JP5140265B2 - Device for carrying out an operating process in a rotatable cylinder of a printing press - Google Patents

Description

The present invention is an apparatus for performing an actuation process in a rotatably supported cylinder of a printing press , which operates in the cylinder, extends from inside the cylinder to the outside of the cylinder and is operated by at least a working fluid. One actuating element is provided, and the actuating element slides the slider in the cylinder parallel to the axis of rotation of the cylinder or unlocks the slider, and includes a clutch operated by the working fluid. , a pressure generator of stationary provided for the working fluid, clutch comprises a first clutch portion and a second clutch part, the first and second clutch portions, mutual respectively have a sealing surface on the side facing the, is capable crimped to each other with a sealing surface, the first clutch part is rotatable together with the cylinder, the second clutch portion sliding in the direction of the body axis of rotation Are possible, and of what the format that is arranged non-rotatably relative to the frame of the printing press.

  In a sheet printing machine capable of changing the mode of operation from single-sided printing to double-sided printing, numerous adjustments must be made at the reversal cylinder during conversion. For example, the fastening between the gears of the double gear must be released. Further, the slider supporting the cam roller for releasing the gripper provided in the gripper bridge must be unlocked. Finally, the slider must be shifted when converting to another driving format. The amount of force that must be applied during adjustment depends on the size of the component that must be adjusted each time and the amount of force required during operation. Hydraulic pressure can be used when large forces have to be applied. The hydraulic system provides a high energy density and can generate a large force in a relatively small construction space compared to a purely mechanical or electromechanical system. In order to carry out the conversion process in the cylinder, a large number of actuators are required. The actuator is loaded with hydraulic pressure through a rotary penetration or other clutch. Many actuators result in high material and cost consumption. Moreover, the reliability of the adjustment system is reduced. Such consumption is particularly high when the switching order of the actuators must be observed.

In the compressed air supply device provided in the cylinder of the printing press described in German Patent No. 4,209,341, pneumatic means are provided for the conversion process. The compressed air guide is formed by a unit detachable from the barrel journal. The connecting piston with the compressed air passage and the sealing element is moved pneumatically towards the barrel journal against the force of the return spring so that the compressed air passage is connected to the journal passage. A separate passage is required for each actuator provided in the cylinder.
German Patent No. 4209341

  The object of the present invention is to improve the device for carrying out the actuation process in a rotary-supported cylinder of the printing press so that as many actuation processes as possible can be carried out in the cylinder with a small number of actuators. Is to do so.

  According to the configuration of the present invention that solves the above problems, the second clutch portion is structurally formed in the working cylinder, and the piston that can slide in the direction of the rotation axis of the cylinder is at least in the working cylinder. It is arranged with one working chamber sealed so that working fluid can be supplied to the working chamber with variable pressure and the piston is mechanically connected to at least one actuating element. did. Advantageous configurations can be found in the dependent claims.

According to the invention, one working fluid clutch is arranged between the barrel journal and the pressure generator. A part of the clutch is formed as a working cylinder, and a piston is arranged inside the working cylinder. The working fluid is supplied to the cylinder by the sliding of the working cylinder. The piston is mechanically connected to an actuating element provided on the barrel. Thereby, the stroke of the working cylinder or piston is used for the operation of the switching elements or regulatory element provided on formation and torso of the working fluid connection to actuating element operated by the working fluid.

  The present invention makes it possible to realize a plurality of functions with one element. In particular, in a reversing cylinder of a printing press, the connection of a hydraulic connection to the reversing cylinder, the release of fastening between the double gears, the release of fastening of the slider and the sliding of the slider can be realized. During the printing operation, the stationary hydraulic connecting element is disconnected from the cylinder. As a result, no wear occurs. The present invention further provides the possibility of advancing individual operations in a pressure-controlled manner in a time-determined order. Thereby, malfunctions are avoided. The number of possible leak locations in the hydraulic clutch location is limited. The device according to the invention can be realized with an integral structure at a low cost. In that case, the tube line in the inaccessible location is unnecessary.

  The present invention will be described below with reference to examples.

  FIG. 1 shows a reversing cylinder 1 having shaft journals 2 and 3. The shaft journals 2 and 3 are held so as to be rotatable around the axis 8 in bearings 4 and 5 provided in the side walls 6 and 7 of the sheet printer. A gripper bridge 9 is provided in parallel to the axis 8. The gripper bridge 9 has a gripper 10 for conveying a sheet, and is fixed to the reversing cylinder 1 in a bearing bracket 11. Further, the reversing cylinder 1 is provided with a slider 12. The slider 12 can slide in the direction of the arrow 13 parallel to the axis 8. To the slider 12, tooth segments 14 and 15 are coupled. The tooth segments 14, 15 are slidable along the cams 21, 22, 23, 24, respectively. The teeth of the tooth segments 14, 15 mesh with the teeth of the tooth segments 16, 17 connected to the gripper bridge 9. For the opening and closing of the gripper 10, the gripper bridge 9 can be pivoted about an axis 18 by means of the tooth segments 16, 17. Cam rollers 19 and 20 are supported on end portions of the tooth segments 14 and 15. Cam rollers 19, 20 cooperate with cams 21, 22 or 23, 24. A hydraulic actuator 25 is provided for sliding the slider 12 in the direction 13. The piston 26 of the hydraulic actuator 25 is connected to the slider 12, and the cylinder 27 is connected to the reversing cylinder 1. Latches 28 and 29 are arranged on the reversing body 1 so as to be pivotable about the bearings 30 and 31 against the force of springs 32 and 33. The bent latches 28 and 29 are connected to the operation rod 34. The operating rod 34 can slide coaxially with respect to the axis 8. At the position of the latches 28, 29, indicated by broken lines, the slider is released for sliding in direction 13.

  Gears 35 and 36 are attached to the shaft journal 2 for rotationally driving the reversing cylinder 1 around the axis 8. The gears 35 and 36 are connected by a lateral press coupling portion 37 that can be dissociated in a hydraulic manner. A clutch plate 38 is attached to the end face of the gear 36 opposite to the shaft journal 2. A surface of the clutch plate 38 opposite to the shaft journal 2 forms a seal surface 39. At the sealing surface 39, the conduit 40 passing through the clutch plate 38 and the gear 36 to the lateral press coupling portion 37 ends. Further, the pipe lines 41 and 42 communicate with the hydraulic actuator 25 from the seal surface 39. The hydraulic pipelines 40 to 42 are positioned opposite to the pipelines 43 to 45 provided in the end wall 46 of the working cylinder 47 at a predetermined rotational position of the reversing cylinder 1. The working cylinder 47 is fixed to the side wall 6 by a torque support 48 so as not to be relatively rotatable. A seal surface 49 is formed on the end wall 46 of the working cylinder 47 so as to face the seal surface 39. The working cylinder 47 is slidable in the direction of the axis 8. As a result, the seal surface 49 can be applied to the seal surface 39. In that case, the pipe lines 43-45 are connected to the pipe lines 40-42. A piston 50 is located in the working cylinder 47. As a result, one working chamber 51 is formed between the piston 50 and the working cylinder 47. The operating rod 34 is guided through the gear 36 and the clutch plate 38 and through the end wall 46 in a sealed state. The operating rod 34 is fixed to the piston 50 by a nut 52. At that time, the operation rod 34 can be rotated with respect to the piston 50 by a bearing. The sliding of the operating rod 34 or the piston 50 in the direction of the axis 8 is limited by a stopper plate 53 fixed to the operating rod 34 inside the gear 36. A surface of the clutch plate 38 opposite to the seal surface 39 forms a stopper surface 54 for the stopper plate 53.

  Pipe lines 55 and 56 communicate with a three-position switching valve 57 from pipe lines 44 and 45 provided in the end wall 46. The switching valve 57 is connected to a pressure generator 59 and a hydraulic oil sump 60 via a pipe line 58. Another pipe 61 passes from the pressure generator 59 through the working cylinder 47 to the working chamber 51.

  The work format of this apparatus will be described in detail with reference to FIGS. In the following description, when a symbol already introduced is used, it should be understood as an element or symbol having an equivalent function or equivalent meaning.

  In the case where the gears 35, 36 should be rotationally adjusted relative to each other in the reversal cylinder 1 and the slider 12 should be slid, so that the cam rollers 19, 20 cooperate with the cams 23, 24. Therefore, the operation of the pressure generator 59 is started at time t1. FIG. 2 shows the device in a no-pressure state. As can be seen from FIGS. 2 to 5, a spring 62 is arranged in the end wall 46. The direction of action of the spring 62 is the direction of the axis 8. The spring 62 is supported by the end wall 46 and the clutch plate 38.

  A curve 63 in FIG. 6.1 shows a pressure course in the working chamber 51. The pressure in the working chamber 51 increases uniformly until the preload of the spring 62 and the friction of the piston 50 are overcome at time t2. From time t2, the working cylinder 47 starts to slide in the direction of the clutch plate 39. The sliding of the working cylinder 47 in the direction of the axis 8 is shown by the curve 64 in FIG. The seal surfaces 39 and 49 come into contact with each other at time t3. In that case, the pipe line 40 and the pipe line 43 are located facing one line. This state is shown in FIG.

  In the end wall 46, a delivery valve 65 that connects the pipe line 43 to the work chamber 51 is disposed. A seal ring 66 is provided coaxially with respect to the conduit 43 in the seal surface 49 for sealing. In the pipe line 40 leading to the lateral press coupling portion 37, the check line 67 and the check valve 68 connected in parallel to the check valve 67 are not connected to each other. Arranged to keep in.

  When the pressure p is further increased by the pressure generator 59, the working chamber 51 expands. At that time, the piston 50 moves away from the end wall 46 between time t4 and time t5 until the stopper plate 53 comes into contact with the stopper surface 54. This is illustrated in FIG. The movement of the piston 50 is shown by the curve 69 in FIG. 6.2. The operating rod 34 slides together with the piston 50. As a result, the latches 28 and 29 are released, and the slider 12 is released. From time t5, the slider 12 can be slid. For this purpose, the valve 57 is operated. As a result, the piston 26 of the actuator 25 is moved in the direction of the shaft journal 2 and entrains the slider 12. As a result, the cam rollers 19 and 20 exist on the cams 23 and 24.

  When the pressure p in the working chamber 51 is further increased toward the value p3, the blocking action of the delivery valve 65 and the check valve 67 is released. This is illustrated in FIG. The pressure in the lateral press coupling part 37 increases rapidly. This is illustrated by curve 70 in FIG. From time t6 to time t7, the pressure in the working chamber 51 is applied to the lateral press coupling portion 37. At the time t7, the lateral press coupling portion 37 between the gears 35 and 36 is released. Gear 35 is rotated as desired relative to gear 36 with respect to phase by an auxiliary drive.

  When all adjustments are performed in the reversing cylinder 1, the pressure p in the working chamber 51 is reduced again from time t8. When the pressure p again falls below the value p3, the gear 35 is again crimped to the gear 36. When the pressure falls below p2, the piston 50 enters the working cylinder 47 within the time t9 to t10. As a result, the latches 28 and 29 reach the corresponding notches provided in the slider 12, and as a result, the slider 12 is locked.

If the pressure still falls below the value p _K, pressure in the working chamber 51 is no longer sufficient to hold the sealing surfaces 39 and 40 to each other. From time t11, the working cylinder 47 moves away from the seal surface 39. Under the pressure p1, the working cylinder 47 is pressed to the starting position by the action of the spring 62. The starting position has been reached at time t12.

  The check valve 67, the delivery valve 68 connected in parallel, and the delivery valve 65 prevent oil from flowing out when the pipe lines 40 and 43 are open.

  7 and 8 show another embodiment of the adjusting device provided in the reversing cylinder 1. The stroke of the piston 50 serves for the sliding of the slider 12 in direction 13. The lock of the slider 47 is released by the sliding of the working cylinder 47.

  Both the piston 50 and the working cylinder 47 can slide in the direction of the axis 8. The working cylinder 47 is fixed to the side wall 6 by a torque support 48 so as not to be relatively rotatable. The piston 50 divides the cylinder inner chamber into two working chambers 71 and 72. The work chambers 71 and 72 are connected to a three-position switching valve 75 via pipe lines 73 and 74. Depending on the position of the switching valve 75, the working chambers 71 and 72 can alternatively be loaded by the pressure of the pressure generator 59. On the end wall 46 of the working cylinder 47, an entrainer 76 for the operation rod 34 is formed. The operation rod 34 is rotatably supported with respect to the piston 50 or the follower 76 by bearings 77 to 79. The bearing 79 is loaded by a spring 80. As a result, the flange 81 of the operating rod 34 is held against the follower 76. Another operating rod 82 is located in the tubular operating rod 34. The operating rod 82 can slide with the piston 50 in the direction of the axis 8. For this purpose, the operating rod 82 is held in the hole of the piston 50 by the nut 52 in the direction of the axis 8. The operation rod 82 is rotatably held with respect to the piston 50 by bearings 83 to 86.

  In the working cylinder 47, the end wall 46 is extended, and a flange 87 having two sealing surfaces 88 and 89 is formed. The seal surface 88 is positioned opposite the seal surface 90 of the clutch plate 38 that can rotate with the gear 36. The second sealing surface 89 cooperates with the sealing surface 91 of the clutch flange 92 that is rigidly coupled to the clutch plate 38. A pipe line 93 leads from the work chamber 71 to a delivery valve 94. The second port of the delivery valve 94 opens at the sealing surface 89. From the work chamber 72, a pipe line 95 leads to a delivery valve 96. The second port of the delivery valve 96 is open at the sealing surface 88. At a predetermined rotational position of the reversing cylinder 1, the pipe lines 97, 98 or 99, 100 are positioned to face each other on the seal surfaces 89, 91, 88, 90. The pipelines 98 and 100 lead to the pipeline 40 that ends at the lateral press coupling portion 37. The clutch plate 38 and the clutch flange 92 can be rotated with respect to the working cylinder 47 or the flange 87 by bearings 101 to 103. The bearings 101, 102 act on the flange 87 via springs 104, 105 in the direction of the axis 8. The clutch plate 38 has a bearing bracket 106 for the swivel bearing 107 of the two-arm lever 108. The pivot axis 107 is perpendicular to the axis 8. One side of the lever 108 is hinged to the operating rod 34. The other side of the lever 108 is hingedly connected to a tappet 109 guided in a sliding bearing 110 of the clutch plate 38. The tappet 109 ends at a distance that can be reached from the sealing surface 88.

  One end of the central operation rod 82 is connected to the follower 111. The entrainer 111 protrudes through the vertical slit 112 of the operation rod 34 and is coupled to the slider 12. The operation rod 82 is guided with respect to the operation rod 34 by a bearing 113.

  Depending on in which direction 13 the slider 12 should travel, after the switching valve 75 is operated, a pressure higher than the first limit value is applied to one of the working chambers 71, 72. In any case, pressure is further applied to the lateral press coupling part 37 after the pipe lines 97 and 98 or the pipe lines 99 and 100 are connected. The movement of the working cylinder 47 in the direction of the axis 8 also releases the fastening of the slider 12 via the follower 76 or the tappet 109 and the lever 108. At that time, the operating rod 34 is always operated in the pulling direction even if the working cylinder 47 moves in the direction of the clutch plate 38 or the shaft journal 2.

  When the pressure in one of the working chambers 71 and 72 rises above the second limit value, the engagement between the gears 35 and 36 is released. Furthermore, the piston 50 is moved in the direction of the axis 8. As a result, the slider 12 is slid as desired by the operating rod 82. Since the fastening of the slider 12 is already released when the pressure is relatively low, there is no danger that the slider 12 is still fastened when the piston 50 moves. In this embodiment, the sequence of releasing the fastening of the slider 12, traveling of the slider 12, and reclosing of the fastening of the slider 12 is uniquely set by the continuous increase in pressure of one of the working chambers 71 and 72. The As already described in the first embodiment, two delivery valves connected in parallel are provided in the pipeline 40 so that the hydraulic oil is not connected to the hydraulic clutch. 40 can be provided to maintain within. The order in which the slider 12 slides and the lateral press coupling portion 37 is released is not important. This is because this is not related to action.

1 is a schematic view of an apparatus for carrying out an actuation process in a reversing cylinder. FIG. 3 is a schematic diagram of a first step of the actuation process. FIG. 3 is a schematic diagram of a second step of the actuation process. FIG. 4 is a schematic diagram of a third step of the actuation process. FIG. 6 is a schematic diagram of a fourth step of the actuation process. It is a graph which shows progress of the pressure (FIG. 6.1) and stroke (FIG. 6.2) of a piston and a working cylinder. FIG. 6 is a schematic view of another apparatus for performing an actuation process in a reversing cylinder. It is an enlarged view of the apparatus shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Reversing body 2, 3 axis journal 4,5 Bearing 6,7 Side wall 8 Axis 9 Gripper bridge 10 Gripper 11 Bearing bracket 12 Slider 13 Arrow 14,15 Tooth segment 16,17 Tooth segment 18 Axis 19,20 Cam roller 21-24 Cam 25 Hydraulic actuator 26 Piston 27 Cylinder 28, 29 Latch 30, 31 Bearing 32, 33 Spring 34 Operation rod 35, 36 Gear 37 Lateral press coupling part 38 Clutch plate 39 Seal surface 40-45 Pipe line 46 End wall 47 Work cylinder 48 Torque support 49 Sealing surface 50 Piston 51 Working chamber 52 Nut 53 Stopper plate 54 Stopper surface 55, 56 Pipe line 57 Switching valve 58 Pipe line 59 Pressure generator 60 Hydraulic oil reservoir 61 Pipe line 62 Spring 3,64 Curve 65 Delivery valve 66 Seal ring 67 Check valve 68 Delivery valve 69, 70 Curve 71, 72 Work chamber 73, 74 Pipe line 75 Switching valve 76 Entrainer 77-79 Bearing 80 Spring 81 Flange 82 Operation rod 83-86 Bearing 87 Flange 88-91 Sealing surface 92 Clutch flange 93 Pipe 94 Delivery valve 95 Pipe 96 Delivery valve 97-100 Pipe 101-103 Bearing 104, 105 Spring 106 Bearing bracket 107 Turning axis 108 Lever 109 Tappet 110 Sliding bearing 111 Entrainer 112 Vertical slit 113 Bearing

Claims (9)

An apparatus for carrying out an operating process in a rotatable cylinder of a printing press,
The actuating element (25) comprises at least one actuating element (25, 34, 82) operating in the torso (1), extending from within the torso (1) to the outside of the torso (1) and operated by working fluid. , 34, 82) slides the slider (12) in the cylinder (1) in parallel with the axis of rotation (8) of the cylinder (1) or unlocks the slider (12). Is what
A clutch (38, 46, 87, 92) operated by a working fluid;
A stationary pressure generator (59) provided for the working fluid;
The clutch (38, 46, 87, 92) includes a first clutch portion (38, 92) and a second clutch portion (46, 87), and the first and second clutch portions ( 38, 46, 87, 92) are provided with sealing surfaces (39, 49; 89, 91; 88, 90) on the mutually facing sides, said sealing surfaces (39, 49; 89, 91; 88, 90) can be crimped together , the first clutch part (38, 92) can rotate with the barrel (1) , and the second clutch part (46, 87) can rotate with the axis of rotation of the barrel (1). It is slidable in the direction of (8) and is disposed so as not to be rotatable relative to the frame of the printing press.
In the form of
The second clutch part (46,87) is formed in the working cylinder (47), said working cylinder (47) is slidable in the direction of the axis of rotation (8) of itself cylinder (1) , and the and into the working cylinder (47), cylinder piston slidable (50) in the direction of (1) the rotational axis (8), sealing at least one working chamber (51,71,72) Arranged in a state,
Said working fluid conduit (61,73,74) extends between the pressure generator and (59) and said working chamber (51,71,72), the working fluid, with at changeable pressure, the Can be supplied to the work rooms (51, 71, 72),
It said piston (50) is a device for carrying out the operation process by mechanically said characterized in that it is connected to the actuating element (34,82), rotatably mounted cylinder of a printing press. Wherein the pressure generator (59) and the working chamber (7 1,72) working fluid conduit between, it is arranged switching valve (7 5), apparatus according to claim 1. Working fluid lines (40, 43, 96, 97, 98, 99, 100) extending through the first and second clutch portions (38, 46, 87, 92) to the lateral press coupling portion (37). The device according to claim 1, wherein a check valve (65, 94, 96) is provided. The check valve (65, 94, 96) is a pressure-operated valve, the check valve (65, 94, 96) has a predetermined working pressure threshold, and the working pressure threshold is exceeded. Sometimes working fluid lines (43, 40; 97, 98; 99, 100) extending through the first and second clutch portions (38, 46, 87, 92) to the transverse press coupling (37) 4. The device of claim 3, wherein is open. 2. The device according to claim 1, wherein the working stroke of the piston (50) is limited by a stopper (53). The sealing surface (39, 49; 89, 91 ; 88, 90 ) is at least one first with the first and second clutch portions (38, 46, 87, 92) not crimped. the force of the spring (62,80,104,105) is held so as to be separated from each other, device according to any one of claims 1 to 5. The device according to claim 6 , wherein the working cylinder (47) is slidable against the force of the first spring (62, 80, 104, 105). At least one latch (28, 29) for locking the slider (12) by the force of at least one second spring (32, 33) is coupled to the actuating element (34, 82), and the piston ( 50) and is slidable against the force of the second spring (32, 33), have a greater stiffness than the second spring (32, 33) said first spring (62) An apparatus according to claim 6 or 7, wherein: Two working chambers (71, 72) is provided with said piston (50) is isolated the two working chambers (71, 72), the two working chambers (71, 72) is selectively work Can be loaded with fluid,
The working cylinder formed in said (47) a second clutch part (87) is provided with two sealing surfaces (88, 89) located opposite each viewed in the direction of the rotational axis (8) ,
The apparatus of claim 1.

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