JP2009154999A - Material supply apparatus and laminate manufacturing apparatus using the same - Google Patents

Abstract

An object of the present invention is to provide a material supply device that is excellent in looseness absorption of sheet material.
A circumferential length difference absorbing mechanism 30 for absorbing a circumferential length difference between a plurality of sheet materials 4a, 4b, and 4c of a laminated roll 5 is attached to an axially opposite end side of a winding core 6 via a bearing. 35, 35, rotating arms 31, 31 and 33, 33 pivotally supported by both mounting bases 35, 35, and both ends pivotally supported on the rotation free end side of the pair of rotating arms, between the pair of rotating arms. Tension applying rolls 32, 34 suspended substantially in parallel to the winding core, and urging means 42, 42 for pressing the tension applying rolls 32, 34 in a direction to absorb the slack of the sheet materials 4b, 4c. It is prepared for. Then, as the rotational force mg × sin θ of the rotating arms 32 and 34 caused by the own weight increases, the rotating arms 32 and 34 are pushed back with a large force Fc × sin α, thereby reducing the change in the rotational force of the rotating arms 32 and 34. Force change reduction means 51 and 53 are further provided.
[Selection] Figure 4

Description

  The present invention relates to a material supply apparatus and a laminate manufacturing apparatus using the material supply apparatus.

  Conventionally, as a laminated plate manufacturing apparatus, a plurality of rolls each wound with a plurality of sheet materials and a plurality of sheet materials unwound from the plurality of rolls are laminated and thermally bonded to each other while being passed in a laminated state. And a product winding device that winds up the laminated plate from the pressing device (see, for example, Patent Document 1).

  For this reason, in the material supply apparatus for supplying a plurality of sheet materials to the press apparatus, at least the number of sheet supporting members that support each roll is required, so that the plurality of roll supporting parts do not interfere with each other. In order to install, a material supply apparatus will enlarge.

If a plurality of roll support parts are arranged so that the material supply device does not increase in size, the plurality of roll support parts come close to each other, and the roll material is attached to the roll support part at the time of setting, or the sheet material is pressed. Work to insert into the device becomes difficult.
JP-A-5-42555 Japanese Patent Laid-Open No. 9-1590

  Therefore, the present inventor made a roll in the form of a roll in a state where a plurality of sheet materials are laminated, and made a laminated roll, and mounted the laminated roll on a laminated roll support part. I came up with a way to pull out.

  According to this method, since a plurality of roll support portions can be combined as one laminated roll support portion, the apparatus can be greatly reduced in size. However, when the sheet material is unwound from such a laminating roll, the amount of unwinding increases as the outer sheet material increases due to the circumferential length difference of each sheet material. There is a risk that wrinkles and creases may be formed when the layers are heat pressed.

  In view of this, a mechanism provided with a circumference difference suction mechanism (see, for example, Patent Document 2) for absorbing the circumference difference can be considered. The present inventor has shown an example of the circumference difference absorption mechanism as shown in FIG. I came up with something. In the circumferential length difference absorbing mechanism shown in FIG. 21, a tension-adding roll 32 is pivotally supported on a rotating arm 31B that is rotatably supported, and the tension-adding roll 32 is pressed against a sheet material 4b that causes slack. In this way, the slack of the sheet material 4b is absorbed. In this case, since the force mg × sin θ urged to the sheet material 4b due to gravity changes depending on the rotation posture of the rotary arm 31B, the urging force is small when such a change in the urging force is large. There is a possibility that a scene in which the sheet material is inferior in looseness absorption due to being too large or too large may occur.

  Accordingly, an object of the present invention is to provide an apparatus for manufacturing a laminated board that is excellent in slack absorption of a sheet material and a material supply apparatus used therefor by reducing the amount of change in rotational force of a rotating arm caused by gravity. .

The invention according to claim 1 is a material supply device that unwinds and supplies each sheet material from a laminating roll that is wound in a roll shape around a core in a state where a plurality of sheet materials are laminated, A circumferential length difference absorbing mechanism that absorbs a circumferential length difference between a plurality of sheet materials is provided, the circumferential length difference absorbing mechanism including a mounting base suspended at both axial ends of the core via bearings, and the both mountings Rotating arms each supported by a base, and tension applied to both ends of the pair of rotating arms that are supported by the rotation free ends and suspended substantially parallel to the winding core between the pair of rotating arms. A roll and biasing means for pressing the tension applying roll against the sheet material in a direction to absorb the slack of the sheet material,
The apparatus further comprises a rotational force change reducing means for reducing a change in the rotational force of the rotary arm by pushing back the rotary arm with a larger force as the rotational force of the rotary arm due to its own weight increases.

  Invention of Claim 2 is the material supply apparatus of Claim 1, Comprising: It is the intermediate roll supported by the said attachment base so that rotation was possible, and was suspended in parallel with the said core between the said attachment bases. And it is further provided with the intermediate roll which contact | abuts to the said sheet material from the opposite side to the said tension | tensile_strength roll.

  A third aspect of the present invention is the material supply apparatus according to the first or second aspect, wherein the rotational force change reducing means is a spring member.

  A fourth aspect of the present invention is the material supply apparatus according to the first or second aspect, wherein the rotational force change reducing means is a driving means capable of changing the direction of the urging force.

  A fifth aspect of the present invention is the material supply apparatus according to the first or second aspect, wherein the rotational force change reducing means is drive means capable of changing the magnitude of the urging force. .

  A sixth aspect of the present invention is the material supply apparatus according to the fourth or fifth aspect, wherein the driving means is an air cylinder.

  A seventh aspect of the present invention is the material supply apparatus according to the fourth or fifth aspect, wherein the driving means is an electric motor.

  Invention of Claim 8 is the material supply apparatus of any one of Claims 1-7, Comprising: The said rotational force change reduction means to the said attachment base of the rotation center side of the said rotation arm to the said attachment base The attachment points are arranged on a straight line in a direction perpendicular to the rotation center of the rotary arm.

  Invention of Claim 9 is a material supply apparatus of any one of Claims 1-8, Comprising: The attachment point by the side of the rotation center of the said rotation arm of the said rotational force change reduction means is the said The mounting base is slidable.

  The invention according to claim 10 is an apparatus for manufacturing a laminated plate, and passes through the material supply device according to any one of claims 1 to 9 and a plurality of sheet materials from the material supply device. And a pressing device that heat-presses a plurality of sheet materials to form a laminated plate.

  According to the first aspect of the present invention, since the circumferential length difference absorbing mechanism that absorbs the circumferential length difference of the plurality of sheet materials drawn from the laminated roll is provided, the multilayer workpiece is drawn when the multilayer workpiece is drawn from the laminated roll. The circumference difference generated between the plurality of sheet materials constituting the sheet can be absorbed by the circumference difference absorption mechanism. As a result, the laminated state of the multilayer workpiece can be stabilized at the sheet inlet of the downstream press device, and manufacturing defects such as wrinkles entering the manufactured laminated plate can be prevented.

  At this time, the force urged to the sheet material is applied by the urging force of the urging means of the circumferential difference absorption mechanism and the rotational force of the rotating arm caused by gravity. The resulting rotational force of the rotating arm changes with the rotational posture of the rotating arm, so that the urging force applied to the sheet material (= the urging force of the urging means of the circumferential length difference absorbing mechanism + the rotating arm resulting from gravity) ) Will change.

  On the other hand, according to the first aspect of the invention, by providing the rotational force change reducing means, the influence of the change in rotational force of the rotary arm caused by gravity can be reduced, and the deflection of the sheet material can be absorbed. Can be improved.

  According to the second aspect of the present invention, since the intermediate roll is further provided, the slack absorption amount of the sheet material can be doubled by the combination of the tension-added roll and the intermediate roll as compared with the structure having only the tension-added roll. .

  According to the third aspect of the present invention, since the rotational force change reducing means is a spring member, the rotational force change reducing means can be configured at low cost.

  According to the fourth aspect of the present invention, since the rotational force change reducing means is a drive means capable of changing the direction of the urging force, even when the rotary arm is installed upside down, the rotary arm caused by gravity is attached. The driving means can be operated so that the influence of the change in the rotational force can be reduced, and the effect of claim 1 can be obtained.

  According to the fifth aspect of the present invention, since the rotational force change reducing means is a driving means capable of changing the magnitude of the urging force, by changing the urging force in accordance with the rotational posture of the rotating arm, It becomes possible to almost completely cancel the rotational force of the rotating arm caused by the above.

  According to the invention described in claim 6, since the driving means is an air cylinder, the structure is simple. In addition, since a constant pressure can be always applied regardless of the rotation posture of the rotary arm, that is, regardless of the expansion / contraction length of the air cylinder, there is an advantage that the urging force can be stably applied. Further, the balance equation can be easily calculated as compared with the case where the rotational force change reducing means is a spring member.

  According to the seventh aspect of the invention, since the driving means is an electric motor, the structure is simple. In particular, since the urging force can be easily changed by adjusting the amount of current, it can be easily applied as a drive unit that can change the magnitude of the urging force.

  According to the eighth aspect of the present invention, since the attachment point on the rotation center side of the rotation arm of the rotational force change reducing means is arranged in a straight line perpendicular to the rotation center of the rotation arm, the rotation arm However, a similar balance equation is established between the state where the pendulum is swung on one side and the state where the pendulum is swung on the other side, and the effect of the rotational force variation reducing means can be exhibited over a wide rotation angle.

  According to the ninth aspect of the present invention, since the attachment point on the rotation center side of the rotary arm of the rotational force change reducing means is slidable, even when the attachment angle of the attachment base is changed, the rotational force change is reduced. The attachment point on the rotation center side of the rotation arm of the means can be arranged on a straight line in a direction perpendicular to the rotation center of the rotation arm. Therefore, the effect of claim 8 can always be obtained regardless of the mounting angle of the mounting base.

  According to the invention of claim 10, a laminate is obtained by thermally welding a plurality of sheet materials by passing through a material supply device and a plurality of sheet materials from the material supply device while passing in a laminated state. In the manufacturing apparatus of a laminated board provided with the pressing apparatus, the same effects as those of the first aspect can be obtained.

  Embodiments of the present invention will be described below with reference to the drawings.

(First embodiment)
The manufacturing apparatus of the laminated board of 1st Embodiment is demonstrated referring FIGS.

"Outline of laminated board manufacturing equipment"
First, the overall structure of the laminate manufacturing apparatus 10 of the present embodiment will be schematically described. As shown in FIG. 2, the laminated board manufacturing apparatus 10 according to the present embodiment includes a material supply device 12, a press device 13, and a product winding device 14.

  The material supply device 12 unwinds the multilayer workpiece 8 (a laminate of a plurality of sheet materials 4a, 4b, and 4c) from each lamination roll 5 and supplies it to the workpiece supply port of the press device 13. Is a laminate 9 by thermally welding (laminating) a plurality of sheet materials 4a, 4b, 4c constituting the multilayer workpiece 8 by thermocompression bonding while allowing the multilayer workpiece 8 from the material supply device 12 to pass through. The laminate 9 thus laminated is wound up by the product winding device 14.

  In addition, the manufacturing method of the lamination | stacking roll 5 is performed by winding up to the core 6 in the roll shape in the state which laminated | stacked the several elongate sheet material 4a, 4b, 4c as shown in FIG. As shown in FIG. 1, a laminating roll manufacturing apparatus 1 for manufacturing the laminating roll 5 includes single-layer rolls 3a, 3b, and 3c in which the sheet materials 4a, 4b, and 4c are separately wound into rolls. Single-layer roll support portions 2a, 2b, 2c to be pivotally supported, and multi-layer roll support portions 7 that support the core 6 for winding in a state in which the sheet materials 4a, 4b, 4c from the single-layer rolls are laminated, As a main component. In this example, the plurality of sheet materials 4a, 4b, and 4c are three, and are composed of a copper foil 4a, a polyimide film 4b, and a copper foil 4c. Therefore, the laminated board 9 manufactured with the manufacturing apparatus 10 shown in FIG. 2 becomes a double-sided copper foil laminated board (laminate sheet) by which both surfaces of the polyimide film 4b become the copper foil layers 4a and 4c. In addition, when the sheet materials 4a, 4b, and 4c are the above-described materials, the thermocompression treatment by the press device 13 is performed in the range of pressure 20 to 80 [bar], temperature 180 to 400 [° C], and time 1 to 10 [min]. It is desirable to do within.

"Material supply device"
Next, the material supply device 12 will be described in more detail.

  As shown in FIGS. 2 and 4, the material supply device 12 includes laminated roll support portions 21 and 23 that rotatably support the core 6 of the laminated roll 5. The laminated roll support portions 21 and 23 are provided at both axial ends of the core 6, and the laminated roll support portion 21 at one axial end side is attached to the mounting wall 20 erected from the floor surface for each laminated roll 5. The laminated roll support portion 23 on the other end side in the axial direction is formed in a columnar shape erected from the floor or ceiling for each laminated roll 5.

  The laminated roll support portions 21 and 23 pivotally support the winding core 6 of the laminated roll 5 via the rotating shaft 25. That is, the core 6 of the laminated roll 5 is formed in a hollow shape (cylindrical in this example), and the rotary shaft 25 penetrating through the hollow core 6 is supported by the laminated roll support portions 21 and 23. . The rotary shaft 25 has a stopper (not shown) that protrudes and protrudes in the radial direction so as to engage with the inner peripheral surface of the core 6, and when the stopper protrudes in the radial direction, the rotary shaft 25 and the core 6 and the rotating shaft 25 and the core 6 are integrally rotated.

  At least one of the laminating roll support portions 21 and 23 has a built-in brake means (not shown) for braking the winding of the laminated plate 9 by the product winding device 14. 8 can be put into the press device 13 in a stretched state.

  However, since the multilayer workpiece 8 is formed of a plurality of sheet materials 4a, 4b, and 4c (thickness t1, t2, and t3), the outer sheet material 4c is an intermediate sheet when unrolled from the laminated roll 5. The material 4b is also unwound longer by 2π × (t2) / 2 per turn, and the inner sheet material 4a is unwound longer by 2π × (t2 + t3) / 2 per turn.

  Therefore, when the multi-layer workpiece 8 is inserted into the press device 13, the sheet material 4a, 4b, 4c is not accurately laminated at the sheet insertion port (reference numeral A in FIG. 2) of the press device 13, and wrinkles are generated. Therefore, there is a possibility of causing a molding failure of the laminated board. Therefore, in order to prevent such a problem from occurring, the material supply device 12 of the present embodiment absorbs the circumferential length difference that absorbs the circumferential length differences of the plurality of sheet materials 4a, 4b, and 4c of the laminated roll 5. A mechanism 30 is provided.

"Circumferential length absorption mechanism"
Next, the circumference difference absorbing mechanism 30 will be described in more detail with reference to FIGS. 5 to 7 are diagrams in which rotational force change reduction means 51 and 53 described later are omitted.

  In the circumferential length difference absorbing mechanism 30 of the present embodiment, a pair of plate-like attachment bases 35 are provided on both ends in the axial direction of the core 6 of the laminated roll 5 via bearings 39. The pair of opposed mounting bases 35 are pivotally supported in a state where intermediate rolls 36 and 37 are suspended so as to be parallel to the core 6, and the pair of rotating arms 31 and the pair of rotating arms 33. The proximal end is rotatably supported. The axially opposite ends of the pair of rotary arms are pivotally supported in a state where the tension applying rolls 32 and 34 are installed so as to be parallel to the core 6.

  The intermediate rolls 36 and 37 guide the sheet materials 4b and 4c of the multilayer work 8 drawn out from the laminated roll 5 in the drawing direction, and the tension applying rolls 32 and 34 have passed through the intermediate rolls 36 and 37. The intermediate rolls 36 and 37 are pressed against the sheet material 4b and 4c from the opposite side to give tension. Here, the number of the intermediate rolls 36 and 37 and the tension applying rolls 32 and 34 may be the same as the number of the sheet materials 4a, 4b and 4c. In this example, the intermediate rolls 36 and 37 and the tension applying rolls are used. 32 and 34 are provided for each of the sheet materials 4b and 4c except for the innermost sheet material 4a among the plurality of sheet materials 4a, 4b and 4c, and the innermost sheet material 4a is an intermediate roll and tension. Since the product take-up device 14 winds through the press device 13 without passing through the additional rolls, the number of intermediate rolls 36 and 37 and tension applying rolls 32 and 34 are the number of sheet materials 4a, 4b, and 4c. 1 less than That is, in this example, the number of sheet materials of the multilayer workpiece 8 is two, and the intermediate rolls 36 and 37 and the tension applying rolls 32 and 34 are two, which is one less.

  The mounting base 35 is held in a fixed posture with respect to the rotating core 6 by its own weight, or the mounting base 35 is connected to a floor surface, a laminated roll support portion, or other fixing points. The posture is kept constant by the rotation posture adjusting means for adjusting or fixing the rotation posture of the mounting base 35 (the rotation is prevented from being carried by the rotating core 6).

  Further, in order to absorb the slack of the sheet materials 4b and 4c due to the difference in circumference, urging means 42 and 42 for rotating the tension applying rolls 32 and 34 (rotating arms 31 and 33) in a predetermined direction are provided. Yes. The biasing means 42 of the present embodiment is air cylinders 42 and 42 that pull the wires 43 and 45 connected to the rotary arms 31 and 33 with a constant pressure. In this case, the pressing force of the tension applying rolls 32, 34 to the sheet material 4b, 4c is determined by the air pressure of the air pump that supplies air to the air cylinders 42, 42, and is almost constant at all times regardless of the rotation posture.

  Note that the direction in which the rotating arms 31 and 33 are pulled by the urging means 42 (the direction in which the slack of the sheet materials 4b and 4c is absorbed) is set almost on the opposite side of the sheet insertion port of the press device 13, and this embodiment In the embodiment, since the feeding direction of the sheet material to the pressing device 13 is substantially horizontal, the pulling direction of the rotating arms 31 and 33 by the biasing means 42 is also substantially horizontal.

  By such a circumferential length difference absorbing mechanism 30, the unwinding length between the plurality of sheet materials 4a, 4b, 4c charged into the press device 13 is absorbed. Specifically, as shown in FIG. 5 → FIG. 6 → FIG. 7, as the multilayer work 8 is unwound from the laminated roll 5, the outer sheet material becomes more slack, so that this is absorbed. The rotary arms 31 and 33 rotate. Thereby, it is prevented that wrinkles generate | occur | produce in the laminated board 9 manufactured.

"Rotational force change reduction means"
Next, the rotational force change reducing means 51 and 53 will be described with reference to FIGS.

  In the circumference difference absorbing mechanism 30 using the rotating arms 31 and 33 as described above, the rotational force mg × sin θ is applied to the rotating arms 31 and 33 due to the weight mg of the rotating arms 31 and 33 and the tension applying rolls 32 and 34. Has occurred (see FIG. 11). Therefore, the force urged to the sheet materials 4b and 4c includes the urging force Fa (see FIGS. 8 to 10) of the urging means 42 of the circumference difference absorbing mechanism 30 and the rotational force mg × of the rotating arm caused by gravity. is the sum of sin θ (see FIGS. 8 to 11). As shown in FIG. 11, the rotational force mg × sin θ of the rotary arms 31 and 33 caused by gravity changes with the rotational posture of the rotary arms 31 and 33, and as a result, is applied to the sheet materials 4 b and 4 c. The urging force (Fa + mg × sin θ) changes.

  Therefore, the present embodiment is configured to include rotational force change reduction means 51 and 53 that reduce the influence of the change in rotational force mg × sin θ of the rotational arms 31 and 33 caused by gravity. In other words, the rotational force change reducing means 51 and 53 push the rotational arms 31 and 33 back with a large force Fc × sin θ as the rotational force mg × sin θ of the rotational arms 31 and 33 due to their own weight increases. , 33, the amount of change in the rotational force (mg × sin θ−Fc × sin θ) is reduced.

  Specifically, the rotational force change reducing means 51 and 53 are constituted by air cylinders 51 and 53 as urging means, and both the air cylinders 51 and 53 are arranged along the longitudinal direction. The urging force Fc is applied by stretching in the extension direction.

  As shown in FIGS. 8 to 10, the air cylinders 51 and 53 are rotatably fixed to a bracket 49 whose one ends 51 a and 53 a are fixed to the mounting base 35, and the other ends 51 b and 53 b are connected to the rotating arms 31 and 33. It is fixed so that it can rotate freely.

  One end 51a, 53a of the air cylinder is provided in the vicinity of the rotation center 31a, 33a of the rotary arm 31, 33, while the other end 51b, 53b of the air cylinder is pivotally supported by the rotary arm 31, 33. It is provided in the vicinity of the tension applying rolls 32 and 34.

  In this example, both ends 51a and 53a of the air cylinders 51 and 53 are on the tension applying roll 34 side relative to the rotation centers 31a and 33a of the rotating arm (that is, the rotating arms 31a and 33a and the tension applying rolls 32 and 34). Between). The other end 53b of the air cylinder 53 is located closer to the rotation center 31a of the rotary arm than the tension applying roll 34 (that is, located between the rotation center 31a of the rotary arm 31 and the tension adding roll 32). The other end 51b of the air cylinder 51 is located on the side away from the rotation center 31a of the rotary arm from the tension applying roll 32 (that is, between the rotation center 31a of the rotary arm 31 and the tension adding roll 32). Is not located).

  In this embodiment, the one ends 51a and 53a of the air cylinders 51 and 53 (that is, the attachment points 51a and 53a on the rotation center 31a and 33a side of the rotation arms 31 and 33) are the rotation centers 31a and 53a of the rotation arms 31 and 33, respectively. It is located just below the gravity direction of 33a.

  Next, the operation of the air cylinders 51 and 53 as the rotational force change reducing means configured as described above will be described mainly with reference to FIG. In the present embodiment, as shown in FIGS. 8 to 10, the positions of the other ends 51 b and 53 b of the air cylinders 51 and 53 as the rotational force change reducing means and the tension applying rolls 32 and 34 coincide with each other. Although not shown in FIG. 11, a simple model in which the other ends 51 b and 53 b of the air cylinders 51 and 53 are matched with the tension applying rolls 32 and 34 will be described as a simple model.

  As shown in FIG. 11, the urging force Fc by the air cylinders 51, 53 is divided into a component force (Fc × cos θ) along the longitudinal direction of the rotary arms 31, 33 and a component force Fc along the rotation direction of the rotary arms 31, 33. When divided into × sin θ, the component force (Fc × cos θ) along the longitudinal direction of the rotary arms 31 and 33 is canceled by being supported by the rotary arms 31 and 33, and in the rotational direction of the rotary arms 31 and 33. The remaining component force Fc × sin θ remains, and the rotational force Fc × sin α of the rotary arms 31 and 33 based on the urging force Fc of the air cylinders 51 and 53 becomes the rotational force mg × sin θ of the rotary arms 31 and 33 caused by its own weight. It will rebound against it. Therefore, as shown in FIG. 11, the sum of the urging forces applied to the rotating arms 31 and 33 is mg × sin θ−Fc × sin α, excluding the urging forces of the urging means 42 and 42 of the circumferential length difference absorbing mechanism 30. Become.

  In the present embodiment, the urging force of the air cylinders 51 and 53 and one end of the air cylinders 51 and 53 (the rotation arms 31 and 33 of the air cylinders 51 and 53 are set so that mg × sin θ−Fc × sin α≈constant. The attachment points 51a and 53a on the rotation center 31a and 33a side and the other ends of the air cylinders 51 and 53 (attachment points 51b and 53b on the tension applying rolls 32 and 34 side of the rotary arms 31 and 33 of the air cylinders 51 and 53). By setting the position, the influence of the change in the rotational force mg × sin θ of the rotary arms 31 and 33 due to the own weight can be reduced.

  As described above, when mg × sin θ−Fc × sin α is set to be substantially constant, the change in the biasing force applied to the sheet materials 4b and 4c becomes small. Will improve.

  Further, for example, the urging force of the air cylinders 51 and 53 and one end of the air cylinders 51 and 53 (the rotation of the rotary arms 31 and 33 of the air cylinders 51 and 53 are set so that mg × sin θ−Fc × sin α≈0. The positions of the attachment points 51a, 53a on the center 31a, 33a side and the other ends of the air cylinders 51, 53 (the attachment points 51b, 53b on the tension applying rolls 32, 34 side of the rotary arms 31, 33 of the air cylinders 51, 53). And the rotational force mg × sin θ of the rotating arms 31 and 33 due to its own weight can be almost completely offset.

  In this case, the urging force applied to the sheet materials 4 b and 4 c can be regarded as only the urging force Fa of the urging means 42 and 42 of the circumferential length difference absorbing mechanism 30. Therefore, the urging force to be applied to the sheet materials 4b and 4c can be designed in consideration of only the urging force Fa of the urging means 42 and 42 of the circumference difference absorbing mechanism 30, and therefore the urging force of the circumference difference absorbing mechanism 30 can be designed. In addition to the advantage that the design of the means 42 and 42 is facilitated, the slack absorbing performance by the circumference difference absorbing mechanism 30 is further improved.

  Next, the main effects of this embodiment will be summarized.

  (1) The laminated sheet manufacturing apparatus 10 and the material supply apparatus 12 used for the laminated sheet manufacturing apparatus 10 of the present embodiment absorb a circumferential length difference between the plurality of sheet materials 4a, 4b, and 4c drawn from the laminated roll 5. 30. Therefore, the circumferential length difference absorbing mechanism 30 can absorb the circumferential length difference generated between the plurality of sheet materials 4 a, 4 b, 4 c constituting the multilayer workpiece 8 when the multilayer workpiece 8 is pulled out from the laminated roll 5. As a result, the laminated state of the multilayer workpiece 8 can be stabilized at the sheet insertion port (symbol A in FIG. 2) of the press device 13, and manufacturing defects such as wrinkles entering the manufactured laminated plate 9 can be prevented.

  (2) In this embodiment, the circumference difference absorbing mechanism 30 is attached to the core 6 of the laminated roll 5. Therefore, since the circumference difference absorbing mechanism 30 can be disposed at a position shifted in the axial direction with respect to the laminated roll support portions 21 and 23, even if the plurality of laminated roll support portions 21 and 23 are disposed close to each other in the radial direction. The circumference difference absorbing mechanism 30 can be prevented from interfering with the laminated roll support portions 21 and 23, and the material supply device 12 can be prevented from being enlarged.

  (3) In this embodiment, as the rotational force mg × sin θ of the rotating arms 31 and 33 caused by the own weight increases, the rotational force change reducing means 51 and 53 that push back with a large force Fc × sin α are provided. The effect of changing the rotational force mg × sin θ of the rotary arms 31 and 33 can be made as small as possible to improve the slack absorption performance.

  (4) In particular, the magnitudes of the rotational force mg × sin θ of the rotating arms 31 and 33 caused by the own weight and the rotational force Fc × sin α associated with the urging force of the rotational force change reducing means are set to be substantially the same. (Ie, mg × sin θ−Fc × sin α≈0), the weights of the rotating arms 31 and 33 can be almost ignored, and the sheet is taken into consideration only by the biasing means 42 and 42 of the circumferential length difference absorbing mechanism 30. The biasing force applied to the materials 4b and 4c can be set. Therefore, the biasing means 42 and 42 of the circumferential length difference absorbing mechanism 30 can be easily designed, and the slack absorbing performance can be further improved.

  (5) Further, in this embodiment, the rotation centers 31a and 33a of the rotary arm and the attachment points 51a and 51b on the rotation centers 31a and 33a side of the rotational force change reducing means 51 and 53 are vertically moved vertically. Are arranged on a straight line (see FIGS. 8 to 11). Therefore, as shown in FIG. 8, the rotary arms 31 and 33 are swung on the right side in the drawing, and as shown in FIG. 10, the rotating arms 31 and 33 are swung on the left side in the drawing, Thus, the same expression (mg × sin θ−Fc × sin α) is established, and the effects of the rotational force change reducing means 51 and 53 can be exhibited over a wide rotation angle.

  (6) In the present embodiment, the rotational force change reduction means 51 and 53 are not spring members but drive means 51 and 53 capable of changing the directions of the urging forces Fc and Fc. Therefore, for example, when the mounting base 35 is mounted upside down as in the second embodiment to be described later, the expansion and contraction directions of the driving means 51 and 53 are reversed (in the first embodiment, in the direction of extension, the second embodiment). In this case, it is possible to cope with the change. That is, whether the tension applying rolls 32 and 34 are below (the first embodiment) or above (the third embodiment) with respect to the rotation centers 31a and 33b of the rotary arms 31 and 33, they are caused by gravity. The influence of the change in the rotational force mg × sin θ of the rotating arms 31 and 33 can be reduced.

  (7) In the present embodiment, the drive means 51 and 53 are the air cylinders 51 and 53. Therefore, a constant force can always be applied regardless of the rotational postures of the rotary arms 31 and 33, and the design is facilitated as compared with the case where the rotational force change reducing means is a spring member.

  (8) In the present embodiment, since the biasing means 42, 42 of the circumferential length difference absorbing mechanism 30 are the air cylinders 42, 42, regardless of the rotational posture of the rotary arms 31, 33 (that is, the air cylinder 42, A constant load can be applied regardless of the amount of expansion / contraction of 42). Therefore, the slack absorbing performance is excellent as compared with the structure using the spring member in which the elastic restoring force changes according to the rotation posture of the rotary arms 31 and 33, that is, according to the amount of expansion and contraction.

  (9) In the present embodiment, intermediate rolls 36 and 37 that are rotatably supported by the attachment base 35 and suspended in parallel with the core 6 between the attachment bases 35, Further comprises an intermediate roll contacting the sheet material 4b, 4c from the opposite side. Therefore, the amount of slack absorption of the sheet materials 4b and 4c can be doubled by the combination of the tension-applying rolls 32 and 34 and the intermediate rolls 36 and 37, compared to the structure having only the tension-adding rolls 32 and 34.

  (10) In the present embodiment, each of the sheet materials 4b and 4c excluding the innermost sheet material 4a in the multilayer work (consisting of a plurality of laminated sheet materials 4a, 4b, and 4c) drawn from the lamination roll 5 is used. On the other hand, intermediate rolls 36 and 37 and tension applying rolls 32 and 34 are provided. That is, the number of intermediate rolls 36 and 37 and tension applying rolls 32 and 34 is one less than the number of sheet materials. Therefore, since the tension applying rolls 32 and 34 and the rotating arms 31 and 33 that support the tension applying rolls 32 and 34 are minimized, the number of parts is reduced, which contributes to cost reduction.

  Hereinafter, other embodiments will be described. In the following description, the same reference numerals are given to the same configurations as those in the above-described embodiment, and the description of the configurations and the operational effects thereof is omitted.

(Second Embodiment)
12 and 13 show the rotational force change reduction means 51 and 53 of the second embodiment.

  The rotational force change reduction means 51 and 53 of the second embodiment are the same as those of the first embodiment in that they are air cylinders 51 and 53. However, as shown in FIG. 12, one end 51a of the air cylinders 51 and 52 is provided. 53a (attachment points 51a, 53a on the rotation centers 31a, 33a side of the rotation arms 31, 33 of the air cylinders 51, 53) are connected between the rotation centers 31a, 33 of the rotation arms 31, 33 and the tension applying rolls 32, 34. It differs from the first embodiment in that it is located outside, that is, on the side away from the tension applying rolls 32, 34 with respect to the rotation centers 31a, 33 of the rotary arms 31, 33, and The air cylinders 51 and 53 differ from the first embodiment in that urging forces Fc and Fc are applied in the contracting direction.

  Therefore, as shown in FIG. 13, as the rotational force mg × sin θ of the rotating arms 31 and 33 caused by the own weight increases by the rotational force change reducing means 51 and 53, the force is pushed back with a larger force Fc × sin α and caused by the own weight. The influence of the change in the rotational force mg × sin θ of the rotary arms 31 and 33 can be reduced. As a result, the same effect as the first embodiment can be obtained.

(Third embodiment)
14 and 15 show the rotational force change reducing means 51 and 53 of the third embodiment.

  The rotational force change reduction means 51 and 53 of the third embodiment have the same structure as that of the first embodiment, and as shown in FIG. 14, upside down and left and right inversion of the circumferential difference absorbing mechanism 30 of the first embodiment. It is attached. As shown in FIG. 15, the third embodiment is different from the first embodiment in that the urging forces Fc and Fc are applied in the direction in which the air cylinders 51 and 53 as the rotational force change reducing means contract. Is different. Also in the third embodiment, the same operational effects as those of the first embodiment can be obtained.

(Fourth embodiment)
16 and 17 show the rotational force change reducing means 51 and 53 of the fourth embodiment. The rotational force change reducing means 51 and 53 of the fourth embodiment have the same structure as that of the second embodiment, and as shown in FIG. 16, upside down and left and right inversion of the circumferential length difference absorbing mechanism 30 of the second embodiment. It is attached.

  And in this 4th Embodiment, as shown in FIG. 17, the biasing force Fc and Fc are added to the direction where the air cylinders 51 and 53 as a rotational force change reduction means extend, and in 2nd Embodiment, it is. Is different. Also in the fourth embodiment, the same operational effects as those of the second embodiment can be obtained.

(Modification)
Although the rotational force change reduction means 51 and 53 of the above-described first to fourth embodiments are air cylinders, the same effect can be obtained even if the rotational force change reduction means 51 and 53 are electric motors. it can. In particular, if the rotational force change reducing means 51 and 53 are electric motors, the magnitude of the urging force can be finely adjusted according to the rotational posture of the rotary arms 31 and 33. It is also possible to almost completely cancel the rotational force mg × sin θ.

  In the above first to fourth embodiments and the present modification, the rotational force change reducing means 51 and 53 are both drive means (air that can change the direction of the urging force and change the magnitude of the urging force. However, it may be a spring member as in the fifth and sixth embodiments, for example.

(Fifth embodiment)
FIG. 18 shows the rotational force change reducing means 51 and 53 of the fifth embodiment. The fifth embodiment is different from the third embodiment in that the rotational force change reducing means 51 and 53 are spring members (a tension spring in this example) as described above. In the fifth embodiment, the tension springs 51 and 53 are extended and the elastic restoring forces Fc and Fc are increased as the rotation angle of the rotary arms 31 and 33 is increased.

  In such a fifth embodiment, the urging forces (elastic restoring forces Fc, Fc) of the rotational force change reducing means 51, 53 change depending on the rotational angle of the rotary arms 31, 33, so the above formula (mg × sin θ Although the calculation of −Fc × sin α≈constant) is slightly complicated, it is possible to obtain substantially the same operational effects as in the third embodiment.

(Sixth embodiment)
FIG. 19 shows rotational force change reduction means 51 and 53 of the sixth embodiment. The sixth embodiment differs from the fourth embodiment in that the rotational force change reducing means 51 and 53 are spring members (in this example, compression springs). In such a sixth embodiment, the compression springs 51 and 53 contract as the rotation angle of the rotary arms 31 and 33 increases, and the elastic restoring forces Fc and Fc increase.

  In such a sixth embodiment, the urging forces (elastic restoring forces Fc, Fc) of the rotational force change reducing means 51, 53 change depending on the rotational angle of the rotary arms 31, 33, so the above formula (mg × sin θ Although the calculation of −Fc × sin α≈constant) is slightly complicated, it is possible to obtain substantially the same operational effects as in the fourth embodiment.

(Seventh embodiment)
FIG. 20 shows a seventh embodiment. In the seventh embodiment, the attachment points 51a and 51b of the rotational force change reducing means 51 and 53 on the rotation center side of the rotary arms 31 and 33 are attached to the attachment base 35 (in this example, the bracket 49 fixed to the attachment base 35). In contrast, the first to sixth embodiments described above are supported in such a manner that they can be slid in a direction intersecting with the rotary arms 31 and 35 (in this example, along the slide rail portion 61). In the seventh embodiment, an inclination measurement sensor 63 for detecting the attachment posture (rotation posture) of the attachment base 35 is provided, and the rotational force change reduction means 51 and 53 are attached based on the detection value of the inclination measurement sensor 63. This is different from the first to sixth embodiments in that it includes a driving means (not shown) that changes the slide positions of the points 51a and 53a.

  More specifically, in the driving means, the attachment points 51 a and 53 a of the rotational force change reduction means 51 and 53 are perpendicular to the rotation centers 31 a and 33 a of the rotary arms 31 and 33 based on the detection value of the inclination measurement sensor 63. The attachment points 51a and 53a are slid so as to coincide vertically with the direction.

  According to the seventh embodiment, even if the mounting angle of the mounting base 35 is changed, the effect (5) of the first embodiment can always be obtained.

(Modification)
Note that if the attachment points 51a and 51b on the rotation center side of the rotary arms 31 and 33 are slidably supported with respect to the attachment base 35, even if the structure does not include the inclination measurement sensor 63 and the driving means. Since the attachment points 51a and 51b can be manually slid and fixed, the same effects as those of the seventh embodiment can be obtained.

  As mentioned above, although this invention was demonstrated taking the above-mentioned various embodiment as an example, this invention is not limited only to the above-mentioned embodiment.

  For example, in the above-described embodiment, the sheet material is a copper foil and a polyimide film, but other sheet materials may be used.

  In the above-described embodiment, the case where the multilayer workpiece is made of three sheet materials has been described. However, if the multilayer workpiece is made of a plurality of sheet materials, the present invention can be used regardless of the number of sheet materials. Applicable.

  In the above-described embodiment, two laminated plates are laminated at the same time. However, in the present invention, one laminated plate may be laminated, or three or more laminated plates may be laminated. A plate may be laminated at the same time.

  Further, in the above-described embodiment, the winding core is attached to the laminated roll support portion via the rotating shaft. However, in the present invention, the winding core is directly attached to the laminated roll support portion not via the rotating shaft. Also good.

  In the above-described embodiment, in order to minimize the number of intermediate rolls, tension applying rolls, and rotating arms, the number of intermediate rolls, tension adding rolls, and rotating arms is one less than the number of sheets constituting the multilayer work. However, in the present invention, the number of sheets and the number of intermediate rolls, tension applying rolls, and rotating arms may be the same or larger.

  In addition, it is needless to say that other embodiments, examples, operation techniques, and the like made by those skilled in the art based on the above embodiment are all included in the scope of the present invention.

It is a schematic diagram of the lamination roll manufacturing apparatus used for the manufacturing apparatus of the laminated board of 1st Embodiment of this invention. The schematic diagram of the manufacturing apparatus of the laminated board of 1st Embodiment. The schematic diagram explaining roughly the manufacturing principle of the laminated board manufactured with the manufacturing apparatus of the same laminated board. The perspective view of the circumference difference absorption mechanism used for the material supply apparatus of the manufacturing apparatus of the same laminated board. It is a side view of the same circumferential length difference absorption mechanism, and is a view showing an initial state of unwinding of the multilayer work, and is a view showing the rotational force change reducing means omitted. It is a side view of the same circumference difference absorption mechanism, and is a diagram showing a state in the middle of unwinding of the multilayer workpiece, and is a diagram in which the rotational force change reducing means is omitted. It is a side view of the same circumferential length difference absorption mechanism, and is a view showing a state in a later stage of unwinding of the multilayer workpiece, and is a view in which the rotational force change reducing means is omitted. It is a side view of the same circumference difference absorption mechanism, Comprising: The figure which shows the initial stage state of unwinding of a multilayer workpiece. It is a side view of the same circumference difference absorption mechanism, Comprising: The figure which shows the state of unwinding of a multilayer workpiece | work. It is a side view of the same circumference difference absorption mechanism, Comprising: The figure which shows the state of the unwinding of a multilayer workpiece | work. Explanatory drawing for demonstrating the principle of a rotational force change reduction means. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 2nd Embodiment. Explanatory drawing for demonstrating the principle of the rotational force change reduction means of the circumference difference absorption mechanism of 2nd Embodiment. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 3rd Embodiment. Explanatory drawing for demonstrating the principle of the rotational force change reduction means of the circumference difference absorption mechanism of 3rd Embodiment. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 4th Embodiment. Explanatory drawing for demonstrating the principle of the rotational force change reduction means of the circumference difference absorption mechanism of 4th Embodiment. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 5th Embodiment. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 6th Embodiment. The side view which shows the vicinity of the rotational force change reduction means of the circumference difference absorption mechanism of 7th Embodiment. Schematic for demonstrating the circumference difference absorption mechanism as a comparative example.

Explanation of symbols

4a ... Sheet material (copper foil)
4b ... Sheet material (polyimide film)
4c ... Sheet material (copper foil)
DESCRIPTION OF SYMBOLS 5 ... Laminated roll 6 ... Core core 9 ... Laminated board 10 ... Laminate board manufacturing apparatus 12 ... Material supply apparatus 13 ... Press apparatus 14 ... Product winding apparatus 30 ... Circumference difference absorption mechanism 31, 33 ... Rotating arm 31a, 33a ... Rotation center 32, 43 ... Tension applying roll 35 ... Mounting base 36, 37 ... Intermediate roll 39 ... Bearing 42 ... Air cylinder (biasing means)
51, 53: Rotational force change reduction means 51a, 53a ... One end 51b, 53b ... The other end

Claims (10)

A material supply device that unwinds and supplies each sheet material from a laminating roll that is wound in a roll shape around the core in a state where a plurality of sheet materials are laminated,
A circumference difference absorption mechanism for absorbing a circumference difference of a plurality of sheet materials of the laminated roll is provided,
The circumference difference absorption mechanism is
A mounting base suspended via bearings at both axial ends of the core;
A rotating arm pivotally supported by each of the mounting bases;
A tension applying roll having both ends pivotally supported on the rotation free end side of the pair of rotating arms and suspended substantially parallel to the winding core between the pair of rotating arms;
Urging means for pressing the tension applying roll against the sheet material in a direction to absorb the slack of the sheet material;
Configured with
The material supply further comprising a rotational force change reduction means for reducing a change in the rotational force of the rotating arm by pushing back the rotating arm with a larger force as the rotational force of the rotating arm resulting from its own weight increases. apparatus. The material supply device according to claim 1,
An intermediate roll that is rotatably supported by the mounting base and is suspended in parallel with the winding core between the two mounting bases, and further includes an intermediate roll that contacts the sheet material from the opposite side of the tension applying roll. A material supply device comprising: The material supply device according to claim 1 or 2,
The material supply device according to claim 1, wherein the rotational force change reducing means is a spring member. The material supply device according to claim 1 or 2,
The material supply device according to claim 1, wherein the rotational force change reducing means is a driving means capable of changing a direction of an urging force. The material supply device according to claim 1 or 2,
The material supply device according to claim 1, wherein the rotational force change reduction means is a drive means capable of changing the magnitude of the urging force. It is a material supply apparatus of Claim 4 or 5, Comprising:
The material supply device, wherein the driving means is an air cylinder. It is a material supply apparatus of Claim 4 or 5, Comprising:
The material supply apparatus, wherein the driving means is an electric motor. The material supply device according to any one of claims 1 to 7,
The rotation point of the rotational force change reducing means is attached to the attachment base on the rotation center side of the rotary arm, and is arranged in a straight line in a direction perpendicular to the rotation center of the rotary arm. Feeding device. The material supply apparatus according to any one of claims 1 to 8,
The material supply device according to claim 1, wherein a point of attachment of the rotational force change reducing means to the attachment base on the rotation center side of the rotary arm is slidable with respect to the attachment base. A laminate manufacturing apparatus,
The material supply device according to any one of claims 1 to 9,
A press device that heat-bonds a plurality of sheet materials to each other by heat-pressing while passing a plurality of sheet materials from the material supply device in a stacked state; and
An apparatus for producing a laminated board, comprising:

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