JP4632516B2 - Stencil printing machine - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a plate cylinder and a stencil printing apparatus having a plate cylinder driving means for rotationally driving the plate cylinder.
[0002]
[Prior art]
Conventionally, digital thermal stencil printing is known as a simple printing method. This is because a thermal head in which fine heating elements are arranged in a row is brought into contact with a heat-sensitive stencil master (hereinafter referred to as “master”) formed by laminating a thermoplastic resin film and a porous support. After the master is transported by transport means such as a platen roller while being energized in a pulsed manner according to the original image, a perforated image based on the image information is formed on the thermoplastic resin film of the master by hot melt perforation, and this perforation is performed. The master made from the plate is wound around a porous cylindrical plate cylinder, and the printing paper is pressed against the outer peripheral surface of the plate cylinder by a pressing member such as a press roller, so that the opening portion of the plate cylinder and the punched portion of the master The exuded ink is transferred to the printing paper to obtain a printed image. In this stencil printing apparatus, as shown in FIGS. 4 and 5, a main motor 2 for rotating and driving a plate cylinder (not shown) is attached to a rear side plate of the housing 1 via a bracket 3. As the main motor 2, a motor with a speed reducer having a motor part 2 a and a speed reducer part 2 b is used for the purpose of increasing the output torque in order to rotate the plate cylinder.
[0003]
Here, the structure of the main motor 2 will be briefly described.
As shown in FIG. 6, the motor part 2a and the reduction gear part 2b which comprise the main motor 2 are integrated by the some screw 2i. A rotatable motor shaft 2c is disposed inside the motor portion 2a, and a gear portion 2d is formed at the tip thereof. An output shaft 2e is rotatably supported by a plurality of bearings 2f and 2g inside the speed reducer portion 2b, and a plastic gear 2h that meshes with the gear portion 2d is integrally attached to the output shaft 2e.
With the above-described configuration, when a current flows in the motor portion 2a, the motor shaft 2c rotates, and this rotational force is transmitted to the output shaft 2e via the gear portion 2d and the plastic gear 2h. The reason why the plastic gear 2h is used is that when a metal gear is used, various problems such as deterioration in durability due to insufficient surface pressure, high processing cost, and increase in noise occur.
[0004]
A small-diameter timing pulley 4 is attached to the middle of the output shaft 2 e of the main motor 2 as shown in FIGS. 4, 5, and 7. Is rotatably supported by a bracket 6 attached to the bracket. A gear 7 is attached to the end of the output shaft 2e protruding from the bracket 6, and the gear 7 meshes with a gear 8 supported by the bracket 6 to transmit driving force to other parts. Two tension pulleys 9 and 10 and a paper discharge timing pulley 11 (see FIG. 7) are rotatably supported on the bracket 6, and the tension pulley 9 can swing on the bracket 6 via a mounting plate 12. Is attached.
A timing belt 13 is stretched over the timing pulley 4 and the paper discharge timing pulley 11, and the timing belt 13 is stretched over a large-diameter timing pulley 15 fixed to the drive shaft 14. The driving force is transmitted to the plate cylinder via the drive shaft 14, and the plate cylinder rotates. A driving force is also transmitted via a timing pulley 15 to a not-shown impression cylinder provided so as to be able to contact with and separate from the plate cylinder.
[0005]
In the stencil printing apparatus having such a configuration, printing is performed using various types of paper. During this printing, if a paper transport jam occurs when printing using thick paper or double feeding, the thick paper or the double fed paper is not easily deformed, which hinders the rotational movement of the plate cylinder or impression cylinder. Will be. At this time, since the plate cylinder or the impression cylinder tries to rotate these papers by forcibly pushing them out, the main motor 2 instantaneously outputs a maximum torque, and this torque acts on the plate cylinder or the impression cylinder, and then the timing pulley 15 and the timing It acts on the speed reducer 2b of the main motor 2 via the pulley 4.
However, since this drive mechanism does not have a mechanism for releasing such a sudden torque, when the sudden torque is applied, the plastic gear 2h of the speed reducer portion 2b, which is the weakest in strength, is damaged, and the main There was a problem that the motor 2 had to be replaced. Although not shown in the figure, a plastic gear is often used in the portion that transmits the driving force from the timing pulley 15 to the impression cylinder. Depending on the timing, the plastic gear may be damaged before the plastic gear 2h is damaged. There is also. Even in this case, there is a problem that the repair on the user side is impossible and the printing operation is interrupted for a long time. When the thin paper is jammed alone, the paper is easily deformed, so that the locked state of the plate cylinder and the impression cylinder hardly occurs, and the gear is hardly damaged.
[0006]
In addition, there are those that have a function to stop the operation of the motor by detecting this when the plate cylinder or impression cylinder locks and an abnormal current flows through the motor due to a sudden torque acting on the motor, Since the relationship between the generated current value and the torque is not accurate, the plastic gear 2h is damaged before detection, and it has not been possible to cope with the momentary generation of high torque in terms of time.
Therefore, a technique has been proposed in which a driving force transmission means is provided with a torque limiter that releases the main motor when it becomes overloaded. According to this technology, when a sudden torque is generated, the torque limiter slides to protect the plate cylinder drive mechanism and to perform inexpensive and quick recovery without requiring expensive parts replacement or long-term repair work. Therefore, it is possible to achieve cost reduction and work efficiency improvement at the same time.
[0007]
[Problems to be solved by the invention]
An example of the driving force transmission means using the above torque limiter is shown in FIG. Note that the torque limiter used here is used in place of the timing pulley 4 described above, and other main configurations are based on the above-described configuration.
A torque limiter 16 is attached to the middle of the output shaft 2e of the main motor 2 as shown in FIGS. 8 and 9, and a gear 19 is connected to the end of the output shaft 2e via a bearing 17 and a shield sleeve 18. Is attached. As shown in FIGS. 8 and 10, the shield sleeve 18 is rotatably supported by a bearing holder 20 attached to the bracket 6 via a bearing 21, and includes one side surface attached to the bracket 6 of the bearing holder 20. A belt adjusting plate 24 that rotatably supports the gear 22 and the timing pulley 23 provided integrally therewith is attached to the other side surface facing the belt. The belt adjustment plate 24 is swingably attached to the bearing holder 20, and a tension spring 25 is attached between the bearing holder 20 and the belt adjustment plate 24. The gear 22 meshes with the gear 19, and a timing belt 27 is stretched between the timing pulley 23 and the timing pulley 26 that is rotatably supported by the housing 1, and the rotational force is transferred to other parts. Communicating. Of the above-described configuration, the driving force transmitting means 28 is configured by the timing belt 13, the timing pulley 15, the torque limiter 16, and the like.
[0008]
As shown in FIG. 11, the torque limiter 16 is mainly composed of an inner ring 29, an outer ring 30, two springs 31 and the like.
The inner ring 29 has a boss part 29a, a body part 29b, a sliding part 29c, and a groove part 29d. A hole 29e into which the output shaft 2e can be fitted is formed at the center of the inner ring 29, and a set screw tap 29f for fixing the inner ring 29 to the output shaft 2e is provided at the boss 29a. Two locations are formed at relative angles. Each spring 31 is mounted on the outer peripheral surface of the body portion 29b, the outer ring 30 is mounted on the sliding portion 29c, and a C retaining ring 32 is mounted on the groove portion 29d.
[0009]
Each spring 31 is wound so that the inner diameter thereof is slightly smaller than the outer diameter of the body portion 29b, and is pressed against the outer peripheral surface of the body portion 29b with a predetermined spring force. Each spring 31 is bent at one end at a right angle to form a standing bent portion 31a. Each spring 31 is attached in such a direction that the contact force with respect to the outer peripheral surface of the body portion 29b is loosened when each of the standing bent portions 31a is fixed and the output shaft 2e is rotated.
[0010]
The outer ring 30 has flange portions 30a and 30b, a sliding portion 30c, a concave portion 30d, and an index 30e. Each flange part 30a, 30b is formed in the both end surface part of the outer ring | wheel 30, the flange part 30a is formed in a larger diameter than the flange part 30b, and it is plural between each flange part 30a, 30b to mesh with a timing belt. The tooth part 30g is formed. A concave portion 30d into which each spring 31 can be fitted is formed at the center of the outer ring 30, and a standing bent portion 31a of each spring 31 is fitted into the concave portion 30d so that the outer ring 30 and each spring 31 are relatively positioned. It is configured not to rotate. A sliding portion 30c is formed on the inner diameter of the flange 30b. The sliding portion 30c is formed in a size that provides a clearance fit with respect to the sliding portion 29c, and the sliding portions 29c and 30c are in sliding contact with each other. Four taps 30f for attaching the shield sleeve 18 are formed on the end surface of the flange portion 30a, and an index 30e is formed on a part of the outer peripheral surface of the flange portion 30b. As shown in FIG. 12, in this example, the index 30e is set at a position tilted 18 degrees from the vertical line when the plate cylinder (not shown) is stopped at the home position. A notch 3a for adjusting 30e to the home position is formed. As shown in FIG. 10, the timing belt 13 is wound around the tooth portion 30 g, and the torque limiter 16 is drivingly connected to the timing pulley 15.
[0011]
Here, the function of the indicator 30e provided on the outer ring 30 will be described.
The number of teeth 30g of the torque limiter 16 used in this example is set to 20 and the number of teeth of the timing pulley 15 is set to 50, and the reduction ratio between the torque limiter 16 and the timing pulley 15 is 2. .5 is set. The number of teeth and the reduction ratio are determined based on tooth strength, total load, motor size, motor output torque, and the like, and cannot be easily changed. Also, the reduction ratio is not usually an integer ratio to avoid hitting the same teeth.
[0012]
Since the reduction ratio is 2.5 as described above, the position of the bending portion 31a of each spring 31 provided in the torque limiter 16 is divided into a partial diagram (a) and a partial diagram (b) in FIG. Alternatively, as shown in the partial diagrams (c) and (d), the position is shifted by 180 degrees for each rotation. In the figure, symbol F indicates the direction of the force generated by the tension of the timing belt 13, and symbol T indicates the direction of torque at the start of printing load. At the start of printing load, the impression cylinder suddenly presses against the plate cylinder and the printing pressure is applied, and the torque fluctuation of the main motor 2 is the largest so that the maximum torque acts on the torque limiter 16. . Further, it is considered that the sliding portion 30c of the outer ring 30 indicated by a broken line in the drawing is deformed as illustrated by being pushed upward by the tension F of the timing belt 13 in the drawing.
[0013]
In the configuration shown in the partial diagrams (a) and (b), the tension F and the torque T both act in the vertical direction, and the force in the horizontal direction does not act. There is not much difference from the state shown in (b). However, in the configuration shown in the partial diagrams (c) and (d), the torque T acts in the left-right direction, and the direction of action differs from the tension F. For this reason, in the state shown in the partial diagram (c), since the acting positions of the tension F and the torque T are separated, the outer ring 30 easily rotates in the same direction as the acting direction of the torque T, and the position is unstable. On the other hand, in the state shown in the partial diagram (d), the operating positions of the tension F and the torque T are substantially the same, and the outer ring 30 is pressed by the tension F, so that it is difficult to rotate. Due to this difference, there has been a problem that the supply position of the sheet to the impression cylinder varies with each rotation of the plate cylinder.
[0014]
In order to investigate the variation in the paper supply position, as shown in FIG. 14, an angle from a point P1 near the paper feeding start position from the registration roller pair to a point P2 near the closing start position of the paper clamper of the impression cylinder The time when the impression cylinder was rotated was measured several times with a time interval analyzer. When the position of the standing bent portion 31a of the spring 31 is the partial drawing (c) and partial drawing (d) of FIG. 13, the variation in the impression cylinder rotation time is as shown in FIG. The variation of the impression cylinder rotation time in the case of the partial diagram (a) and the partial diagram (b) in FIG. 13 is the result shown in FIG. As apparent from the figure, in FIG. 15, two peaks of time variation appear and the width of the variation is large, whereas in FIG. 16, there is only one peak of time variation and the width is small. It has been found that the variation in the paper supply position relative to the impression cylinder can be suppressed by specifying the position of the bent portion 31a. Therefore, the index 30e is used to determine the position of the standing and bending portion 31a so as to be the position shown in FIGS. 13A and 13B where the variation in the paper supply position is the smallest.
[0015]
However, even if the standing and bending portion 31a is positioned using the index 30e, the position of the standing and bending portion 31a is shifted by 180 degrees for each rotation, so that the variation in the paper supply position is converged within a certain range. When accurate printing is performed, the allowable value may be exceeded. It is also clear from FIG. 13C that the sliding portion 30c, which is a hole portion into which the inner ring 29 and the outer ring 30 are fitted, is easily deformed, and that the variation in the paper supply position increases as the gap increases. It is.
The object of the present invention is to solve the above-mentioned problems and to provide a driving force that has a torque limiter and can release the main motor when it is overloaded and can keep the paper supply position constant. An object of the present invention is to provide a stencil printing apparatus provided with a transmission means.
[0016]
[Means for Solving the Problems]
According to the first aspect of the present invention, the plate cylinder, the plate cylinder driving means for rotationally driving the plate cylinder, and the plate cylinder driving means for transmitting the driving force from the plate cylinder driving means to the plate cylinder are overloaded. A torque limiter that releases the state when it is in a state, a timing pulley provided on the drive shaft of the plate cylinder, and a drive having a timing belt that is spanned between the tooth portion provided on the torque limiter and the timing pulley In the stencil printing machine comprising force transmission means, a reduction ratio of the rotational speed of the plate cylinder to the rotational speed of the plate cylinder driving means is an integral multiple, and the number of teeth of the timing pulley is the number of teeth of the tooth portion. It is an integral multiple of .
[0017]
According to a second aspect of the present invention, in the stencil printing apparatus according to the first aspect, the torque limiter is further provided with an inner ring and an outer ring having the teeth provided around the inner ring, and between the inner ring and the outer ring. And a part of the outer ring is press-fitted into a part of the inner ring.
[0018]
According to a third aspect of the present invention, in the stencil printing apparatus according to the second aspect, at least one of the inner ring and the outer ring is made of a resin.
[0019]
According to a fourth aspect of the present invention, in the stencil printing apparatus according to any one of the first to third aspects of the present invention, the stencil printing machine further includes an impression cylinder that is detachably attached to the plate cylinder, the impression cylinder being the drive It is rotationally driven by the driving force from a force transmission means.
[0020]
【Example】
FIG. 1 is a schematic view of a main part of a stencil printing apparatus adopting an embodiment of the present invention. In this embodiment, the same components as those shown in the prior art are given the same components, and detailed descriptions thereof are omitted. In the figure, reference numeral 33 denotes a plate cylinder, and reference numeral 34 denotes an impression cylinder.
A main motor 35 as plate cylinder driving means is configured in the same manner as the main motor 2, and a torque limiter 36 is attached to the middle of the output shaft 35e as shown in FIGS. A gear 19 is attached to the end via a bearing 17 and a shield sleeve 18. A timing belt 13 is wound around the torque limiter 36, and the timing belt 13 is wound around a timing pulley 37 that functions in the same manner as the paper discharge timing pulley 11 and the timing pulley 15. A predetermined tension is applied.
[0021]
A small-diameter gear 38 is integrally provided on the same axis of the timing pulley 37, and this gear 38 is mounted on a shaft 39a (see FIG. 4) of a bracket 39 supported so as to be swingable on the same axis of the drive shaft 14. It meshes with a gear 40 that is rotatably supported. A gear 41 having a smaller diameter than the gear 40 is integrally provided on the same axis as the gear 40, and the gear 41 meshes with a gear 42 that is rotatably supported by the drive shaft 14 (see FIG. 4). A timing pulley 43 having a diameter larger than that of the gear 42 is integrally attached on the same axis as the gear 42, and a timing belt 44 is wound around the timing pulley 43. The timing belt 44 is also wound around a timing pulley 46 attached to a support shaft 45 (see also FIG. 4) supported by a side plate 57 (see FIG. 4), and the rotational driving force of the main motor 35 is the support shaft 45. Is transmitted to a gear 47 provided integrally with the timing pulley 46.
[0022]
In the vicinity of the gear 47, a pressure drum drive shaft 48 that is rotatably supported by the side plate 57 and supports the pressure drum 34 is disposed, and a gear 49 that meshes with the gear 47 is attached to an end portion thereof. Yes. A gear 50 that meshes with the gear 47 is disposed at a position facing the position where the gear 49 is disposed via the gear 47. The gear 50 is attached to an end portion of a support shaft 51 that is rotatably supported by a side plate (not shown) of the housing 1, and the support shaft 51 is used to apply a predetermined printing pressure to the impression cylinder 34. Two printing pressure cams 52 are attached.
[0023]
With the above-described configuration, when the main motor 35 is driven to rotate and the torque limiter 36 is rotated in the counterclockwise direction in FIG. 1, the timing pulley 37 that is drivingly connected to the torque limiter 36 by the timing belt 13 rotates. The barrel 33 is driven to rotate counterclockwise. Further, a gear 40 meshed with a gear 38 that rotates integrally with the timing pulley 37, a gear 42 meshed with a gear 41 that rotates integrally with the gear 40, a timing pulley 43 that rotates integrally with the gear 42, and a timing belt 44 The impression cylinder 34 is rotationally driven in the clockwise direction of FIG. 1 via the timing pulley 46 that is driven and connected by the gear 49 and the gear 49 that meshes with the gear 47 that rotates integrally with the timing pulley 46. Among these components, the timing belt 13, the torque limiter 36, the timing pulley 37, the gears 38, 40, 41, 42, the timing pulleys 43, 46, the gears 47, 49, and the like constitute the driving force transmission means 53. ing.
[0024]
As shown in FIG. 3, the torque limiter 36 is mainly composed of an inner ring 54, an outer ring 55, two springs 56, and the like.
Similar to the inner ring 29 described above, the metal inner ring 54 has a boss portion 54a, a trunk portion 54b, a sliding portion 54c, a groove portion 54d, a hole 54e, and two taps 54f. Each spring 56 is mounted on the outer peripheral surface of the body portion 54b, the outer ring 55 is mounted on the sliding portion 54c, and the C retaining ring 32 is mounted on the groove portion 54d. The spring 56 having the standing bent portion 56 a is formed in the same manner as the spring 31, and is attached on the outer peripheral surface of the trunk portion 54 b like the spring 31.
[0025]
The outer ring 55 has flange portions 55a and 55b, a sliding portion 55c, a concave portion 55d, and an index 55e. The flange portions 55a and 55b are configured in the same manner as the flange portions 30a and 30b of the outer ring 30 described above, and a plurality of tooth portions 55g are formed between the flange portions 55a and 55b. A concave portion 55d similar to the concave portion 30d is formed in the central portion of the outer ring 55, and a sliding portion 55c is formed on the inner diameter of the flange portion 55b. The sliding portion 55c is formed in a size that provides an interference fit with the sliding portion 54c, and the sliding portions 54c and 55c are in pressure contact with each other. The pressure contact force of each sliding portion 54c, 55c is set to be sufficiently smaller than the spring force of each spring 56. On the end surface of the flange portion 55a, there are formed four taps 55f for attaching the shield sleeve 18 and three inlay portions 55h that fit into notches 18a (see FIG. 2) formed in the shield sleeve 18. An index 55e similar to the index 30e is formed on a part of the outer peripheral surface of the flange portion 55b. By forming the inlay portion 55h, the shield sleeve 18 can be reliably positioned and the strength of the resin outer ring 55 can be increased.
[0026]
The number of teeth 55g of the torque limiter 36 used in this embodiment is set to 22 and the number of teeth of the timing pulley 37 is set to 44, and the reduction ratio between the torque limiter 36 and the timing pulley 37 is 2. .0 is set. The main motor 35 is selected as a motor that generates an output torque and a linear velocity that match the number of teeth and the reduction ratio.
Since the reduction ratio is 2.0 as described above, the position of the standing bent portion 56a of each spring 56 provided in the torque limiter 36 is always the same for each rotation. As a result, the working position relationship between the tension F and the torque T is always in the same state, and it is possible to prevent the occurrence of a problem that the paper supply position to the impression cylinder varies every rotation. At this time, as the initial position of the index 55e, the position of the partial diagram (a) or the partial diagram (b) in FIG. 13 is desirable. Further, since the sliding portions 54c and 55c are fitted so as to have an interference fit, the amount of deformation of the sliding portion 30c (sliding portion 55c in this embodiment) in FIG. 13 can be reduced. Therefore, more stable paper supply can be performed. With the configuration of this example, the state shown in FIG. 16 could be maintained as the paper supply position to the impression cylinder.
[0027]
In the above embodiment, the torque limiter 36 is attached to the output shaft 35e of the main motor 35. However, the torque limiter 36 is located at other positions such as the timing pulley 37 and the gears 38, 40, 41, 42. The timing pulleys 43 and 46 and the gears 47 and 49 may be attached. In the above-described embodiment, the torque limiter 36 having the metal inner ring 54 and the resin outer ring 55 is used. However, as the torque limiter, at least one of the inner ring and the outer ring may be made of resin, and both strengths are strong. When both are made of metal, it is desirable to embed a member (for example, graphite or the like) that reduces the coefficient of friction in each sliding portion so that each member does not wear abnormally during the press-contact rotation.
[0028]
【The invention's effect】
According to the present invention, the driving force transmitting means has a torque limiter and the reduction ratio of the rotational speed of the plate cylinder to the rotational speed of the plate cylinder driving means is an integral multiple. When the drive means outputs a high torque, the torque limiter releases the load associated with the high torque output and prevents damage to the drive force transmission means or the plate cylinder drive means, thus simultaneously reducing cost and improving printing efficiency. This can be achieved, and a good printed matter can be obtained by keeping the paper supply position at a fixed position.
[Brief description of the drawings]
FIG. 1 is a schematic perspective view of a main part of a stencil printing apparatus employing an embodiment of the present invention.
FIG. 2 is a sectional view around a main motor showing an embodiment of the present invention.
3A is a left side view of the torque limiter used in one embodiment of the present invention, FIG. 3B is a front sectional view, and FIG.
FIG. 4 is an exploded perspective view showing a plate cylinder driving mechanism of a conventional stencil printing apparatus.
FIG. 5 is a cross-sectional view around a main motor of a conventional stencil printing apparatus.
FIG. 6 is a partial cross-sectional view of a main motor of a conventional stencil printing apparatus.
FIG. 7 is a schematic diagram illustrating driving force transmission means of a conventional stencil printing apparatus.
FIG. 8 is a sectional view of the periphery of the main motor of the stencil printing machine provided with driving force transmission means having a torque limiter.
FIG. 9 is a schematic view showing an assembled state of the torque limiter to the main motor in the stencil printing apparatus shown in FIG.
10 is a schematic perspective view showing driving force transmission means of the stencil printing apparatus shown in FIG. 8. FIG.
11A is a left side view of the torque limiter used in the stencil printing apparatus shown in FIG. 8; FIG. 11B is a front sectional view;
FIG. 12 is a schematic diagram for explaining an index provided in the torque limiter.
FIG. 13 is a schematic diagram for explaining an external force acting on a torque limiter.
14 is a schematic view for explaining measurement of a paper supply position to the impression cylinder in the stencil printing apparatus shown in FIG.
FIG. 15 is a chart showing variations in the sheet supply position with respect to the impression cylinder in the states of FIGS. 13 (c) and (d).
FIG. 16 is a chart showing variations in the sheet supply position with respect to the impression cylinder in the states of FIGS.
[Explanation of symbols]
33 Plate cylinder 34 Impression cylinder 35 Plate cylinder drive means (main motor)
36 Torque limiter 53 Driving force transmission means 54 Inner ring 55 Outer ring 56 Spring

Claims (4)

A plate cylinder, a plate cylinder driving means for rotating the plate cylinder, and a driving force transmitted from the plate cylinder driving means to the plate cylinder when the plate cylinder driving means is overloaded. A stencil provided with a torque limiter for escaping, a timing pulley provided on the drive shaft of the plate cylinder, a driving force transmitting means having a tooth belt provided on the torque limiter and a timing belt stretched over the timing pulley. In the printing device,
Stencil printing characterized in that a reduction ratio of the rotational speed of the plate cylinder to the rotational speed of the plate cylinder driving means is an integral multiple, and the number of teeth of the timing pulley is an integral multiple of the number of teeth of the tooth portion. apparatus. In the stencil printing apparatus according to claim 1,
The torque limiter includes an inner ring , an outer ring having the tooth portion provided around the inner ring, and a spring interposed between the inner ring and the outer ring, and a part of the outer ring is a part of the inner ring. hole plate printing device you characterized in that it is pressed against. In the stencil printing apparatus according to claim 2,
Hole plate printing apparatus at least one of said inner ring and said outer ring you characterized by being composed of a resin. In the stencil printing apparatus according to any one of claims 1 to 3,
The plate cylinder has a separable freely provided the impression cylinder, the impression cylinder is hole plate printing apparatus you, characterized in that it is rotated by a driving force from the driving force transmitting means.

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