CH704221B1 - Apparatus for shaping hollow cylindrical bodies and method for operating this device. - Google Patents

Apparatus for shaping hollow cylindrical bodies and method for operating this device. Download PDF

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Publication number
CH704221B1
CH704221B1 CH01943/11A CH19432011A CH704221B1 CH 704221 B1 CH704221 B1 CH 704221B1 CH 01943/11 A CH01943/11 A CH 01943/11A CH 19432011 A CH19432011 A CH 19432011A CH 704221 B1 CH704221 B1 CH 704221B1
Authority
CH
Switzerland
Prior art keywords
rotary
tool carrier
movement
drive
circular path
Prior art date
Application number
CH01943/11A
Other languages
German (de)
Other versions
CH704221A2 (en
Inventor
Wilfried Abt
Thomas Rehm
Carsten Brechling
Original Assignee
Schuler Pressen Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE102010061248A priority Critical patent/DE102010061248B4/en
Application filed by Schuler Pressen Gmbh filed Critical Schuler Pressen Gmbh
Publication of CH704221A2 publication Critical patent/CH704221A2/en
Publication of CH704221B1 publication Critical patent/CH704221B1/en

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D51/00Making hollow objects
    • B21D51/16Making hollow objects characterised by the use of the objects
    • B21D51/26Making hollow objects characterised by the use of the objects cans or tins; Closing same in a permanent manner
    • B21D51/2692Manipulating, e.g. feeding and positioning devices; Control systems
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02Advancing work in relation to the stroke of the die or tool
    • B21D43/04Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/14Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by turning devices, e.g. turn-tables
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D51/00Making hollow objects
    • B21D51/16Making hollow objects characterised by the use of the objects
    • B21D51/26Making hollow objects characterised by the use of the objects cans or tins; Closing same in a permanent manner

Abstract

The invention relates to a device (10) for forming hollow cylindrical bodies (11), which are in particular formed from a one-piece sheet-metal part. For the forming, a plurality of processing stations (12a) are arranged on a tool carrier (14) along a circular path about a longitudinal axis (L). The processing stations (12a) each have a processing tool (13a). The tool carrier (14) is caused by a main drive (15) of the device (10) to a lifting movement (H) along the longitudinal axis (L). At a distance from the tool carrier (14) a rotatable about the longitudinal axis (L) arranged rotary member (21) is present. There are arranged on a circular path coaxial with the longitudinal axis (L) holding means (23) evenly distributed. The holding means (23) serve to hold a body (11). A rotary drive (27) causes the rotational movement of the rotary member (21). The temporal course of the lifting movement (H) and the time course of the rotational movement can be changed with respect to each other, so that there is no fixed relationship between these temporal progressions.

Description

The invention relates to a device for forming hollow cylindrical bodies and a method for operating this device. In the production of containers made of thin-walled sheet metal, for example for aerosol cans, a hollow-cylindrical body open at one end is first produced as a semi-finished product in a deep drawing and ironing apparatus. This hollow cylindrical body must then be further formed in a further process, in particular in the region of its bottom and / or the upper edge region. The device according to the invention or the method according to the invention is used for this purpose. Such a device is often referred to as Einziehmaschine.
Today Einziehmaschinen are known for forming hollow cylindrical bodies having a plurality of stations that are designed as processing stations or as measuring and testing stations. Each processing station has a processing tool. The processing tools are arranged along a circular path on a common tool carrier. At a distance from the tool carrier, a rotary part is provided with a plurality of holding means arranged along a circular path for the body. The holding means are arranged on a circular path which corresponds to the radius of the circular path on which the machining tools are seated on the tool carrier. By intermittently rotating the rotating part, the hollow cylindrical bodies are transported from one station to the next. This intermittent rotational movement of the rotating part must be performed synchronized with the stroke movement of the tool carrier. For this purpose, it is provided in machines available on the market, that the main drive for generating the lifting movement of the tool carrier also causes the rotational movement of the rotating part. For this purpose, for example, a stepping gear can be coupled to the main drive, which moves the rotary member by a predetermined angle of rotation during the return stroke of the tool carrier.
Such a known device is inflexible. The rotary motion of the rotating part is permanently synchronized with the main drive. If, for example, hollow cylindrical bodies are to be machined with a greater axial height, this is not readily possible. Because of the required for the rotation of the rotary part of the return stroke (so-called overstroke) of the tool carrier must not fall below a minimum value to ensure on the stepping gear further rotation of the rotating part. However, the rotation of the rotary part can only begin when all machining tools are out of engagement with the hollow cylindrical bodies. Since the total stroke of the device is limited, this results in the maximum height of the machinable hollow cylindrical body.
It is an object of the present invention to improve the flexibility of the device. In particular, the possibility should be created to increase at the same maximum available stroke of the tool carrier, the maximum height of the machinable hollow cylindrical body over known devices.
This object is achieved by a device having the features of claim 1 and a method for operating this device with the features of claim 9.
The invention provides to decouple the skin drive for generating the lifting movement of the tool carrier from the rotary drive for generating the intermittent rotational movement of the rotating part. The rotary member is therefore associated with a separate rotary drive, in particular an electric motor. The time profile of the rotational movement of the rotary member is adjustable or adjustable in a predetermined range relative to the time profile of the lifting movement. This makes it possible, for example, to reduce the number of strokes of the tool carrier, ie the number of strokes per unit time of the tool carrier, while at the same time setting the time required for the rotational part to move between two predetermined rotational positions to be shorter than that for the reduced number of strokes would be necessary. By compared to the lifting movement of the tool carrier faster rotary part movement of the available for forming part of the stroke can be increased. Thus, bodies with a greater axial height can be processed on the same device than was previously the case. This is due to the fact that the proportion of the time duration for the movement of the rotary part between two successive rotational positions on the period for a complete stroke can be reduced. This results in a smaller overstroke of the tool carrier. The available for the transformation of the body proportion of the entire stroke can be increased.
Advantageously, the main drive is designed as an eccentric drive. Such an eccentric drive converts a continuous rotational movement of a motor, for example an electric motor of the main drive, into an oscillating movement of the tool carrier. By means of an eccentric adjustment, it is also possible to set the stroke, that is to say the distance between the two reversal points of the lifting movement.
In a preferred embodiment, the rotary drive on a separate electric motor, which is preferably connected without the interposition of a transmission for reduction or for translation with the rotary member. In particular, the electric motor can be designed as a direct drive and connected directly to the rotary part. The electric motor can therefore be designed as a servomotor or torque motor. In the direct connection of the electric motor with the rotating part accounted for play and wear-related gear parts. The positioning of the rotating part can be done very accurately relative to the processing tools.
In a further advantageous embodiment, the electric motor is formed by a so-called segment motor. Such a motor allows the stabilization of the driven part bearing-free by reluctance forces for several degrees of freedom. In this way, the wear can be further reduced.
To control the rotational position of the rotary part, the transport device for hollow cylindrical body preferably has a position sensor. The sensor signal is supplied, for example, to a control unit which controls the rotary drive, so that position control can be achieved with great accuracy. Alternatively or additionally, other parameters of the rotational movement of the rotating part can be controlled or regulated, such as the angular velocity and / or the angular acceleration of the rotating part.
Preferably, the time required by the rotary drive for rotation of the rotary member between two consecutive predetermined rotational positions, adjustable by an operator. In a given area, this period of time can also be changed during the operation of the device.
It is also advantageous if the ratio between the stroke rate of the tool carrier and the time required for the rotary drive to rotate the rotary member between two consecutive predetermined rotational positions, is adjustable. In this way, the temporal behavior of the lifting movement relative to the rotational movement of the rotary member can be changed very easily matched.
Advantageous embodiments of the device will become apparent from the dependent claims and the description. The drawing is to be used as a supplement. Show it: <Tb> FIG. 1 <SEP> is a schematic side view of a first embodiment of an inventive device in a sectional view, <Tb> FIG. 2 <SEP> the rotary part of Figure 1 in plan view according to line II-II, <Tb> FIG. 3 <SEP> a second embodiment of a rotary drive for the rotary member in a schematic side view in a sectional view, <Tb> FIG. 4 <SEP> a third embodiment of a rotary drive for the rotary member in a schematic side view in the sectional view and <Tb> FIG. 5 <SEP> the time course of the rotational movement of the rotary member and the stroke movement of the tool carrier in an exemplary schematic representation.
In Fig. 1, a device 10 for forming hollow cylindrical bodies 11 is shown. The hollow cylindrical bodies 11 have been deep-drawn from thin-walled sheet metal in a preceding method and / or drawn and closed at one axial end over a bottom. The bodies 11 are made of a single metallic material and are embodied, for example, in one piece without seaming or joining points. The device 10 serves to further reshape these hollow cylindrical body 11 closed on one side. For this purpose, the device 10 has a plurality of processing stations 12a. In each processing station 12a is a processing tool 13a for performing the corresponding forming step.
The processing tools 13a are arranged on a common tool carrier on a circular path about a central longitudinal axis L. Between successive processing stations 12a, test or measuring stations 12b can also be interposed with a testing or measuring tool 13b on this circular path in order to test the previous forming processes on the body 11. Measuring stations 12b and processing stations 12a form stations 12, which are arranged on the circular path regularly distributed around the longitudinal axis L, so that a complete closed circuit is formed.
The tool carrier 14 is driven by a main drive 15 and performs a lifting movement H between two reversal points UA and UB. In this case, the tool carrier 14 moves with the tools 13a, 13b on the body to be processed 11 until it has reached the first reversal point UA. In this first reversal point UA, the Hubbewegungsrichtung is reversed, and the tool carrier 14 moves away again from the bodies to be machined 11 to the second reversal point UB. This stroke H is repeated cyclically. In order to achieve the oscillating stroke movement H of the tool carrier 14, the main drive 15 may be designed, for example, as an eccentric drive. An electric motor of the main drive 15 drives an eccentric whose eccentric motion is converted via a connecting rod in the stroke H of the tool carrier 14. In a preferred embodiment, the stroke of the tool carrier 14 can be adjusted or changed on the eccentric.
The tool carrier 14 is slidably guided in the direction of its stroke H. For example, for this purpose, a central guide column 16 may be present, which is enclosed by the annular tool holder 14 coaxial with the longitudinal axis L. Between the guide column 16 and the tool carrier 14, a first bearing 17, for example, a plain bearing or roller bearings, is provided.
A transport device 20 serves to transport the body 11 between the stations 12 and to position the bodies 11 with respect to the tool 13a, 13b. For this purpose, the transport device 20 on a rotatably driven rotary member 21 which is arranged coaxially to the longitudinal axis L and rotatably supported about this. In the first embodiment of the device 10 shown in Fig. 1, the rotary member 21 is rotatably mounted on the central guide column 16 via a second bearing 22a and / or 22b. The second bearing can be supported either between the rotary part 21 and the guide column 16 (bearing 22a in FIG. 1) and / or via a coaxial with the longitudinal axis L at a distance from the guide column 16 second bearing (bearing 22b in Fig. 1). The rotary member 21 has an annular shape. It can therefore also be called a turntable or turntable.
On the tool carrier 14 facing side of the rotary member 21 holding means 23 are provided, each holding means 23 for holding a hollow cylindrical body 11 is used. As shown schematically, the holding means 23 on a receiving trough 24, which receives the bottom-side portion of the body 11. In the area of the receiving trough 24 jaws, not shown, may be present to clamp the body 11 in the desired position in the receiving trough 24. The holding means 23 are arranged on a circular path K, which runs coaxially to the longitudinal axis L. The circular path K has the same radius as the circular path on which the stations 12 are arranged. In this way, in each case a body 11 can be positioned in alignment with a holding means 23 in the direction of the lifting movement H for a machining tool 13a or a measuring or testing tool 13b. The transport of the bodies 11 between successive stations 12 takes place by an intermittent or stepwise rotation of the rotary member 21 in a direction of rotation D between two successive rotational positions αi and αi + 1. The number of these rotational positions αi (i = 1 to n) corresponds to the number n of stations 12 on the tool carrier. The holding means 23 are arranged at regular intervals along the circular path K. In Fig. 2, only some of the existing receiving wells 24 are shown.
For the drive of the rotary member 21 is independent of the main drive 15 separate rotary actuator 27 is present. The rotary drive 27 has an electric motor 28, which is controlled by a control unit 29. The control unit 29 controls the electric motor 28 in such a way that the rotary member 21 within a period T of the lifting movement H between two successive rotational positions αiund αi + 1 on the corresponding rotation angle Δα is further rotated. The period of time required for this purpose by the rotary drive 27 is designated by .tau. The rotation angle Δα is 360 ° divided by the number n of the holding means 23.
The rotary drive 27 is preferably designed as a direct drive, so that the electric motor 28 is connected directly to the rotary member 21 without the interposition of a transmission. As illustrated in FIG. 1, however, a transmission 30 may also be interposed between the electric motor 28 and the rotary part 21.
The rotational position αides rotary member 21 is detected by at least one position sensor 31. The position signal is transmitted to the control unit 29. In this way, a position-controlled operation of the rotary member 21 is possible.
The time profile of the rotational movement α (t) can be set or changed with respect to the time profile of the stroke movement H (t). This is possible because there is no mechanical, fixed coupling between the main drive 15, which moves the tool carrier 14, and the rotary part 21, which is moved via the separate rotary drive 27. The method for operating the device 10 will be explained with reference to FIG. 5.
The first stroke H0 (t) corresponds to the maximum possible stroke rate of the device. The tool carrier 14 requires the period τmin for a complete stroke movement from the first reversal point UA to the second reversal point UB and back to the first reversal point UA.
During a period τminum the first time tB0 when reaching the second reversal point UB around, the rotary member 21 is moved by the rotation angle Δα between two consecutive rotational positions αi, αi + 1 (first rotational movement α0 (t)). During this time τmin, the processing tools 13a as well as the testing and measuring tools 13b must be out of engagement with the hollow cylindrical bodies 11. This means that during this period, the distance of the tool carrier 14 must be greater than a minimum value, which can be referred to as Nutzhub. The phase of the lifting movement H0 (t) during which the turntable 21 is rotated constitutes a so-called overstroke, which can not be used to machine the bodies 11. This results in the available first useful stroke N0 for the first lifting movement H0 (t) when the tool carrier is moved with the maximum number of strokes. This first Nutzhub N0 thus also indicates the maximum height of the body 11, which can be edited at maximum stroke rate.
The second stroke movement H1 (t) in FIG. 5 represents a stroke movement whose period T1 is greater than the minimum period Tmin. The tool carrier 14 is therefore moved more slowly during the lifting movement H1 (t). It is assumed that the rotary member 21 is rotated by the rotary drive 27 with maximum angular velocity ω or maximum angular acceleration dω about the longitudinal axis L. The time required for the return of the angle of rotation Δα between two successive rotational positions is therefore minimal and corresponds to the minimum time duration τmin. The second rotational movement α1 (t) of the rotary member 21 can be performed symmetrically in time to the second time tB1 of reaching the second reversal point UB. Because of the increased period T1 of the second stroke H1 (t) thereby increases the available for the processing body 11 second Nutzhub N1 to the value N1> N0. By increasing the period T of the lifting movement H (t), therefore, the Nutzhub N of the device 10 can be increased and compared to the maximum stroke rate of the device axially higher body 11 are processed. The device 10 thus has greater flexibility in order to be able to process different sizes and shapes of bodies 11.
The two rotational movements α0 (t) and α1 (t) are shown in Fig. 5 only very schematically as a rectangular signal and actually have deviating temporal courses.
By the control unit 29, the rotary drive 27 can optimize the rotational movement α (t) not only in terms of the required period of time τ. It is also possible to specify or set further movement parameters of the rotational movement .alpha. (T). For example, a smooth rotational movement α (t) can be set with a constant change in acceleration, which is advantageous especially in the case of very thin-walled sensitive bodies 11, in order to prevent accidental damage to the bodies 11. It is also possible to specify minimum and / or maximum angular velocity values ω or angular acceleration values dω. In addition, a time-dependent desired course for the rotational movement α (t) and / or for the angular velocity ω (t) and / or for the angular acceleration dω (t) can also be predetermined and controlled by the control unit 29. By temporal derivation of the position signal of the position sensor 31, the actual values of the angular velocity and the angular acceleration can be determined. It can thus be set or adjusted arbitrary laws of motion for the rotational movement of the rotary member 21.
In Fig. 3, a second embodiment of the device 10 is shown. The second embodiment differs in mechanical structure from the first embodiment of the device 10 of FIG. 1. The operation in the control or regulation of the rotary drive 27 corresponds to the first embodiment, so that reference is made to the above description.
In the second embodiment of FIG. 3, the electric motor 28 of the rotary drive 27 is coupled directly to the rotary member 21 without the interposition of a transmission. For this purpose, the rotor 35 of the electric motor 28 is rotatably connected via a connecting part 36 with the rotary member 21. The connecting part 36 is formed in the embodiment of FIG. 3 as a stepped ring member which is axially connected to the rotor 35 and the stator 37 of the electric motor 28 engages over an axial end face. Coaxially around the connecting part 36 around a pivot bearing 38 is arranged, that the rotary member 21 rotatably supported on a holding part 39. While the rotary member 21 via the pivot bearing 38 is axially supported on the holding part 39, the stator is fixed to the radially inner side of the holding part 39. The holding part 39 thus surrounds the stator 37 coaxially. In the embodiment 3, the electric motor 28 is designed as a hollow shaft motor, so that there is a cylindrical clearance around the longitudinal axis L, through which the guide column 16 can be passed for the tool carrier 16 when needed. This free space is also suitable, for example, for carrying out drive elements, electrical lines or other supply lines to the tool carrier 14. Also, the drive rod for generating the lifting movement H can protrude through the space.
The longitudinal axis L may be aligned both vertically and horizontally in the first and the second embodiment.
In a third embodiment of FIG. 4, the electric motor 28 of the rotary drive 27 is arranged annularly about the longitudinal axis L, wherein the rotor 35 is provided axially adjacent to the stator 37. As in the previous second embodiment, the rotary member 21 is supported via a rotary bearing 38 in the axial direction on a holding part 39, on the radially inner side of the stator 37 is attached.
The electric motor 28 is designed as a so-called segment motor. In this embodiment, large diameter for the tool carrier 14 and the rotary member 21 can be achieved so that more complex forming processes with many processing stations 12 and correspondingly many holding means 23 on the rotary member 21 can be realized. In particular, the longitudinal axis L is vertically aligned in this third embodiment of the device 10. A horizontal alignment of the longitudinal axis L is alternatively also possible.
The segment motor has a permanently excited disc-shaped rotor 35. In the third exemplary embodiment of the device 10, the rotor 35 of the segment motor has a plurality of pole pairs, each with oppositely magnetized permanent magnets. The magnetization direction can be radial or tangential to the direction of rotation of the rotor 35. The stator has a different and in particular smaller number of poles, which are each formed by an electromagnet. As an alternative to the illustrated embodiment, the segment motor may also have a stator 37 coaxially disposed about the rotor 35.
The invention relates to a device 10 for forming hollow cylindrical bodies 11, which in particular consist of a one-piece sheet metal part. For the forming a plurality of processing stations 12a are arranged on a tool carrier 14 along a circular path about a longitudinal axis L. The processing stations 12a each have a processing tool 13a. The tool carrier 14 is caused by a main drive 15 of the device 10 to a lifting movement H along the longitudinal axis L. At a distance from the tool carrier L a rotatable about the longitudinal axis L arranged rotary member 21 is present. There are arranged on a circular path K coaxially to the longitudinal axis L holding means 23 evenly distributed. A rotary drive 27 causes the rotational movement α (t) of the rotary member 21. The time profile of the lifting movement H (t) and the time course of the rotational movement α (t) can be changed from each other so that there is no fixed relationship between these temporal processes.
[0036] List of Reference Numerals: <Tb> 10 <September> Device <Tb> 11 <September> Body <Tb> 12 <September> Station <Tb> 12 <September> processing station <tb> 12b <SEP> Testing or measuring station <Tb> 13 <September> Cutting tool <tb> 13b <SEP> Testing or measuring tool <Tb> 14 <September> tool carrier <Tb> 15 <September> main drive <Tb> 16 <September> guide column <tb> 17 <SEP> First camp <Tb> 20 <September> transport device <Tb> 21 <September> Drehteil <tb> 22 <SEP> Second camp <Tb> 23 <September> holding means <Tb> 24 <September> receiving trough <Tb> 27 <September> rotary drive <Tb> 28 <September> electric motor <Tb> 29 <September> control unit <Tb> 30 <September> Gear <Tb> 31 <September> position sensor <Tb> 35 <September> Rotor <Tb> 36 <September> connecting part <Tb> 37 <September> stator <Tb> 38 <September> pivot <Tb> 39 <September> holding part <Tb> Δα <September> rotation angle <Tb> .alpha..sub.i <September> rotational position <Tb> α (t) <September> rotational movement <Tb> D <September> direction of rotation <Tb> H (t) <September> stroke movement <Tb> K <September> circular path <tb> UA <SEP> First reversal point <tb> UB <SEP> Second reversal point <tb> tB0 <SEP> first time <tb> tB1 <SEP> second time <Tb> τ <September> time <Tb> T <September> period <Tb> ω <September> angular velocity <Tb> dw <September> angular acceleration

Claims (9)

1. Device (10) for forming hollow cylindrical bodies (11), with a plurality of processing stations (12a) arranged along a circular path and each having a processing tool (13a), the processing tools (13a) being arranged on a common tool carrier (14), with a main drive (15) for generating a lifting movement (H) of the tool carrier (14) between two reversal points (UA, UB), with a transport device (20), which serves to transport the bodies (11) between the processing stations (12a), and a rotary part (21) having a plurality of holding means (23), arranged along a circular path (K), for each body ( 11), and with a separate rotary drive (27) for generating an intermittent rotational movement of the rotary member (21), the time course (α (t)) with respect to the time course of the lifting movement (H (t)) is adjustable.
2. Apparatus according to claim 1, characterized in that the main drive (15) is designed as an eccentric drive, which converts a continuous rotational movement of a motor into an oscillating movement of the tool carrier (14) between the reversal points (UA, UB).
3. Apparatus according to claim 1, characterized in that the rotary drive (27) has an electric motor (28), which is in particular connected without the interposition of a transmission or reduction gear (30) with the rotary member (21).
4. Apparatus according to claim 3, characterized in that the electric motor (28) is formed by a segment motor or a torque motor or a servomotor.
5. Apparatus according to claim 1, characterized in that the control unit (29) comprises a position sensor (31) which serves to detect the rotational position (αi) of the rotary member (21).
6. Apparatus according to claim 1 characterized in that the control unit (29) regulates the position and / or the angular velocity (ω) and / or the angular acceleration (dω) of the rotary member (21).
7. Apparatus according to claim 1, characterized in that the period of time (τ) required by the rotary drive (27) to rotate the rotary member (21) between two consecutive predetermined rotational positions (αi) is adjustable.
8. Apparatus according to claim 1, characterized in that the ratio between the number of strokes of the tool carrier (14) and the time (τ) required by the rotary drive (27) to rotate the rotary member (21) between two consecutive predetermined rotational positions (αi) is adjustable.
9. A method for operating a device (10) for forming hollow cylindrical bodies (11) according to one of the preceding claims, wherein a stroke movement (H) of the tool carrier (14) between two reversal points (UA, UB) is caused, wherein the bodies (11) between the processing stations (12a) are transported by means of the rotary part (21) along a circular path (K), wherein an intermittent rotational movement (α) of the rotary member (21) is caused, the time course (α (t)) with respect to the time course of the lifting movement (H (t)) is adjustable.
CH01943/11A 2010-12-15 2011-12-07 Apparatus for shaping hollow cylindrical bodies and method for operating this device. CH704221B1 (en)

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CH704221B1 true CH704221B1 (en) 2015-08-14

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DE102013202879A1 (en) 2013-02-21 2014-08-21 Mall + Herlan Schweiz Ag Feeding device and method for successive feeding
DE102013106784B4 (en) 2013-06-28 2018-07-19 Schuler Pressen Gmbh Apparatus and method for forming hollow cylindrical bodies
DE102013018421A1 (en) * 2013-11-04 2015-05-07 Schweikert GmbH Pivoting device for a cutting tool of a processing machine
EP3025804B1 (en) * 2014-11-25 2018-06-27 SPL Soluzioni S.r.l. Apparatus for working metallic bodies
ITUB20155832A1 (en) * 2015-11-23 2017-05-23 Spl Soluzioni S R L Equipment for processing metal bodies.
DE102016119076A1 (en) * 2016-10-07 2018-04-12 Weiss Gmbh drive unit
CN106694671A (en) * 2017-03-06 2017-05-24 东莞市金拓机械有限公司 Multi-station rotating disc type force measuring type hydraulic machine
DE102017118654B4 (en) * 2017-08-16 2019-06-27 Schuler Pressen Gmbh Ironing arrangement, forming device with a Abstreckwerkzeuganordnung and method for forming a cup-shaped output part

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JP2002336999A (en) * 2001-05-10 2002-11-26 Mitsubishi Electric Corp Press machine and its controller
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CH704221A2 (en) 2012-06-15
DE102010061248A1 (en) 2012-06-21
JP5659132B2 (en) 2015-01-28
JP2012125840A (en) 2012-07-05

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