluid,
Or, it is controlled by a control means for controlling the intake, degassing, or discharging of compressed air. The control system provides the rollers of the present invention with a variable length of stroke so that the rollers of the present invention may be co-located with adjacent rollers, or at a lower or higher speed, if desired. It can be moved axially with variable dwell time. Thus, the wiping operation between the oscillating roller according to the invention and the adjacent oscillating roller and with the plate cylinder can be optimized. The motion of the oscillating roller according to the present invention provides compressed air with high air pressure adjusted 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 a variable area orifice, Or it is achieved by venting. Changing the size of the discharge orifice changes the roller speed. Naturally, the level of the supply pressure also changes the vibration speed. Adjustment of feed 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 roll roller according to the invention is to provide a pneumatic mechanism which can be easily installed on a printing press in order to eliminate the "ghost phenomenon".

Another object of the roll roller of the present invention is to provide an air piston-cylinder configuration that causes axial movement without controlling rotational movement.

Yet another object of the traversing roller and method of the present invention is that it is isolated from the outside of the body or core of the roller and / or enclosed at the end of the roller, thus eliminating deflection of the roller and minimizing hold down. It is to provide a pneumatic piston-cylinder arrangement as described above.

Yet another object of the oscillating roller according to the invention is to allow one or more piston-cylinder structures to be provided on each side of the roller, so that even small radius rollers provide the desired vibration. It is an object of the present invention to provide a configuration capable of developing a sufficient force.

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

Yet another object of the traversing roller of the present invention is that
To eliminate "ghosting", adjacent inks are moved in an axially opposite direction to maximize fluid distribution, such that both rollers are synchronized to operate at the same cycle speed or frequency. An object of the present invention is to provide a foam roller that can be used together with a transfer roller.

It is yet another object of the present invention to provide a structure for pneumatically vibrating rollers in an ink or dampening system of a press.

It is another object of the present invention to provide a vibrating roller structure that is particularly suitable for retrofitting into a press, instead of a non-vibrating roller.

These and other objects and advantages of the present invention will become apparent from the accompanying drawings and the following description.

Embodiment Referring to FIG. 1, there is shown one type of printing press that can use a traversing roller according to the present invention. The press shown here is a lithographic or offset printing press having both an ink train and a dampening train, but the press is of the type that combines these two systems, an ink system and a dampening system. Or a different type of press, such as a gravure or flexographic press.

In the double-sided press shown in FIG. 1, the web (9) has its own plate cylinder or roller (1).
Pass between two offset or blanket cylinders or rollers (10) running against 1). Each plate cylinder provides a supply of ink fluid from a liquid reservoir (12), and a supply of dampening fluid from a tray (13), and in some presses rollers (14) which may be ink fountain rollers. , A distribution roller (15), an axial traversing ink transfer roller (17) and a foam train (18) resting against the plate cylinder. Further, a rider roller (20) is shown on the foam roller (18). The traversing roller according to the invention is designated by the reference numeral 1
At the positions indicated at 7, 18 and / or 20, the rollers can also be used.

Referring to FIG. 2, a first embodiment of the oscillating roller (30) according to the present invention is illustrated. Although this figure actually shows only one end (left side) of the traversing roller (30), the other end is generally of the same construction and the differences that exist between them are described below. Or from FIG.

As shown in the figure, the roll roller (30)
It is mounted in a partly represented press hanger or frame (32). For the sake of reference, it is assumed that the oscillating roller (30) is used at the position numbered 20 in FIG. In this example, the roll roller (30) was retrofitted to replace the live shaft. To this end, the press frame (32) is provided with a bearing cavity (34) provided with a dummy bearing (36) to perform the conversion in this example. This dummy bearing (36) is positioned or clamped in the press frame (32) by conventional means (not shown) to prevent its rotation. The small diameter pilot end (38) of the roller shaft (40) extends into the dummy bearing (36) and is held by a roll pin (42). Roller shaft (40)
The other end (not shown) is similarly attached to the press frame. The roller shaft (40) is a dead shaft, that is, a non-rotating shaft.

As can be seen from FIG. 2, the roller shaft (4
0) is enlarged from the pilot end (38) to a larger diameter. The shaft (40) extends across the press to a completely opposite hanger or frame. It has been increased to better withstand the bending loads imposed on the shaft by contact with the rollers.
(See FIG. 1) In order to supply pressurized fluid or compressed air to the operation mechanism of the oscillating roller (30) according to the present invention, the center of the roller shaft (40) is located in the axial direction of the roller shaft (40). A passage (44) is formed. In some cases, the outer end of the passageway (44) can be used to connect to the air supply / vent, but in this example this is not possible due to the robust press frame (32). Yes,
The outside end of the passage (44) is closed by a pipe plug (46) or the like. Roller shaft (4) to draw and discharge pressurized fluid into and out of passage (44)
Within 0) there is a short radial passage (48), with suitable fittings (50) and hoses or tubing (52) connecting this to the control system. Suitable control means are shown in FIG. 6 or FIG. Similarly, a radial passage (54) is provided to supply or exhaust air from the passage (44), which is
It is to be in fluid communication with the air being supplied or discharged through the pipe (52).

The structure of the oscillating roller (30) according to the present invention which causes and accepts sliding or axial oscillating movement will now be described. At a few inches from each end, the roller shaft (40) is provided with a groove for a ring clip (56), which is positioned towards the inside of the radial passage (54). Slidably mounted on the roller shaft (40) is an annular piston (58) that abuts against the outside of the ring clip (56). The annular piston (58) has a groove on its inner diameter and outer shape, and the annular piston (58)
O-ring (60) for sealing to the adjacent surface
(62) can be accepted. The annular cylinder member (64) also slides on the roller shaft (40) and has a connected cylinder wall portion (68) and a cylinder head portion (66) into which the annular piston (58) can slide. The inner surface of the cylinder head (66) adjacent to the roller shaft (40) is also grooved, and is
The ring (70) can be received. Therefore, a variable volume space is formed by the roller shaft (40), the annular piston (58), and the annular cylinder member (64). The air is introduced into the variable volume space formed between the annular piston (58) and the annular cylinder member (64) by pushing the annular piston (58) to the right and causing the ring clip (56) to abut. Then, the annular cylinder member (64) is moved to the left. Of course, the entrapment of air in the variable volume space between the piston and the cylinder member (not shown) on the other side of the roller shaft (40) will cause this cylinder member to move to the right. This axial vibration to the left and right is caused by pressurizing the variable volume space in the axial direction on the left or right side of the roller shaft (40) and / or
Or it can be caused by bleeding.

The widthwise movement of the annular cylinder member (64) is transmitted to an oil-impregnated bronze annular sleeve (72) that is also slidable on the roller shaft (40). As shown in FIG. 2, the right end of the annular sleeve (72) abuts the left end of the annular cylinder member (64) for this purpose. In this example, the annular sleeve (72) has an inner race (74) for a rolling bearing (76). Grooves are provided on the inner and outer surfaces of the annular sleeve (72) to provide a secure fit for the over-shaft sleeve, such that the inner race (74) rotates on the annular sleeve (72), O-rings (78), (80), and (82) that prevent the 72) from rotating on the roller shaft (40) can be stored. Therefore the annular sleeve (7
2) and inner race (74) receive only axial movement and do not receive rotational movement.

The rolling bearing (76) has a roller body that supports the roller covering (88) or an outer race (84) that meshes with the core (86). Therefore, the roller covering (88) and the core (86) are rotatably mounted by the rolling bearing (76) so that they can rotate freely. Again, the core (86) helps with an interference fit with the outer race (84) without requiring extremely tight tolerances,
There is a groove to accommodate an O-ring (90) that rotates the outer race (84) and core (86) together,
The outer race (84) and the core (86) are both free to rotate in relation to the roller shaft (40).

Since the illustrated rolling bearing (76) does not take in axial thrust, a thrust bearing (92) consisting of a radial roller (94), an inner race (96), and an outer race (98) forms an annular sleeve (72). Are matched. The end of the annular sleeve (72) is stepped in this example to accommodate the inner race (96). Outside race (98)
Rests on an end ring (100) which is held in place by an outer ring ring (102) in a groove on the end of the roller core (86). Again, an O-ring (103) is provided in the end ring (100),
The relative rotation between the end ring (100) and the roller core (86) can be prevented.

To position the outer race (98) within the core (86)
The end ring (100) is the outer race (8) of the rolling bearing (76).
4) and stacked against the "L" shaped cross-section keeper (104), all of which are formed within the outer end of the core (86) and within the enlarged diameter portion (105). It is in.
The keeper (104) consists of an annular sleeve (72) and an inner race (7
4) Grasping radial roller (94) and inner race (9
6) is provided so that it always remains supported on the annular sleeve (72). Close the rollers and keep the lubrication in place for the thrust bearings (92) and rolling bearings (76) in the end ring (100)
A seal (106) is provided between the roller shaft (40). A grease fitting (108) and a grease passage (110) may be provided in the end ring (100) to lubricate the rolling bearing (76) and the thrust bearing (92).

According to the structure described above, the axial movement is completely decoupled from the rotational movement, and the pneumatic seal is not at all subjected to rotational movement as well. Thus, there is no tendency for the rotating seal to act as a brake, as in the prior art, or to provide additional resistance to rotation.

Preferably, the axial vibration of the roller of the present invention is the sixth vibration.
It can be controlled by the control system shown in the figure or in FIG. First, the system of FIG. 6 will be described.
In this figure, the oscillating roller (30) of the present invention is composed of a plate cylinder (not shown in FIG. 6) and an ink transfer roller (120) mechanically vibrated in the axial direction by a press driving device. Touch the form position (18 in FIG. 1).
No.). As shown, the vibration of an adjacent traversing ink transfer roller (120) detects the roller turning at the end of its axial movement (trigger point) and a proximity switch (122 or 12).
4) Means (cylindrical alternating current, manufactured by Furnas,
Or a proximity switch such as a DC type). Of course, devices of other types than proximity switches (122 and 124), such as microswitches or pneumatic logic devices, could be used, or the timing signals could also be driven by a press drive or ink transfer roller drive. It can be imported from anywhere on the device. If desired, instead of detecting the ink transfer roller (120) itself, detect one of two adjustable collars (125) mounted on the opposite side of the shaft of the ink transfer roller (120) You can also. With an adjustable collar, these trigger points can be easily changed. Similarly, the position of the proximity switch can be changed to adjust the trigger point. When the end of the axial travel of the ink transfer roller (providing a trigger point) (120) or the collar (125) is detected, a solenoid-operated four-way control valve (126) (Schrade
r Direc manufactured by Bellows, Parker Hamnifin
tair2 valve, direct pipe port, like a four-way double solenoid spool valve), one signal is sent, this valve deflates the variable volume space on one side of the oscillating roller (30) .

As shown, the slidable valve body (121) in the valve (126) has a solenoid coil (121) such that one variable volume space is pressurized and the other variable volume space is vented. 123) by one or the other.
As shown in FIG. 6, the variable volume space in the left figure is
The right side is pressurized while the right side is evacuated, as represented by the solid arrow 125a, so that the traversing roller (30) and its covering (86) move the piston and cylinder head of the right variable volume space together. In contact, it will move to the left until further movement is limited or until the ink transfer roller (120) reverses direction.

When the right end of the ink transfer roller (120) reaches the re-right end of its stroke, it trips the proximity switch (124), which itself is partially shown by a dotted line at the right end of the valve body (121). As shown, the right solenoid coil (123) is activated to move the valve body (121) from its leftmost position shown to the right, and as such is indicated by the dashed arrow (127). Then, the right variable volume space is pressurized, and the left side is evacuated. When the above occurs, the core (86) and the covering (88) of the oscillating roller (30) begin to move, and the piston and cylinder head of the left variable volume space come into contact or the subsequent ink transfer roller (120). Keep moving to the right until the change of direction occurs.

During this time, the ink transfer roller (120) is moving to the left, and when it reaches the leftmost point of its stroke, the roller trips the switch (122) and then begins to return to the right. When the switch (122) is disengaged, the left solenoid coil (123) is activated, the valve body (121) is again turned over, and the core (86) and the covering (88) of the oscillating roller (30) are again turned on. Move left. The above operation is repeated continuously as necessary to oscillate the roll roller (30). Accordingly, the control system of FIG. 6 relocates the core (86) and covering (88) of the oscillating roller (30) to the adjacent oscillating ink transfer roller (12).
At about the same time as the direction change of 0), the direction is changed.

Here, it has moved in the opposite direction to the traversing roller according to the invention as described above, but if desired, this depends on which side of the traversing roller according to the invention is pressurized and vented, It can also move in the same direction as the adjacent roll roller. The vibration speed of the roller of the present invention may be higher, lower, or equal to the vibration speed of the adjacent ink transfer roller. Of course, if the speed is higher, there may be a dwell time at the end of the stroke. Similarly, the length of the vibration can be controlled.
For example, if the roller of the present invention moves slowly and the full stroke is not completed before the change of direction occurs,
Assuming that the axial speed of the adjacent roll roller (which trips the vibration of the roller of the present invention) is constant, it will have a shorter vibration than if it moved at a higher speed. right. The axial speed of the oscillating roller according to the invention can be increased by increasing the supply pressure via a conventional regulating device (128) and / or by reducing the throttle of the valve (130) controlling the air release. Can be increased. Of course, the speed can be reduced by reducing the feed pressure and / or by increasing the throttle of the valve (130) (reducing the flow area).

Also, if desired, the oscillating roller (30) can be prevented from oscillating, or simply biased toward either side of the breath. For example, one of the solenoid coils (123) may be kept activated to keep the valve body in the position shown in FIG. 6 and the roller covering (88) may be biased to the left. Alternatively, such biasing can be achieved pneumatically, such as by applying pressure only to the left variable volume space. Another variant embodiment is:
A different type of valve that also provides a centered position is to replace valve (126). In any case, whether biased to either side or centered, the roll roller (30) of the present invention never leaves the ink transfer roller (30) because the ink transfer roller (120) is longer. There is no problem at all, since the foam never leaves the edge of the foam on the plate cylinder because it is inside the end of the covering (88) of the traversing roller (30).

Referring to FIG. 7, a second embodiment of the control system is shown, which differs from the system shown in FIG. 6 in which the vibration was synchronized to adjacent rollers. It is an automatic vibration type. A system such as the one shown in FIG. 7 applies the vibration of one roller according to the invention to the vibration of another roller, as is the case with the roller numbered 15 in FIG. Ideal when there is no need or desire to synchronize to Also, the system of FIG. 7 is used to self-oscillate one roller and the system of FIG. 6 is used to vibrate adjacent rollers such as foam rollers for dampening or inking systems and ink transfer rollers. You can also. This consideration is extremely useful in retrofitting two adjacent traversing rollers to a press that had non-vibrating rollers.

As can be seen from FIG. 7, in this example, the oscillating roller (30) has at its ends the same left and right air supply / vent lines for the left and right variable volume spaces.
(52L and 52R). These air lines
Two function valves (140 and 141) that detect the presence or absence of pressure in the lines (52L and 52R), respectively, to self-oscillate the rollers (model No. 7818-54 made under the trademark of Grigris)
Connected to something like 20). As shown, after leaving the function valve, the lines (52L and 52R) each have a variable area throttle valve (142 or 143) (such as valve (130) shown in FIG. 6). A one-way valve (144) that permits flow only when the first part with the ball and its ball leaves its valve seat in the direction of its respective variable volume space.
Or 145) to a second part with For convenience, both the one-way valve (142 or 143) and the throttle valve (144 or 145) can be integrated into a single valve body, such as in the SCI sold by Humphrey. These lines then resemble those of the valve (126) with the valve body (121), but differ in that the valve body is pneumatic rather than electrical, with the slidable segmented valve body (147 ) And into this. As shown, the valve body (14
7) Each end has a piston-cylinder configuration (148 and 14).
9) (such as the 34A type manufactured by Humphrey, an air operator for valve (146)), which is connected back to either of the two function valves. The function valves (140 and 141) and the four-way valve (146) are all connected to a high pressure supply, such as a pressure regulator (128).

According to the control system as shown in place in FIG. 7, the left-hand variable between the roller left piston cylinder from the adjuster (128) to the four-way valve (146) as indicated by the left arrow. High pneumatic pressure is applied to the volume and to both function valves (140 and 141). As the left line (52L) is pressurized, the left function valve (14
0) is closed due to its configuration and the right piston cylinder (148) on the valve body (147) through the line from the adjustment device
Suppress the passage of pressurized air up to However, the right piston cylinder in the roller is vented through a function valve (141), a variable area throttle valve (143) and a four-way valve (146), as indicated by the right arrow. As the pressure in the right variable volume falls, the right function valve (141) opens due to its configuration and passes through the right function valve from the regulator to the left piston cylinder (1) of the valve body (147).
Enable the flow up to 49) and move it to the right. At the same time, the increased pressure in the line (52L) causes the left function valve (140) to pump pressure down to the piston cylinder (148) on the right side of the valve body. As a result, at about the same time as the roller core (86) and the covering (88) have moved to their full leftmost position on the shaft, the valve body (147) slides to the right (partially shown by the dotted line to the right). Pressurize the variable volume space on the right side of the roller (as described in the description of the operation shown in FIG. 6) and bleed the variable volume space on the left side of the roller (as described in the operation description). The core (86) and covering will then be returned to the right, the position shown in FIG. Again, the subsequent pressure increase in the left function valve (140) and the pressure decrease in the right function valve will cause the valve body (147) to slide again, causing another stroke.
This procedure is repeated as desired to self oscillate the rollers. It should be considered that any suitable roller biasing or centering arrangement, such as that described in connection with FIG. 6, can also be adapted to the self-excited braking control system of FIG.

Just as any control system is shown used with the swaying roller (30), depending on the field of application, any one with the subsequently described embodiment of the roller of the present invention. It can be used.

Referring to FIG. 3, there is shown a second embodiment of a roller (150) according to the present invention. This roller is generally similar to the roller shown in FIG. 2 and is given the same number as shown in FIG. 2 as long as it is similar. The main difference between the rollers shown in FIGS. 2 and 3 is that the roller (150) in FIG. 3 has a stacked piston that develops an additional axial force to oscillate the rollers. And a cylinder structure. As mentioned above, this configuration is particularly advantageous when the rollers are of small diameter, especially for developing a suitable force to vibrate the rollers against the opposite axial vibration of the adjacent rollers. It is difficult to provide a variable volume space with a cross-sectional area.

As shown, instead of having a single piston on each side of the roller shaft (151), a second piston is provided on each side.
The same inner piston (152) is provided. This second piston is interlocked with a second ring ring (154) provided in a second ring ring groove on the roller shaft (151) in a direction inward of the ring clip (56) and its groove. The second piston (152) and the second cylinder (1
56) both have the same O-rings as the first piston and the first cylinder. The second cylinder (156) simply abuts the annular cylinder member (64). The supply or degassing of air for the second piston and cylinder is provided in passage (44), designated 158, and therethrough and between the second cylinder (156) and the second piston (152). Is merely a continuation of the radial passageway (160) that also communicates with the second axially variable volume formed in the second passageway.

The force generated in the second piston-cylinder is
In addition to the force generated by the piston-cylinder, and doubles its output. Of course, if additional force is required, additional piston-cylinder configurations can be stacked on each side of the roller.

With reference to FIG. 4, a third embodiment of the oscillating roller (180) according to the present invention is shown and described, which is particularly suitable for small diameter rollers. In this example, instead of rotating the rolling bearing on the inner race on the inner annular sleeve as shown in FIGS. 2 and 3, the roller (182) is directly on the roller shaft (184). It is spinning. The roller shaft can be cured or heat treated in the area below the roller, if necessary. As a result, the structure can be adapted to rollers of significantly smaller diameter. As shown, this type of configuration is used for the stacked piston and cylinder configuration described above. That is, a plurality of pistons (186 and 18) and cylinders (190 and 190) at each end of the roller to provide sufficient axial direction.
A plurality of axially variable volumes are constructed during 192). This configuration is suitable for small diameter rollers (the area between the roller core (192) and the shaft (184) is small).

Another difference between the third embodiment (180) and the previously described embodiments is the positioning of the thrust bearing. In a third embodiment, the roller (7
The thrust bearing (194) outside of 6) is inside the roller (182). Any positioning is acceptable and works well as long as the rotating part is separated from the non-rotating part by a thrust bearing.

For any of the embodiments shown, the axial load capacity of the combination of the radial load bearing capacity of the rolling bearing and the rolling thrust bearing is such that a rolling bearing with tape, a thrust angular contact ball bearing, or even a sliding ball bearing. It should be disaggregated that it can be filled in another form. However, the use of a rolling bearing with another thrust bearing provides a larger radial load capacity with a more compact diameter. Although rolling bearings or ball bearings are preferred, it is also possible to use a suitable sliding bearing, such as an oil-impregnated type.

Referring to FIG. 5, the roller oscillating in the axial direction (19)
A fourth embodiment 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 bearings or rolling bearings (202) held on a press hanger or frame (204). Thus, the entire shaft (200) is freely rotated by adjacent rollers, whether they are plate cylinders or other adjacent rotating rollers. Of course, according to this configuration, the shaft (200) has a gear (not shown) on one end driven by a press drive.
It can easily be adapted to be rotated mechanically, for example.

Roller shaft (200) as shown
The air passage (206) has a first radial connection passage (206) starting from the air shaft coupling (210) and a second radial passage (211) communicating with the piston and cylinder structure of the variable volume space. 206), which is described below. The air shaft coupling (210) is then stationary and can supply or bleed 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 is provided for the air shaft coupling, the body (210) itself can act as a bearing,
It may be made of a suitable bearing material such as oil-impregnated bronze. The body has two parts (21
6) There is. Immediately inside the section (216), an annular collector chamber (218) is formed in the body to maintain constant communication with the rotating passage (208). This annular chamber (218), on the other hand, has an air supply / vent vent line (224) from the control system via passage (220) and fittings (222).
It is connected to the. Use a shaft (20
A pair of seals (226) that are in close contact with 0) are provided on the end of the body. This seal (226) is held in place by two washer rings (228),
On the other hand, these rings are two ring clips, or rings (230), located in grooves on the shaft (200).
It is fixed by. Alternatively, these seals (226) may be omitted and the body may be removed with a small amount of airflow leaking around the shaft (200) so that rotation of the shaft is not limited by air pressure on the seal. The air shaft coupling body (21
Within 0), shaft bores with tight tolerances can be provided. The body (210) itself, the air line (22
4) preferably prevents rotation by a torque strap (not shown) connecting the body (210) to the press frame.

As shown, a second radial passage (211)
Communicates with a variable volume space at each end of the roller that causes the outer surface of the roller to vibrate axially. As shown, and as in the previous embodiment, each of the variable volumes is provided with a piston and cylinder structure. Piston (232) is an annular member slidably mounted on shaft (200). Again, the piston (232) has an inner O-ring (234) and an outer O-ring (236) to seal the piston with both the shaft (200) and the cylinder (238), respectively, so that any tight It is not necessary. In this example, the cylinder itself is
It is formed by one end of a stepped roller core (240) as shown at (242) to form a shoulder (244) to limit the travel of the piston. The stroke of the piston in relation to the shaft in one direction inward is thus limited by the ring ring (246) engaged in a groove in the roller shaft (200). The other end of the annular, variable volume cylinder structure is another annular ring (250) or roller shaft (200)
It is closed by a slidable cylinder head.
In this way, the annular ring (250) is in close contact with both the shaft (200) and the cylinder wall (238) by the pair of O-rings (252 and 254). Annular ring (250)
Can slide on the roller shaft (200), but the core (2
The abutment with the ring ring (256) held in the groove formed in the outer end of 40) prevents further movement relatively outward from the roller core (240).

The core (240) itself is coated with a roller covering (258) suitable for the location where the roller is to be operated. Due to the use of O-rings (234), (236) on member (232) and O-rings (252), (254) on member (250), these two members and shaft (200) become core (240) and covering (258) and will be rotated. Thus, all relative rotation occurs within the bearing (202).

The structure described above is preferably duplicated on the other side, and two air supply / venting lines are connected to the control system in the manner shown in FIGS. This pressurized air is under pressure from the variable volume space at the other end of the roller (not shown) such that the roller core (240) and its covering (258) oscillate or move to the left. While the air is being vented or deflated, it may be supplied to the end shown in FIG. 5 to axially expand the variable volume space 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 the covering WAG to the right to complete one cycle. Then, the air connection is reversed. This operation is repeated and can be varied as described above.

To indicate the approximate size of the described roller size, the diameter of the roller shaft may be 3/4 "to 3" and the outer diameter of the roller covering may be 2 "to 8". Of course, a particularly small size applies to the embodiment shown in FIG.
The arrangement according to the invention is particularly advantageous for rollers having a length of 36 inches or more, but it can also be used for smaller rollers such as 12 inches in length or for larger lengths such as 80 inches or more.

The control system is shown using a four-way valve,
A three-way valve could be used instead. Thus, given a suitable timing device, such as a multi-contact relay, multiple single solenoid valves could alternatively be used to perform various functions.

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

As pointed out, the vibration speed of the roller adjusts the throttle in the line where air is bleed, more specifically by pressurizing the variable volume space at one end and bleeding the variable volume space at the other end of the roller Caused by what can be done. This method provides a smoother operation and avoids convulsive operations, which often occur when speed is controlled only by adjusting the high pressure input.

Several preferred embodiments of the oscillating roller device according to the present invention and the method of oscillating the roller according to the present invention have been shown and described, but from the foregoing it will be appreciated that variations, modifications, and equivalent structures are possible. , And steps should be understood to fall within the scope of the claims herein.

[Brief description of the drawings]

The drawings illustrate an embodiment of the present invention, and FIG. 1 is a cross-sectional view of one type of press that can use a traversing roller according to the present invention. FIG. 2 is a cross-sectional view of one end of a first embodiment of the traversing roller of the present invention using a dead shaft, that is, a non-rotating shaft. FIG. 3 is somewhat similar to that shown in FIG. 2, but differs in that it has two stacked piston-cylinder structures instead of one.
FIG. 4 is a cross-sectional view of one end of a second embodiment of the oscillating roller according to the present invention. FIG. 4 shows a swaying roller according to the invention that is somewhat similar to that shown in FIG. 2, but differs in that it is particularly suitable for small diameter rollers. It is sectional drawing of one end of 3rd Embodiment. FIG. 5 is a cross-sectional view of a fourth embodiment of a roll roller according to the present invention using a live or rotating shaft. FIG. 6 is a schematic diagram of one embodiment of a control system for a swing roller according to the present invention. FIG. 7 is a schematic diagram of a second embodiment of the control system for the roll roller according to the present invention. (9) Web paper (10) Blanket cylinder (11) Plate cylinder (12) Liquid storage container (13) Tray (14) Ink discharge roller (15) Distribution roller ( 17) Ink roller for axial traverse ink transfer (18) Foam roller (20) Rider roller (30) Roller roller (32) Press hanger (frame) (34) Bearing Cavity (36) Dummy bearing (38) Pilot end (40) Roller shaft (42) Roll pin (44) Opening (passage) (46) Pipe plug (48) ... Radial passage (50) ... Fitting (52) ... Hose (54) ... Path (56) ... Ring clip (58) ... Circular piston (60) (62) "0" ring (64) …… Circular cylinder member (66) …… Cylinder head (68) … Cylinder wall (70)… “0” ring (72)… Annular sleeve (74)… Inner race (76)… Rolling bearing (78) (80) (82) “0” ring (84) Outer race (86) Core (88) Roller covering (90) Zero 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 fitting ( 110) Crease passage (120) Ink transfer roller (121) Valve body (122) (124) Proximity switch (123) Coil (125) Color (126) Valve (128) Adjustment device (130) Valve (140) (141) Function valve (142) (143) Throttle valve (144) (145) 1-way valve (146) ... 4-way valve ( 147) Valve body (148) Right piston cylinder (149) Left piston cylinder (150) Roller (151) Roller shaft (152) Second piston (154) Ring Ring (156) Second cylinder (160) Radial passage (180) Rolling roller (182) Roller (184) Roller shaft (186) (188) Piston (190) ( 192) Cylinder (192) ... Core (194) ... Thrust bearing (198) ... Roller (200) ... Shaft (202) ... Rolling bearing (204) ... Press hanger (206) ... Radial connection passage (208) ... passage (210) ... air shaft joint (210) (212) body (214) ... opening (216) ... two parts (218) ... collector chamber (220) )… Passage (222)… mounting fixture (224)… air supply / gas release line (226 … A pair of seals (228)… Washer ring (230)… Ring clip (232)… Piston (234) (236) “0” ring (238)… Cylinder wall (240)… Core (246) ) Ring ring (250) Ring ring (252) (254) Zero ring (258) Covering

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-227343 (JP, A) JP-A-1-258952 (JP, A) Fully open Showa 60-38737 (JP, U) Really open Showa 63- 151838 (JP, U) (58) Fields surveyed (Int. Cl. ⁷ , DB name) B41F 31/14 B41F 31/26 B41F 7/24

Claims (16)

(57) [Claims] An oscillating roller for one of an ink and a dampening fluid system of a printing press, comprising: an axially extending roller shaft adapted to be mounted across the width of the printing press; An annular cylinder member that is concentrically supported on the roller shaft in contact with the roller shaft and that is disposed so as to be movable in the axial direction; and An annular piston that is supported and attached to the roller shaft in a non-rotatable and slidable manner inside the annular cylinder member and abuts the annular cylinder member,
A variable volume space formed by being surrounded by the roller shaft, the annular piston, and the annular cylinder member; and a roller covering rotatably disposed via a bearing on the annular cylinder member concentrically with the roller shaft. An ink transfer roller provided adjacent to and in contact with the roller covering and mechanically moved in the axial direction;
A detecting means for detecting an end point of the axial movement of the ink transfer roller; and a fluid flowing into and out of the variable volume space based on the detection of the detecting means for detecting the axial movement of the ink transfer roller. Control means for sliding the roller covering in the axial direction. 2. The oscillating roller has a variable volume space on each side thereof, and the control means alternately applies the variable volume space to oscillate the oscillating roller. 2. The roll of claim 1, further comprising means for pressing and venting. 3. A bearing means for rotatably mounting said roller covering, said bearing means being slidable on said roller shaft and axially movable by said variable volume space. The traversing roller according to claim 1, having a movable inner part. 4. The control means for inflowing and outflowing a pressurized fluid further comprises a control valve for pressurizing the variable volume space based on the detection of the detection means and then bleeding air.
The traversing roller according to claim 1, further comprising an adjusting device that supplies pressurized air to the variable volume space. 5. The traversing roller according to claim 1, wherein the traversing roller is a rider roller. 6. The roller according to claim 1, wherein the roller is a foam roller. 7. The variable volume space is provided on each side of the oscillating roller, the means for inflow and outflow of pressurized fluid is connected to both of the variable volume spaces, and the control valve is connected to one of the variable volume spaces. 5. The traversing roller according to claim 4, wherein the other variable volume space is simultaneously pressurized while evacuating the variable volume space. 8. An oscillating roller for one of the ink and dampening fluid systems of a printing press, comprising: an axially extending roller shaft adapted to be mounted across the width of the printing press; An annular cylinder member that is concentrically supported on the roller shaft in contact with the roller shaft and that is disposed so as to be movable in the axial direction; and An annular piston that is supported and attached to the roller shaft in a non-rotatable and slidable manner inside the annular cylinder member and abuts the annular cylinder member,
A variable volume space formed by being surrounded by the roller shaft, the annular piston, and the annular cylinder member; and a roller covering rotatably disposed via a bearing on the annular cylinder member concentrically with the roller shaft, An adjusting device that supplies fluid to a pipeline connected to the variable volume space, and a fluid that flows into and out of the variable volume space by detecting the presence or absence of pressure in the pipeline connected to the pipeline. Control means for self-exciting the oscillating roller in the axial direction, and oscillating the roller adjacent to the oscillating roller by self-excited vibration of the oscillating roller by the control means. 9. An ink and dampening fluid system of a printing press having an ink transfer roller oscillating at a predetermined cycle speed, separated from the tray and plate cylinder of the damping fluid system or the plate cylinder. One or more oscillating rollers for transporting dampening fluid from a tray of the dampening fluid system to a plate cylinder in contact with the shaft, the shaft being adapted to be mounted across the width of a printing press. A roller shaft extending in the axial direction, an annular cylinder member concentric with the roller shaft, supported on the roller shaft in contact with the roller shaft and disposed so as to be movable in the axial direction, and the roller shaft. Concentric with the roller shaft and on the annular cylinder An annular piston that is supported and attached to the roller shaft in a non-rotatable and slidable state inside the material and abuts the annular cylinder member, and is surrounded by the roller shaft, the annular piston, and the annular cylinder member. A variable volume space formed by
A bearing disposed at an end of the roller shaft, a roller covering concentric with the roller shaft and rotatably disposed on the annular cylinder member via a bearing, and adjacent to which the roller covering contacts. An ink transfer roller provided and mechanically moved in the axial direction, detection means for detecting the end point of the axial movement of the ink transfer roller, and detection of the detection means for detecting the axial movement of the ink transfer roller Control means for causing the roller covering to slide in the axial direction by flowing a fluid into and out of the variable volume space based on the swinging roller. 10. The means for oscillating the roller covering in relation to the roller shaft further comprises an axially variable variable volume space having two parts and the means in relation to the roller shaft. 10. The variable volume space for moving the roller covering in the axial direction and control means for inflow and outflow of pressurized fluid therefrom are included.
The roll roller described in 1. 11. The traversing roller according to claim 9, wherein said traversing roller is a foam roller in said dampening system and said ink transfer roller is in said dampening system. 12. The traversing roller according to claim 11, wherein the ink transfer roller is in contact with the foam roller. 13. The ink and dampening fluid system of a printing press having an ink transfer roller that oscillates at a predetermined cycle speed, away from the tray and plate cylinder of the dampening fluid system or the plate. One or more oscillating rollers for contacting a cylinder to carry dampening fluid from a tray of the dampening fluid system to the plate cylinder, a roller shaft adapted to be mounted on a printing press; An annular cylinder member disposed concentrically with the roller shaft and supported on the roller shaft in contact with the roller shaft and disposed so as to be movable in the axial direction; And cannot rotate inside the annular cylinder member. An annular piston which is supported and mounted on the roller shaft in a state where it is possible and which also comes into contact with the annular cylinder member; and a variable volume space formed by being surrounded by the roller shaft, the annular piston and the annular cylinder member. A roller covering rotatably disposed via a bearing on the annular cylinder member concentrically with the roller shaft for both rotation and axial vibration, and provided adjacent to the contact of the roller covering. Detecting means for detecting the end point of the axial movement of the roller, and vibrating the roller covering in relation to the roller shaft based on the detection of the axial movement of the roller contacted by the roller covering. Pneumatic control means for causing
A throttle valve which is provided in an air line which is a part of the pneumatic control means and which can change the vibration speed by increasing or decreasing the area of the air line;
A traversing roller comprising: 14. The traverse roller according to claim 13, wherein the traverse roller vibrates at the same speed as the ink transfer roller. 15. The apparatus according to claim 15, wherein said oscillating roller oscillates in a direction opposite to that of said ink transfer roller.
14. The traversing roller according to 14. 16. The traverse roller according to claim 15, wherein the traverse roller is a foam roller.