CN101530868A - Roll feeder - Google Patents

Abstract

A roller feeder (8) includes a pair of rollers (9, 10) for performing a web material feeding operation by gripping and rotating the web material. The support member (frame 13) is provided only on one side of each roller (9, 10), where each roller (9, 10) is mounted so as to be able to rotate freely. Each roller is hollow inside. In a cantilevered structure, each roller is mounted on a shaft (18, 19) formed to extend from the support member into the interior of each roller. The upper roller (9) is installed to be able to rotate freely on the circumference of the shaft (18), and the shaft (18) cooperates with the rolling bearing (23) between the outer peripheral surface of the shaft (18) and the inner peripheral surface of the roller (9), And it can swing around the centerline of the roller (9) by relative motion inside the rolling bearing (23) in a direction inclined relative to the centerline of the shaft (18).

Description

Roller feeder

technical field

The present invention relates to a roll feeder for feeding strip material, for example to an extrusion machine.

Background technique

In general, a strip-shaped plate material composed of steel, aluminum, etc. (hereinafter referred to as a strip-shaped material) is continuously supplied to an extrusion machine with a series of equipment, and mechanical processing such as extrusion processing, cutting processing, etc. is performed, such as in Japan Patent Application Publication No. 2003-181573 is published.

In the above-mentioned apparatus, extrusion processing and the like are performed (see Japanese Patent Application Laid-Open Publication Nos. 2003-181573 and 2004-142876). That is, as the strip material wound into a roll (ie, coil stock) is rotated in the unwinding direction by a mechanism called an uncoiler, a desired strip is drawn out from the outer circumference. shape material. Using a mechanism called a roll feeder (or coil feeder) and positioned at the slipstream of the unwinder (the processing stream before the extrusion machine, etc.), the above-mentioned strip material is sent out to Specified quantity for each extrusion machine,.

In the above equipment, the roller feeder includes a pair of rollers (an upper roller and a lower roller), and performs a feeding operation of the strip-shaped material by clamping and rotating the strip-shaped material.

Incidentally, in the above-mentioned roller feeder, the supporting structure of each roller is a conventional prior art, that is, each roller has a two-end structure, such as disclosed in Japanese Patent Application Laid-Open Publication No. 2001-30029.

More specifically, members mounted on or on a part of a housing (referred to as "casing", "frame", etc.) fixed to the installation site are positioned on both sides of each roller to As a supporting member for each roller. In addition, for example, shafts protruding from both ends of each roller are rotatably mounted on each supporting member via rolling bearings such as ball bearings. In this way, each roller is rotatably supported on the housing.

For example, in the case of a roller feeder as disclosed in Japanese Patent Application Laid-Open Publication No. 2001-30029, the supporting members (i.e., the fixing plates 5, 12 and the Moving plates 7) are positioned on both sides of each roller 2,3 as a supporting member for each roller 2,3. In addition, shafts (i.e. rotatable shaft right end 2a, rotatable shaft left end 2b, rotatable shaft right end 3a and rotatable shaft left end 3b) protrude from both sides of each roller 2,3 , and are mounted to freely rotate relative to each support member (ie, fixed plates 5, 12 and movable plate 7) via bearings 6, 8, 11 and 13. In this way, each roller 2 , 3 is rotatably supported by the machine housing 4 as described above.

Since the above-mentioned support structure for each roll has a two-end type structure, this conventional roll feeder has various problems as follows:

(a) The structure of the frame (casing) housing the support member is complex due to the large number of expensive parts such as bearings;

(b) Since it is a structure in which the entire roll cannot be visually inspected and human hands cannot easily access the area near the roll, the condition inspection or cleaning of the roll cannot be carried out without difficulty;

(c) Adjusting the roll gap or releasing the amount of opening is a difficult task due to the inability to visually inspect the entire roll;

(d) Due to the weight of the parts lifted and lowered by the release operation whenever the release operation is completed at high speed, there is a problem that the momentary impact force of the roller in contact with the strip material being processed is large and causes dents in the material .

In addition, the release operation is to raise one side of the upper and lower rollers in a direction away from the other side to open from a state where the web material is inserted to a state where the web material is not inserted. Usually, in the case of being processed with an extrusion machine, after a predetermined amount of strip-shaped material has been fed, it is necessary to perform a release operation and temporarily release the strip-shaped material each time; and

(e) When the roll replacement work is performed, the disassembly of the frame cannot be performed. For example, in the case of the conventional prior art Japanese Patent Application Laid-Open Publication No. 2001-30029, the rollers 2, 3 cannot be replaced unless the supporting members (ie, the fixed plates 5, 12 and the movable plate 7) are removed. For this reason, the work of replacing the rollers is troublesome.

And, naturally, it is necessary to replace the rollers damaged by wear and tear, etc., in order to prolong the service life. In addition, even if wear and tear and the like have not progressed further, the roller needs to be replaced appropriately whenever the physical properties of the outer peripheral surface in contact with a specific belt-like material are different corresponding to the physical properties of the belt-like material and the like.

Contents of the invention

An object of the present invention is to provide a roll feeder which solves the above problems with a simple roll support structure.

In order to achieve the above objects, there is provided a roller feeder comprising a pair of rollers for performing a feeding operation of a strip-shaped material by clamping and rotating the strip-shaped material, wherein a support is provided only on one side of each roller member, each roller is mounted on the side so as to be freely rotatable; the inside of each roller is hollow; and each roller is mounted on a shaft formed to extend from the support member to the inside of each roller.

Here, the "support member" refers to a part of the housing fixed to the installation site of the roller feeder or a member fixed to the housing.

In a preferred embodiment of the present invention, the roller feeder includes at least one of the rollers mounted to be able to rotate freely on the circumference of the shaft, and can be moved around the centerline of the roller along the relative A structure in which the centerline of the shaft oscillates in a direction inclined, and the shaft cooperates with a rolling bearing positioned between the outer peripheral surface of the shaft and the inner peripheral surface of the roller.

Here, the "relative movement inside the rolling bearing" means, for example, the movement of the outer ring constituting the rolling bearing relative to the inner ring.

And, in a preferred embodiment of the present invention, the support member comprises a mounted pair of covers that is displaceable to a closed position covering each roller or an open position exposing each roller.

In a preferred embodiment of the present invention, the roller feeder further includes a roller position adjustment mechanism for adjusting the gap of each roller during the feeding operation.

In a preferred embodiment of the present invention, the roller feeder further comprises a roller release mechanism operable to perform a release operation in which the gap of each roller is temporarily wider than the gap during the feeding operation; and, wherein the The above-mentioned roller release mechanism includes a rod, and the release operation is completed by the displacement of the rod.

The beneficial effects of the present invention are as follows:

(a) Since the roller feeder of the present invention has a structure in which a support member is provided only on one side of each roller and the rollers are installed in a cantilever shape, the structure of the support member is relatively simplified, and the number of parts such as bearings does not increase , thus becoming more economical;

(b) Since each roller is mounted from the support member on a shaft formed to extend from the support member to the inside of each roller, the entire roller can be visually inspected;

(c) Since the roller feeder of the present invention has a structure in which human hands can easily access the area near the rollers, the condition inspection or cleaning of the rollers can be carried out effortlessly;

(d) Since the entire roll of each roll can be visually inspected, the adjustment of the roll gap G or the release opening amount (gap G during the release operation) is an easy task;

(e) Because the weight of the parts lifted and lowered by the release operation is reduced by a simple structure in which each roller is installed in a cantilever shape. Even when the releasing operation is performed at high speed, the momentary impact force of the rollers in direct contact with the strip-like material will not be great and will not cause dents in the strip-like material; and

(f) The task can be accomplished without dismantling the support member even when the rollers are alternately working.

The above and other objects and novel features of the present invention will appear more fully from the following detailed description when read in conjunction with the accompanying drawings. It should be clearly understood, however, that the drawings are for purposes of illustration and are not intended as a definition of the boundaries of the invention.

Description of drawings

Figure 1 is a perspective view showing the cover of the roller feeder in a closed position;

Figure 2 is a perspective view showing the cover of the roller feeder in an open position;

Fig. 3 is the front view of roller feeder;

Fig. 4 is the back view of roller feeder;

Fig. 5 is the right side view of roller feeder;

Fig. 6 A is the vertical sectional view of the roller feeder (i.e. the longitudinal sectional view of the V1 section in Fig. 3);

Fig. 6B is a view for explaining the supported state of the upper roll;

Fig. 7 is a horizontal sectional view of a roller feeder (i.e. a cross-sectional view of H1 section in Fig. 4);

8A to 8C are views for explaining the principles of a roller position adjustment mechanism and a roller release mechanism; and

9A and 9B are views explaining the swing of the upper roller.

Detailed ways

Hereinafter, preferred embodiments of the present invention will be explained in detail with reference to the accompanying drawings.

A. The overall structure of the roller feeder

Fig. 1 is a perspective view showing the roller feeder 8 of the embodiment with the covers 11, 12 in the closed position (the state where the covers 11, 12 are in the closed position to be described).

Fig. 2 is a perspective view showing the roller feeder 8 with the covers 11, 12 in the open position (a state where the covers 11, 12 are in the open position to be described).

FIG. 3 is a front view of the roller feeder 8 .

FIG. 4 is a rear view of the roller feeder 8 . FIG. 4 shows a state to be described later in which a lid 17, a handle 15, etc. (shown in FIG. 7) have been removed.

FIG. 5 is a right side view of the roller feeder 8 .

6A is a vertical sectional view of the roller feeder 8 (ie, a longitudinal sectional view of the V1 section in FIG. 3 ) and FIG. 6B is a view for explaining the supporting state of the upper roller 9 .

Fig. 7 is a horizontal sectional view of the roller feeder 8 (ie, a cross-sectional view of the H1 section in Fig. 4); in addition, Fig. 3 and Fig. 5-7 show the state where the covers 11, 12 have been removed.

Hereinafter, as a way of expressing the horizontal direction, the right side in FIG. 6A (the upper side in FIG. 7 ) is termed the front side or the front side, and the left side in FIG. 6B (the lower side in FIG. 7 ) is termed the front side. Rear or rear side.

Here, as shown in FIGS. 1, 2, 4, etc., the roller feeder 8 includes a pair of rollers 9, 10; a motor for driving the rollers 9, 10; a frame on which the rollers 9, 10 and the motor 14 are mounted. 13; a cover 11, 12 capable of covering each roller 9, 10; a handle 15 for roller position adjustment; and a lever 16 for release operation.

In addition, the frame 13 is provided with a driving mechanism 40 for driving the rollers 9, 10, wherein the motor 14 serves as a driving source; a roller position adjusting mechanism 50 for adjusting the gap G of the rollers 9, 10 corresponding to the operation of the handle 15; and The roller release mechanism 70 is used to realize the release operation of the rollers 9, 10 through the operating lever 16.

Hereinafter, the roller 9 located on the upper side will be referred to as an upper roller 9 and the roller 10 located on the lower side will be referred to as a lower roller 10 in some cases. In addition, the cover 11 on the upper side will be referred to as an upper cover 11 , and the cover 12 on the lower side will be referred to as a lower cover 12 .

The frame 13 is a casing fixed to the place where the roller feeder 8 is already installed. The inside of the frame 13 is like a hollow box. The frame 13 has a convex overall shape (overall shape when viewed from the front or back) with a lower portion having a larger width than the lower portion, as shown in FIGS. 3 and 4 .

Said frame 13 is manufactured in cast material obtained from metals such as steel and aluminium. In addition, the back side of the frame 13 is open, as shown in FIGS. 4 and 7 . In the assembled state, however, the rear opening of the frame 13 is closed with a cover 17 (shown in FIG. 7 ). As previously described, FIG. 4 shows a state in which the cover 17 and the handle 15 have been removed when viewing the inside of the frame 13 from the rear side. The frame 13 functions as the supporting member of the invention, with the rollers 9, 10 mounted in a cantilever shape.

As shown in Fig. 6A, the rollers 9, 10 are cylindrical. The rollers 9, 10 carry out the strip material feeding operation by clamping and rotating, the strip material is fed through with the outer peripheral surface. For example, the strip of material is fed proximally to distally in a direction perpendicular to the gap shown in Figure 5 or Figure 6A. In Fig. 3, the strip material is fed from left to right. The gap G between the rollers 9, 10 (shown in Fig. 6A) is set to be the thickness of the strip material that is pressed and shrunk by the pressure weight from the thickness of the strip material sheet (by the pressure of the rollers 9, 10). size) deducted value.

In addition, the rollers 9, 10 are mounted on the frame 13 in a cantilever shape. Therefore, the supporting member 13 (frame 13) is provided only on one side of each roller 9, 10 where each roller 9, 10 is mounted so as to be able to rotate freely. And, each roller 9, 10 is formed to be mounted on a shaft 18, 19 extending from the frame 13 to the inside of each roller 9, 10, respectively. Hereinafter, the shaft 18 on which the upper roll 9 is mounted will be referred to as an upper roll shaft 18 , and the shaft 19 on which the lower roll 10 is mounted will be referred to as a lower roll shaft 19 .

B. Supporting structure and circumferential structure of upper roller

The supporting structure of the upper roll 9 and the circumferential structure of the upper roll 9 will be explained below. As shown in FIGS. 7 and 6A , a cylindrical upper roller mounting portion 13 a is formed at the horizontal center of the upper portion of the front portion of the frame 13 extending forward. In addition, a bearing hole 13b is formed inside the upper roller mounting portion 13a, having a circular cross-sectional shape moving forward and backward.

Further, the upper roller shaft 18 is a solid shaft (not a hollow shaft) having a circular cross-sectional shape, and is arranged to pass through the bearing hole 13b. The upper roller shaft 18 is divided into a plurality of parts having different outer diameter sizes in the axial direction. Therefore, as shown in FIG. 6A, the upper roller shaft 18 is sequentially divided into a part I 18a, a part II 18b, a part III 18c, a part IV 18d and a part V 18e from the rear side end. Of these parts, part II 18b and part IV 18d have larger outer diameter dimensions than the other parts (part I 18a, part III 18c and part V 18e). The rolling bearing 20 is fitted between the outer circumference of the portion II 18b and the inner circumference of the bearing hole 13b (ie, the inner circumference of the upper roller mounting portion 13a). A rolling bearing 21 is fitted between the outer circumference of the portion IV 18d and the inner circumference of the bearing hole 13b. With the rolling bearings 20, 21, the upper roller shaft 18 can rotate centered on the center line C1 (shown in FIGS. 4 and 7) of the bearing hole 13b. The center line C1 corresponds to the center line of the part II 18b and the part IV 18d of the upper roll shaft 18.

Incidentally, as shown in FIGS. 4 and 7 , the center line C2 of the portion I 18a and portion V 18e of the upper roll shaft 18 is slightly offset by an eccentricity dimension D1 with respect to the center line C1. That is, the eccentricity of the portion I 18a and the portion V 18e relative to the portion II 18b and the portion IV 18d is slight in the dimension D1.

Next, a ball bearing 22 (rolling bearing) is fitted between the outer circumferential surface of the portion 118a and the inner circumference of a movable piece 55 described later. And, a ball bearing 23 (rolling bearing) is fitted between the outer peripheral surface of the portion V 18e and the inner peripheral surface of the upper roller 9 (large diameter portion 9b described later). A ball bearing is a type of rolling bearing including a plurality of balls fitted between an inner ring and an outer ring, and a clearance (space) of each ball is maintained by a cage.

The reference numerals of the main structural elements of the ball bearing 23 will be explained here.

Specifically, as shown in FIG. 7, the ball bearing 23 includes a plurality of balls 23c fitted between the inner ring 23a and the outer ring 23b, and a retainer (not shown) is used to maintain the clearance of each ball 23c of the ball bearing 23. .

The inner ring 23a of the ball bearing 23 is inserted on the outer circumference of the part V 18e of the upper roller shaft 18, and the end plate 24 installed on the upper roller shaft 18 prevents the bearing 23 from slipping. End plate 24 is a doughnut shaped plate having an outer diameter larger than portion V 18e and smaller than inner ring 23a. The end plate 24 is arranged to be in contact with the outer periphery of the end face of the inner ring 23a, and is fixed to the front end surface of the upper roller shaft 18 (the front end surface of the portion V 18e) with a screw 25 which passes through the end face side of the upper roller shaft 18. Plate 24 and fastened to part V 18e.

In addition, there is a ring-shaped spacer 26 between the portion IV 18d of the upper roller shaft 18 and the inner ring 23a. A spacer 26 is inserted onto the outer circumference of the portion V 18e of the upper roll shaft before the inner ring 23a.

On the other hand, the outer ring 23b of the ball bearing 23 is attached to the inner peripheral surface of the upper roll 9 at a position substantially in the axial center.

The small-diameter portion 9 a is formed in a portion of the front side on the inner peripheral surface of the upper roll 9 , and the large-diameter portion 9 b is formed in a portion of the rear side on the inner peripheral surface of the upper roll 9 . The diameter of the large-diameter portion 9 b is larger than that of the small-diameter portion 9 a and is approximately equal to the outer diameter of the outer ring 23 b of the ball bearing 23 . A stepped portion 9c in contact with the end surface of the outer ring 23b is formed on the boundary of the small-diameter portion 9a and the large-diameter portion 9b.

The outer ring 23b of the ball bearing 23 is mounted on the inner peripheral surface of the upper roll 9 at a substantially central position in the axial direction (the frontmost portion of the large diameter portion 9b), and the outer ring 23b is inserted into the large diameter portion 9b, one end surface of which is aligned with the large diameter portion 9b. The stepped portion 9c is in contact, and the other end surface is in contact with the spacer 27 . The spacer 27 is an annular portion, and is inserted into the large-diameter portion 9b behind the outer ring 23b. One end surface of the spacer 27 is in contact with the outer ring 23 b, and the other end surface is in contact with the retainer ring 28 . The retaining ring 28 is inserted into a slit (reference number omitted) formed in the large-diameter portion 9b to prevent the outer ring 23b or the spacer 27 from slipping.

The upper roll 9 is mounted on the upper roll shaft 18 so as to be able to rotate freely with one of the ball bearings 23 as explained above.

Furthermore, the center of the upper roll 9 must coincide with the above-mentioned center line C2, and the center of the upper roll 9 must rotate relative to the upper roll shaft 18 on the center line C2. More specifically, the upper roll 9 must rotate around the center line C2 with the ball bearings 23 .

Regarding the rolling bearing explained above, such as the ball bearing 23 and the like, relative movement is possible within the bearing to such an extent that the center line of the inner ring 23a and the center line of the outer ring 23b are relatively inclined. More specifically, for example, the outer ring 23b can swing relative to the inner ring 23a to some extent by sliding between the balls 23c and the inner ring 23a or the outer ring 23b. For this reason, the centerline of the upper roll 9 is swingable in a direction inclined with respect to the centerline C2 of the upper roll shaft 18 .

FIG. 6B is a view for clearly explaining the supported state of such movement of the upper roller 9 .

And FIGS. 9A and 9B are views for clearly explaining an example of the swinging motion of the upper roller 9 .

In FIG. 6B, the upper roller 9 is able to swing slightly in the direction indicated by the circular arrow. More specifically, for example, the front side of the roller 9 can swing in the downward direction as shown in FIG. 9A , and the front side of the upper roller 9 can swing in the upward direction as shown in FIG. 9B . Even if the lower roller 10 is tilted somewhat from the normal position (horizontal in this case) by the deviation of the lower roller shaft 19 caused by the reaction force from the strip material or the like, the upper roller 9 will follow the swing. The effect obtained is to enable the respective alignment of the upper roll 9 and the lower roll 10 to always remain parallel.

Furthermore, as shown in FIG. 7 , a timing gear 29 is fixed to the rear side edge of the upper roller 9 . The timing gear 29 rotates with the upper roller 9 around the center line C2.

In addition, since the upper roller 9 is mounted on the upper roller shaft 18 as described above, the upper roller 9 can be easily removed by loosening the screw 25 . More specifically, when the screw 25 is loosened and then the screw 25 and the end plate 24 are removed, the upper roller 9 installed inside the ball bearing 23 can be pulled outward to the front side and removed from the upper roller shaft 18 .

C. The installation structure and circumference structure of the lower roller

The mounting structure of the lower roll 10 and the circumferential structure of the lower roll 10 will be explained below.

As shown in FIG. 6A, at the front of the frame 13, at the lower position of the above-mentioned upper roller mounting portion 13a, the lower roller mounting portion 13c extends forward and rearward. A bearing hole 13d is formed inside the lower roller mounting portion 13c, having a circular cross-sectional shape moving forward and backward.

Also, the lower roller shaft 19 is a solid shaft (not a hollow shaft) having a circular cross-sectional shape, and is arranged to pass through the bearing hole 13d. The lower roller shaft 19 is axially divided into a plurality of sections having different outer diameter sizes. Therefore, as shown in FIG. 6A, the lower roller shaft 19 is sequentially divided into a part I 19a, a part II 19b, a part III 19c, a part IV 19d and a part V 19e from the rear side end. Of these parts, part II 19b has a larger outer diameter dimension than part I 19a. And Part III 19c has a larger outer diameter dimension than Part II 19b, and is the largest diameter dimension. In addition, the outer peripheral surface of the part IV 19d is inclined in the axial direction, wherein the outer dimension is smaller toward the front side. More specifically, the outer peripheral surface of the portion IV 19d has a conical shape with a smaller outer diameter toward the front side. Section V 19e is significantly smaller than the smallest outer diameter of section IV 19d.

Two ball bearings 30, 31 are fitted axially (horizontal direction in FIG. 6A) between the outer circumference of part II 19b of the lower roller shaft 19 and the inner circumference of the bearing hole 13d (i.e., the inner circumference of the lower roll mounting portion 13c). in the gap between. More specifically, the ball bearing 30 is fitted between the rear side edge of the part II 19b and the bearing hole 13d, and the ball bearing 31 is fitted between the front side edge of the part II 19b and the bearing hole 13d. The lower roller shaft 19 can rotate around the center line (not shown) of the bearing hole 13d by the ball bearings 30 and 31 . The centerline of the bearing hole 13d coincides with the centerline of the lower roller shaft 19 and is parallel to the above-mentioned centerline C1 or C2 as long as the deviation (related to flexibility) of the lower roller shaft 19 and the like is ignored. And the centerline of the bearing hole 13d is positioned below the above-mentioned centerline C2.

On the other hand, the front side portion of the lower roller shaft 19 (the portion accommodating the portion IV 19d and the portion V 19e) is inserted onto the inner side of the lower roller 10. And a portion IV 19d of the lower roller shaft 19 is fixed to the lower roller 10, being pressed against the inner surface of the lower roller 10 at a substantially center position in the axial direction (ie, a conical portion 10a described later).

More specifically, as shown in FIG. 6A, a conical-shaped portion 10a is formed at an axially substantially center position on the inner peripheral surface of the lower roll 10, which is inclined as the diameter becomes smaller toward the front side. The geometry of the conical part 10a corresponds to the outer circumferential surface of the conically shaped part IV 19d, which enables the outer circumference of the part IV 19d to cooperate with the conical part 10a.

Further, in front of the conical portion 10a in the inner peripheral surface of the lower roll 10, a rear small-diameter portion 10b and a front large-diameter portion 10c are sequentially formed further to the front side. And behind the conical portion 10a in the inner peripheral surface of the lower roll 10, a rear large-diameter portion 10d is formed on the rear side. The rear small-diameter portion 10b has the same diameter as the smallest diameter of the conical portion 10a, while the front large-diameter portion 10c has a larger diameter than the rear small-diameter portion 10b. Further, the diameter of the rear large-diameter portion 10d is larger than the maximum diameter of the conical portion 10a, and is set larger than the outer diameter of the portion III 19c of the lower roller shaft 19. A stepped portion 10e in contact with the end surface of the fixing plate 32 is formed on the boundary of the rear small-diameter portion 10b and the front large-diameter portion 10c.

The fixing plate 32 is an annular plate whose outer diameter is substantially the same as that of the front large diameter portion 10c and is inserted into the front large diameter portion 10c, and the inner diameter of the central hole is smaller than that of the rear small diameter portion 10b. The shaft of the screw 33 is inserted into the central hole of the fixing plate 32 . The shaft of the screw 33 is inserted into the central hole of the fixing plate 32 from the front side, and the screw end is fastened in a threaded hole formed in the center of the front surface of the lower roller shaft 19 (ie, the front surface of the part IV 19e). The head of the screw 33 is larger than the central hole of the fixing plate 32 and is in contact with the front side surface of the fixing plate 32 . Therefore, when the screw 33 is tightly fastened and supported by the fixing plate 32 , the lower roller shaft 19 is pulled to the front side relative to the lower roller 10 by the pulling force of the screw 33 . Furthermore, when the lower roller shaft 19 is pulled to the front side with respect to the lower roller 10, the outer peripheral surface (cone-shaped surface) of the portion IV 19d of the lower roller shaft 19 is strongly pressed to the conical portion 10a of the lower roller 10. superior. The lower roller shaft 19 is firmly fixed on the lower roller 10 by the pressure connection (push-fit connection) of the part IV 19d with the conical part 10a.

In addition, in the front large-diameter portion 10c of the lower roller 10, the separation plate 34 is inserted into the front side instead of the screw 33. As shown in FIG. The space shape of the separation plate 34 is substantially the same as that of the fixing plate 32 . After inserting the separating plate 34 into the front large diameter portion 10c with the screws 33 fastened in place, these parts are in a ring shape. The rear side surface of the separation plate 34 is opposed to the screw 33 with a slight gap, and the front side surface is in contact with the retaining ring 35 . The retaining ring 35 is a member inserted into a groove formed in the front large-diameter portion 10c to prevent the separation plate 34 from slipping. Further, although the inner diameter of the central hole in the separation plate 34 is smaller than the head of the screw 33 , the central hole constitutes a size such that a tool such as a hex nut driver can be inserted to rotate the screw 33 .

With this configuration, the following effects can be achieved.

Specifically, when the screw 33 is rotated in the loosening direction with the above tool, the head of the screw 33 will be pressed against the separation plate 34 on the front side. As a result, the lower roller 10 will be pressed on the front side relative to the lower roller shaft 19 . For this reason, simply by turning the screw 33 in the loosening direction with the above-mentioned tool, the pressure connection between the above-mentioned part IV 19d and the conical part 10a can be easily released, and the lower roller 10 can be quickly removed from the lower roller shaft 19 removed.

According to the structure explained above, the lower roller 10 is fixed to the lower roller shaft 19 . And the centerline of the lower roll 10 coincides with the centerline of the lower roll shaft 19 and is positioned below the centerline C2 of the upper roll 9 as described above.

As shown in FIG. 6A , a timing gear 36 is fixed to the rear side edge of the lower roller 10 . The timing gear 36 meshes with the above-mentioned timing gear 29 of the roller 9 and rotates with the lower roller 10 . And, the gear tooth gap between the synchronous gear 36 and the synchronous gear 29 is set so that even if the gap G of the rollers 9, 10 is adjusted by the meshing of the roller position adjustment mechanism 50, it will not cause a gap due to looseness, rattling, etc. (tooth gap). Mechanical failure.

In addition, a driven pulley 42 described later is fixed within the outer circumference of the rear side edge of the lower roller shaft 19 (ie, part I 19a).

D. Structure of the cover

The covers 11, 12 will be explained below.

The covers 11 , 12 are parts having an implementable shape capable of covering the outer circumference and the front side end face of each roller 9 , 10 , as shown in FIG. 1 or 2 . Covers 11, 12 are connected to each other by hinges 11a, 12a and frame 13, and covers 11, 12 can be displaced to cover each roller 9, 10 in a closed position (as shown in Figure 1) and to expose each roller 9, The open position of 10 (as shown in Figure 2).

In addition, as shown in Figures 1 and 2, there is a screw-type knob 37 for locking each cover 11, 12 in the closed position, the screw-type knob 37 is tightly tightened so that the end face of each cover 11, 12 Side clipped together.

Further, each cover 11, 12 has a transparent portion on the outer peripheral side of each roller 9, 10 when viewed from the closed position. Thus, the condition of each roller 9, 10 can be checked visually even in the closed position.

Secondly, a motor 14 is mounted on the front lower left side of the frame 13 and parallel to each roller 9,10. The motor 14 is a motor for servo-controlling the rotation of each roller 9, 10, and is controlled by a control system (illustration omitted).

Next, as shown in FIG. 4 , the drive mechanism 40 includes a driven pulley 41 fixed to the output shaft of the motor 14 and a driven pulley 42 fixed to the rear end of the lower roller shaft 19 , a belt wound around the driven pulley 41 and the driven pulley 42 . 43 (such as a timing belt) and a tension pulley 44 for maintaining proper tension on the belt 43. The driven pulley 42 has a larger diameter than the driven pulley 41 . Therefore, the rotation of the motor 14 has a configuration in which deceleration is transmitted to the lower roller shaft 19 and the lower roller 10 . Furthermore, the rotation of the lower roll 10 is transmitted to the upper roll 9 by the synchronous gears 36, 39 explained above. Therefore, the upper roller 9 is interlocked with the lower roller 10 and rotates together.

Also as shown in FIG. 4 , the solid line shows a state where the driven pulley 42 and the belt 43 have been removed. Dashed lines show driven pulley 42 and belt 43 .

E. Roller position adjustment mechanism

Next, a roller position adjustment mechanism for adjusting the gap G of the rollers 9, 10 corresponding to the operation of the handle 15 will be explained.

The roller position adjustment mechanism 50 is a mechanism for adjusting the gap G while the rollers 9 , 10 for gripping and rotating the strip material are feeding the strip material (ie, during the feeding operation). That is, the gap G is in a state where the release operation has not yet occurred.

As shown in Figure 7 and Figure 4, the roller position adjustment mechanism includes a handle 15, an upper roller shaft 18, a handle presser 51, a handle return spring 52, a handle shaft 53, a slider 54, a movable piece 55, a position positioning pin 56, etc. wait. In addition, the upper roller shaft 18, the movable piece 55, and the like also constitute members of a roller release mechanism described later.

As shown in FIG. 7, the position positioning pin 56 is a part embedded in the upper right edge on the rear portion of the frame 13, and has an acute-angled tip protruding rearward.

The handle 15 has a complete disk shape, and a through hole 15a is formed in the center. On the rear surface of the handle 15, the circumference of the through hole 15a has a cylindrical hub 15b extending rearward. In addition, a cylindrical grip 15 c is formed on the outer periphery of the handle 15 . Further, the position positioning hole 15 d is formed in a dotted circular shape marked with a plurality of predetermined gaps where the tip of the position positioning pin 56 is fitted to the front of the handle 15 .

The handle 15 is installed so as to be able to move back and forth with respect to the handle shaft 53 . However, when the rear end portion (part I 53a described later) of the handle shaft 53 is locked with the key 57 inserted into the through hole 15a, this makes it impossible for the handle 15 to rotate.

The handle presser 51 is fixed to the rear end surface of the handle shaft 53 with a screw 58 . The handle return spring 52 is a coil spring located on the outer circumference of the sleeve 15 b of the handle 15 , and fits to be pressed and contracted between the handle 15 and the handle presser 51 . The handle return spring 52 energizes the handle 15 forward. By resisting the energizing force of the handle return spring 52 and pulling it backward, the handle 15 can be moved to a state where the position positioning pin 56 is disengaged from the position positioning hole 15d. However, in a natural state where no external force is applied, the energizing force of the handle return spring 52 presses the handle 15 forward and maintains the handle 15 at any position where the position positioning pin 56 has been inserted into the position positioning hole 15d.

As shown in FIG. 3 , there is a scale plate 59 mounted on the front periphery of the handle 15 , which has a scale etched with numbers indicating the gap G of the rollers 9 , 10 . In addition, as shown in FIG. 1 or FIG. 5 , a groove 60 is formed on the right side surface showing an adjustment position corresponding to the scale plate 59 . For example, as far as the positioning of the groove 60 is concerned, when the scale plate 59 reads "1.0" on the scale, it can be known that the gap G should be adjusted to 1.0 mm. In addition, when realizing the value of each gap G (for example, 0.2 mm, 0.4 mm, 0.6 mm, 0.8 mm, 1.0 mm, 1.2 mm, 1.4 mm, 1.6 mm, 1.8 mm) corresponding to each scale of the scale plate 59 Each position of the above-mentioned position positioning hole 15d is formed.

The handle shaft 53 is a solid shaft having a circular cross-sectional shape, except for a key groove portion where the key 57 is inserted, and is divided into a plurality of parts different in outer diameter size in the axial direction. More specifically, as shown in FIG. 7, the handle shaft 53 is sequentially divided into a portion I 53a, a portion II 53b, a portion III 53c, a portion IV 53d and a portion V 53e from the rear side end. Of these parts, part II 53b has a larger outer diameter than part I 53a. And Part III 53c has a larger outer diameter dimension than Part II 53b and is the largest diameter dimension. Furthermore, part V 53e has approximately the same outer diameter as part II 53b.

Furthermore, the handle shaft 53 is attached to the handle shaft attachment portion 13 e of the frame 13 . More specifically, as shown in FIGS. 1 and 7 , a cylindrical handle shaft mounting portion 13 e is formed on the left upper portion of the front portion of the frame 13 to extend forward. A bearing hole 13f is formed inside the handle shaft mounting portion 13e, having a circular cross-sectional shape moving forward and backward. As shown in FIG. 7 , the centerline C3 of the bearing hole 13 f is parallel to the centerlines C1 , C2 of the upper roller shaft 18 . Further, in the bearing hole 13f, a cylindrical front side bearing portion 61 is inserted from the rear side. The front end portion (portion V 53e) of the handle shaft 53 is inserted into the front side bearing portion 61 so as to be freely rotatable.

In addition, the rear end surface of the front bearing portion 61 faces the slider 54 with a slight gap. In addition, the slide bearing 62 intervenes in the gap between the inner circumference of the front side bearing portion 61 and the outer circumference of the portion V 53e, and in the gap between the front side bearing portion and the slider 54. The sliding bearing 62 is, for example, an oil-free sliding bearing using a solid lubricant.

Furthermore, as shown in FIG. 7 , the rear bearing portion 63 is positioned behind the handle shaft mounting portion 13 e in the frame 13 . The rear bearing portion 63 is fixed to the upper wall of the frame 13 at the top edge with a screw stopper (illustration omitted). A through hole (reference number omitted) is formed in the lower portion of the rear bearing portion 63 at the position where the portion II53b of the handle shaft 53 is inserted. The centerline of the through hole of the rear bearing part coincides with the centerline C3. Further, the lower front surface of the rear bearing portion 63 is opposed to the rear edge surface of the portion III 53c of the handle shaft 53 with a slight gap. In addition, the sliding bearing 64 intervenes in the gap between the rear bearing portion 63 and the portion III 53c, and the gap between the inner circumference of the through hole of the rear bearing portion 63 and the outer circumference of the portion II 53b. Similar to the above-described sliding bearing 62, the sliding bearing 63 is, for example, an oil-free sliding bearing using a solid lubricant.

Also, in addition to the handle 15 , a state in which the handle shaft 53 , the rear bearing portion 63 and the like are removed is shown in FIG. 4 .

As described above, the handle shaft 53 is mounted to the frame 13 with the two-end support structure including the front side bearing portion 61, the sliding bearing 62 and the rear bearing portion 63, and the handle shaft 53 is rotatable around the center line C3. The centerline C3 indicated above coincides with the centerlines of the portion II 53b and the portion V 53e of the handle shaft 53. In addition, the center line C3 also coincides with the center line of the portion I 53a of the handle shaft 53 and the center line of the handle 15 mounted on the portion I 53a.

Incidentally, as shown in FIG. 7, the centerline C4 of the portion IV 53d of the handle shaft 53 is slightly offset by an eccentricity dimension D2 with respect to the centerline C3. That is, the eccentricity of the portion IV 53d relative to the portion II 53b and the portion V 53e is slight in the dimension D1.

Next, the slider 54 is a complete cylindrical part, and has a through hole 54a at a position where the part IV 53d of the handle shaft 53 is inserted on the inner side. The center line of the through hole 54a coincides with the above-mentioned center line C4. Two planes 54b, 54c (shown in FIG. 4 ) are formed on the upper and lower peripheral sides of the slider 54 , and the slider 54 slidably contacts the upper and lower inner surfaces of a recessed area 55b described later on the movable piece 55 .

In addition, when the handle 15 is turned and the handle shaft 53 is rotated, the center line C4 rotates on the circumference of the center line C3. In connection therewith, the slider 54 will also oscillate about the centerline C3. When viewed from the rear side as shown in FIG. 4, the slider 54 will move up and down while sliding in a generally back and forth direction.

Next, the movable piece 55 is a plate-like part approximately equal to the cross-sectional width of the part IV 53d for the handle shaft 53 and the slider 54 (as shown in FIG. 7 ). The movable piece 55 is formed in a substantially rectangular shape when viewed from the rear side in FIG. 4 , and is centered horizontally on the above-mentioned center line C2. A bearing hole 55 a is formed at the center of the movable piece 55 . The bearing hole 55a is fitted with the ball bearing 22 described above. Part I 18a of the upper roller shaft 18 is inserted on the inner side of the ball bearing 22 (see FIG. 6A ). The center line of the bearing hole 55a coincides with the above-mentioned center line C2. Therefore, the movable piece 55 is rotatable about the center line C2 with respect to the upper roller shaft 18 .

Further, a recessed area 55b is formed on the right end surface of the movable piece 55 when viewed from the rear side (rear side), and a recessed area 55c is formed on the left end surface of the movable piece 55 . Also, two planes (reference numerals omitted) are formed in the upper and lower inner surfaces of the recessed area 55b, which are slidably unified with the planes 54b, 54c of the slider 55 described above. In this way, the slider 54 can move linearly (ie, slide) relative to the movable piece 55 in a direction following the plane 54b.

Also, under the reference state where the handle 15 is set at the reference adjustment position (for example, the scale plate 59 is set at the groove 60 position of the scale for reading the indication gap G adjusted to 1.0 mm as mentioned above Bottom), centerline C1 , centerline C2 , centerline C3 , and centerline C4 are configured to all exist on substantially the same horizontal plane, as shown in FIG. 4 .

In addition, as shown in FIG. 6A, a recessed area 55d is formed in the central upper surface of the movable piece 55 fitted with a roller pressing spring 65 at the bottom end. Although the roller pressing spring 65 is simplified and shown in FIG. 6A , the roller pressing spring 65 is actually the same compression spring as the handle return spring 52 described above. The upper portion of the roller pressing spring 65 is accommodated inside the roller pressing button 66 . The roller push button 66 is a cylindrical member with a threaded portion 66a formed on the lower outer circumference, and a gripping portion 66b having a larger diameter than the screwed portion 66a is formed on the upper outer circumference. The recessed area 55d forms a threaded hole 13i at an upper position in the upper wall of the frame 13, to which the threaded portion 66a of the roller press button 66 can be fastened. The roller press button 66 is mounted on the upper wall of the frame 13 by fastening the threaded portion 66a into the threaded hole 13i from the upper portion.

Also, the roller pressing spring 65 fits between the upper wall of the roller pressing button 66 and the above-mentioned recessed area 55d to be pressed and contracted, and the center of the movable piece 55 is downwardly energized.

In this way, the downward pressing force of the roller pressing spring 65 acts so that the upper roller shaft 18 rotates in the descending direction (ie, the descending direction of the upper roller 9 ) with the center line C1 as the center. Therefore, when a strip-shaped material thicker than the set gap G is inserted between the rollers 9, 10, the roller pressure applied to the strip-shaped material (the force by which the rollers 9, 10 clamp the strip-shaped material) and the roller pressing spring 65 The endowment capacity is equivalent.

Also, when the roller press button 66 is grasped and rotated by the grip portion 66b, the tension amount of the roller press button 66 is adjusted. Therefore, it is possible to change the length of the roller pressing spring 65 (the length in the state of being pressed and contracted), which adjusts the energizing force of the roller pressing spring 65 (ie, the roller pressure).

F. Roll release mechanism

The roller release mechanism 70 for effecting the manual or automatic release operation of the rollers 9, 10 will be explained below.

As shown in FIGS. 4 and 7 , the roller release mechanism 70 includes a rod 16 , an upper roller shaft 18 , a movable piece 55 , a cam follower 71 , a release shaft 72 and an air cylinder 73 .

FIG. 4 is a lateral view showing the cam follower shaft 71a installed at the upper position of the recessed area 55c in the above-mentioned movable piece 55. As shown in FIG. The cam follower 71 is a small cylindrical roller mounted so as to be free to rotate relative to the cam follower shaft 71a. The lower outer circumference of the cam follower 71 protrudes slightly into the recessed area 55c, as shown in FIG. 4 .

The lever 16 and the release shaft 72 are mounted to the release shaft mounting portion 13 g of the frame 13 .

More specifically, as shown in FIGS. 3 and 7 , the release shaft mounting portion 13 g is cylindrical and formed on the right upper portion of the front portion of the frame 13 to extend forward. A bearing hole 13h is formed inside the release shaft mounting portion 13g, having a circular cross-sectional shape moving forward and backward. The release shaft 72 is a solid shaft having a circular cross-sectional shape except for a notch 72 described later and the like, and is divided into a plurality of parts whose outer diameter sizes differ in the axial direction. More specifically, as shown in FIG. 7, the release shaft 72 is sequentially divided into a portion I 72a, a portion II 72b, and a portion III 72c from the rear side end. Of these parts, part II 72b has a larger outer diameter than part I 72a and part III 72c. In addition, as shown in FIG. 4, on a part of the outer circumference, a semicircular fan-shaped portion 72d is formed in a portion I 72a, and the axially right-angled cross-sectional shape of the portion I 72a is a thick crescent.

In addition, the portion 172a is located in the recessed area 55c of the movable piece 55. The release shaft 72 is positioned at the position where the part III 72c is inserted into the bearing hole 13h. In addition, the bottom end of the rod 16 is fixed to the front end of the release shaft 72 with a screw 77 and supported with a plate 76 . The centerline of the release shaft 72 coincides with the centerline of the bearing hole 13h. Plate 76 is an annular plate inserted between the head of screw 77 and the bottom end of rod 16 . A through hole (reference number omitted) is formed at the center of the bottom end of the rod 16 . The shank of the screw 77 passes through the inner side of the plate 76 and the through hole of the rod 16 , and is centrally fastened to the front end surface of the release shaft 72 . In this way, the lower portion of the lever 16 is fixed to the front end of the release shaft 72 . Also, the release shaft 72 and the lever 16 mounted in the bearing hole 13h by the sliding bearings 74, 75 can rotate around the center line of the bearing hole 13h. The slide bearings 74, 75 are completely cylindrical. Of these sliding bearings, the sliding bearing 74 is fitted between the rear side of the part III 72c and the bearing hole 13h, and the sliding bearing 75 is fitted between the front side of the part III 72c and the bearing hole 13h. The sliding bearings 74, 75 are, for example, oil-free sliding bearings using a solid lubricant.

Furthermore, a portion I72a of the release shaft 72 is positioned below the cam follower 71 and is in contact with the cam follower 72 . In addition, whenever the lever 16 is in the normal position shown by the solid line in FIG. 3 (the position in the normal state where no release operation takes place), the sector 72d of the portion I 72a shown in FIG. The upper position, and the lower portion of the outer circumference of the cam follower 71 will be in contact with the sector 72d. In this structure, the gap G used during feeding (during non-discharging operation) and the setting made with the roller position adjustment mechanism will be maintained.

And, whenever lever 16 changes to the release position (the position of completing the release operation) shown in dotted line among Fig. 3, when viewing from the rear, the fan-shaped portion 72d of part 172a will be in the position facing to the upper left tilt, and The lower portion of the outer circumference of the cam follower 71 will contact and push up the side of the sector 72d. As a result, this moves the movable piece 55 so that the left side of the movable piece 55 moves (raises) upward (when viewed from the rear in FIG. 4 ). In this structure, the releasing operation is performed so that the gap G of each roller 9, 10 is temporarily wider than the gap during the feeding operation.

Therefore, when the release operation is performed, the upper roller 9 moves upward and is separated from the lower roller 10 in the upward direction. Generally speaking, this is when the rollers 9, 10 are in the wide open position (ie released), when the strip material changes from the clamped to the unclamped condition.

In addition, the rod 16 can be manually indexed and used during the screw operation to initially insert the strip material between the rollers 9,10. For example, as a configuration that is mechanically interlocked and operated with the crankshaft of an extrusion machine, this configuration can also mechanically respond and effectively perform a release operation during machining.

As shown below in FIG. 4 , the air cylinder 73 is arranged at a lower position on the left edge portion of the movable piece 55 (lower position of the above-mentioned recessed area 55 c ) when viewed from the rear. The air cylinder 73 pushes up the piston 73a with air pressure supplied through the pipe 78, and has a coil spring 73b that returns the piston 73a to a normal position. The piston 73 a is fitted on the lower side of the left edge portion of the movable piece 55 . When air pressure is supplied, the left edge portion of the movable piece 55 is pushed upward and moves a predetermined distance. This constitutes a configuration in which the release operation is accomplished in a similar manner as when the lever 16 is indexed to the release position.

g. to operate

The operations of the roller position adjustment mechanism 50 and the roller release mechanism 70 in the above configuration will be explained below with reference to FIG. 8 .

8A to 8C are views for explaining the principles of the roller position adjustment mechanism 50 and the roller release mechanism 70 .

Of these drawings, FIG. 8A is a schematic diagram for explaining the mechanism of the roller position adjustment mechanism 50 and the roller release mechanism 70 . In addition, FIG. 8B is a schematic diagram for explaining the adjustment state with respect to a thin metal sheet (relatively thin strip material), and FIG. 8C is a diagram for explaining an adjustment state with respect to a thick metal sheet (relatively thick strip material). schematic diagram.

When looking at the mechanisms within the configuration of the roller adjustment mechanism 50 and the roller release mechanism 70 , a movable piece 55 is provided relative to the frame 13 as shown in FIG. 8A . In addition, in FIGS. 8A to 8C , the ring marks represent the reference symbols C1-C4, which illustrate the above-mentioned mechanism of the revolving pair centered on the above-mentioned centerlines C1-C4 (for example, realized by the bearing 20, the bearing 22, the bearing 62, etc.).

Furthermore, since the configuration involves the sliding pair of the slider 54 relative to the movable piece 55, a rectangle is shown in FIG. 8A. Also, while being supported from the lower surface by the piston 73a of the above-mentioned air cylinder 73, the left end of the movable piece 55 is similarly supported by the portion 172a of the release shaft 72. In this regard, illustration of the release shaft 72 has been omitted in FIG. 8A .

In the configuration shown in FIG. 8A , when the left side edge portion of the movable piece 55 is pushed up by the air cylinder 73 of the roller release mechanism 70 or by the operating rod 16 , the movable piece 55 moves clockwise along the center line C4. As the center swings, and is accompanied by the sliding operation of the slider 54 . As a result, the upper roller shaft 18 rotates and the centerline C2 moves upward (rises), thereby causing the centerline C2 to rotate around the circumference of the centerline C1 . In this case, since the upper roller 9 is centrally installed on the centerline C2, the upper roller 9 also moves upward to the centerline C2, and a releasing operation of temporarily widening the gap G of each roller 9, 10 is performed.

Next, in a normal state where no release operation occurs, and when viewed from the rear, the above-mentioned handle 15 is rotated in the clockwise direction. As shown by the arrow in FIG. 8A , the handle shaft 53 is rotated so that the centerline C4 rotates around the circumference of the centerline C3. In connection therewith, the upper roll shaft 18 rotates so that the centerline C2 rotates around the circumference of the centerline C1. The movable piece 55 moves upward while maintaining a substantially horizontal position about the centerlines C2 and C4.

In this case, since the upper roller 9 is installed at the center of the centerline C2, the upper roller 9 also moves upward to the centerline C2, and the gap G of each roller 9, 10 increases correspondingly to the amount of rotation of the handle 15 by more than base state. Therefore, in order to continue to align the centerline C4 directly above the centerline C3, the handle 15 can be rotated clockwise within 90 degrees from the reference state, and can be adjusted to increase the gap G.

For example, as described above, when the "1.0" scale of the scale plate 59 is aligned with the position of the groove 60, the gap G is maintained as a reference state adjusted to 1.0 mm in a normal state where the release operation does not occur. Further, this reference state can be changed by pulling back on the handle 15 to disengage the position positioning pin 56 and then rotating the handle 15 in the clockwise direction. For example, when the scale "1.4" on the dial 59 is aligned with the position of the groove 60 and the handle 15 returns to the position of the position positioning pin 56 for position change setting, the gap G will be adjusted to 1.4 mm and maintained at normal status.

Also, in the normal state described above, adjustment of the gap G (gap G during feeding operation) (ie, adjustment by the roller adjustment mechanism 50 ) can also be similarly achieved in the opposite direction. More specifically, when the handle 15 is rotated in the counterclockwise direction when viewed from behind, the handle shaft 53 and the upper roller shaft 18 are rotated in the opposite direction. As indicated by the arrow in FIG. 8A , the movable piece 55 moves (falls) downward while maintaining a substantially horizontal position about the center lines C2 and C4.

As a result, the upper roller 9 also moves downward to the center line C2, and the gap G of each roller 9, 10 decreases in proportion to the amount of rotation of the handle 15 beyond the reference state. Therefore, to continue operation so that the centerline C4 is aligned directly below the centerline C3, the handle 15 can be rotated counterclockwise within 90 degrees from the reference state, and adjustments can be made to reduce the gap G.

For example, the reference state can be changed by pulling back on the handle 15 to disengage the position positioning pin 56 and then rotating the handle 15 in a counterclockwise direction. For example, when the scale "0.6" on the dial 59 is aligned with the position of the groove 60, and the handle 15 returns to the position of the positioning pin 56 to change the setting, the gap G will be adjusted to 0.6 mm and kept in the normal state .

Also, regarding the adjustment by the roller position adjustment mechanism 50 described above, as shown in FIGS. 8B and 8C , the position of the center line C4 moves up and down corresponding to the fulcrum of the release operation of the roller release mechanism 70 .

More specifically, FIGS. 8B and 8C show the adjustment by the roller position adjustment mechanism 50 in which the value of the gap G has been set (the state where the release operation has not occurred). First, as shown in FIG. 8B, using a strip-like material of a thin metal plate, the center line C4 descends on the fulcrum of the release operation. Next, as shown in FIG. 8C, using a strip material of a thick metal plate, the center line C4 rises on the fulcrum of the release operation. Also, the release operation by the roller release mechanism 70 temporarily widening the gap G from the above normal state causes the movable piece 55 to swing mainly around the position of the center line C4 set by adjusting the above roller position adjustment mechanism 50 .

H. Effects of the present invention

Based on the roller feeder structure of the present invention, the following various effects can be obtained:

(a) Because the roller feeder of the present invention has a simpler structure in which a supporting member is provided only on one side of each roller 9, 10 and the rollers 9, 10 are installed in a cantilever shape, the structure of the supporting member is relatively simplified , the number of parts such as bearings does not increase, so it becomes more economical;

(b) Each roller 9, 10 is mounted on a shaft 18, 19 extending from the support member to the inside of each roller 9, 10, respectively. Also, the covers 11, 12 for covering each roller 9, 10 are transparent on the outer peripheral side. Furthermore, the covers 11 , 12 can be displaced into an open position fully exposing each roller 9 , 10 , as shown in FIG. 2 . To this end, in addition to being able to see the rollers 9, 10 to some extent when the lids 11, 12 are in the closed position, each roller 9, 10 can be inspected completely visually when the lids 11, 12 are in the open position. In particular, since the present invention has a structure in which human hands can easily access the area around the rolls 9, 10 as long as the covers 11, 12 are in the open position or removed, the condition check or cleaning of the rolls 9, 10 can be carried out effortlessly;

(c) As above, each roller 9, 10 can be inspected completely visually. Since all roll gaps can be visually inspected directly from the side of the roll feeder, the adjustment of the roll gap G for feeding operation or release opening amount (gap G during release operation) is an easy task;

(d) Because of a simpler structure in which each roller 9, 10 is installed in a cantilever shape, the weight of the parts lifted and lowered by the release operation is reduced. Even when the release operation is completed at high speed, the momentary impact force of the rollers that will come into direct contact with the strip material will not be large and will not cause dents in the strip material;

(e) Even when the rollers 9, 10 are being replaced, this task can be accomplished without dismantling the support member (frame 13);

(f) Since the gap G adjustment for the feeding operation or the release opening amount (gap G during the release operation) is an easy task, the release opening amount can be set to a required minimum value. For this reason, dents caused during clamping of the strip material are significantly reduced. And as a result this contributes to a speed improvement of the release operation.

(g) As mentioned earlier, using a rolling bearing (ball bearing 23) fitted between the outer peripheral surface of the upper roller shaft 18 and the inner peripheral surface of the upper roller 9, the upper roller 9 is installed so as to be able to wind the upper roller Shaft 18 rotates freely. The centerline of the upper roller 9 is swingable in a direction inclined relative to the centerline of the shaft 18 by relative movement within the rolling bearing (see FIGS. 6B and 9 ). For this reason, even if the lower roller 10 is changed from the normal position (horizontal in this case) by, for example, a change in the lower shaft 19 due to an assembly error or a processing error of various materials, or by a reaction force from a strip material, etc. Slightly inclined, the upper roller 9 will also follow this oscillation. The effect obtained is that the respective alignment of the upper roll 9 and the lower roll 10 can always be kept parallel. Also in the present invention each roller 9, 10 is supported in a cantilever frame. In conventional constructions, the probability of less parallel positioning due to variations of the roller axes 18, 19, etc. is relatively high. Furthermore, when the positioning of the rollers becomes less parallel, there is a possibility that the web material may not be fed properly and that the pressure being exerted on the web material will be disproportionate and cause dents, scratches, etc. in the web material. On the contrary, in the structure of the present invention, the upper roller 9 as described above can swing to follow the lower roller 10 . Therefore, since the present invention includes the structure in which the respective rollers are supported in the cantilever shape, the postures of the respective rollers can always be kept parallel to each other, and the normal feeding operation can be performed with high reliability;

(h) During operation, safety can be ensured by placing the covers 11, 12 in the closed position. For this reason, operability such as cleaning of the above-mentioned rollers can be considerably improved with suitably increased safety.

(i) The main body portion of the roller feeder 8 is equipped with a lever 16 to mechanically perform a releasing operation. For this reason, the release operation can be performed by manually displacing the rod 16 closer to the rollers 9 , 10 , even without moving the cylinder 73 by operation of a button of a separately placed control system. Since the release operation can also be performed manually close to the rollers 9, 10, the maneuverability of the screw operation for initially inserting the strip material between the rollers 9, 10 is more effective. Whenever the lever 16 interlocked to the extrusion machine is deflected, a mechanical release operation can be done and further contributes to an improvement in the speed of the release operation.

(j) Each roller 9, 10 can be easily disassembled by loosening each screw 25, 33 as previously described. Conversely, by tightening each screw 25, 33, each roller 9, 10 can be easily mounted; and

(k) Since the lower roll 10 is fixed by pressure-connecting the conical surface to the lower roll shaft 19, such as with a key, as previously described, the lower roll shaft 19 is firmly fixed without any loosening when the shaft 19 is engaged, Flapping etc. (backlash). As a result, the rotation of the motor 14 can be transmitted to the lower roller 10 without backlash, resulting in precise and advanced feeding operations (such as position calibration accuracy in servo control, etc.).

Although the invention has been described with reference to preferred embodiments, it is intended that the invention not be limited to any details of its description but include all embodiments falling within the scope of the appended claims.

Claims (5)

1. roll feeder, this roll feeder comprise and being used for by clamping and the rotation strip material realizes the pair of rolls of strip material feeder operation,

It is characterized in that,

Supporting member, this supporting member only are arranged on a side of each roller, and each roller is mounted to and can rotates freely in this side;

Each roller inside is hollow; And

Each roller is installed in to form from described supporting member and extends on the axle of each roller inside.

2. roll feeder as claimed in claim 1, it is characterized in that, in each roller at least one is mounted to and can rotates freely on the circumference of described axle, rolling bearing between the inner circumferential surface of described axle and external peripheral surface that is positioned at described axle and described roller cooperates, and described axle can be swung around the center line of described roller on the direction of the inclination of the center line with respect to described by the relative motion of described rolling bearing inside.

3. roll feeder as claimed in claim 1 or 2 is characterized in that, described supporting member comprises that the installation lid is right, and this installation lid is to being displaced to closing position that covers each roller or the open position that exposes each roller.

4. as any described roll feeder in the claim 1 to 3, it is characterized in that described roll feeder further comprises the roller position adjusting mechanism, be used for during feeder operation, adjusting the gap of each roller.

5. as any described roll feeder in the claim 1 to 4, it is characterized in that, described roll feeder further comprises exercisable roller relieving mechanism, is used to carry out wideer than the gap during the feeder operation provisionally releasing operation in gap that makes each roller; And

Wherein said roller relieving mechanism comprises bar, finishes described releasing operation by making described bar displacement.

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