EP0629574A1 - Dispositif de chargement pour du matériau, en particulier pour des bobines de papier - Google Patents

Dispositif de chargement pour du matériau, en particulier pour des bobines de papier Download PDF

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Publication number
EP0629574A1
EP0629574A1 EP94107813A EP94107813A EP0629574A1 EP 0629574 A1 EP0629574 A1 EP 0629574A1 EP 94107813 A EP94107813 A EP 94107813A EP 94107813 A EP94107813 A EP 94107813A EP 0629574 A1 EP0629574 A1 EP 0629574A1
Authority
EP
European Patent Office
Prior art keywords
axis
roller
bearing
control
path
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP94107813A
Other languages
German (de)
English (en)
Other versions
EP0629574B1 (fr
Inventor
Wolfgang Trefz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bielomatik Leuze GmbH and Co KG
Original Assignee
Bielomatik Leuze GmbH and Co KG
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
Application filed by Bielomatik Leuze GmbH and Co KG filed Critical Bielomatik Leuze GmbH and Co KG
Publication of EP0629574A1 publication Critical patent/EP0629574A1/fr
Application granted granted Critical
Publication of EP0629574B1 publication Critical patent/EP0629574B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H19/00—Changing the web roll
    • B65H19/10—Changing the web roll in unwinding mechanisms or in connection with unwinding operations
    • B65H19/12—Lifting, transporting, or inserting the web roll; Removing empty core
    • B65H19/126—Lifting, transporting, or inserting the web roll; Removing empty core with both-ends supporting arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/02—Stationary loaders or unloaders, e.g. for sacks
    • B66F9/04—Stationary loaders or unloaders, e.g. for sacks hydraulically actuated or controlled
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/40—Type of handling process
    • B65H2301/41—Winding, unwinding
    • B65H2301/417—Handling or changing web rolls
    • B65H2301/4171—Handling web roll
    • B65H2301/4172—Handling web roll by circumferential portion, e.g. rolling on circumference
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2405/00—Parts for holding the handled material
    • B65H2405/40—Holders, supports for rolls
    • B65H2405/42—Supports for rolls fully removable from the handling machine
    • B65H2405/422—Trolley, cart, i.e. support movable on floor

Definitions

  • the invention relates to a loading device with which large roller bodies or the like. up to several hundred or thousands of kilograms of weight can be lifted from a supported position into a working position so that they can be used to remove the material, e.g. for unwinding a material web are freely accessible or can rotate freely. Such rolls can have a maximum diameter of over 1.5 m, for example.
  • the receiving axis of the roller carrier should be easy to align with the roller axis in order to be able to bring the roller hub, which is formed, for example, by an axle sleeve, into engagement with the respective receiving head of the roller carrier.
  • the roller carrier can be controlled so that its receiving axis runs through an approximately linear or vertical path of movement, which coincides with the axial plane in which the roller axes are independent of the roller diameter when the rollers in a predetermined and supported location are provided.
  • the material carrier can be traversable with a carriage, but this results in a complex and proportionate process arrangement taking up a lot of space. Furthermore, the alignment of the receiving axis on the respective material axis is difficult because, independently of one another, the slide must be adjusted transversely to the vertical axial plane of the material unit and the material carrier in the height direction of the material unit on its material axis.
  • the invention has for its object to provide a device in which disadvantages of known designs or the type described are avoided and which in particular ensures simple feeding of the material and alignment of the receiving axis on the material axis regardless of the distance between the material axis due to its outer width from the support.
  • control means which on the one hand move the receiving axis of the material carrier approximately rectilinearly over the area in which the material axes of the material units to be processed can lie and which are also suitable for transferring the loading device into a position in which the respective Material unit regardless of its outer width in an approximately linear longitudinal movement and without driven transverse conveying can be transferred to a stationary loading position so that it can only get out of it Movements of the loading device can be brought into engagement with the respective material carrier.
  • the control means bring about a continuously linear, forced movement over the alignment path, so that it is not necessary to coordinate two movements lying transversely and separately to be driven so that the receiving axis can be adjusted coaxially to the roller axis.
  • the cam controller can have a control cam with a cam follower guided thereon, which moves the receiving axis transversely as a function of the stroke path and thereby inevitably forces the straightening of the alignment path.
  • the design according to the invention is particularly suitable for those roller carriers which are not moved linearly or by means of a parallelogram linkage over the stroke path, but which can be pivoted in the manner of a rocker about a pivot axis, for example approximately parallel to the receiving axis, of a lifting bearing and are free from the bearing axis in the manner of a cantilever protrude to the receiving axis.
  • the receiving axis then executes an arc path during a pivoting movement about the pivot axis via the stroke path corresponding to the alignment path, which is straightened by the curve control.
  • a control curve it is then appropriately curved or not straight. If the control curve lies on the side of the pivot axis facing away from the receiving axis, the control curve is curved in the opposite direction to the arc path that the receiving axis executes about the pivot axis of the supporting bearing.
  • the stroke bearing is movably mounted transversely to the receiving axis in relation to the device base in order to enable the alignment path of the receiving axis to be straightened.
  • a pivoting movement about a bearing axis lying approximately parallel to the pivot axis or the receiving axis is expediently provided, the distance from the pivot axis of which can be substantially smaller than the distance between the pivot axis and the receiving axis.
  • the pivot axis and the bearing axis are advantageously approximately vertically one above the other, so that there are very favorable load conditions.
  • control means or the curve control With the control means or the curve control, the movement of the receiving axis and its path between the alignment path and the loading position can also be controlled at the same time, so that the receiving axis can be continuously controlled over its entire path of movement without mutually transverse movements being coordinated with one another interruptions of the movement sequences are necessary for this.
  • the control curve can continuously transition from the curve section belonging to the alignment path into a subsequent curve section which controls the movement path up to the loading position.
  • a single drive which can also consist of several drive units, for example cylinder units, is sufficient for control via the straightened alignment path and for control up to the loading position. But it is also conceivable to influence the movement path between the alignment path and the loading position with a further drive, which then works synchronously with the lifting drive which moves the receiving axis via the alignment path. In this case, it may be sufficient to provide the control cam only for control over the stroke.
  • the control means expediently act on a rod of the lifting bearing, along which the respective roller carrier can be displaced, in order to be able to adjust the roller axially when worn or to align it with a machine processing the material web.
  • the cam control does not carry out this axial movement, but is stationary in the area of the associated base, which can have the control cam in a stationary base plate.
  • the loading device 1 has a stationary device base 2 and a roller carrier 3 movably mounted thereon for carrying out lifting and evasive movements, which is provided at the end of an exposed support section 4 with a receiving or clamping head 6, which determines a horizontal receiving axis 5 .
  • a pivot bearing with a horizontal bearing axis 8 or a bearing axis 8 parallel to the receiving axis 5 is provided as the lifting bearing 7, about which the carrier 3 need only be pivoted over an arc angle of approximately 90 ° in order to carry out the required functional movements.
  • the lifting bearing 7 can be moved approximately horizontally or transversely to the receiving axis 5 with respect to the base 2 and is pivotably supported in a supporting bearing 9 about a pivot axis 11 which is approximately parallel to the axis 5 or 8 and with the bearing axis 8 in an approximately vertical axial plane .
  • the maximum required swivel angle for the lifting bearing 7 is only a few degrees, namely less than 10 or 5 °, the distance between the axes 8, 11 being less than half the distance between the axes 5, 8 or about a third thereof .
  • the stroke bearing 7 or the supporting section 4 with the clamping head 6 can execute a transverse or horizontal movement which is synchronously superimposed on its lifting movement in such a way that the receiving axis 5 instead of a pure curved path about the bearing axis 8 over a predetermined swivel angle an approximately rectilinear or vertical movement executes.
  • This swivel angle is suitably below 60 or 45 ° and in the order of 30 °.
  • the Support bearing of the support bearing 7 hangs on a supporting link 12 which is narrower than its outer width and rigidly connected to it and which is pivotally mounted at its upper end about the pivot axis 11.
  • control means 10 are provided which are essentially completely on the side of the axes 8, 11 or the lifting bearing 7 and the support bearing 9 facing away from the receiving axis 5, essentially at the same height as the straightened trajectory lies.
  • the clamping head 6 or the support section 4 On the side facing away from the carrier 3, there is a control arm 13 connected to it in a rotationally connected manner via the bearing axis 8, with which the clamping head 6, the support section 4 or the entire carrier 3, on the one hand, in its longitudinal direction or approximately in the direction of the connecting straight line between the axes 5, 8 moves, namely can be pivoted about the pivot axis 11 and with which, on the other hand, the clamping head 6 with the carrier 3 can be moved in the vertical direction or around the bearing axis 8. Due to the design described, the clamping head 6 or the support section 4 does not have to be adjustable in the longitudinal direction relative to the rest of the support 3, but the entire support 3 executes the movement which is necessary to straighten the movement path which is otherwise curved about the bearing axis 8.
  • the control means 10 have a cam control 14 which acts directly on the control arm 13 and which, under positive control, leads to a movement of the support unit consisting of the carrier 3 and the lifting bearing 7 about the pivot axis 11, specifically depending on the stroke or pivoting path of the carrier 3 about the bearing axis 8
  • a rotor 16 runs on a control cam 15, which is expediently arranged fixed on the base 2, so that the control arm 13 at its end remote from the axis 8 only needs to be provided with the rotor 16, for example a roller, and engages with this rotor 16 in a positive manner in the control cam 15.
  • the control curve 15 can accommodate the rotor 16 between opposite and approximately parallel curve flanks, so that the carrier 3 is inevitably controlled in both opposite directions about the pivot axis 11.
  • the rotor 16 expediently lies approximately in a common axial plane with the axes 5, 8.
  • the control cam 15 extends upwards and downwards beyond the height of the bearing axis 8 and is essentially curved over its entire extent.
  • a curve section 17 reaching to an upper end of the control curve 15 serves to straighten the movement path and to limit the stop of the carrier 3 in its lowermost position.
  • a continuously longer and longer curve section 18 of the control curve 15 adjoining the lower end of the curve section 17 serves to guide the carrier 3 during movements beyond the upper end of the straightened movement path in such a way that practically no movements take place about the pivot axis 11, but rather the stroke bearing 7 is secured in the position it occupies when the receiving axis 5 is approximately at the upper or lower end of the straightened movement path.
  • the associated end of the entire path of movement of the carrier 3 is also limited by the fact that the rotor 16 runs to the end of the curve section 18.
  • the path of movement of the rotor 16 or the length of the curve section 17 is correspondingly shorter than the straightened path of movement of the receiving axis 5 , so that there is a reduction ratio and a very compact design.
  • the Curve section 18 is curved approximately in the shape of a part circle, but with a substantially larger radius of curvature corresponding to its distance from the bearing axis 8, while the radius of curvature of the curve section 17 is smaller than its distance from the bearing axis 8.
  • a lifting drive 19 acts on the control arm 13 in a region which is at a greater distance from the bearing axis 8 than from the rotor 16. With the lifting drive 19, the carrier 3 is moved in its movement path and at the same time the rotor 16 is guided along the control curve 15.
  • the linear actuator 19 acts in the manner of a linear drive with a push rod directly on the control arm 13 in such a way that it drives both the pivoting movement about the bearing axis 8 and that about the pivot axis 11.
  • the rollers 21, 22 are fed to the loading device 1 via a roller support 20, the obtuse prism-shaped bearing surface for the outer circumference of the roller 21, 22 ensures that the roller axes always assume the same position relative to the base 2 parallel to the support plane or horizontally, independently the distance between the roller axles due to the different roller diameters from the support.
  • the maximum axle height 23 results and with the smallest diameter of the roller 22 the minimum axle height 24, the maximum axle height being approximately two to three times greater than the minimum axle height 24.
  • the distance between the two shaft heights 23, 24 determines the straightened movement path, namely the alignment path 25, via which the clamping head 6 should also be able to be engaged with any intermediate size of rollers.
  • This alignment 25 is through the curve section 17 or through one with the Pivotal movement about the bearing axis 8 simultaneous pivotal movement about the pivot axis 11 straightened so that it lies vertically above the longitudinal center plane of the support 20.
  • the support 20 is formed by a roller or underfloor conveyor which conveys the support 20 with the roller 21, 22 centered on it parallel to the roller axis or to the receiving axis 5 from the outside into the working area of the carrier 3.
  • the carriers 3 are further upward and rearward from the upper end of the alignment path 25 into a loading position 26 transfer in which they and all other device parts - seen parallel to the receiving axis 5 - lie outside the outer circumference of the largest possible roller 21 when it is supported on the support 20.
  • a completely free roller entrance 27 is thereby formed.
  • the movement path from the upper end of the alignment path 25 to the position 26 is an approximately part-circular arc path controlled by the curve section 18, which adjoins the alignment path 25 at an obtuse angle that deviates by only a few degrees of angle of 180 ° and whose arc angle can be less than 90 ° .
  • the roller 21 lies between the planes of the carriers 3, these can be pivoted back again, so that the respective clamping head 6 is moved freely from the outer circumference of the roller 21 along its associated end face into a position in which its receiving axis 5 is approximately coaxially with Roller axis lies.
  • the carrier 3 or the clamping heads 6 are then moved towards each other so far that they engage in the hub opening of the roller 21 or 22 and thereby positively connected to the roller are.
  • the carrier 3 is pivoted upwards again by the lifting drive 19 into a roll-off position in which the material web can be pulled off the outer circumference of the roll 21 for processing.
  • the rolling position can coincide with the loading position 26 or lie between this and the upper end of the alignment path 25.
  • the respective base 2 is angular with an upright angle leg 28 and an approximately horizontal angle leg 29 adjoining its lower end, which projects freely in the direction of the support 20.
  • the two carriers 3 are arranged on a common support shaft 30 lying in the bearing axis 8 in a rotationally locking but steplessly longitudinally displaceable manner and for this purpose each have a support hub 31 surrounding the support shaft 30 at the rear end, which is spaced from the inside of the associated base 2 .
  • the support shaft 30 passes through the protruding corner between the two base legs 28, 29 of the associated base 2 and, including the lifting bearing 7, lies below the upper end of the base leg 28 and behind the front end of the base leg 29.
  • the lifting bearing 7 has a bearing outer hub 32 surrounding the support shaft 30, which lies adjacent to the outside of the associated support 3 in the recessed corner between the base legs 28, 29 and from the top of which the rigidly connected support link 12 projects upward.
  • This support arm 12 is pivotally mounted between two support arms 34 about the pivot axis 11, which protrude from the upper end of the base leg 28 approximately parallel to the support 3 so that the lifting bearing 7 with the support shaft 30 by a few angular degrees with respect to the base 2 without contact around the Swing axis 11 can swing.
  • the support shaft 30 is freely rotatable in the outer hub 32.
  • a control hub 33 is arranged on the associated end of the support shaft 30 in a rotationally locking and axially secured manner, which carries the control arm 13 and overlaps the base 2 in a plan view according to FIG.
  • a cylinder 35 of the lifting drive 19 with a drive bearing 36 is pivotally mounted about an axis approximately parallel to the axes 5, 8, 11, which lies in the region of the lower end of the upright cylinder 35.
  • the end of the hanging piston rod of the cylinder 35 is articulated to the control arm 13 via a connecting joint 37.
  • the central axis of the linear drive 19 lies approximately at right angles to the axial plane of the rotor 16 and the bearing axis 8, so that favorable force relationships result.
  • the control curve 15 extends approximately over the entire height of the base leg 28 and extends with its lower end into the area of the base leg 29.
  • control means 10 can be encapsulated or protected in a housing-like manner.
  • the two carriers 3 are opposite with a longitudinal adjustment 38 and / or synchronously in the same direction the support shaft 30 slidably.
  • a bearing hub 39 is arranged on the support shaft 30 in a rotationally locking but axially secured manner such that it lies immediately adjacent to the inside of the outer hub 32.
  • Two support arms 41 protrude obliquely upwards and forwards from this bearing hub 39, between which a drive 40, for example a gear or angle motor, is fastened and to which one is at the level of the pivot axis 11 when the carrier 3 is positioned according to FIG lying adjusting spindle 42 is rotatably mounted.
  • the drive 40 located above the carrier 3 serves for the stepless drive of the spindle 42 and pivots with the carrier 3 about the bearing axis 8 and about the pivot axis 11, being in front of and in the loading position behind the pivot axis 11.
  • a spindle nut 43 or the like is provided, in which the spindle 42 engages in such a way that rotational movements of the threaded spindle 42 lead to longitudinal displacements of the carrier 3.
  • the carriers 3 can also be set to different roller lengths and in such a way that the roller they carry lies in the region of different longitudinal sections of the supporting shaft 30 which is substantially longer than it. The adjustability is possible regardless of the position of the carrier 3.
  • the carrier 3 is transferred to the loading position 26 and the roller is moved with the support 20 parallel to the receiving axis 5 into the area between the pivoted carrier 3.
  • the carriers 3 are then lowered and their clamping heads 6 are brought into engagement with the roller by axial movement.
  • the arc path about the bearing axis 8 straightened the curve section 17 inevitably or positively, so that the receiving axis 5 runs over the vertical alignment path 25. If the roller is raised upward beyond the upper end of the alignment path 25, then the curve section 18 is effective, which moves the receiving axis 5 up to the upright upward loading position 26 of the carrier 3 along a circular path.
  • FIGS. 3 and 4 the same reference numerals are used for corresponding parts as in FIGS. 1 and 2, but with different letter indices.
  • the bearing axis 8 lies approximately vertically above the pivot axis 11 via the alignment path, so that the supporting link 12a is provided in an approximately vertical position.
  • the lifting drive 19a engages on a drive arm 44 separate from the control arm 13a, which is arranged on the support shaft with a hub separate from the control hub or with the bearing hub 39a on the inside of the suspension arm 12a.
  • the support arm 12a projects like the lift drive 19a over the top of the relatively low base 2a, the lift drive 19a projecting upward to the connecting joint 37a being in front of the support link 12a and being provided approximately parallel to the support link 12a in each position of the support 3a.
  • the drive 40a of the longitudinal adjustment is mounted on the drive arm 44.
  • the cam control 14a is here on a stand 28a separate from the base 2a provided, which is at a distance behind the base 2a and the control curve 15a is provided so that its ends are approximately vertically one above the other.
  • the curve section 18a is selected so that the movement path of the receiving axis 5a from the upper end of the alignment path to the loading position is substantially flattened compared to a pure circular movement about the fixed bearing axis 8a, because during this movement the bearing axis 8a is pivoted backwards, until in the loading position 26a the axial plane of the axes 8a, 11a is inclined approximately 45 ° backwards to the stand 28a and the 'bearing axis 8a is substantially lower than during the movement path over the alignment path.
  • the conveyor 45 for the support 20a is shown in more detail. It has driven roller carriages which carry individual segments of the support 20a lying one behind the other and essentially the same on their upper sides.
  • control curve 15b has only the curve section 17b for the alignment path, while the rest of the movement path is determined by a curve control which is brought about by a drive 18b.
  • This control drive 18b embodied, for example, as a cylinder drive, pivots the supporting link 12b relative to the base 2b in approximately the same way as the curve section 18b according to FIG. 3, namely simultaneously with the movement of the carrier 3b by the lifting drive 19b and / or separately therefrom.
  • the rotor 16b lifts completely from the control curve 15b, so that the control curve 15b is then not effective.
  • the curve section 17b is not formed by a groove, but only by a single convex circumferential curve or curve flank against which the rotor 16b is controlled by the control drive 18b via the Alignment path created and from which the rotor 16b is lifted over the remaining movement path by the control drive 18b and by the lifting drive 19b.
  • the control drive 18b can also lie essentially in front of the supporting link and cross in a side view according to FIG. 4 with the lifting drive 19b in that it is inclined upwards and backwards from the front end of the base 2b. In the loading position, the control drive 18b is thereby inclined flatter to the rear than in the position associated with the alignment path, so that it in no way hinders the insertion of the rollers along the support 20b. In a corresponding manner, the lifting drive 19b is pivoted in the loading position 26b into a release position inclined to the rear.
  • the loading device can work fully automatically, with a corresponding control device coordinating the movement sequences described, namely transferring the roller into the area of the carrier, then bringing the carrier into engagement with the roller and finally lifting it into the unwind position.
  • Sensors can determine the shaft heights and the length of the roll and control the roll carriers accordingly. The removal of a roll can also be controlled automatically.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Transportation (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Replacement Of Web Rolls (AREA)
  • Tyre Moulding (AREA)
EP94107813A 1993-06-04 1994-05-20 Dispositif de chargement pour du matériau, en particulier pour des bobines de papier Expired - Lifetime EP0629574B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4318632A DE4318632A1 (de) 1993-06-04 1993-06-04 Ladevorrichtung für Material-Rollen, insbesondere für Papier-Rollen
DE4318632 1993-06-04

Publications (2)

Publication Number Publication Date
EP0629574A1 true EP0629574A1 (fr) 1994-12-21
EP0629574B1 EP0629574B1 (fr) 1998-01-28

Family

ID=6489665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94107813A Expired - Lifetime EP0629574B1 (fr) 1993-06-04 1994-05-20 Dispositif de chargement pour du matériau, en particulier pour des bobines de papier

Country Status (3)

Country Link
US (1) US5863175A (fr)
EP (1) EP0629574B1 (fr)
DE (2) DE4318632A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19824695A1 (de) * 1998-06-03 1999-12-09 Bhs Corr Masch & Anlagenbau Abroll-Vorrichtung

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19523286C1 (de) * 1995-06-27 1996-10-10 Reifenhaeuser Masch Coilmanipulator in einer Wickelvorrichtung zum Aufwickeln einer Kunststoffbahn
NL1015560C2 (nl) * 2000-06-28 2002-01-02 Don Hoogerwerf Hefinrichting.
DE102014223965B4 (de) * 2014-11-25 2021-01-28 Koenig & Bauer Ag Vorrichtung zum Aufwickeln einer Materialbahn zu einer Rolle oder zum Abwickeln der Materialbahn von der Rolle
CN109516194A (zh) * 2018-12-05 2019-03-26 温州市维凯机械有限公司 一种全自动装料装置
CN114261818B (zh) * 2021-12-31 2024-06-14 华晓精密工业(苏州)有限公司 用于极片对接的姿态调整平台

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2180226A (en) * 1985-09-10 1987-03-25 Manuel Torres Reel stand
US4930713A (en) * 1989-03-10 1990-06-05 Mitsubishi Jukogyo Kabushiki Kaisha Mill roll stand
JPH02182650A (ja) * 1989-01-10 1990-07-17 Mitsubishi Heavy Ind Ltd ロール状原紙供給装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3587888A (en) * 1969-03-03 1971-06-28 William H Warren Transferring horizontal batches of articles to a different level
US4090624A (en) * 1976-01-26 1978-05-23 Krein Vernon R Round bale transporter

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2180226A (en) * 1985-09-10 1987-03-25 Manuel Torres Reel stand
JPH02182650A (ja) * 1989-01-10 1990-07-17 Mitsubishi Heavy Ind Ltd ロール状原紙供給装置
US4930713A (en) * 1989-03-10 1990-06-05 Mitsubishi Jukogyo Kabushiki Kaisha Mill roll stand

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 14, no. 460 (M - 1032) 4 October 1990 (1990-10-04) *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19824695A1 (de) * 1998-06-03 1999-12-09 Bhs Corr Masch & Anlagenbau Abroll-Vorrichtung
EP0968945A2 (fr) * 1998-06-03 2000-01-05 BHS CORRUGATED MASCHINEN- UND ANLAGENBAU GmbH Dispositif de déroulage
EP0968945A3 (fr) * 1998-06-03 2000-08-23 BHS CORRUGATED MASCHINEN- UND ANLAGENBAU GmbH Dispositif de déroulage
US6267320B1 (en) 1998-06-03 2001-07-31 Bhs Corrugated Maschinen-Und Anlagenbau Gmbh Unroll device

Also Published As

Publication number Publication date
DE59405150D1 (de) 1998-03-05
US5863175A (en) 1999-01-26
DE4318632A1 (de) 1994-12-08
EP0629574B1 (fr) 1998-01-28

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