EP0759847A1 - Transport device for a continuous moving web of material, in particular a stretching device for plastic film webs - Google Patents
Transport device for a continuous moving web of material, in particular a stretching device for plastic film websInfo
- Publication number
- EP0759847A1 EP0759847A1 EP96907481A EP96907481A EP0759847A1 EP 0759847 A1 EP0759847 A1 EP 0759847A1 EP 96907481 A EP96907481 A EP 96907481A EP 96907481 A EP96907481 A EP 96907481A EP 0759847 A1 EP0759847 A1 EP 0759847A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- material web
- guide rail
- linear motor
- action
- distance
- 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.)
- Withdrawn
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C55/00—Shaping by stretching, e.g. drawing through a die; Apparatus therefor
- B29C55/02—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets
- B29C55/10—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial
- B29C55/12—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial biaxial
- B29C55/16—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial biaxial simultaneously
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C55/00—Shaping by stretching, e.g. drawing through a die; Apparatus therefor
- B29C55/02—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets
- B29C55/10—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial
- B29C55/12—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial biaxial
- B29C55/16—Shaping by stretching, e.g. drawing through a die; Apparatus therefor of plates or sheets multiaxial biaxial simultaneously
- B29C55/165—Apparatus therefor
Definitions
- Transport device for a moving material web in particular a stretching system for plastic film webs
- the invention relates to a transport device for material webs, in particular to a stretching system for plastic film webs according to the preamble of claim 1, 3 or 4.
- Devices for stretching a moving material web are used in particular in the production of plastic films.
- transverse, longitudinal and simultaneous stretching systems are known in which the material web, i.e. the plastic film web is simultaneously subjected to longitudinal and transverse stretching.
- clips or clip carriages are used, which are moved along a guide device, usually a guide rail.
- a device for the simultaneous biaxial stretching of a moving material web, in particular a plastic web has become known, for example, from DE 37 41 582 C2.
- a plurality of clips or clip carriages run along guide rails, which are connected to one another by means of chain shear levers. Due to the specific separate guidance of the chain levers, the distance between the individual tenter carriages can be deliberately increased in the stretching zone, so that the longitudinal and transverse stretching ratios can be adjusted.
- tensioning devices are provided on the clip wagons, by means of which the edge of the material web to be treated can be gripped and moved.
- a device for spreading and fixing film webs has become known, for example, from DE 40 06 440 C2, in which the individual chain or clip wagons are moved by means of a revolving transport chain, the distance between the individual clip wagons remaining essentially unchanged.
- Supporting rollers are guided horizontally.
- the bearing forces on the clapper body relative to the guide rail are significantly minimized compared to conventional solutions.
- the advantages according to the invention can already be partially realized when using a so-called dual rail, that is to say two guide rails which are generally arranged one above the other and thus transversely to the material web, and the linear motor comprising an upper and lower linear motor drive are arranged in such a way that the position of the upper guide rail and the upper linear drive in the direction of the material web is reversed from their sequence to the linear motor and the lower guide rail below.
- the action lines are the connecting lines of the points of application of the forces acting in the longitudinal direction and thus parallel to the guide rail, which meet at a common point.
- the tipping and thus bearing or frictional forces introduced onto the clip wagon should be kept as low as possible.
- the bearing forces acting on the clip carriage are as low as possible if these forces are symmetrical to the clamping point, i.e. to the clamping or folding point, at which the material web is held clamped on the tipper carriage.
- the geometry is chosen so that the forces applied to the dolly carriage (motor drive forces; forces introduced by the guide rail system, in particular friction forces, etc.) lead to the lowest possible introduction of torque and thus contribute to less stress on the dome bearing.
- Double rail systems are preferred
- the drive device can also be designed in such a way that a linear motor drive is provided on both sides of the guide rail. In principle, this can also be achieved by integrating the guide rail into the linear motor.
- the tenter geometry according to the invention ensures that the forces acting on the tenter carriage are largely balanced, that is to say they cancel each other out as symmetrically as possible, so that the introduction of force of the material web (that in the manufacture of plastic films, particularly in the longitudinal or Simultaneous stretching occurs) is minimized.
- An embodiment is also possible within the scope of the invention, in which not only one drive device provided on opposite sides of the clip body and engaging on the clip body, in particular in the form of the linear motor drive mentioned, but only one only drive device in the form of a side and preferably comes to rest on the side of the guide rail or guide rail sections opposite the clamped material web edge.
- FIG. 1 a schematic cross-sectional illustration perpendicular to the longitudinal direction of a guide rail and a clip body which can be moved longitudinally thereon;
- FIG. 2 a schematic side view of two clip bodies which are moved adjacent to one another and along the guide rail;
- Figure 3 a schematic representation comparable to the embodiment of Figure 1 to explain the occurring force ratios and the geometry of the Kluppenwa ⁇ carriage and the drive and guide rail system;
- FIG. 4 a cross-sectional representation modified from FIG. 1;
- FIG. 5 another exemplary embodiment modified from FIG. 1 in a schematic cross section transverse to the longitudinal direction of the guide rail;
- FIG. 6 a further modified exemplary embodiment of FIG. 1; and FIG. 7: an exemplary embodiment modified to FIG. 3.
- a clip body 1 is shown in a schematic front view, which can be moved along a guide rail system 3 — that is, perpendicular to the plane of the drawing — by means of a linear motor drive 5.
- the clip body 1 comprises a clamping or clip lever 9 which can be pivoted about a pivot axis 7.
- a material web in the case of plastic film manufacture a plastic film web to be stretched at the edge between the lower clamping point 9 'of the clip lever 9 and the so-called clip table 13 during the movement of the material web and in particular during of the stretching process is kept clamped. As a result, tensile forces are introduced onto the clip body 1 via the material web.
- the guide rail system 3 consists of an upper guide rail 3 'and a lower guide rail 3', which in the exemplary embodiment shown in FIG. 1 lie one above the other in a common guide rail plane, which in the exemplary embodiment shown is perpendicular to the material plane 11 and thus perpendicular to the material web tensile forces ZK.
- cross-sectionally U-shaped sliding bodies 17 are provided, which are held and fastened in a suitable manner in the clip body 1 (for example, by means of a positive connection, that is, with the formation of interlocking parts on the sliding body and / or on the adjacent section of the
- the guide recesses 19 engage in one another on the clip body 1, but alternatively or in addition there is also a non-positive connection
- Anchoring of the sliding body 17 is possible, for example, by using an adhesive or vulcanization technique).
- the sliding bodies 17 are generally of shorter dimensions with respect to the length of the claw body 1 running parallel to the guide rail 3, so that, for example, at least two spaced-apart sliding bodies 17 are provided on the respective upper and lower guide rail sections 3 'and 3 " (Likewise, opposite angular sliding body sections in the relevant groove-shaped guide recesses 19 in the claw body 1 can also be designed to be movable therewith.)
- FIG. 2 shows a schematic side view with two adjacent cupping bodies 1, which are shown between one upper rail 3 'and a lower rail 3 "can be moved. In the side view from the side of the material web 11, a section of the lower guide rail 3 "upstream linear motor 5" is shown. The overhead linear motor 5 * lies behind the upper guide rail 3 '.
- the upper and lower sliding bodies 17 are shown schematically, by means of which the clip carriages are slidably supported on the guide rail 3 1 or 3 ".
- the two guide rails 3 'and 3 are part of a cross-sectionally C-shaped guide rail support 21, with a linear drive 5' on the upper guide rail support section 21 'having a laminated core 25 penetrated by a large number of wire windings to form a winding head 23 and lower guide rail section
- the magnets required for the linear motor drive are in each case at the adjacent sections on the clip body 1.
- te, ie permanent magnets 29 provided.
- the upper linear motor 5 ' is on the side of the upper guide section 3' opposite the material web and the linear motor 5 '' on the side of the lower guide rail section 3 facing the material web "arranged.
- the clip construction is now selected such that the clamping point 35, at which the edge of the material web between the lower clamping point 9' of the clip lever 9 and the clip table 13 comes to lie as close as possible to an intersection S, through which lines of action or connecting lines of the points of application of the occurring forces are formed.
- this is the line of action or connecting line MK, which is caused by the motor forces, ie the propulsion or braking forces generated and caused in particular by the linear motor drive and around the active or connecting line RK formed by the frictional forces, the points of action of the active line MK being approximately in the middle of the linear motor drive between the primary part linear motor 5 ', 5 "and the center of the adjacent permanent magnet selected 29 horizontally.
- the points of attack of the guide system 3 coincide with the end faces 41 of the guide rails 3 ', 3 "which are pointing towards one another.
- the lines of action represent the connecting lines between the respective points of application of the forces acting on the clip carriage. In fact, this represents a certain simplification in two respects. Because on the one hand, it is not a "point of attack”, but rather attack vectors running parallel to the feed movement of the clip, that is to say parallel to the linear motor or to the guide rail, that is to say directed quantities, the corresponding tilting and torques on the Transfer clip body and thereby contribute to increasing the bearing and frictional moments.
- resulting attack vector that is perpendicular to the plane of the drawing f all this does not necessarily have to lie in the middle of the linear motor (or in the middle of the permanent magnet), but can also be at least slightly offset off-center.
- the actual position of the resulting force-attack vector A MK results from an integral sum analysis.
- the lines of action MK and RK drawn in FIG. 1 thus represent the resultant lines of action of the averaged attack vectors which result in a simplified form and which act perpendicularly to the plane of the drawing in FIG. 1 with respect to the linear motors and the guide rail system on the clip body 1.
- intersection S does not come to lie exactly in the center of the length of the lines of action.
- FIG. 3 largely corresponds to the exemplary embodiment according to FIG. 1 and differs only in that, in the schematically represented exemplary embodiment according to FIG. 3, the two guide rails 3 'and 3 "are also flat if they are laterally offset from each other.
- the geometry is such that the clamping point 35 is arranged so that the vertical, perpendicular to
- Distance a measured at the material web level is less than or equal to 0.6 times the height H, which is formed by the distance between the guide rail sections 3 'and 3 "formed perpendicular to the material web. Furthermore, the clamping point 35 is arranged such that the horizontal Ab ⁇ stand b is less than or equal to 0.6 times the guide distance F of the clip carriage, the guide distance of the clip carriage is shown in Figure 2. It essentially corresponds to the maximum outside distance of the one or more sliding bodies 17, which may be with the Length of the clip body 1 coincide or at least partially can correspond wisely.
- the size of the guide distance with respect to the roller bearing results from the center distance between a leading and trailing roller, about which the Kluppenwagen 1 is guided.
- the center distance corresponds to the distance of the line contact of the castors, which are offset in the longitudinal direction.
- the horizontal distance b which is thus defined parallel to the plane of the material web, is less than or equal to the pitch T of the dolly carriage, i.e. less than or equal to the small ⁇ most distance between two tenter tables 13 when gripping the material web, in the case of a plastic film web before gripping the films before longitudinal or simultaneous stretching.
- the division T is shown in Figure 2.
- the overall arrangement has a 180 "symmetry, ie that the upper guide rail 3 'and the upper linear drive 5' to the intersection S have a 180 ° symmetry with the lower guide rail 3 "and to the underlying linear motor 5".
- Line of action MK, RK but from it, for example deviates less than 50%, preferably less than 40%, 30%, 20% and in particular 10% of the respective total length of the line of action MK or RK.
- FIG. 4 shows an arrangement substantially corresponding to the schematic representation according to FIG. 3, in which the upper and lower guide rails 3 ', 3 "lie differently close to the material web.
- the arrangement here is such that the line of action MK and the Cut the line of action RK so that its intersection S comes to lie exactly at the clamping point 35 on the clip table 13.
- FIG. 5 shows an embodiment in which the upper and lower guide rails 3 ', 3 "are essentially integrated in the center of the linear motor 5', 5". If the upper and lower linear drives 5 ', 5 "are considered to be the respective unit for the linear drive, the line of action of the drive forces MK would be congruent with the line of action of the guide system RK, namely perpendicular to the material web plane 11.
- the upper and lower linear ⁇ motor can also be interpreted as a double linear motor drive, so that here two motor characteristic curves MK 'and MK "are alternately formed, which in this embodiment are again located in a common plane perpendicular to the material web 11, guide rails 3', 3 ", ie cut with the line of action RK of the guide rail system 3 at the intersection S (at the level of the material web plane 11).
- the horizontal distance b between the intersection S and the clamping point 35 or the vertical distance a become, as explained above , chosen.
- a modified exemplary embodiment is shown on the basis of FIG. 6, in which only one linear motor 5 is provided in a vertical orientation, which is at the level of FIG Material web 11 is arranged symmetrically.
- the clip body 1 has a vertically oriented permanent magnet 29.
- the guide rails 3 'and 3 are in turn arranged perpendicular to the plane of the material web 11 one above the other in a common plane.
- the force application point of the motor forces is shown here in the middle between the linear motor 5 and the permanent magnet 29 and is denoted by A MK in FIG. 6. Since a second linear motor for driving the clip body shown in FIG. 6 is missing, the optimal geometry must be selected here such that the vertical distance a from the center of the line of action of the guide system RK to the clamping point 35 is less than or equal to 0.6 times the height H (namely that of the vertical distance between the guide rails) and the horizontal distance b between the clamping point 35 on the clamp table both to the force application point A MK and to the guide rail system line of action RK is less than or equal to 0.6 times the guide distance F or the 0 , 4 times the division T between two tenter tables (when gripping the film before stretching) corresponds.
- the two guide rails and possibly also the two linear motors can be arranged in the same order lying transversely to the material web, that both lines of action RK and MK are not, or at least not in the area between the guide rails or between cut the linear motors.
- the desired advantages can still be realized at least if the clamping point 35 is placed so close to the two effects that the distance between the clamping point and the line of action RK as well as the distance from the clamping point to the line of action MK less than or equal to 0.6 times the guide distance F or else corresponds at least to 0.4 times the division T between two Klup ⁇ pentician.
- the clamping point 35 should not be further than a maximum of 0.6 times the height H (ie the vertical distance between the guide rails) from the center of the line of action RK or MK.
- FIG. 7 in which a basic illustration that is slightly modified from FIG. 3 is shown.
- the exemplary embodiment according to FIG. 7 differs from that according to FIG. 3 solely in that the upper and lower linear motors with their active surface are not aligned parallel to the plane of the material web 11, but rather are tilted relative thereto.
- the clapper carriage would also have to be adapted so that the permanent magnet 29 provided on the clapper carriage is oriented at the same angle, so that only a usual air gap between the appropriately aligned permanent magnet and the lower active surface 41 of the respectively assigned linear ⁇ motors 5 'and 5 ".
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Shaping By String And By Release Of Stress In Plastics And The Like (AREA)
- Advancing Webs (AREA)
- Linear Motors (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19510141 | 1995-03-21 | ||
DE19510141A DE19510141C1 (en) | 1995-03-21 | 1995-03-21 | Linear motor transporter mounted on double rail system to stretch esp. plastic sheet |
PCT/EP1996/001114 WO1996029191A1 (en) | 1995-03-21 | 1996-03-14 | Transport device for a continuous moving web of material, in particular a stretching device for plastic film webs |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0759847A1 true EP0759847A1 (en) | 1997-03-05 |
Family
ID=7757222
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96907481A Withdrawn EP0759847A1 (en) | 1995-03-21 | 1996-03-14 | Transport device for a continuous moving web of material, in particular a stretching device for plastic film webs |
Country Status (6)
Country | Link |
---|---|
US (1) | US5737812A (en) |
EP (1) | EP0759847A1 (en) |
JP (1) | JP3998265B2 (en) |
KR (1) | KR100196021B1 (en) |
DE (1) | DE19510141C1 (en) |
WO (1) | WO1996029191A1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20040122391A1 (en) * | 2002-12-23 | 2004-06-24 | Kimberly-Clark Worldwide, Inc. | Apparatus and method for magnetically controlling a moving web of material |
AT506369B1 (en) * | 2008-01-23 | 2011-08-15 | 3S Swiss Solar Systems Ag | CLAMPING RAIL FOR A MEMBRANE OF A MEMBRANE PRESS |
DE102008021506A1 (en) * | 2008-04-30 | 2009-11-05 | Lindauer Dornier Gmbh | Device for transverse stretching of film webs |
DE102013011965A1 (en) * | 2013-07-18 | 2015-01-22 | Brückner Maschinenbau GmbH & Co. KG | Linear motor driven transport system, in particular stretching system |
KR20150052683A (en) * | 2013-11-06 | 2015-05-14 | 삼성전자주식회사 | Tenter apparatus |
DE102014011513A1 (en) | 2014-07-31 | 2016-02-04 | Brückner Maschinenbau GmbH & Co. KG | Tackle with toggle arrangement |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3457608A (en) * | 1965-09-15 | 1969-07-29 | Dornier Gmbh Lindauer | Chain track assembly for tenter clips |
JPS4838779B1 (en) * | 1970-07-06 | 1973-11-20 | ||
FR2147876B1 (en) * | 1971-08-05 | 1974-03-29 | Cellophane Sa | |
US3748704A (en) * | 1972-01-04 | 1973-07-31 | Kampf Maschf Erwin | Clamp for biaxial stretching machines |
GB1442113A (en) * | 1973-06-13 | 1976-07-07 | Bakelite Xylonite Ltd | Web stretching apparatus |
FR2317076A2 (en) * | 1975-07-07 | 1977-02-04 | Cellophane Sa | Flat drawing plastic films with self-propelling grippers - preventing wastage of film edges due to arching |
DE3333938C2 (en) * | 1983-09-20 | 1987-02-05 | Brückner Trockentechnik GmbH & Co KG, 7250 Leonberg | Transport chain for clamping machines |
DE3339150A1 (en) * | 1983-10-28 | 1985-05-09 | H. Krantz Gmbh & Co, 5100 Aachen | COMBINED NEEDLE CLAMP CHAIN |
DE3512417A1 (en) * | 1985-04-04 | 1986-10-16 | Brückner Trockentechnik GmbH & Co KG, 7250 Leonberg | CLAMPED TENSION CHAIN |
DE206317T1 (en) * | 1985-06-25 | 1987-04-09 | Mitsubishi Jukogyo K.K., Tokio/Tokyo | RECKING MACHINE. |
JPS63141252A (en) * | 1986-12-02 | 1988-06-13 | Hitachi Ltd | Low pressure discharge lamp |
DE3716603C1 (en) * | 1987-05-18 | 1989-03-09 | Dornier Gmbh Lindauer | Device for simultaneous biaxial treatment of film webs |
DE3741582A1 (en) * | 1987-12-08 | 1989-06-22 | Brueckner Maschbau | Apparatus for stretching a moving web of material |
US5051225A (en) * | 1988-06-22 | 1991-09-24 | E. I. Du Pont De Nemours And Company | Method of drawing plastic film in a tenter frame |
US5072493A (en) * | 1988-06-22 | 1991-12-17 | E. I. Du Pont De Nemours And Company | Apparatus for drawing plastic film in a tenter frame |
DE3928454A1 (en) * | 1989-08-29 | 1991-03-07 | Kampf Gmbh & Co Maschf | CLOCK AND TRANSPORT DEVICE |
DE4015309C2 (en) * | 1989-11-14 | 1998-04-09 | Dornier Gmbh Lindauer | Clip chain with infinitely adjustable division for simultaneous, biaxial treatment of film webs |
DE4006440A1 (en) * | 1990-03-01 | 1991-09-05 | Brueckner Maschbau | DEVICE FOR WIDTH DISTANCE AND FIXING OF FILM COATINGS |
-
1995
- 1995-03-21 DE DE19510141A patent/DE19510141C1/en not_active Expired - Fee Related
-
1996
- 1996-03-14 KR KR1019960706333A patent/KR100196021B1/en not_active IP Right Cessation
- 1996-03-14 US US08/737,822 patent/US5737812A/en not_active Expired - Fee Related
- 1996-03-14 JP JP52805796A patent/JP3998265B2/en not_active Expired - Fee Related
- 1996-03-14 EP EP96907481A patent/EP0759847A1/en not_active Withdrawn
- 1996-03-14 WO PCT/EP1996/001114 patent/WO1996029191A1/en not_active Application Discontinuation
Non-Patent Citations (1)
Title |
---|
See references of WO9629191A1 * |
Also Published As
Publication number | Publication date |
---|---|
KR100196021B1 (en) | 1999-06-15 |
US5737812A (en) | 1998-04-14 |
KR970702783A (en) | 1997-06-10 |
DE19510141C1 (en) | 1996-08-14 |
JPH10500914A (en) | 1998-01-27 |
JP3998265B2 (en) | 2007-10-24 |
WO1996029191A1 (en) | 1996-09-26 |
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