JPH04228209A - Rolling equipment for tapered leaf spring - Google Patents

Abstract

PURPOSE:To offer a rolling equipment capable of rolling tapered leaf springs in accurate shapes. CONSTITUTION:An upper roll 16 and a lower roll 17 which are set in the main body 11 of a rolling mill are synchronously driven in vertical direction while maintaining a state in parallel to each other by means of a crank mechanism and a servomotor. At a measuring part 12, a rotary contactor 90 is adopted. This contactor 90 is rotated around the axial line along the direction of the length of the workpiece as the workpiece A comes out of a gap between the rolls 16, 17, and is tilted against the tip face A1 of a horizontal workpiece; therefore, even a thin contactor 90 is not detached from the tip face A1 of the workpiece. Consequently, the contactor 90 is fully set into the gap between the rolls 16, 17 before rolling.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tapered leaf spring rolling apparatus used for rolling tapered leaf springs such as suspension leaf springs for automobiles.

0002

2. Description of the Related Art A rolling mill 1 as shown in FIG. 9 has been proposed as a conventional device for rolling tapered leaf springs. This rolling mill 1 uses hydraulic servo cylinders 4 and 5 to change the rolling amount of a pair of upper and lower rolls 2 and 3 from time to time according to the tapered shape of a leaf spring (work A) to be rolled. There is. The distance between the upper roll 2 and the lower roll 3 is detected by sensors 6 and 7 such as Magnescale,
By feeding back the detected value to the hydraulic servo cylinders 4 and 5, the roll spacing is controlled to a predetermined roll interval.

[0003] Furthermore, in an apparatus that performs such taper rolling, it is necessary to accurately grasp the longitudinal position of the workpiece A, and a contactor 8 as shown in FIG. 10 is used as length measuring means for this purpose. It has been adopted. This contactor 8 is brought into contact with the tip end surface A1 of the workpiece A, and moves forward together with the workpiece A as rolling progresses. Therefore, in this case, by detecting the position of the contactor 8, the longitudinal position of the workpiece A can be measured. Then, the above-mentioned roll interval control is performed according to the measured length value.

0004

In the case of the conventional rolling mill 1, since hydraulic servo cylinders 4 and 5 are used, rolling accuracy decreases due to changes in oil temperature. In addition, since the servo systems are independent on the left and right sides, a slight synchronization difference in the servo systems will impair the parallelism of the upper roll 2 to the lower roll 3, resulting in a thickness difference in the width direction of the workpiece A. This may cause warpage or bending in the width direction of the long workpiece A. This tendency becomes more pronounced as the rolling speed increases, and thus becomes an obstacle to increasing the rolling speed. Furthermore, the hydraulic servo cylinders 4 and 5 not only require special consideration to prevent oil leakage, but also have problems in operational reliability and maintainability, such as not allowing the slightest amount of dirt to get mixed in.

Furthermore, when the conventional contact 8 described above is employed, if the thickness (vertical dimension) t of the contact 8 is small, the contact 8 tends to come off from the tip surface A1 of the workpiece A, making measurement difficult. length may become impossible. For this reason, contact 8
It is necessary to make the thickness t considerably large, but if the contactor 8 is made thicker, the end surface 8a of the contactor 8 cannot be sufficiently inserted between the rolls 2 and 3 at the initial stage of rolling. As a result, a length L0 from the tip of the workpiece A becomes a dead zone in which length measurement is impossible, and the portion of length L0 cannot be tapered rolled, leading to deterioration of yield.

Therefore, an object of the present invention is to be able to accurately maintain the parallelism between rolls and the distance between the rolls without using a hydraulic servo cylinder, and to make it possible to accurately maintain the parallelism between rolls without using a hydraulic servo cylinder. It is an object of the present invention to provide a rolling device that can perform desired taper rolling over the entire length of a workpiece without coming off.

[0007]

[Means for Solving the Problems] The apparatus of the present invention developed to achieve the above object comprises a frame, a pair of rolling rolls including an upper roll and a lower roll provided on the frame, and a rolling roll pair provided on the frame. a pair of left and right upper roll holders that are mounted on the frame and rotatably support both left and right ends of the upper roll and are movable in the vertical direction with respect to the frame; A pair of left and right lower roll holders are supported on the upper roll holder, a pair of pressure rams are provided on each of the upper roll holders and can move vertically together with the upper roll holder, and A crankshaft having an eccentric shaft portion that can be driven in a direction, a drive unit equipped with a servo motor for rotating the crankshaft, and a roll interval corresponding to the tapered shape of the tapered leaf spring to be formed. and a controller that controls the movement of the servo motor so that the servo motor is moved.

Further, the length measuring section is a rotary type that is provided on the exit side of the widthwise center of the pair of rolling rolls, is brought into contact with the end surface of the workpiece, and is rotatable around an axis along the longitudinal direction of the workpiece. At the position where the contactor enters the gap between the upper roll and the lower roll, the contactor is tilted horizontally to align the contactor with the tip of the workpiece, and the workpiece is removed from the gap. It includes a contact rotation mechanism that rotates the contact around the axis as it is fed out, and a detector that detects the position at which the contact has moved in the longitudinal direction of the workpiece.

[0009]

[Operation] The servo motor is rotated according to the shape of the tapered leaf spring to be formed. When the crankshaft is rotated by the servo motor, the left and right pressurizing rams move up and down in synchronization with each other according to the amount of eccentricity of the eccentric shaft portion of the crankshaft, and the upper roll holder is moved up and down. , the roll spacing of the rolling roll pair changes. By constantly changing the roll interval, the workpiece is rolled into a desired tapered shape.

[0010] Before rolling starts, the contactor is inserted into the gap between the upper roll and the lower roll. When rolling starts, as the workpiece comes out of the pair of rolling rolls, the contactor is pushed and moved, and its position is detected by a detector. As the workpiece comes out of the pair of rolling rolls, this contactor rotates around the axis along the longitudinal direction of the workpiece, and is tilted with respect to the horizontal workpiece tip surface, so that the contactor tip surface is thin. The contact will not come off the front end surface of the workpiece even when the contactor is in contact with the widthwise center of the workpiece.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 1 to 7. The rolling apparatus 10 of this embodiment is for forming a steel workpiece (a plate spring as a rolled object) into a desired tapered shape by rolling it in its thickness direction. The rolling mill body section 11 shown in FIG. 4 and the length measuring section 12 shown in FIGS. 4 to 6 are constructed.

First, the configuration of the rolling mill main body 11 will be explained below. A rolling roll pair 18 consisting of an upper roll 16 and a lower roll 17 is provided on a frame 15 serving as a base of the rolling mill main body 11 . The upper roll 16 and the lower roll 17 are rotationally driven in the rolling direction in synchronization with each other by a roll drive mechanism 19 (see FIG. 1). The roll drive mechanism 19 includes a motor 20 and a pulse generator 21.

The upper roll 16 is rotatably supported by a pair of left and right upper roll holders 22 and 23 provided on the frame 15. The lower roll 17 is supported by the frame 15 by a pair of left and right lower roll holders 25 and 26.

The lower roll holders 25 and 26 hold the roll 16
, 17, the height adjustment mechanism 30,
31, the vertical positions can be finely adjusted independently of each other. The height adjustment mechanisms 30 and 31 are
Tapered arrows 32 and 33 that are movable in the horizontal direction and a tapered receiving member 35 that slides on the upper surface side of the tapered arrows 32 and 33
, 36, and driving means 37, 38 for driving the tapered arrows 32, 33 in the above direction. Drive means 37, 3
8 is equipped with threaded rods 43, 44 rotated by motors 41, 42 with reduction gears, and the tapered arrows 32, 33 are horizontally moved by a desired amount according to the direction and amount of rotation of the threaded rods 43, 44. It is designed to move only. When the tapered arrows 32, 33 are moved in the horizontal direction, the heights of the lower roll holders 25, 26 change.

The lower roll holders 25 and 26 are provided with roll balance cylinders 47 and 48 that operate in the vertical direction. The roll balance cylinders 47 and 48 bias the upper roll holders 22 and 23 in the upward direction.

Pressure rams 51, 52 are provided above the upper roll holders 22, 23. This pressurizing ram 51,
52 is vertically movably held by the frame 15 so as to be vertically movable together with the upper roll holders 22 and 23. The pressure rams 51 and 52 are moved up and down by a crank mechanism 53.

The configuration of the crank mechanism 53 is as described below. As shown in FIG. 3, pressurizing rams 51, 52
Guide portions 55 and 56 are provided on the upper part of the rectangular hole using the upper and lower horizontal surfaces of the rectangular hole. This guide part 55,5
6 are in contact with rectangular sliders 57 and 58. The length L1 of the sliders 57, 58 is shorter than the length L2 of the guide portions 55, 56, and the height H of the sliders 57, 58 is shorter than the length L2 of the guide portions 55, 56.
is set to be slightly smaller than the height of the guide portions 55 and 56. Therefore, the sliders 57 and 58 can only move relative to the guide portions 55 and 56 in the horizontal direction (in the horizontal direction in FIG. 3), and are restricted from moving in the vertical direction.

Circular holes 61 and 62 are provided in the sliders 57 and 58.
is provided. The crankshaft 6 is inserted into these holes 61 and 62.
Eccentric shaft portions 64 and 65 of No. 3 are rotatably inserted therethrough. The main shaft portions 66 and 67 of the crankshaft 63 are connected to the frame 1.
5 is rotatably supported. As shown in FIG. 2, the center C2 of the eccentric shaft portions 64, 65 is
They are each eccentric by Δd with respect to the rotation center C1 of No. 7. Therefore, when the crankshaft 63 rotates, the eccentric shaft portions 64 and 65 rotate eccentrically at a radius of Δd.

The crankshaft 63 is rotated by a drive section 70. The drive section 70 includes a servo motor 71. The rotational force of the servo motor 71 is transmitted to the primary drive shaft 74 via the reducer 72 and the coupling 73. The primary drive shaft 74 is connected to a secondary drive shaft 77 via a joint mechanism 76 . The joint mechanism 76 equalizes the power transmission to the crankshaft 63 by the gears 80 to 83 described below on the left and right sides.
The relative positions of the drive shafts 74 and 77 in the rotational direction can be adjusted.

Drive gears 80 and 81 are attached to the drive shafts 74 and 77, respectively. Drive gears 80 and 81 mesh with driven gears 82 and 83. driven gear 82,
83 is attached to the main shaft portions 66 and 67 of the crankshaft 63. Therefore, when the servo motor 71 rotates, the eccentric shaft parts 64 and 65 rotate eccentrically depending on the direction and amount of rotation, and the sliders 57 and 68 move eccentrically accordingly.

That is, when the crankshaft 63 rotates, the pressure rams 51 and 52 move in the vertical direction together with the sliders 57 and 58 due to the vertical movement components of the eccentric shaft portions 64 and 65. Further, due to the horizontal movement components of the eccentric shaft parts 64 and 65, the sliders 57 and 58 move toward the guide part 55.
, 56 in the horizontal direction.

The rotation angle of the servo motor 71 can be detected by an encoder 85 using a pulse generator or the like. Servo motor 71 is controlled by a computer numerical controller (CNC) 86.

Next, the length measuring section 12 will be explained. Figure 1
As shown in FIG. 4, a contactor 90 is provided downstream of the rolling rolls 16 and 17. The contactor 90 is rotatably supported at the end of the carriage 91 about a support shaft 92 . The support shaft 92 is located on the central extension of the gap G between the rolling rolls 16 and 17 in the width direction. A lever 93 is provided on the support shaft 92. carriage 9
1 is movable along a guide member 94 in the horizontal direction, that is, in the direction in which the workpiece A moves. The guide member 94 is provided on the frame 15a.

A roller 95 is rotatably attached to the tip of the lever 93. This roller 95 is adapted to fit into a grooved cam 96. The grooved cam 96 is firmly fixed to a frame (not shown). The cam surface of the grooved cam 96 extends obliquely to the moving direction of the workpiece A, as shown in FIG. This grooved cam 96 holds the lever 93 so that the contactor 90 is kept in a horizontal state while the roller 95 is in rolling contact with the front part of the grooved cam 96 at the beginning of rolling of the workpiece A. . As rolling progresses, roller 95
The lever 93 is shaped to move so that the contact 90 comes up as it rolls into contact with the rear part of the grooved cam 96. The lever 93, roller 95, and grooved cam 96 constitute a contact rotation mechanism 98 for rotating the contact 90 around an axis along the longitudinal direction of the workpiece A.

The lever 93 is biased toward the stopper 101 by a spring 100. This stopper 1
01 is provided so that the lever 93 can be stopped at a position where the roller 95 can enter the grooved cam 96 again when the roller 95 moves to the position where it comes out of the grooved cam 96. When the lever 93 is in contact with the stopper 101, the contact 90 is maintained obliquely inclined with respect to the horizontal plane, as shown by the two-dot chain line in FIG.

The contactor 90 is pressed toward the gap G between the rolls 16 and 17 by a biasing mechanism 105. An example of the biasing mechanism 105 includes a belt 109 wound around pulleys 107 and 108, an air motor 112 that applies a force to the pulley 107 to press the contact 90 toward the gap G, and the like.

The tip end surface 90a of the contactor 90 is similar to the tip end surface A1 of the workpiece A before rolling of the workpiece A begins.
It takes a horizontal attitude along the line, and can enter into the reference position within the gap G between the rolls 16 and 17 as shown in FIG. The reference position here is, for example, on a line segment connecting the centers of the rolls 16 and 17. The contactor 90 holds the tip surface 90 of the workpiece A until just before it is rolled.
a is made to stand by at the reference position.

The contactor 90 may be provided with a force relief mechanism such as an air motor 112, an air cylinder (not shown), an electric motor, or a powder clutch. This force relief mechanism biases the workpiece A in the opposite direction to the moving direction, but this biasing force is smaller than the force that moves the workpiece A, so after rolling has started, the rolls 16, Tip surface A of workpiece A coming out from 17
1 will push it back. Therefore, contact 9
The end face 90a of the workpiece A is always kept in contact with the end face A1 of the workpiece A and moves together with the workpiece A.

The detection means 120 for detecting the amount of movement of the contact 90 includes a cable 123 wound around pulleys 121 and 122, and a joint member 125 that connects the contact 90 to the cable 123. , a detector 126 such as a rotary encoder for detecting the amount of rotation of the pulley 121. Note that a linear motion detector such as a Magnescale may be used instead of the encoder.

The output signal of the detector 126 is input to the controller 86. Information regarding the shape of the tapered leaf spring to be formed, that is, data regarding the position of each part in the longitudinal direction of the tapered leaf spring and the plate thickness at that position is input in advance to the controller 86.

Next, the operation of the above embodiment device 10 will be explained. The workpiece A heated to a hot state is transferred to the roll 16
, 17, the rolling is started by roll 1 until then.
The tip end surface 90a of the contactor 90, which was waiting at the gap G between the rolls 16 and 17, moves while being pushed by the workpiece tip surface A1 sent out from the rolls 16 and 17. When the workpiece tip surface A1 moves while pushing the contact 90, the roller 95 of the contact 90 moves along the grooved cam 96. The movement of the roller 95 is converted into a rotational movement of the contactor 90 via the lever 93, and as shown in FIG. 7, the tip surface 90a of the contactor 90 gradually tilts in the direction of rising from the horizontal state.

The shape of the grooved cam 96 is such that even if the contactor 90 rotates while moving as described above, the contactor 90 does not keep up with the roll 16.
, 17, and this contact 90 is made thinner than the plate thickness of work A.
The contact 90 can be sufficiently inserted into the gap G between the rolls 16 and 17 to a predetermined position. Since this contactor 90 is tilted diagonally with respect to the workpiece tip surface A1 after rolling has started, the position of the workpiece tip surface A1 shifts in the vertical direction during the process of moving while being pushed by the workpiece A. Even if the tip surface 90a of the contactor 90 is the workpiece tip surface A1
Moreover, the contact 90 can contact the center portion of the workpiece A in the width direction. Therefore, using this contactor 90, it is possible to accurately measure the entire length of the workpiece A.

The amount of movement of the contactor 90 is detected by the detector 126 and inputted to the controller 86. and,
The distance between the rolls 16 and 17 is changed from time to time by driving the servo motor 71 based on data regarding the tapered shape of the leaf spring that has been input into the controller 86 in advance.

That is, the rotational force of the servo motor 71 is transmitted to the crankshaft 63 via the drive gears 80, 81 and the driven gears 82, 83, and the eccentric shaft portions 64, 65 move eccentrically, and the eccentric movement causes the slider to move eccentrically. 57 and 58. The sliders 57, 58 and the pressurizing rams 51, 52 are moved by the vertical motion components of the eccentric shafts 64, 65.
move in synchronization with each other in the vertical direction by the same amount.

When the pressure rams 51 and 52 move in the vertical direction, the upper roll holders 22 and 23 move in the vertical direction by the same amount in synchronization with each other in accordance with the amount of movement. Therefore, the upper roll 16 moves vertically while maintaining parallelism to the lower roll 17, and as a result, the distance between the rolls changes from time to time, and a desired tapered leaf spring is formed according to the change in the distance between the rolls. Ru. After one piece of work A is rolled into a predetermined tapered shape in this way, a new work A is brought to the entrance side of rolls 16 and 17, and the contactor 90 is again inserted into the gap between rolls 16 and 17. and a new rolling cycle is repeated.

Furthermore, as shown in FIG. 8, the rolls 16,
By providing support rollers 130 and 131 on the downstream side of the workpiece 17, the tip of the workpiece A after rolling may be prevented from being displaced in the vertical direction. Support rollers 130 and 131 are pressed against workpiece A by springs 132 and 133. Support rollers 132, 13
An air cylinder or a hydraulic cylinder may be applied to 3. By using such support rollers 130 and 131, it is possible to more reliably prevent the contactor 90 from coming off the workpiece A.

[0037]

According to the apparatus of the present invention, the parallelism and roll spacing between the upper roll and lower roll can be accurately controlled without using a hydraulic servo cylinder in the main body of the rolling mill. Since the present invention uses a mechanical crank mechanism, maintenance etc. are easy. In the length measurement section, a rotary contact is used to prevent the contact from coming off the tip of the workpiece, and a thin contact that can be inserted into the gap between the rolls allows the workpiece to be rolled immediately after rolling starts. It is possible to measure the length accurately over the entire length, which is very effective in shaping the tapered leaf spring into an accurate shape.

[Brief explanation of the drawing]

FIG. 1 is a diagram schematically showing the entire rolling mill according to an embodiment of the present invention.

FIG. 2 is a partially cross-sectional front view of the rolling mill main body in the rolling apparatus shown in FIG. 1;

FIG. 3 is a side view, partially in section, of the rolling mill main body in the rolling apparatus shown in FIG. 1;

FIG. 4 is a side view, partially in cross section, of the length measuring section of the rolling apparatus shown in FIG. 1;

FIG. 5 is a plan view of the length measuring section shown in FIG. 4.

FIG. 6 is a rear view of the length measuring section seen from the VI-VI line direction in FIG. 4;

FIG. 7 is a diagram showing the relationship between the contact and the workpiece in the length measuring section shown in FIG. 4;

FIG. 8 is a side view of a part of a rolling device with support rollers.

FIG. 9 is a sectional view of a conventional rolling device.

FIG. 10 is a side view showing a part of a length measuring section of a conventional rolling machine.

[Explanation of symbols]

A...Workpiece, 10...Rolling device, 11...Rolling mill main body, 1
2... Length measuring section, 16... Upper roll, 17... Lower roll, 18...
Roll pair, 22, 23... Upper roll holder, 25, 2
6... Lower roll holder, 30, 31... Height adjustment mechanism, 51
, 52... Pressure ram, 53... Crank mechanism, 63... Crank shaft, 64, 65... Eccentric shaft section, 70... Drive section, 71... Servo motor, 80, 81... Drive gear, 82, 83... Driven gear, 86 ...Controller, 90...Contactor, 126...Detector.

Claims (5)

[Claims] 1. A frame, a pair of rolling rolls including an upper roll and a lower roll provided on the frame, and a pair of rolling rolls provided on the frame and rotatably supporting both left and right ends of the upper roll; a pair of left and right upper roll holders that are movable in the vertical direction relative to the frame, a pair of left and right lower roll holders that are provided on the frame and rotatably support both left and right ends of the lower roll, and a pair of left and right lower roll holders that are provided on the upper roll holder. a crankshaft having a pair of pressurizing rams that are mounted on the upper roll holder and can move vertically together with the upper roll holder; and an eccentric shaft portion that can respectively drive the pair of pressurizing rams vertically. and a drive unit including a servo motor that rotates the crankshaft, and a controller that controls the movement of the servo motor so that the roll interval corresponds to the tapered shape of the tapered leaf spring to be formed. A tapered leaf spring rolling device featuring: 2. The pressure ram is provided with a horizontal guide portion, a slider is in contact with the guide portion so as to be slidable in the horizontal direction, and an eccentric shaft portion of the crankshaft is rotated by the slider. The rolling device according to claim 1, wherein the rolling device is fitted freely. 3. The pair of lower roll holders has a height adjustment mechanism having a horizontally movable tapered arrow.
The rolling apparatus according to claim 1, wherein each rolling apparatus is supported so as to be movable up and down. 4. A pair of rolling rolls comprising an upper roll and a lower roll provided on a frame, and a rolling roll provided on the exit side of the widthwise center of the pair of rolling rolls and brought into contact with the leading end surface of the workpiece. A rotary contact element that can rotate around an axis along the longitudinal direction, and a contact element that can be tilted to a horizontal position at a position where the contact element enters the gap between the upper roll and the lower roll. a contact rotation mechanism that raises the contact by aligning the contact with the front end surface of the workpiece and moving the contactor around the axis as the workpiece is fed out of the gap, and a position where the contactor moves in the longitudinal direction of the workpiece. A rolling device for a tapered leaf spring, characterized in that it is equipped with a detector for detection. 5. A support roller is provided on the exit side of the pair of rolling rolls to support the workpiece after rolling.
The rolling equipment described.