JP2964213B2 - Roll bending equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a roll bending apparatus, and more particularly to a so-called three-roll type roll bending apparatus including an upper roll and a pair of lower rolls provided in parallel with the upper roll.

[0002]

2. Description of the Related Art A so-called three-roll type roll bending apparatus provided with a pair of lower rolls below a metal upper roll is used for various bending processes because the apparatus is simple. In this type of three-roll type roll bending apparatus, as shown in FIG. 1, both ends of a lower roll (2a) (2b) are supported by a support arm (65) swinging within a certain range. 65), the lower rolls (2a) and (2b) are supported by the upper roll (1).
Is adjustable in a range between a state in which it is in contact with and a state in which it is separated by a certain distance therefrom.

Accordingly, the bending curvature of the work (W) can be adjusted by this adjustment, and the end of the work (W) can be bent. Further, when the width of the work (W) is large or when the thickness of the work (W) is large, the lower rolls (2a) and (2b) having a relatively small diameter are likely to bend during bending. . When such bending occurs, the bending curvature in the width direction of the work (W) is not constant. Work (W) according to the deflection
At the center (the center of the lower rolls (2a) and (2b)) is smaller than the bending curvature at both ends.

As a countermeasure in such a case, as shown in FIG. 2, there is a method in which the central portion of the lower rolls (2a) (2b) can be supported from below by a pair of backup rolls (41) (41). . In this case, since the central portion of the lower rolls (2a) and (2b) is supported from below, the above-described bending is unlikely to occur,
The disadvantage that the bending curvature is not uniform in the width direction of the work (W) is solved.

[0005] The support position of the backup rolls (41) and (41) must be adjustable. Conventionally, a support mechanism using hydraulic pressure or the like is employed. In the case of using this method, the backup roll (41) (41)
Although there is an advantage that the supporting position of the lower roll (2a) (2b) is independent of the swinging motion of the supporting arms (65) (65) of the lower roll (2a) (2b), the lower roll (2a) (2b) In order to smoothly swing and operate the backup rolls (41) and (41) synchronously with them, a special interlocking control device is required.

The present invention has been made in view of the above point, and has been made in consideration of the following problem: "A pair of lower rolls provided below the upper roll (1)".
(2a) Both ends of (2b) are supported by support arms (65) and (65), and the central part of these lower rolls (2a) and (2b) is a backup roll (41).
(41) While supporting from below, said support arm (65)
(65), the support position of the lower rolls (2a) and (2b) and the support position of the backup rolls (41) and (41) are adjustable.
b) Support position adjustment operation and backup roll (41) (4)
It is an object of the present invention to synchronize the operation of adjusting the support position of the center portion of the lower roll according to 1) with certainty of the synchronous operation and smoothly and promptly performing these operations.

[0007]

[Technical Means] The technical means of the present invention for solving the above problems is as follows: "The backup rolls (41) and (41) are
5) An arm whose fulcrum is a fulcrum axis (69) coaxial with the fulcrum (650) of (65)
(42) so that the arm (42) and the supporting arm
(65) an adjusting device for adjusting the support position of (65), a gear portion (66) provided on each of the support arms (65) and a similar gear portion (43) provided on the arm (42), It comprises a gear train (7) (7) of the same configuration that meshes with these gear parts individually, and a driving device (8) that rotationally drives a common driving shaft (71) of these gear trains (7) (7). did"
That is.

[0008]

The above technical means operates as follows. When the driving device (8) is driven to rotate, the driving shaft
The gear trains (7) and (7) rotate according to the rotation angle of (71). Accordingly, each of the lower rolls (2a) and (2b) is provided with a supporting arm (65) (65) and an arm (4) according to the amount of forward / reverse rotation of the driving device (8) corresponding thereto.
2) is rocked. Since the gear trains (7) and (7) interposed between these and the driving shaft (71) have the same configuration, the swing angle of the support arms (65) (65) and the arm (42) Are matched, and the movement ends.

Thus, the respective supporting positions of the lower rolls (2a) and (2b) can be adjusted. When the work (W) is a thin plate, a predetermined bending process may be executed as it is.

[0010]

According to the present invention having the above-described configuration, the present invention has the following specific effects. When adjusting the respective supporting positions of the lower rolls (2a) and (2b), the support arm (65) (65) supporting both ends by the operation of the gear train (7) interlocked with the driving device (8), and the backup arm Since the arm (42) supporting the central portion swings synchronously via the rolls (41) and (41), the adjusting operation of the supporting position of the lower rolls (2a) and (2b) can be performed smoothly and at high speed. .

[Invention of Claim 2]
In the invention of the present invention, the support position of the lower roll central portion by the backup roll (41) (41) can be set higher than the support position of both ends by the support arms (65) (65),
It is an object of the present invention to perform an operation for this purpose smoothly and promptly.

The technical means to be acted on for this is "arm (42)
One intermediate shaft (72) of the gear train (7) meshing with the gear portion (43) of
A linear drive device (73) is provided which makes the intermediate shaft (72) freely movable in the axial direction and reciprocates the intermediate shaft (72) in the axial direction between the retracted position and the advanced position, and extends the intermediate shaft (72) from the retracted position. A paired screw mechanism (74) for rotating the arm (42) in the direction to lift the lower roll by rotating the driven side of the gear train (7) forward by a certain angle by moving is there.

In the method employing this means, the work (W)
Is a thick plate, or the width is wide (bending area is wide)
In this case, the central part of the lower rolls (2a) and (2b) should be closer to the upper roll (1) than both ends in order to eliminate bending failure due to excessive bending of the lower rolls (2a) and (2b) during bending. The support positions of the backup rolls (41) and (41) are set so as to be slightly approached (higher eyes).

In order to do this, the support position of the lower rolls (2a) (2b) by the support arms (65) and (65) and the support position by the arm (42) are set, and then the intermediate shaft (72). Is moved from the retracted position to the advanced position. In conjunction with this, the driven side of the gear train (7) is positively rotated by the action of the screw pair mechanism (74), and the backup rolls (41) (41) provided on the arm (42) are moved to the central portion of the lower roll. To the upper roll (1) side. The above operation for pushing up the center of the lower roll gear train (7) toward the upper roll (1) can be performed separately for the lower rolls (2a) and (2b).

In this way, by simply moving the intermediate shaft (72), each of the lower rolls (2a) and (2b) is set in a state in which the center is slightly lifted toward the upper roll (1) from both ends. I can do it. Further, this operation can be arbitrarily performed as needed. In addition, the center of the lower rolls (2a) and (2b) is
(1) To lift to the side, only the intermediate shaft (72) is linearly moved from the retracted position to the advanced position, so that the operation for this can be performed quickly. Further, it is easy to link with adjustment of the support position of the lower rolls (2a) (2b).

[Other inventions] The invention defined in claim 4 is a limitation on the structure of the screw pair mechanism (74) in the invention of claim 2, and the structure is described as follows. A first gear (701) transmitted to the driving side of the gear train (7) and a second gear (702) transmitted to the driven side are attached to the first gear (7).
01) is a spur gear, and the screw pair mechanism (74) is a combination of the second gear (702) configured as a helical gear and a helical gear type driven side gear meshing with the second gear (702). The direction of the rib is the direction in which the driven gear is driven to rotate forward by the movement of the intermediate shaft (72) from the retracted position to the advanced position ”. According to this, since the screw pair mechanism (74) is constituted only by using the helical gear, the screw pair mechanism (74)
Can be simplified.

The invention defined in claim 5 is that the screw pair mechanism (74) in the invention of claim 2 is limited to another configuration, and the configuration is such that the intermediate shaft (72) has a gear. A first gear (701) transmitted to the driving side of the row (7) and a second gear (702) transmitted to the driven side are mounted, and the intermediate shaft (72)
Is divided into a driving side shaft portion including the first gear (701) and a driven side shaft portion including the second gear (702). A spline shaft coupling (721) having a configuration in which the driven shaft portion is connected to the driven shaft portion so as to be relatively movable in the axial direction and the spline groove is twisted with respect to the axis line, and the direction of the torsion of the spline groove is changed to the intermediate shaft (72). The spline shaft coupling by moving from the retracted position to the advanced position.
(721) is set to the direction in which the driven side is driven to rotate forward. ”

Also in this case, by moving the intermediate shaft (72) from the retracted position to the advanced position, the spline shaft coupling (7
21) The driving side moves relative to the driven side. Thus, the driven side of the spline shaft coupling (721) is driven to rotate forward, so that the screw-and-even mechanism (74) can be constituted by a simple mechanism as in the case of the fourth aspect. In this case, there is no need to move the driven gear in the axial direction.

[0019]

Next, an embodiment of the present invention will be described in detail with reference to the drawings. The embodiment shown in FIGS. 3 to 6 uses the upper roll (1).
The present invention is embodied in a three-roll type roll bending apparatus including a lower roll (2a) and a lower roll (2b) provided in parallel on both lower sides of the roll. Further, in this device, the fulcrum (650) of the support arm (65) (65) for swingably supporting both ends of the lower roll (2a) and the support arm (65) (65) for supporting both ends of the lower roll (2b) Fulcrum (65) (6
50) are provided coaxially below the upper roll (1), and a fulcrum coaxial with the fulcrum (650) is provided on the arm (42) of the lower roll (2a) (2b).
The fulcrum shaft (69) of (42) is used.

Hereinafter, each part will be described in detail. [Supporting structure of upper roll (1)] Both ends of the upper roll (1) are rotatably supported by a main arm (11) and an auxiliary arm (12) provided on side frames (61) (61). You. One main arm (11)
As shown in FIG. 3, the main arm (11) has a built-in drive motor (M) for driving the upper roll (1) to rotate integrally with the right side frame (61). . The other left side frame (61) has a shaft support (122) provided on its outer surface.
Thus, the auxiliary arm (12) is rotatably supported. The auxiliary arm (12) has a bearing (121) for supporting the tip of the upper roll (1) at the upper end, and the lower end serves as the shaft support (122).

A hydraulic cylinder (62) is swingably attached to the side frame (61), and its output shaft extends outward from a shaft support (122) at the lower end of the auxiliary arm (12). It is rotatably connected to the tip of the arm. Therefore, when the hydraulic cylinder (62) is operated and its output shaft is advanced, the auxiliary arm (12) stands upright, and the bearing (121) at the tip moves to the upper roll.
When the output shaft is retracted from this state, the auxiliary arm (12) falls outward and the space between the upper roll (1) and the side frame (61) is lowered. It will be in the open posture.

[Regarding Lower Rolls (2a) and (2b)]
a) and (2b) are provided before and after the upper roll (1), and the distance between the upper roll (1) and the upper roll (1) is adjustable. Therefore, both ends of each of the lower rolls (2a) and (2b) are supported by a support arm (65) provided in the side frame (61) so as to be reciprocally rotatable, as shown in FIGS. . The support arm (65) is provided at a fulcrum (6) below both ends of the upper roll (1) in the side frame (61).
50), and the arc-shaped peripheral edge on the tip side is a gear portion (66). In this embodiment, the fulcrum (650) of the support arm (65) (65) supporting the lower roll (2a) and the fulcrum (650) of the support arm (65) (65) supporting the lower roll (2b) And as a common axis. Therefore, the bearing portion serving as the rotation fulcrum of the support arm (65) of the lower roll (2a) overlaps from the outside of the bearing portion serving as the rotation fulcrum of the support arm (65) of the lower roll (2b) and overlaps with the fulcrum (650). ). This point is not shown.

A gear train (7) transmitted to a driving shaft (71) meshes with the gear portion (66). The driving shaft (71) is configured to be normally and reversely rotated by a driving device (8). Therefore, the lower rolls (2a) (2
The support arms (65) and (65) supporting both ends of b) are reciprocated synchronously and swing in the direction of an arc. Lower roll (2
In the middle of a) and (2b), as shown in FIGS. 3 and 5, a pair of backup rolls (41) and (41) come into contact with each other from below. The backup rolls (41) and (41) are rotatably supported by a pair of arms (42) and (42), and the arms (42) and (42) are supported by the support arms (6).
The fulcrum shaft (69) is coaxial with the fulcrum of (5), and is supported by a fulcrum shaft (69) installed between a pair of first frame plates (68) (68) at the center. A gear (43) is provided at the tip of the arm (42), and a gear train (7) provided between the arm (42) and the driving shaft (71) meshes with the gear (43). The gear ratio of each meshing part of the gear train (7) meshing with the support arm (65) and the gear train (7) meshing with the arm (42), and from the fulcrum of the support arm (65) and the arm (42) to the center of the lower roll Are set to the same length.

Therefore, the arm (42) is rotated by the same angle in synchronization with the support arm (65), and
Even if it is reciprocated so that the distance between (1) and the lower rolls (2a) (2b) is adjusted, the backup rolls (41) (41) (41) ) Is supported in contact with. Further, no matter where the lower rolls (2a) and (2b) are located, the contact positions of the backup rolls (41) and (41) do not change. That is, the relationship between the backup roll and the lower rolls (2a) (2b) does not change.

As shown in FIG. 3, an intermediate shaft reciprocally driven in the axial direction by a linear drive device (73) is provided on the gear train (7).
(72) is provided. This intermediate shaft has a first gear (701) transmitting to the driving side of the gear train (7), and a second gear (701) transmitting to the driven side.
And the first gear (701) is a spur gear, and the second gear (702) is a helical gear.
Accordingly, when the intermediate shaft (72) is moved from the retracted position to the advanced position by the linear drive device (73), the second gear (702) and the driven gear engaged with the second gear (702) are operated by the meshing of the helical gear. Is driven to the constant angle forward side. In this embodiment, the meshing portion of the helical gear is the screw pair mechanism (74) described above.

[Actual Roll Bending] In this roll bending apparatus, the gear trains (7) and (7) corresponding to the lower rolls (2a) and (2b) respectively.
Since the driving devices (8) and (8) are separately provided to drive the lower rolls (8) and (8), the lower rolls (2a) and (2b) and the upper roll ( 1) Separately adjust the interval with.

In this state, the upper roll (1) and the lower roll (2a)
When the upper roll (1) is rotated by the drive motor (M) with the work (W) interposed between the work (W) and the work (W), the work (W) is bent to a predetermined curvature. In order to bend the work (W), for example, as shown in FIGS. 4 and 5, the front end of the work (W) is pressed between the upper roll (1) and the lower roll (2a). Thereafter, the driving device (8) corresponding to (2b) is driven to drive the gear train.
In conjunction with (7), the lower roll (2b) is lifted to a predetermined position. Thereby, end bending can be performed.

When bending the other end, the rear end of the work (W) is pressed by the upper roll (1) and the lower roll (2b), and the lower roll (2a) is pressed in the same manner as described above. What is necessary is just to lift to a predetermined position. At the time of this end bending, or at the time of the above-described bending of the intermediate portion, when the thickness of the work (W) is large, etc.,
After driving the driving devices (8) and (8) to set the support positions at both ends of the lower rolls (2a) and (2b) to predetermined positions, the linear driving device (7
3) is driven forward. Thereby, the intermediate shaft (72) advances from the retreat position to the advance position by a certain distance. Then, the first gear (701) of the intermediate shaft (72) meshes with the driving side spur gear, and the second gear (702) meshes with the driven side helical gear.
Is advanced to the driven gear side. As a result, the driven helical gear rotates forward, and the gear portion (4) in the gear train (7) is rotated.
The arm (42) is lifted by the transmission operation of the engagement portion with (3). Therefore, the center of the lower rolls (2a) (2b)
(65) Roll above the support position supported by (65)
(1) Lifted to the side. That is, the central portion of each of the lower rolls (2a) and (2b) bends to a certain degree toward the upper roll (1) in accordance with the forward drive operation of the linear drive device (73).

Thus, the lower roll (2a) (2
Bending failure due to the center part of b) flexing in the direction away from the upper roll (1) can be prevented. [Others] In the above embodiment, the lower rolls (2a) and (2b) are moved by linearly moving the meshing portions of the helical gears.
The driven side of the gear train (7) is driven at a fixed angle positive so that the center of each of the gears is bent toward the upper roll (1) side. However, as shown in FIG. On the other hand, a configuration using a splined shaft coupling (721) twisted can be adopted.

In this embodiment, the intermediate shaft (72) is connected to the first gear (70).
1), a driving-side shaft portion (722) including the second gear (702);
The driven side shaft portion (723) and the driven side shaft portion (722) are connected to the driven side shaft portion (723) so as to be relatively movable in the axial direction. A splined shaft coupling (721) having a twisted configuration, wherein the direction of the torsion of the groove of the spline is moved from the retracted position to the advanced position of the intermediate shaft intermediate shaft (72).
Is driven in the direction of forward rotation.

In this case, since the first gear (701) of the spur gear type provided on the driving shaft (722) is engaged with the driving side, the driving shaft (722) is driven by the linear drive device (73). Is linearly moved from the retracted position to the advanced position, the driving side shaft (722) is moved without rotating. Accordingly, the input side of the spline shaft coupling (721) is linearly moved in a fixed posture without rotating. When the output side of the spline shaft coupling (721) meshes with the input side, the second gear (702) is driven forward only by an angle corresponding to the twist angle of the groove of the spline.

As a result, the driven side of the gear train (7) is driven forward and the central portion of the lower rolls (2a) and (2b) is bent toward the upper roll (1). In this case, the spline joint (721)
This is the screw pair mechanism (74) described above. In any of the above embodiments, it is desirable that the driving device (8) is a brake motor. The drive train (8) drives the gear train.
The lower rolls (2a) and (2b) are individually lifted toward the upper roll (1) due to the interlocking action with (7).
The reverse drive force acts on the gear train (7) by the pushing force of (2a) and (2b). As described above, when the driving device (8) is a brake motor, the reverse rotation can be prevented by the braking force. A drive device of a type in which a blocking force against a return drive external force always acts like other hydraulic drive devices.
(8)

Further, a braking mechanism may be separately added.
In addition, regarding the screw pair mechanism (74), since the rotation angle on the driven side with respect to the axial movement distance is set to be small,
There is a self-locking action (reverse rotation preventing action). Therefore, the screw pair mechanism (74) does not require a special device for preventing reverse rotation due to external force.

In the above embodiment, the arc-shaped gear (66) is formed at the tip of the support arm (65), and the arc-shaped gear (43) is formed at the tip of the arm (42). These gear portions are not limited to the above-described configuration, and may be configured such that the separately formed gear portion rotates integrally with the support portion (65) and the arm (42).

[Brief description of the drawings]

FIG. 1 is an explanatory view of a conventional example.

FIG. 2 is an explanatory view of another conventional example.

FIG. 3 is a front view of the embodiment of the present invention.

FIG. 4 is a sectional view taken along line XX.

FIG. 5 is a sectional view taken along line YY.

FIG. 6 is an explanatory view of a main part of another embodiment.

[Explanation of symbols]

 (1) ... Upper roll (2a) (2b) ... Lower roll (W) ... Work (41) ... Backup roll (650) ... Support point (65) ... Support arm ( 69) ・ ・ ・ Support shaft (42) ・ ・ ・ Arm (66) ・ ・ ・ Gear part (43) ・ ・ ・ Gear part (7) ・ ・ ・ Gear train (72) ・ ・ ・ Intermediate shaft (73) ・..Linear driving devices (74) ・ ・ ・ Screw pair mechanism

Claims (5)

(57) [Claims] 1. Both ends of a pair of lower rolls (2a) (2b) provided below an upper roll (1) are supported by support arms (65) (65),
The central part of these lower rolls (2a) (2b) is a backup roll
(41) While being supported from below by (41), the support arm
(65) In a three-roll type roll bending apparatus in which the support position of the lower rolls (2a) and (2b) by the (65) and the support position by the backup rolls (41) and (41) can be adjusted, the backup roll (41) (41) is swingably supported by an arm (42) having a fulcrum shaft (69) coaxial with a fulcrum (650) of the support arms (65) and (65), and the arm (42) and the support arm are supported. (65) A gear unit provided on each of the support arms (65) with an adjusting device for adjusting the support position of (65).
(66) and similar gear portions (43) provided on the arm (42), gear trains (7) and (7) of the same configuration individually meshing with these gear portions, and these gear trains (7) and (7) And a driving device (8) for rotatingly driving the common driving shaft (71). 2. A gear train meshing with a gear portion (43) of an arm (42).
(7) a linear drive device (73) that makes one intermediate shaft (72) freely movable in the axial direction and that reciprocates the intermediate shaft (72) in the axial direction between the retracted position and the advanced position; The intermediate shaft (7
2) is moved from the retracted position to the advanced position to rotate the driven side of the gear train (7) forward by a predetermined angle and rotate the arm (42) in the direction of lifting the lower roll (7).
The roll bending apparatus according to claim 1, further comprising (4). 3. The gear part (66) is an arc-shaped gear part formed at the swing end of the support arm (65), and the gear part (43) is formed at the swing end of the arm (42). 3. The roll bending apparatus according to claim 2, wherein the gear section has an arc shape. 4. A first gear (701) transmitted to the driving side of the gear train (7) and a second gear (702) transmitted to the driven side of the gear train (7) are mounted on the intermediate shaft (72). (701) is a spur gear,
The screw pair mechanism (74) is a combination of the second gear (702) configured as a helical gear and a driven-side gear of a helical gear type that meshes with the second gear (702). (72) The roll bending apparatus according to claim 2 or 3, wherein the driven gear is driven to rotate forward by movement from the retracted position to the advanced position. 5. An intermediate shaft (72) is provided with a first gear (701) transmitted to the driving side of the gear train (7) and a second gear (702) transmitted to the driven side. (72), a driving-side shaft portion provided with the first gear (701), and the second gear (70).
2) and the driven side shaft section with
4) A spline shaft coupling (721) in which the driving side shaft portion and the driven side shaft portion are connected so as to be relatively movable in the axial direction and the spline groove is twisted with respect to the axis, and the spline groove is provided. 4. The roll bending apparatus according to claim 2, wherein the direction of the torsion is such that the driven side of the splined shaft coupling (721) is driven to rotate forward by the movement of the intermediate shaft (72) from the retracted position to the advanced position. .