WO2016208659A1 - Roll-molding device - Google Patents

Abstract

In order to enable, with a simple and an inexpensive structure, stably roll-molding a tapering material of which the plate thickness changes in the longitudinal direction, a roll-molding device (1) is structured by comprising: two parallel roller shafts (7A, 7B); fixed rollers (11A, 11B) provided so as to be concentric with respect to one of these roller shafts (7A, 7B); floating rollers (12A, 12B) which are provided so as to be eccentric with respect to the other one of the roller shafts (7A, 7B) with clearances (CA, CB) therebetween, which oppose the fixed rollers (11A, 11B), and which sandwich a belt-shaped metallic material (M') with the fixed rollers (11A, 11B); a pressing roller (19) which is in contact with the outer circumferential sections, of the floating rollers (12A, 12B), on the sides opposite to the contacts with the fixed rollers (11A, 11B); and actuators (23A, 23B) which press the floating rollers (12A, 12B) against the fixed roller (11A, 11B) sides via the pressing roller (19).

Description

Roll forming equipment

The present invention relates to a roll forming apparatus that feeds a band-shaped metal material between a plurality of sets of forming rolls and forms the cross-sectional shape of the metal material into a predetermined shape. Specifically, when the thickness of the metal material changes. The present invention also relates to a roll forming apparatus that can cope with the above.

For example, when the flat strip-shaped metal material M shown in FIG. 1A is formed into an aircraft stringer member S or the like having a bent cross-sectional shape shown in FIG. 1k, a plurality of forming steps shown in FIGS. 1B to 1J are performed. After that, it is shaped in stages.
These plural forming steps are performed by a roll forming apparatus called a roll forming line in which a plurality of sets of forming rolls having different cross-sectional shapes are arranged on a line as shown in FIG. The metal material M is formed in stages as it passes between a plurality of sets of forming rolls arranged in a roll forming apparatus.
Conventionally, such a roll forming apparatus is provided such that each forming roll is concentric with the roll axis, that is, the axis with respect to the roll axis is not changed.

Japanese Patent Publication No. 7-29146

As shown in FIG. 2A, a recent aircraft stringer member is formed into a shape called a taper stringer as shown in FIG. 2B by using a taper material M ′ whose thickness changes in a taper shape along the longitudinal direction. It has come to be. Such a taper stringer TS is designed to reduce the weight by keeping the plate thickness Tmax of the portion to be coupled with other members of the machine body large and minimizing the plate thickness Tmin of the other portions.

In order to form such a taper material M ′ with the roll forming apparatus described in Patent Document 1, the forming roll that comes into contact with the uneven surface of the taper material M ′ is moved up and down together with the roll shaft by a servo motor or the like. Therefore, it is necessary to control to follow the uneven shape. For this reason, there existed a subject that the structure of a roll forming apparatus became complicated and cost increased.

This invention is made | formed in view of such a situation, and provides the roll forming apparatus which can carry out the roll forming of the taper raw material from which a plate | board thickness changes to a longitudinal direction stably by simple and cheap structure. For the purpose.

In order to solve the above problems, the present invention employs the following means.

The roll forming apparatus according to the present invention includes two parallel roll shafts, a fixed roll provided concentrically with respect to one of the two roll shafts, and a clearance with respect to the other of the two roll shafts. A floating roll that is arranged eccentrically through the surface and faces the fixed roll, a pressing roll that contacts an outer peripheral portion of the floating roll opposite to the contact point with the fixed roll, and the floating roll through the pressing roll And an actuator for pressing the roll toward the fixed roll.

In the roll forming apparatus configured as described above, a band-shaped metal material is fed between a fixed roll provided concentrically on one roll shaft and a floating roll provided on the other roll shaft so as to be eccentric. Presses the floating roll to the fixed roll side via the pressing roll. Thereby, the cross-sectional shape of a metal material is shape | molded according to the shape of a fixed roll and a floating roll.

For example, even if the thickness of the metal material is a taper material that changes in a taper shape along the longitudinal direction, the floating roll is eccentric with respect to the roll axis in accordance with the change in the thickness of the metal material. The thickness difference is absorbed.

At that time, the pressing force of the actuator is applied to the floating roll itself via the pressing roll, and is not applied to the roll shaft provided with the floating roll. For this reason, regardless of the eccentric position of the floating roll with respect to the roll axis, that is, regardless of the thickness of the metal material, the metal material can be formed into a predetermined shape while applying a constant pressing force.

Therefore, it is not necessary to move the forming roll up and down together with the roll shaft by a servo motor or the like as in the prior art, and a taper material whose thickness changes in the longitudinal direction can be stably roll-formed with a simple and inexpensive configuration.

In the above configuration, a plurality of the pressing rolls are provided at a position symmetrical with respect to an axis connecting line connecting the axis lines of the two roll shafts when viewed in the axial direction of the two roll axes. ing.

According to this configuration, the pressing force of the actuator is evenly applied to the floating roll from the plurality of pressing rolls provided at positions symmetrical with respect to the axis connection line. Accordingly, the position of the pressing roll and the floating roll can be prevented from escaping in the radial direction by the pressing force of the actuator, and the metal material can be stably roll-formed by reliably applying the pressing force of the actuator to the floating roll. .

In the above configuration, the plurality of pressing rolls are pivotally supported by a common roll carrier, and the actuator has an intersection position with the axis connection line in the roll carrier when viewed in the axial direction of the two roll shafts. Press.

According to this configuration, the intermediate points of the plurality of pressing rolls provided at positions symmetrical with respect to the axis connection line are pressed by the actuator. For this reason, the pressing force of the actuator can be equally applied to the plurality of pressing rolls, and the floating roll can be stably pressed.

In the above-described configuration, an axis that connects the axis lines of the two roll shafts within a range between the shaft support position of the roll shaft on which the floating roll is provided and the shaft support position of the pressing roll. You may further have a pair of guide roll which is pivotally supported by the both sides of this axial center connection line on both sides of a connection line, and contact | abuts the outer peripheral part of the said floating roll.

According to this configuration, when the pressing force of the actuator is applied to the floating roll via the pressing roll, the floating roll is held from both outer sides in the radial direction by the pair of guide rolls. For this reason, the position of the floating roll can be prevented from escaping in the radial direction due to the pressing force of the actuator, and the pressing force of the actuator can be reliably applied to the floating roll.

In the above configuration, the pressing force of the actuator is set to a constant force that changes only the cross-sectional shape of the metal material without damaging the plate thickness of the metal material sandwiched between the fixed roll and the floating roll. .

If the pressing force of the actuator is set in this way, even if the floating roll is pressed against the metal material by the pressing force of the actuator, the thickness of the metal material is not impaired, and the metal material is kept at the originally planned thickness. Is roll-formed into a predetermined cross-sectional shape.

For this reason, for example, even if the thickness of the metal material is a taper material that changes in a tapered shape along the longitudinal direction, the thickness of each part of the metal material is not impaired, and the quality of the product is improved. Can do.

In the above configuration, a plurality of sets of the fixed roll and the floating roll are provided, and the two roll shafts are provided with the fixed roll and the floating roll adjacent to each other in the axial direction. The fixed roll provided on the roll shaft is opposed to the floating roll provided on the other roll shaft, and is supported by one roll shaft and adjacent to each other. A plurality of driving concave portions arranged in a circumferential direction are formed on one adjacent surface, and a plurality of driving convex portions loosely fitted in the driving concave portion are formed on the other adjacent surface. An eccentric margin for allowing the floating roll to be eccentric is provided between the concave portion and the driving convex portion.

According to this configuration, the rotational force of the fixed roll provided integrally with the roll shaft is transmitted to the floating roll by the fitting between the driving concave portion and the driving convex portion. For this reason, it is possible to improve the roll formability of the metal material by reliably rotating the floating roll without slipping.

Since there is an eccentric margin that allows the floating roll to be eccentric between the driving concave portion and the driving convex portion, it can be rotated while allowing the eccentricity of the floating roll, and the plate thickness changes. Even metal materials can be molded smoothly.

In the above configuration, the width of at least one of the fixed roll and the floating roll can be changed.

According to this configuration, for example, even if the cross-sectional shape of the metal material has a channel-shaped recess, the width of the fixed roll or the floating roll can be adjusted to the inner dimension, and the metal material can be accurately rolled. Can be molded.

As described above, according to the roll forming apparatus of the present invention, it is possible to stably roll-form a tapered material whose plate thickness varies in the longitudinal direction with a simple and inexpensive configuration.

It is sectional drawing which shows a shaping | molding process until a flat strip | belt-shaped metal material is shape | molded by the stringer member of an aircraft. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is sectional drawing which similarly shows the formation process of a metal material. It is a perspective view which shows the taper raw material from which plate | board thickness changes to a taper shape along a longitudinal direction. It is a perspective view which shows the taper stringer roll-formed using the taper raw material of FIG. 2A. It is a longitudinal cross-sectional view of the roll forming apparatus which concerns on embodiment of this invention. FIG. 4 is a longitudinal sectional view of the roll forming apparatus taken along line IV-IV in FIG. 3. It is a longitudinal cross-sectional view of the roll forming apparatus which shows a state when the plate | board thickness of a metal material becomes thinner than FIG. It is a longitudinal cross-sectional view of the roll forming apparatus which shows a state when the plate | board thickness of a metal material becomes thicker than FIG. It is a figure which shows the eccentric state of a floating roll in case the plate | board thickness of a metal material changes. It is a figure which similarly shows the eccentric state of a floating roll. It is a figure which similarly shows the eccentric state of a floating roll.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

FIG. 3 is a longitudinal sectional view of the roll forming apparatus according to the embodiment of the present invention, and FIG. 4 is a longitudinal sectional view taken along line IV-IV in FIG. 3 is a longitudinal sectional view taken along line III-III in FIG.

For example, the roll forming apparatus 1 can easily form a taper material M ′ (metal material) whose thickness changes in a taper shape along the longitudinal direction shown in FIG. 2A into a taper stringer TS shown in FIG. 2B. it can. The roll forming apparatus 1 in the present embodiment performs, for example, the final process on a roll forming line in which a plurality of sets of forming rolls having different cross-sectional shapes are arranged on the line. You may perform the process and the shaping | molding of an intermediate process. Moreover, not only a roll forming line but roll forming may be performed alone.

As shown in FIG. 3, the roll forming apparatus 1 includes a base pedestal 2 positioned at a lower portion, a pair of left and right stands 3L and 3R standing up from the base pedestal 2, and upper ends of the left and right stands 3L and 3R. And an upper beam 4 for connecting the two.

Between the two stands 3L and 3R, two horizontal roll shafts 7A and 7B are installed rotatably via a bearing 6. The two roll shafts 7A and 7B are engaged with each other by gears 8A and 8B fixed to the ends thereof. Then, for example, when a rotational driving force R is applied from a driving source such as an electric motor (not shown) provided on one roll shaft 7A, the two roll shafts 7A and 7B are interlocked with each other at a constant speed in opposite rotation directions. Rotate. That is, the roll shaft 7A is a drive shaft and the roll shaft 7B is a driven shaft.

The fixed rolls 11A and 11B are provided concentrically on the roll shaft 7A and the roll shaft 7B, respectively. These fixed rolls 11A and 11B rotate integrally with the roll shafts 7A and 7B, respectively. For example, the upper fixed roll 11B is a stepped roll.

Floating rolls 12A and 12B are provided on the roll shaft 7A and the roll shaft 7B so as to be eccentric, respectively. These floating rolls 12A and 12B are rotatable relative to the roll shafts 7A and 7B, respectively.

The roll shaft 7A is provided with a fixed roll 11A and a floating roll 12A adjacent in the axial direction, and the roll shaft 7B is provided with a fixed roll 11B and a floating roll 12B adjacent in the axial direction. The fixed roll 11A provided on the roll shaft 7A faces the floating roll 12B provided on the roll shaft 7B, and the fixed roll 11B provided on the roll shaft 7B faces the floating roll 12A provided on the roll shaft 7A. is doing. The roll shaft 7B is provided with a spacer 13 for restricting the movement of the floating roll 12B in the axial direction.

As shown in FIGS. 3, 5, and 6, a taper material M ′ (taper stringer TS) is formed between the fixed roll 11A and the floating roll 12B and between the floating roll 12A and the fixed roll 11B. Is done. As described above, the upper fixed roll 11B is a stepped roll, and the outer periphery of the floating roll 12A is sandwiched between the fixed roll 11B and the floating roll 12B. Shape). In this case, the tapered material M 'is also sandwiched between the side surface of the floating roll 12A and the side surface of the floating roll 12B, and between the side surface of the floating roll 12A and the side surface of the fixed roll 11B.

As shown in FIGS. 3 and 4, clearances CA and CB are provided between the roll shaft 7A and the floating roll 12A and between the roll shaft 7B and the floating roll 12B, respectively. The floating rolls 12A and 12B can be eccentric with respect to the fixed rolls 11A and 11B by the clearances CA and CB. The sizes of the clearances CA and CB need to be larger than the difference between the maximum plate thickness and the minimum plate thickness of the taper material M ′. For example, when the maximum plate thickness of the taper material M ′ is 3 mm and the minimum plate thickness is 1 mm, the clearances CA and CB are set larger than the plate thickness difference of 2 mm.

As shown in FIGS. 3 and 4, one adjacent surface in the adjacent portion of the fixed rolls 11 </ b> A and 11 </ b> B and the adjacent floating rolls 12 </ b> A and 12 </ b> B, for example, the side surface of the fixed rolls 11 </ b> A and 11 </ b> B A plurality of (for example, eight) driving recesses 15 are formed in a row.
The same number of drives that are loosely fitted in the driving recesses 15 of the fixed rolls 11A and 11B on the other adjacent surface of the adjacent portions of the fixed rolls 11A and 11B and the floating rolls 12A and 12B, for example, the side surfaces of the floating rolls 12A and 12B. A convex portion 16 is formed.

Eccentric margins EA and EB are provided between the driving concave portion 15 and the driving convex portion 16 so that the floating rolls 12A and 12B can be eccentric. The sizes of the eccentric margins EA and EB are set to be approximately the same as the sizes of the clearances CA and CB between the roll shafts 7A and 7B and the floating rolls 12A and 12B.
In this embodiment, the driving concave portion 15 is formed on the fixed rolls 11A and 11B side and the driving convex portion 16 is formed on the floating rolls 12A and 12B side. Conversely, the driving concave portion 15 is driven on the fixed rolls 11A and 11B side. The convex portion 16 for driving may be formed, and the concave portion 15 for driving may be formed on the floating rolls 12A and 12B side.

For example, the roll width W of the floating roll 12A can be changed. As shown in FIG. 3, the floating roll 12A includes two movable roll faces 12a and 12b that are movable in the axial direction, and sleeves 12c and 12d are integrally formed with the movable roll faces 12a and 12b. Is provided. A flange 12e is provided at the end of the sleeve 12d on the opposite side of the movable roll face 12b.

The sleeve 12d is closely fitted on the outer periphery of the sleeve 12c and is slidable in the axial direction. The sleeves 12c and 12d slide relative to each other in the axial direction so that the axial distance between the movable roll faces 12a and 12b is increased. As a result, the roll width W of the floating roll 12A is changed.

A pressing force in the axial direction is applied to the end of the sleeve 12c and the flange 12e from a hydraulic device (not shown). For example, a constant force toward the side surface of the floating roll 12B is applied to the end portion of the sleeve 12c in the axial direction as indicated by an arrow f1. Further, as indicated by an arrow f2, a certain force toward the side surface of the fixed roll 11B is applied to the flange 12e in the axial direction.

Thereby, it is controlled so that the interval between the movable roll faces 12a and 12b is always opened with a constant force, that is, the roll width W of the floating roll 12A is increased. The above-described clearance CA is provided between the inner peripheral surface of the sleeve 12c and the outer peripheral surface of the roll shaft 7A so that the entire floating roll 12A can be eccentric with respect to the fixed roll 11A.

In the floating roll 12A, the driving convex portion 16 is formed on the movable roll face 12b side, and the driving convex portion 16 penetrates the movable roll face 12a and is provided in the fixed roll 11A. 15 is loosely fitted. For this reason, when the roll shaft 7A and the fixed roll 11A rotate, the rotation is transmitted to the movable roll faces 12a and 12b through the fitting of the driving concave portion 15 and the driving convex portion 16, and the floating roll 12A is rotationally driven. .

As shown in FIG. 4, two pressing rolls 19 are in contact with each other in the vicinity of the outer peripheral portion of the floating rolls 12A and 12B opposite to the contact points with the fixed rolls 11A and 11B. These press rolls 19 are, for example, distributed to positions that are symmetrical with respect to an axis connecting line O that connects the axis C1 and C2 of the roll shafts 7A and 7B when viewed in the axial direction of the two roll shafts 7A and 7B. Is provided.

Similarly, when the roll shafts 7A and 7B are viewed in the axial direction, orthogonal lines L1 and L2 that are orthogonal to the axis connection line O and pass through the axis C1 and C2 of the roll shafts 7A and 7B are the outer circumferences of the floating rolls 12A and 12B. A pair of guide rolls 20 that are in contact with the outer peripheral portion so as to sandwich the floating rolls 12A and 12B are provided at positions that intersect the part. The pressing roll 19 and the guide roll 20 are pivotally supported by common roll carriers 21A and 21B.

As shown in FIG. 4, the shape of the roll carriers 21A, 21B is, for example, a substantially semicircular shape surrounding the lower half of the floating roll 12A and the upper half of the floating roll 12B as viewed in the axial direction of the roll shafts 7A, 7B. Two pressing rolls 19 are axially supported side by side at the center of each of the roll carriers 21A and 21B, and a guide roll 20 is axially supported at both ends of the roll carriers 21A and 21B. In the present embodiment, the two pressing rolls 19 and the two guide rolls 20 are both arranged symmetrically with the axis center connection line O in between, but they are not necessarily positively symmetric.

Furthermore, actuators 23A and 23B for pressing the floating rolls 12A and 12B to the fixed rolls 11A and 11B via the pressing roll 19 are provided. As these actuators 23A and 23B, for example, a hydraulic cylinder, an air cylinder or the like is used.

The actuator 23A is fixed to the base pedestal 2, and the actuator 23B is fixed to the upper beam 4. The actuators 23A and 23B are arranged in the direction along the axis connection line O with the pressing force F at the intersections with the axis connection line O in the roll carriers 21A and 21B, respectively, when viewed in the axial direction of the two roll shafts 7A and 7B. Press.

For this reason, the intermediate point of each pressing roll 19 is pressed toward the floating rolls 12A and 12B by the pressing force F of the actuators 23A and 23B.
The pressing force F of the actuators 23A and 23B is set to a constant force that changes only the cross-sectional shape without changing the plate thickness of the taper material M ′.

The shaft support position (height) of the guide roll 20 should be a position that is orthogonal to the axis connection line O and coincides with the orthogonal lines L1 and L2 that pass through the axis C1 and C2 of the roll axes 7A and 7B. Although desirable, it may be pivotally supported at a position closer to the pressing roll 19 than this position. That is, as shown in FIG. 4, in a range Z1 and Z2 between the shaft center lines C1 and C2 of the roll shafts 7A and 7B and the shaft support position of the pressing roll 19, the shaft center connection line O is sandwiched. What is necessary is just to be axially supported by the both sides of the axial center connection line O. However, it is preferable to set the position as far as possible from the pressing roll 19 within the ranges Z1 and Z2, that is, the positions close to the orthogonal lines L1 and L2.

The roll forming apparatus 1 is configured as described above. When forming the taper material M ′, the fixed roll 11A concentrically provided on the roll shaft 7A and the floating roll 12A provided eccentrically, and the fixed roll 11B provided concentrically on the roll shaft 7B. Further, the taper material M ′ is fed between the floating roll 12B provided so as to be eccentric.

Then, the actuators 23A and 23B press the floating rolls 12A and 12B toward the fixed rolls 11A and 11B via the pressing rolls 19, respectively. Thereby, the cross-sectional shape of the taper material M ′ is finally formed according to the shapes of the fixed rolls 11A and 11B and the floating rolls 12A and 12B.

The plate thickness of the taper material M ′ changes in a taper shape along the longitudinal direction, but the floating rolls 12A and 12B are eccentric with respect to the roll shafts 7A and 7B in accordance with the change in the plate thickness. The thickness difference is absorbed.
For example, as shown in FIG. 3 and FIG. 7B, when the plate thickness of the taper material M ′ is T2 (for example, 2 mm) of the basic plate thickness, the floating roll 12A (B) is moved relative to the roll shaft 7A (B). Are concentric.
As shown in FIGS. 5 and 7A, when the thickness of the taper material M ′ is T1 (for example, 1 mm) thinner than T2, the floating roll 12A (B) faces the roll shaft 7A (B). To decenter in the direction approaching the fixed roll 11B (A).
As shown in FIGS. 6 and 7C, when the thickness of the taper material M ′ is T3 (for example, 3 mm) thicker than T2, the floating roll 12A (B) faces the roll shaft 7A (B). It is eccentric in the direction away from the fixed roll 11B (A).

At that time, the pressing force F of the actuators 23A and 23B is applied to the floating rolls 12A and 12B themselves via the pressing roll 19, and is not applied to the roll shafts 7A and 7B on which the floating rolls 12A and 12B are provided. For this reason, the taper material M ′ is predetermined while applying a constant pressing force F regardless of the eccentric position of the floating rolls 12A and 12B with respect to the roll shafts 7A and 7B, that is, regardless of the thickness of the taper material M ′. It can be formed into a shape.

Therefore, it is not necessary to move the forming roll up and down together with the roll shaft by a servo motor or the like as in the prior art, and the taper material M ′ whose thickness changes in the longitudinal direction is stably roll-formed with a very simple and inexpensive configuration. be able to.

In this roll forming apparatus 1, each of the two pressing rolls 19 that respectively press the floating rolls 12 </ b> A and 12 </ b> B is distributed to positions that are symmetrical with respect to the shaft center connection line O in the axial direction of the roll shafts 7 </ b> A and 7 </ b> B. Is provided. Thereby, the pressing force F of the actuators 23A and 23B is equally applied from the two pressing rolls 19 to the floating rolls 12A and 12B, respectively.

For this reason, for example, compared with the case where one pressing roll 19 is provided at a position that coincides with the axial center connection line O and the floating rolls 12A and 12B are pressed, the pressing roll 19 is pressed by the pressing force of the actuators 23A and 23B. And it can prevent that the position of floating roll 12A, 12B escapes to radial direction. Accordingly, the taper material M ′ can be stably roll-formed by reliably applying the pressing force F of the actuators 23A and 23B to the floating rolls 12A and 12B.

In this roll forming apparatus 1, two pressing rolls 19 that press the floating rolls 12 </ b> A and 12 </ b> B are respectively supported by common roll carriers 21 </ b> A and 21 </ b> B, and the actuators 23 </ b> A and 23 </ b> A are viewed in the axial direction of the roll shafts 7 </ b> A and 7 </ b> B. 23B presses the position of the intersection of the roll carriers 21A and 21B with the axis connection line O.

As a result, the intermediate point of the two pressing rolls 19 provided at positions symmetrical with respect to the axis connection line O is pressed by the actuators 23A and 23B, and therefore the pressing force F of the actuators 23A and 23B is applied to a plurality of pressing forces F. Evenly applied to the roll 19, the floating rolls 12A and 12B can be stably pressed.

In this roll forming apparatus 1, the roll carriers 21A and 21B pass through the axis C1 and C2 of the roll shafts 7A and 7B perpendicular to the axis connection line O when viewed in the axial direction of the roll shafts 7A and 7B. A pair of guide rolls 20 that are in contact with the floating rolls 12A and 12B so as to sandwich the floating rolls 12A and 12B are further pivotally supported at positions where the orthogonal lines L1 and L2 intersect the outer peripheral portions of the floating rolls 12A and 12B.

By providing the pair of guide rolls 20, when the pressing force F of the actuators 23 </ b> A and 23 </ b> B is applied to the floating rolls 12 </ b> A and 12 </ b> B via the pressing roll 19, the guide rolls 20 cause the floating rolls 12 </ b> A and 12 </ b> B to have a diameter. It is held from both directions.

Therefore, the positions of the floating rolls 12A and 12B are prevented from escaping in the radial direction by the pressing force F of the actuators 23A and 23B, and the pressing force F of the actuators 23A and 23B can be reliably applied to the floating rolls 12A and 12B. it can. Thus, by providing the pair of guide rolls 20 at the positions (heights) of the orthogonal lines L1 and L2 passing through the axis C1 and C2 of the roll shafts 7A and 7B, the floating rolls 12A and 12B can be It can be held most stably at the diameter portion.

The pressing force F of the actuators 23A and 23B is set to a constant force that changes only the cross-sectional shape of the taper material M 'without damaging the plate thickness of the taper material M' by the floating rolls 12A and 12B.

If the pressing force F of the actuators 23A and 23B is set to a constant force in this way, even if the floating rolls 12A and 12B are pressed against the tapered material M ′ by this pressing force F, the thickness of the tapered material M ′ is impaired. In other words, the taper material M ′ is roll-formed into a predetermined cross-sectional shape while maintaining the originally planned thickness.

Therefore, the thickness of each part of the taper material M ′ whose thickness changes in a taper shape along the longitudinal direction is not impaired, and the product quality of the taper stringer TS of the aircraft can be improved.

Between the fixed roll 11A provided on the roll shaft 7A and the floating roll 12A, and between the fixed roll 11B provided on the roll shaft 7B and the floating roll 12B, a driving concave portion 15 and a driving convex portion 16 are respectively provided. The rotation of the fixed rolls 11A and 11B is transmitted to the floating rolls 12A and 12B. Further, eccentric margins EA and EB are provided between the driving concave portion 15 and the driving convex portion 16 so that the floating rolls 12A and 12B can be eccentric.

Thereby, the rotational force of the fixed rolls 11A and 11B provided integrally with the roll shafts 7A and 7B is transmitted to the floating rolls 12A and 12B by the fitting of the driving concave portion 15 and the driving convex portion 16. For this reason, it is possible to reliably rotate the floating rolls 12A and 12B without slipping, thereby improving the roll formability of the tapered material M '.

Moreover, since the eccentric margins EA and EB that allow the floating rolls 12A and 12B to be eccentric are provided between the driving concave portion 15 and the driving convex portion 16, the floating rolls 12A and 12B are connected to the roll shaft 7A, The taper material M ′ whose thickness can be changed can be formed smoothly while being rotationally driven while allowing eccentricity with respect to 7B.

Since the roll width W of the floating roll 12A can be changed, even if the cross-sectional shape of the metal material such as the taper material M ′ has a channel-shaped recess, the inner dimension of the floating roll 12A The width W can be matched, and the metal material can be accurately roll-formed.

In this embodiment, only the floating roll 12A can change the roll width W, but the floating width can also be changed for the floating roll 12B and the fixed rolls 11A and 11B.

As described above, according to the roll forming apparatus 1 according to the present embodiment, it is possible to stably perform roll forming even with the taper material M ′ whose thickness changes in the longitudinal direction with a simple and inexpensive configuration. .

It should be noted that the present invention is not limited to the configuration of each of the embodiments described above, and can be appropriately modified or improved within the scope not departing from the gist of the present invention. The form is also included in the scope of the right of the present invention.

For example, in the above-described embodiment, the two roll shafts 7A and 7B are provided in a state in which the distance between the axes is fixed, but the distance between the axes may be variable.
Further, the shape of the taper material M ′ and the shape of the taper stringer TS formed by the taper material M ′ are not limited to those of the above embodiment.

DESCRIPTION OF SYMBOLS 1 Roll forming apparatus 7A, 7B Roll axis | shaft 11A, 11B Fixed roll 12A, 12B Floating roll 15 Drive recessed part 16 Drive convex part 19 Press roll 20 Guide roll 21A, 21B Roll carrier 23A, 23B Actuator CA, CB Clearance C1, C2 Roll axis shaft center line EA, EB Eccentric margin F Actuator pressing force L1, L2 Orthogonal line M 'orthogonal to axis center connection line Metal material O Center axis connection line T1, T2, T3 connecting axis center line Thickness W Roll width Z1, Z2 Range between the pivot position of the roll shaft and the pivot position of the pressing roll

Claims (7)

1. Two parallel roll axes,
   A fixed roll provided concentrically with respect to one of the two roll shafts;
   A floating roll that is provided eccentrically via a clearance with respect to the other of the two roll shafts and faces the fixed roll;
   A pressing roll in contact with the outer peripheral portion of the floating roll opposite to the contact with the fixed roll;
   An actuator for pressing the floating roll toward the fixed roll via the pressing roll;
   A roll forming apparatus comprising:
2. A plurality of the pressing rolls are provided at a position symmetrical with respect to an axis connecting line connecting the axis lines of the two roll shafts when viewed in the axial direction of the two roll axes. The roll forming apparatus according to 1.
3. The plurality of pressing rolls are pivotally supported by a common roll carrier, and the actuator presses an intersection position of the roll carrier with the axis connection line as viewed in the axial direction of the two roll shafts. 2. The roll forming apparatus according to 2.
4. An axis connecting line connecting the axis lines of the two roll shafts is sandwiched between the axis support position of the roll shaft provided with the floating roll and the axis support position of the pressing roll. The roll forming apparatus according to any one of claims 1 to 3, further comprising a pair of guide rolls that are pivotally supported on both sides of the axis connection line and abut against the outer peripheral portion of the floating roll.
5. The pressing force of the actuator is set to a constant force that changes only the cross-sectional shape of the metal material without impairing the plate thickness of the metal material sandwiched between the fixed roll and the floating roll. The roll forming apparatus according to any one of 4.
6. A plurality of sets of the fixed roll and the floating roll are provided,
   The two roll shafts are provided with the fixed roll and the floating roll adjacent to each other in the axial direction,
   The fixed roll provided on each of the roll shafts is opposed to the floating roll provided on the other roll shaft,
   A plurality of driving recesses arranged in the circumferential direction are formed on one adjacent surface of the fixed roll and the floating roll that are supported by one roll shaft and adjacent to each other, and the other adjacent surface has A plurality of drive protrusions that are loosely fitted in the drive recesses are formed,
   The roll forming apparatus according to any one of claims 1 to 5, wherein an eccentric margin that allows the floating roll to be eccentric is provided between the driving concave portion and the driving convex portion.
7. The roll forming apparatus according to any one of claims 1 to 6, wherein a roll width of at least one of the fixed roll and the floating roll can be changed.

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