JP5659132B2 - Apparatus and method for reshaping a hollow cylinder - Google Patents

Description

  The present invention relates to an apparatus for reshaping a hollow cylinder and a method for reshaping the hollow cylinder. For example, in the manufacture of thin metal sheet containers, aerosol cans, that is, hollow cylinders that are open on one side, are produced as semi-finished products by deep drawing and / or ironing equipment. During another process step, this hollow cylinder must then be reshaped, in particular in the bottom region and / or in the upper peripheral region. This is achieved with the device according to the invention and the method according to the invention, respectively. Such devices are often referred to as swaging machines.

  Currently, upsetting machines for reshaping hollow cylinders are known, which machines serve as a machining station (machining station) or a plurality of stations arranged as measurement and test stations. Prepare. Each machining station comprises a machining tool. The machining tools are arranged along a circular path on the shared tool transporter. At some distance from the tool transporter, a rotating component is installed, the rotating component having a plurality of holding means for the cylinder arranged along a circular path. The holding means is arranged on a circular path corresponding to the radius of the circular path on which the machining tool sits on the tool transporter. The hollow cylinder is transferred from one station to the next by intermittent rotation of the rotating components. This intermittent rotational movement of the rotating component must be made to be synchronized with the reciprocating movement of the tool transporter. For this purpose, there are commercially available machines where the main drive that generates the reciprocating motion of the tool transporter is also designed to cause the rotational motion of the rotating components. To achieve this, for example, it is possible to combine the main drive with an index drive, which rotates by a pre-specified rotation angle during the return stroke of the tool transporter. Move components.

  Such known devices are not flexible. The synchronization of the rotational movement of the rotating components by the main drive is fixed. For example, if a hollow cylinder with a greater axial height is to be machined, this is not always possible. The reason is that part of the tool transporter's return stroke path (so-called excessive movement) must not fall below the minimum limit to check the duration of rotation of the rotating component by means of an indexing drive. is there. However, rotation of the rotating component can only begin when all machining tools are not engaged with the hollow cylinder. As long as the overall reciprocation of the device is limited, this results in the maximum height of the hollow cylinder that can be machined.

  The object of the present invention is to improve the flexibility of this device. In order to achieve this, in particular the maximum effective movement of the tool transporter remains the same while realizing the possibility of increasing the maximum height of the hollow cylinder that can be machined compared to known devices. Don't be.

  This object is achieved by a device having the features of claim 1 and by a method having the features of claim 9.

  The present invention provides that the main drive that generates the reciprocating motion of the tool transporter is disengaged from the rotary drive to generate intermittent motion of the rotating components. A separate rotary drive, in particular an electric motor, is therefore assigned to the rotating component. The time series of the rotational motion of the rotating component can be adjusted or set within a range specified in advance with respect to the time series of reciprocating motion. As a result of this, for example, it is possible to reduce the stroke speed, i.e. the number of strokes per unit time of the tool transporter, while at the same time by means of rotating components in motion between two pre-specified rotational positions. It is possible to adjust the required duration to a smaller time period value that would be necessary for a reduced stroke speed. As a result of the faster partial rotational movement relative to the reciprocating movement of the tool transporter, it is possible to increase the portion of the stroke that is available for reshaping. As a result, it is possible to machine on the same device an object with a higher axial height than previously applied on the same device. This is due to the fact that the portion of the time period for moving the rotating component between two consecutive rotational positions can be reduced on the duration side of the overall reciprocating cycle. As a result, excessive movement of the tool transporter is reduced. The portion of the overall reciprocation that can be used to reshape the object can be increased.

  Advantageously, the main drive is designed as an eccentric drive mechanism. Such an eccentric drive mechanism converts a continuous rotational movement of a motor, for example an electric motor of a main drive, into a swinging movement of the tool transporter. In doing so, it is also possible to adjust the stroke, i.e. the distance between the two reversal points of the reciprocating movement, via adjustment of the eccentric drive mechanism.

  Considering the preferred embodiment, the rotary drive comprises a separate electric motor that is connected to the rotating component, preferably without inserting a gearing that reduces or increases speed. In particular, the electric motor can be configured as a direct drive and can be directly connected to a rotating component. Therefore, the electric motor may be configured as a servo motor or a torque motor. In the case of a direct connection between the rotating component and the electric motor, gear device components that are subject to tolerances and generate wear are omitted. Thus, any positioning of the rotating component can be performed very accurately with respect to the machining tool.

  Considering another advantageous embodiment, the electric motor is implemented as a so-called segment motor. With such a motor, it is possible to stabilize driven components without bearings by means of reluctance forces for some degree of freedom. In this way, wear can be further reduced.

  In order to control the rotational position of the rotating component, the transfer device for the hollow cylinder preferably comprises a position sensor. The sensor signal is output to a control device, which, for example, activates the rotary drive so that the position adjustment can be achieved very accurately. Alternatively or additionally, it is also possible to control or adjust further parameters of the rotational motion of the rotational motion of the rotating component such as, for example, the angular velocity and / or angular acceleration of the rotating component.

  The duration required by the rotary drive that rotates the rotating component between two consecutive pre-specified rotational positions is preferably adjustable by the operator. Within a pre-specified range, this duration can also be changed during operation of the device.

  Furthermore, it is advantageous to be able to adjust the relationship between the stroke speed of the tool transporter and the duration required by the rotary drive that rotates the rotating component between two consecutive pre-specified rotating stands. It is. In this way, it is very easy to change the behavior of the reciprocating motion over time with respect to the rotational motion of the rotating component to suit.

  Advantageous embodiments of the device and method are evident from the dependent patent claims and the description. The description is limited to the essential features of the invention. The drawing should be considered as a supplementary reference.

1 is a schematic side view of a cross-sectional view of a first exemplary embodiment of an apparatus of the present invention. FIG. 2 is a plan view taken along line II-II of the rotating component of FIG. 1. FIG. 6 is a schematic side view of a cross-sectional view of a second exemplary embodiment of a rotary drive for a rotating component. FIG. 6 is a schematic side view of a cross-sectional view of a third exemplary embodiment of a rotary drive for a rotating component. FIG. 3 is an exemplary schematic diagram of a time series of rotational movement of a rotating component and reciprocating movement of a tool transporter.

  FIG. 1 shows an apparatus 10 for reshaping a hollow cylinder 11. The hollow cylinder 11 is made of a thin metal sheet and is deep-drawn and / or ironed and closed over the entire bottom on one axial end. The cylindrical body 11 is made of a single metal material, and is made, for example, without a seam or a joint. The device 10 is further arranged for reshaping these hollow cylinders 11 that are closed on one side. In order to accomplish this, the apparatus 10 comprises several machining stations 12a. In each of these machining stations 12a there is a machining tool 13a that performs an appropriate reshaping step.

  The machining tool 13a is disposed on a shared tool transporter on a circular path centered on the central longitudinal axis L. It is also possible to insert a test or measurement station 12b with a test or measurement tool 13b between successive machining stations 12a on this circular path in order to confirm the reshaping process previously performed on the cylinder 11. Is possible. Measuring station 12b as well as machining station 12a represent stations 12 that are uniformly arranged on a circular path centered on the longitudinal axis L so that a completely closed circle is formed.

  The tool transporter 14 is driven by the main drive device 15 to perform a reciprocating motion H between the two reversing points UA and UB. In doing so, the tool transporter 14 with the tools 13a, 13b moves towards the cylindrical body 11 to be machined until the tool transporter reaches the first reversal point UA. At this first reversal point UA, when the direction of movement is reversed, the tool transporter 14 leaves the cylinder 11 to be machined again up to the second reversal point UB. This reciprocation H is repeated periodically. In order to achieve the rocking reciprocating motion H of the tool transporter 14, the main drive 15 may be designed as an eccentric drive mechanism, for example. At that time, the electric motor of the main drive unit 15 is driven eccentrically, and the eccentric eccentric motion is converted into the reciprocating motion H of the tool transporter 14 by the eccentric rod. Considering the preferred embodiment, it is also possible to adjust or change the stroke of the tool transporter 14 in eccentricity.

  The tool transporter 14 is supported so as to be guided so as to be movable in the direction of the reciprocating motion H. For example, to achieve this, a central guide pylon 16 may be installed, which is enclosed by an annular tool carrier 14 in a direction coaxial with the longitudinal axis L. A first bearing 17, for example a friction bearing or a roller bearing, is installed between the guide pylon 16 and the tool transporter 14.

  The transfer device 20 is arranged to transfer the cylindrical body 11 between the stations 12 and to position the cylindrical body 11 on the opposite side of the tools 13a and 13b. To achieve this, the transfer device 20 comprises a rotationally driven rotating component 21 arranged coaxially with respect to the longitudinal axis L so as to be rotatable about the axis. Considering the first exemplary embodiment of the apparatus 10 shown in FIG. 1, the rotating component 21 is rotatably supported on the central guide pylon 16 via the second bearings 22a and / or 22b. . The second bearing is arranged coaxially with respect to the longitudinal axis L between the rotating component 21 and the guide pylon 16 (bearing 22a in FIG. 1) and / or slightly away from the guide pylon 16. You may support to some extent via a 2nd bearing (bearing 22b in FIG. 1). The rotating component 21 has an annular shape. Therefore, it can also be called a rotating disk or a turntable.

The holding means 23 is installed on the side of the rotating component 21 facing the tool transporter 14, and each of the holding means 23 is arranged to hold one hollow cylindrical body 11. As shown in the schematic view, the holding means 23 includes a receiving cavity 24 that receives a bottom side portion of the cylindrical body 11. In order to fix the cylindrical body 11 to a predetermined position in the receiving cavity 24 at a desired position, a fixing jaw portion not specifically shown may be installed in the region of the receiving cavity 24. The holding means 23 is disposed on a circular path K extending coaxially with the longitudinal axis L. Circular path K has the same radius as the circular path in which station 12 is disposed. In this way, it is possible to position each cylindrical body 11 so as to cover the holding means 23 in alignment with the direction of the reciprocating motion H of the machining tool 13a or the measurement or test tool 13b. Transfer of the cylinder 11 between successive stations 12 is achieved by intermittent or stepwise rotation of the rotating component 21 in the direction of rotation D between two successive rotational positions α _i and α _{i + 1} . The number of these rotational positions α _i (i = 1 to n) corresponds to the number n of stations 12 on the tool transporter. The holding means 23 are arranged at regular intervals along the circular path K. FIG. 2 shows only a few of the existing receiving cavities 24.

A dedicated rotary drive device 27 independent of the main drive device 15 is installed to drive the rotary component 21. The rotary drive device 27 includes an electric motor 28 that is activated by a control device 29. The control device 29 controls the electric motor 28 so that the rotating component 21 continues to rotate in the period T of the reciprocating motion H between the two consecutive rotational positions α _i and α _{i + 1} by the rotational angle Δα. To do. The duration τ is what is required by the rotary drive 27 to achieve this. The rotation angle Δα is 360 ° divided by the number n of holding means 23.

  Preferably, the rotary drive device 27 is configured as a direct drive device, and the electric motor 28 is directly connected to the rotary component 21 without the intervention of a gear device. However, it is also possible to insert the gear device 30 between the electric motor 28 and the rotating component 21 as shown in FIG.

The rotational position α _i of the rotating component 21 is detected by at least one position sensor 31. The position signal is output to the control device 29. In this way, the position control operation of the rotating component 21 is possible.

  The time series of the rotational motion α (t) can be adjusted or changed with respect to the time series of the reciprocating motion H (t). This is because there is no mechanical fixed connection between the main drive 15, i.e. the drive for moving the tool carrier 14, and the rotary component 21, which is a separate rotary drive. 27. The method and function of the apparatus 10 will be described with reference to FIG.

The first reciprocating motion H ₀ (t) corresponds to the maximum possible number of strokes of the device. The tool transporter 14 requires a period T _min for one complete reciprocating movement from the first reverse point UA to the second reverse point UB and back to the first reverse point UA. During a first duration τ _min centered on a first time point t _B0 when the second reversal point UB is reached, the rotating component 21 moves between two consecutive rotational positions α _i , α _{i + 1} (first Is moved by the rotation angle Δα with the rotational motion α ₀ (t)). During this duration τ _min , the machining tool 13 a and the test and measurement tool 13 b must be in a state of not engaging the hollow cylinder 11. This means that during this duration, the distance of the tool transporter 14 must exceed a minimum value, which may be referred to as an effective travel line. While the turntable 21 rotates, the stage of the reciprocating motion H ₀ (t) represents a so-called excessive movement that cannot be used to machine the cylinder 11. This results in a first available effective stroke N ₀ of the first reciprocating motion H ₀ (t) when the tool transporter is moved at the maximum stroke speed. Therefore, this first useful stroke N ₀ also indicates the maximum height of the cylinder 11 that can be machined at the maximum stroke speed.

The second reciprocating motion H ₁ (t) in FIG. 5 represents a reciprocating motion having a period T ₁ that exceeds the minimum period T _min . As a result, the tool transporter 14 moves more slowly during the reciprocating motion H ₁ (t). In this connection, it is assumed that the rotating component 21 is rotated by the rotary drive device 27 at the maximum angular velocity ω or at the maximum angular acceleration dω about the longitudinal axis L. Therefore, the duration required to move the rotation angle Δα between two consecutive rotational positions is minimal and corresponds to a minimum duration τ _min . The second rotational movement α ₁ (t) of the rotating component 21 can be performed time-symmetrically with respect to the second time point t _B1 when the second reversal point UB is reached. Due to the increase of the period T ₁ of the second reciprocation H ₁ (t), the second effective stroke N ₁ available for machining the cylinder 11 increases to a value N ₁ > N ₀ . . Therefore, by increasing the period T of the reciprocating motion H (t), the effective stroke N of the apparatus 10 can be increased, and any cylindrical body 11 that is faster in the axial direction than the maximum stroke speed of the apparatus can be machined. It is. As a result, the device 10 exhibits greater flexibility to allow machining of various sizes and shapes of the cylinder 11.

In FIG. 5, the two rotational movements α ₀ (t) and α ₁ (t) are only shown very schematically as rectangular signals and are actually different in time series.

  Using the control device 21, the rotary drive 2 can optimize the rotational motion α (t) not only for the required duration τ. It is also possible to predesignate or adjust further motion parameters of the rotational motion α (t). For example, it is possible to adjust the rotational motion α (t) without jerk to achieve a stable acceleration change, which is particularly thin in order to prevent accidental damage to the cylinder 11. This is advantageous in the case of the cylindrical body 11 that is susceptible to being subjected to damage. It is also possible to designate in advance at least one of the minimum or maximum angular velocity value ω or the angular acceleration value dω. It is also possible to specify and adjust in advance, via the control device 29, a desired time-dependent course of at least one of the rotational motion α (t) and the angular acceleration dω (t). As a result of the position signal output by the position sensor 31 over time, it is possible to determine the actual values of angular velocity and angular acceleration. As a result, any motion law can be specified or applied in advance for the rotational motion of the rotating component 21.

  FIG. 3 shows a second exemplary embodiment of the device 10. Considering the mechanical design, the second exemplary embodiment is different from the first exemplary embodiment of the apparatus 10 of FIG. Considering the control or adjustment of the rotary drive 27, the operation corresponds to the first exemplary embodiment, so reference is made to the earlier description herein.

  Referring to the second exemplary embodiment as in FIG. 3, the electric motor 28 of the rotary drive 27 is coupled directly at the rotary component 21, i.e. without the insertion of a gear unit. In order to achieve this, the rotor 35 of each electric motor 28 is connected to the rotating component 21 via a connecting member 36 without twisting. As in the case of FIG. 3, in the exemplary embodiment, the connecting member 36 is connected to the rotor 35 in the axial direction and covers the stator 37 of the electric motor 27 on the end in the axial direction. It is configured as a stepped annular portion that extends. The rotary bearing 38 is arranged coaxially around the coupling member 36 so that the rotary component 21 is rotatably supported on the holding component 39. The rotating component 21 abuts the holding component 39 in the axial direction via the rotating bearing 38, while the stator is mounted radially inward of the holding component 39. As a result, the holding component 39 surrounds the stator 37 in the coaxial direction. In the exemplary embodiment 3, the electric motor 28 is configured as a hollow shaft motor, so that a cylindrical open area occurs around the longitudinal axis L, in this space, if necessary, for the tool transporter 16. Guide pylon 16 can be passed. For example, this empty area is also suitable for the passage of drive elements, electrical lines or other power supply lines leading to the tool transporter 14. It is also possible for the connecting rod used to generate the reciprocating motion H to extend through the empty area.

  With reference to the first and second exemplary embodiments, the longitudinal axis L may be oriented vertically as well as horizontally.

  As in FIG. 4, in the third exemplary embodiment, the electric motor 28 of the rotary drive 27 is arranged like a ring around the longitudinal axis L, so that the rotor 35 is , Located axially next to the stator 37. As in the case of the previous second exemplary embodiment, the rotating component 21 is supported axially by the holding component 39 via the rotating bearing 38 so that the stator 37 is supported by the holding component. 39 is attached inward in the radial direction.

  The electric motor 28 is configured as a so-called segment motor. Considering this design, large diameters can be achieved for the tool transporter 14 or the rotating component 21, so that many machining stations 12 on the rotating component 21 and correspondingly many holding means 23 are used. Even reshaping operations can be complicated. In particular, the longitudinal axis L in this third exemplary embodiment of the device 10 is oriented in the vertical direction. Alternatively, left-right orientation of the vertical axis L is possible.

  The segment motor includes a permanent excitation type disk-shaped rotor 35. In a third exemplary embodiment of the apparatus 10, the segment motor rotor 35 comprises several pairs of poles each having a reverse magnetized permanent magnet. The direction of magnetization may be radial or tangential to the direction of rotation of the rotor 35. The stator has a different number of poles, in particular a smaller number of poles each formed by an electromagnet. As an alternative to the illustrated embodiment, the segment motor may include a stator 37 that is coaxially disposed about the rotor 35.

  In particular, the present invention relates to an apparatus 10 for re-forming a hollow cylindrical body 11 made of a single metal sheet. For reshaping, the stations 12 are arranged on the tool transporter 14 along a circular path around the longitudinal axis L. The station 12 includes a machining tool 13a or a test or measurement tool 13b. The tool transporter 14 is urged to reciprocate H along the longitudinal axis L by the main drive 15 of the device 10. There is a rotating component 21 which is arranged a little away from the tool transporter 14 so as to be rotatable about the longitudinal axis L. Therefore, the holding means 23 is uniformly disposed on the circular path K so as to be coaxial with the longitudinal axis L. The holding means 23 is arranged to hold one cylindrical body 11 at a predetermined position. The rotational drive device 27 promotes the rotational motion α (t) of the rotational component 21. The time series of the reciprocating motion H (t) and the time series of the rotational motion α (t) can be adjusted relative to each other so that there is no invariant relationship between these time series.

DESCRIPTION OF SYMBOLS 10 Apparatus 11 Cylindrical body 12 Station 12a Machining station 12b Test or measurement station 13a Machining tool 13b Test or measurement tool 14 Tool transporter 15 Main drive device 16 Guide pylon 17 First bearing 20 Transfer device 21 Rotating component 22 2 bearing 23 holding means 24 receiving cavity 27 rotation drive device 28 electric motor 29 control device 30 gear device 31 position sensor 35 rotor 36 connecting member 37 stator 38 rotation bearing 39 holding component Δα rotation angle α _i rotation position α ( t) rotational motion D rotational direction H (t) reciprocating motion K circular path UA first reversal point UB second reversal point t _B0 first time point t _B1 second time point τ duration t period ω angular velocity dω angular acceleration

Claims (9)

An apparatus (10) for reshaping a hollow cylinder (11),
A plurality of machining stations (12a) each comprising a machining tool (13a) disposed along a circular path, each disposed on a shared tool transporter (14);
A main drive (15) for generating a reciprocating motion (H) of the shared tool transporter (14) between two reversal points (UA, UB);
A plurality arranged for transferring the hollow cylinder (11) between the machining stations (12) and arranged on a circular path (K), each directed to one hollow cylinder (11) A transfer device (20) comprising a rotating component (21) having a holding means (23) of
A separate rotational drive (27) for generating intermittent rotational movement of the rotating component (21),
The time series of the intermittent rotational movement (α (t)) can be adjusted with respect to the time series of the reciprocating movement (H (t)),
The duration (τ) required by the rotary drive (27) rotating the rotating component (21) between two consecutive pre-specified rotational positions (αi) can be adjusted ;
The rotational speed of the intermittent rotational motion of the rotating component (21) by the rotational drive device (27) is a predetermined angular velocity, and the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15). Is the first reciprocating motion (H0) of the first period (Tmin) and the rotational angle of the intermittent rotational motion of the rotational component (21) by the rotational drive device (27) is the predetermined angular velocity and the A second reciprocating motion (H1) of a second cycle (T1) in which the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15) is longer than the first cycle (Tmin); A device, characterized in that An apparatus (10) for reshaping a hollow cylinder (11),
A plurality of machining stations (12a) each comprising a machining tool (13a) disposed along a circular path, each disposed on a shared tool transporter (14);
A main drive (15) for generating a reciprocating motion (H) of the shared tool transporter (14) between two reversal points (UA, UB);
A plurality arranged for transferring the hollow cylinder (11) between the machining stations (12) and arranged on a circular path (K), each directed to one hollow cylinder (11) A transfer device (20) comprising a rotating component (21) having a holding means (23) of
A separate rotational drive (27) for generating intermittent rotational movement of the rotating component (21),
The time series of the intermittent rotational movement (α (t)) can be adjusted with respect to the time series of the reciprocating movement (H (t)),
The holding tool required by the rotary drive (27) that rotates the rotating component (21) between the stroke speed of the shared tool transporter (14) and two consecutive pre-specified positions (αi). it is possible to adjust the relationship between the connection time (τ),
The rotational speed of the intermittent rotational motion of the rotating component (21) by the rotational drive device (27) is a predetermined angular velocity, and the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15). Is the first reciprocating motion (H0) of the first period (Tmin) and the rotational angle of the intermittent rotational motion of the rotational component (21) by the rotational drive device (27) is the predetermined angular velocity and the A second reciprocating motion (H1) of a second cycle (T1) in which the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15) is longer than the first cycle (Tmin); A device, characterized in that The main drive (15) is designed as an eccentric drive mechanism that converts the continuous rotational movement of the motor between two reversing points (UA, UB) into a swinging movement of the shared tool carrier (14). The device according to claim 1 or 2, characterized in that   The separate rotary drive (27) comprises a separate electric motor (28) connected to the rotating component without inserting a gear unit (30) that reduces or increases speed. An apparatus according to claim 1 or claim 2. Electric motor (28), characterized in that a segment motor or torque motor or servo motor, The device of claim 1 or claim 2.   3. The transfer device (20) according to claim 1 or 2, characterized in that it comprises a position sensor (31) arranged for detecting the rotational position (αi) of the rotating component (21). The device described. Said transfer device (20), position, angular velocity (omega), and characterized by adjusting at least one of the angular acceleration (d [omega)), according to claim 1 or claim of the rotating component (21) 2. The apparatus according to 2. A method of operating a device (10) for reshaping a hollow cylinder (11),
Each includes a plurality of machining stations (12a) disposed along a circular path, each comprising a machining tool (13a), said machining tool (13a) being mounted on a shared tool transporter (14). Arranged in
The reciprocating motion (H) of the shared tool transporter (14) is urged between two reversal points (UA, UB);
The hollow cylinder (11) is transferred between the machining stations (12) along a circular path (K) by a rotating component (21);
The intermittent rotational motion (α) of the rotating component (21) is prompted, and the time series (α (t)) of the intermittent rotational motion is adjusted with respect to the time series (H (t)) of the reciprocating motion. Can
The duration (τ) required by the rotary drive (27) rotating the rotating component (21) between two consecutive pre-specified rotational positions (αi) can be adjusted ;
The rotational speed of the intermittent rotational motion of the rotating component (21) by the rotational drive device (27) is a predetermined angular velocity, and the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15) is The first reciprocating motion (H0) of the first period (Tmin) and the rotational angle of the intermittent rotational motion of the rotational component (21) by the rotational drive device (27) are the predetermined angular velocity and the main rotational speed. The second reciprocating motion (H1) of the second cycle (T1) in which the cycle of the reciprocating motion of the shared tool transporter (14) by the drive device (15) is longer than the first cycle (Tmin). A method characterized in that it is possible. A method of operating a device (10) for reshaping a hollow cylinder (11),
Each includes a plurality of machining stations (12a) disposed along a circular path, each comprising a machining tool (13a), said machining tool (13a) being mounted on a shared tool transporter (14). Arranged in
The reciprocating motion (H) of the shared tool transporter (14) is urged between two reversal points (UA, UB);
The hollow cylinder (11) is transferred between the machining stations (12) along a circular path (K) by a rotating component (21);
The intermittent rotational motion (α) of the rotating component (21) is prompted, and the time series (α (t)) of the intermittent rotational motion is adjusted with respect to the time series (H (t)) of the reciprocating motion. Can
Sustainable are needed the by a rotational driving device for rotating rotary component (21) (27) between the stroke speed and the two successive pre-specified position of the shared tool transporter (14) (.alpha.i) it is possible to adjust the relationship between the time (τ),
The rotational speed of the intermittent rotational motion of the rotating component (21) by the rotational drive device (27) is a predetermined angular velocity, and the cycle of the reciprocating motion of the shared tool transporter (14) by the main drive device (15) is The first reciprocating motion (H0) of the first period (Tmin) and the rotational angle of the intermittent rotational motion of the rotational component (21) by the rotational drive device (27) are the predetermined angular velocity and the main rotational speed. The second reciprocating motion (H1) of the second cycle (T1) in which the cycle of the reciprocating motion of the shared tool transporter (14) by the drive device (15) is longer than the first cycle (Tmin). A method characterized in that it is possible.

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