JP2010179441A - Bar cutter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bar cutter having various options of cutting length, which can perform cutting at an optional timing or cutting while moving a movable cutting edge at high speed. <P>SOLUTION: The bar cutter includes a fixed cutting edge 1 and a movable cutting edge 2 for cutting a bar S; a reciprocating motion mechanism 12 which causes a slider 3 to generate upward/downward motion to be given to the movable cutting edge 2; an intermittent drive mechanism which transmits the upward/downward motion of the slider to the movable cutting edge 2; a feed means 21 which feed the bar S to be cut; and a control means which controls the motion of the intermittent drive mechanism 23 based on the feed state of the bar S. The intermittent drive mechanism 23 includes a rocking head 5 which presses the movable edge 2 at the lower end of the slider 3, and the control means selectively switches, based on the feed state of the bar S, the attitude of the rocking head 5 between a valid position to press the edge 2 and an invalid position not to press the edge 2. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a bar cutting machine (hereinafter referred to as a cutting machine), and in particular, an intermittent drive mechanism that can perform cutting and material feeding at an arbitrary timing without using a clutch / brake. It is about.

Generally, a cutting machine includes a die set in which a round or U-shaped fixed blade and a movable blade are integrated (for example, see Patent Document 1 below), and is a slider that moves forward and backward by a reciprocating mechanism. Is applied with sufficient pressure for cutting (see, for example, Patent Document 2 below).
In addition, the round or U-shaped fixed blade and the movable blade are drilled with a straight round hole or U-shaped groove perpendicular to the cutting ends of both blades that rub against each other, and a bar (bar) is inserted. Or it can be accommodated.
As the reciprocating mechanism, a crank mechanism or a scotch yoke mechanism (for example, see Patent Document 3 below) can be employed.

Japanese Patent Laid-Open No. 1-210210 Japanese Patent Publication No. 58-37097 JP 2000-65290 A

  In order to perform continuous cutting using a cutting machine, it is indispensable to perform an operation of feeding a bar material at each cutting (hereinafter referred to as a feeding operation) at an appropriate timing. This is because if the timing and operation of the feeding operation are inadequate, the movable blade and the bar will come into contact with each other during the feeding operation, leading to damage to the member and erroneous cutting of the bar.

Since the conventional cutting machine does not have an intermittent drive mechanism and the movable blade has always moved up and down at a constant cycle, the time allowed to supply the bar material according to the number of times of cutting per unit time (hereinafter referred to as supply time). ) Is limited, and the length (cutting length) of the bar that can be supplied at that time is also limited.
Therefore, when cutting the bar continuously with a long cutting length, it is possible to reduce the moving speed of the movable blade or to attach a clutch / brake to the reciprocating drive source of the reciprocating mechanism, etc. In the meantime, it was necessary to take a method of forcibly stopping the operation of the reciprocating mechanism.

However, even if such a method is adopted, the reciprocating mechanism is decelerated at each feeding operation or the connection between the reciprocating mechanism and the reciprocating drive source is cut off. Must be re-accelerated every time However, since the problem that the supply time is limited as described above has not been solved at all, it is inevitable that cutting by moving the movable blade at high speed becomes difficult.
As described above, the conventional cutting machine has a problem that not only the cutting length of the bar that can be cut is limited, but also the accuracy of the cut surface cannot be increased.

  The present invention has been made in view of the above circumstances, and can be cut at an arbitrary timing or by moving a movable blade at a high speed, and a bar with a wide choice of cutting length of a bar that can be cut. The purpose is to provide a material cutting machine.

  A bar cutting machine according to the present invention that solves the above-described problems includes a fixed blade and a movable blade for cutting a bar, a reciprocating mechanism for causing the slider to move up and down to be applied to the movable blade, and a slider moving up and down. An intermittent drive mechanism for transmission, a feed means for supplying a bar to be cut, and a control means for controlling the movement of the intermittent drive mechanism based on the supply status of the bar are provided.

  The intermittent drive mechanism includes a swing head that presses the movable blade or receives pressure from the slider at the lower end of the slider or the upper end of the movable blade, and the control means is based on the supply status of the bar. Is selectively switched between an effective phase that pressurizes the movable blade, an invalid phase that does not pressurize the movable blade, an effective phase that receives pressure from the slider, or an invalid phase that does not receive pressure from the slider. is there.

  Control that has a swing head at the lower end of the slider or the upper end of the movable blade, and selectively switches the posture of the intermittent drive mechanism (swing head) to the effective phase or the invalid phase based on the supply status of the bar By providing the means, the action of the slider on the movable blade can be validated or invalidated without breaking the connection between the reciprocating mechanism and the reciprocating drive source.

As a result, cutting can be performed at an arbitrary timing as compared with the conventional case, and the cutting operation can be performed with the movable blade moved at a higher speed than the conventional one while maintaining the operation of the reciprocating mechanism at a constant speed. It becomes possible.
As described above, it is possible to provide a bar cutting machine that has a wider range of choices of cutting lengths of bars that can be cut and can obtain a highly accurate cutting surface as compared with the conventional art.

It is principal part sectional drawing seen from the side which shows an example of the bar cutting machine (at the time of an effective phase) by this invention. It is principal part sectional drawing seen from the side which shows an example of the bar cutting machine (at the time of an invalid phase) by this invention. It is the principal part front view seen from the movable blade side which shows an example of the bar cutting machine (cutting completion position and return position) by this invention. It is the front view seen from the fixed blade side which shows an example of the bar cutting machine by this invention. It is a flowchart which shows an example of the cutting | disconnection operation | work by the bar cutting machine (A) by this invention, and the conventional bar cutting machine (B). It is process drawing which shows an example of the cutting operation (at the time of an effective phase) using the bar cutting machine by this invention. It is process drawing which shows an example of the cutting operation (at the time of an invalid phase) using the bar cutting machine by this invention.

Embodiments of a bar cutting machine according to the present invention will be described below with reference to the drawings.
In the example shown in FIGS. 1 to 4 and FIGS. 6 and 7, a die set 7 that cuts the bar S on the frame 10 and a reciprocating motion in the vertical direction to be applied to the die set 7 (hereinafter referred to as a lifting motion). ), A reciprocating drive source 13 for applying a driving force to the reciprocating mechanism 12, an intermittent driving mechanism for transmitting a lifting motion to the die set 7, and a bar S to be cut into the die set 7. A control unit is provided that supports the feeding unit 21 to be supplied and controls the movement of the intermittent drive mechanism 23 based on the feeding information generated by the feeding unit 21.

  The die set 7 includes a round fixed blade 1 and a movable blade 2, a pair of left and right cutting guides 8 that support the movable blade 2, and an abutment 6 that supports and integrates them. The fixed blade 1 is fixed to the abutment 6, and the movable blade 2 is supported by the cutting guide 8 so as to be movable up and down.

  The movable blade 2 in this example is obtained by loading the movable blade body 2b into the die holder 2c.

  When inserting the bar S, the fixed blade 1 and the movable blade 2 communicate with each other so that the round holes 1b and 2d of the fixed blade 1 and the movable blade 2 face each other (hereinafter referred to as a return position). When the cutting is completed, the round holes 1b and 2d of the fixed blade 1 and the movable blade 2 are displaced from each other, and the positions where the respective cut ends 1a and 2a seal the respective round holes 2d and 1b. A relationship is established (hereinafter, a position in this state is referred to as a cutting completion position).

Hereinafter, the reciprocating mechanism will be described.
The reciprocating mechanism 12 includes a slider 3 that moves up and down and a lifting guide 11 that supports the slider 3 so as to be lifted up and down, and employs a Scotch yoke mechanism.
The driving force of the reciprocating mechanism 12 is provided by a reciprocating driving source 13 supported by the frame 10.

  The slider 3 is incorporated as a yoke of a scotch yoke mechanism, and includes a guide hole 3b through which the movable bearing 3a can move left and right. The moving bearing 3a supports an eccentric disk 13b included in the eccentric shaft 13a, and transmits the turning motion of the eccentric disk 13b accompanying the rotation of the eccentric shaft 13a to the slider 3 via the moving bearing 3a. At that time, the lateral swing of the turning motion of the eccentric disk 13b is canceled by the reciprocating motion of the movable bearing 3a within the guide hole 3b, and only the vertical motion is applied to the slider 3. Become.

  The eccentric shaft 13a is supported by the frame 10, and the driving force is obtained from a reciprocating drive source 13 fixed to the frame 10 via a pulley and a transmission belt (not shown). The maintenance of the rotational energy for continuing the up-and-down movement of the slider 3 is obtained by attaching flywheels (not shown) suitable for cutting the bar S to both ends of the eccentric shaft 13a.

The scotch yoke mechanism is advantageous in that the apparatus does not become bulky, but is not limited to the scotch yoke mechanism, and a crank mechanism or a lever mechanism can be used.
A motor is employed as the reciprocating drive source 13.

  The elevating guide 11 is located above the movable blade 2 and is in a positional relationship such that the elevating orbit of the movable blade 2 and the elevating orbit of the slider 3 are on the extension line of each other or parallel to the extension line. 3 is fixed to the frame 10 in a state of being arranged in parallel on the left and right sides of 3.

The frame 10 includes a sensor such as a rotary encoder that detects the position of the slider 3 in the reciprocating mechanism 12 as a rotational phase of the eccentric shaft 13a (not shown, hereinafter referred to as an eccentric shaft sensor).
Further, the return mechanism 4 is embedded in the position below the die set 7, and the through hole 9 is provided in the frame 10 along the extension line of the lifting orbit of the movable blade 2. The return mechanism 4 of this example uses an air cylinder, and its operating rod abuts against the movable blade 2 through the through-hole 9 so that when the movable blade 2 returns, the movable blade 2 is pushed up by atmospheric pressure. When the movable blade 2 descends, a buffering action by air is obtained.

Hereinafter, the intermittent drive mechanism will be described.
In this example, an intermittent drive mechanism 23 is provided between the slider 3 and the movable blade 2.
The intermittent drive mechanism 23 oscillates the rotational force of the oscillating head 5 that transmits the moving motion of the slider 3 to the movable blade 2, the oscillating drive source 16 such as a servo motor fixed to the frame 10 to drive the oscillating head 5. It consists of a shaft 15 that transmits to the head 5.

The oscillating head 5 in this example has an oscillating shaft 5a integrally protruding on both side surfaces of the base end portion of the head main body 5b. The head main body 5b in this example has a rectangular parallelepiped shape, and the end surface opposite to the base end portion on which the swing shaft 5a is provided serves as a pressure surface 5c for pressing the pressure receiving portion of the movable blade 2.
The head main body 5b of the oscillating head 5 is supported by the lower end portion of the slider 3 so as to be able to hang down and tilt by holding the oscillating shaft 5a.

The oscillating head 5 transmits the lifting / lowering motion of the slider 3 to the movable blade 2 on the condition that the swinging head 5 is in a vertically suspended posture, and avoids the transmission of the lifting / lowering motion on the condition that it is tilted.
Therefore, the length between the rocking shaft 5a and the pressure surface 5c and the thickness of the rocking head 5 are sufficiently different from the pressure receiving portion of the movable blade 2 due to the tilt allowed by the rocking head 5. It is necessary to set the length and the thinness to be obtained, and it is necessary to provide an amount of rocking that enables this.

The swing shaft 5 a includes a transmission arm 19 that protrudes in the centrifugal direction, and a tip end portion of the swing shaft 5 a is connected to the slider 3 via a retracting mechanism 22.
The retraction mechanism 22 is an urging member such as a spring, and is a forced retraction mechanism in an emergency such as when the power of the swing drive source 16 is cut off.
The retracting mechanism 22 urges the pressing surface 5c of the oscillating head 5 in a direction to retract from the ascending / descending track of the movable blade 2 by using the pulling force.

  In this example, the tilt permitted by the swing head 5 starts in the suspended state, only tilts in the direction corresponding to the movement of the transmission arm 19 by the biasing action of the retracting mechanism 22, and tilts to the opposite side. It is regulated by a stopper (not shown) or the like.

Hereinafter, the drive mechanism of the oscillating head 5 will be described.
The oscillating shaft 5 a of the oscillating head 5 receives a rotational force capable of adjusting the angle from the oscillating drive source 16 via the shaft 15. The swing drive source 16 is installed on an extension line of the swing shaft 5a. The shaft 15 that connects the swing shaft 5a and the swing drive source 16 is connected by a universal joint 17 that can be bent or expanded (slided), and the slider 3 is placed on the frame 10 that is always stationary. The driving force can be transmitted in response to the up-and-down movement.

  With this connection structure, according to this configuration, the setting range of the specification of the slider 3 is widened, and optimum conditions are set when the cutting force is applied to the movable blade 2 according to the type of the bar S. Becomes easy.

Hereinafter, the operation of the swing head 5 will be described.
When the swing head 5 is in a suspended position, the slider 3 is separated from the movable blade 2 at the return position by a predetermined distance when the slider 3 is located at the top dead center (see FIG. 4). ) When the slider 3 is lowered with the movable blade 2 abutting at a certain position (see FIGS. 3B and 6B) in the lowering process of the slider 3 and is positioned at the bottom dead center, the swing head 5 is in a state where the movable blade 2 is pushed down to the cutting completion position (see FIGS. 1, 3A, and 6C). Hereinafter, the operation of the slider 3 during the descending period is referred to as a cutting operation. ).

  On the other hand, when the oscillating head 5 is tilted at a predetermined angle, the tip of the oscillating head 5 deviates from the pressure receiving portion of the movable blade 2 and is movable in the cutting operation with the same amplitude as the movement of the slider 3. The blade 2 cannot be pressurized and a substantial cutting action cannot be obtained (see FIGS. 2 and 7B, 7C, and 7D). That is, the raising / lowering of the slider 3 during that time becomes an invalid operation for the operation of the movable blade 2.

The feeding means 21 is provided with a plurality of pinch rollers 20 on which the bar material S is mounted and conveyed.
The feeding means 21 supplies a supply signal output when the material is supplied by the operation of the pinch roller 20, an arrival signal output when the material arrives at the stopper 24, and a stop signal output when the pinch roller 20 and the bar S are stopped. Then, a non-detection signal output when the bar S does not exist on the pinch roller 20 is generated as feed information.
The arrival signal in this example is generated when the stopper 24 is provided at a position facing the round hole 2d of the movable blade 2 and the bar S comes into contact with the stopper 24.

Hereinafter, control of this bar cutting machine will be described.
The control means controls the posture of the oscillating head 5 based on the feed information indicating the supply status of the bar S and the rotational phase of the eccentric shaft 13a.

  That is, the control means reads the direction in which the eccentric disk 13b is swung along with the rotation of the eccentric shaft 13a from the eccentric shaft sensor that detects the rotational phase of the eccentric shaft 13a, and the direction in which the eccentric disk 13b is swung is The oscillating head 5 is rotated only when it is above the position of the support shaft 13c of the eccentric shaft 13a, and the pressure surface 5c of the oscillating head 5 is inserted into the elevating orbit of the movable blade 2, or the elevating orbit. Control to evacuate outside.

  Specifically, the control means sets the phase when the direction in which the eccentric board 13b is swinging to be 0 degrees, and the direction in which the eccentric board 13b swings is 270 degrees, which is one horizontal direction. The rocking head 5 is rotated during a period from 0 to 90 degrees after passing through 0 degrees. Actually, according to the swing speed of the swing head 5, the swing head 5 is moved within a period for which a preliminary angle for preventing interference is expected (in this example, between 140 degrees from about 290 degrees to 70 degrees). It is desirable to rotate (hereinafter, the start timing of such a period is referred to as a swing start point).

The control of the rotation angle of the oscillating head 5 by the control means switches between an effective phase in which the elevation of the slider 3 acts on the movable blade 2 and an invalid phase in which the elevation of the slider 3 does not act on the movable blade 2. To do. At each phase position, a sensor 18 for detecting that the oscillating head 5 is in each phase is installed.
These sensors 18 detect a transmission arm 19 that rotates together with the oscillating head 5 to generate a valid signal for confirming that it is in an effective phase and an invalid signal for confirming that it is in an invalid phase.

When supplying the bar S, the control means detects that the eccentric shaft 13a has reached the swing start point by the eccentric shaft sensor, and executes a process of rotating the swing head 5.
In this example, when the direction in which the eccentric disk 13b is touching is directly above, the pressing surface 5c of the oscillating head 5 is spaced upward by a fixed length (60 mm in this example) from the movable blade 2 at the return position. (See FIGS. 4, 6A, and 7D).

  The control means receives the signal detected by the eccentric shaft sensor (hereinafter, referred to as a swing start signal) that the eccentric shaft 13a has reached the swing start point, drives the swing drive source 16, and swing head The pressure surface 5c of 5 is retracted instantaneously outside the lifting orbit of the pressure receiving portion. As a result, the upward and downward movement of the slider 3 continues without applying any force to the movable blade 2 because the pressing surface 5 c of the oscillating head 5 deviates from the movable blade 2. In this example, this time is an intermittent time for the bar cutting operation (see FIGS. 7B, 7C, and 7D).

  The control means operates the pinch roller 20 simultaneously with these controls, feeds the material to a position where it abuts against the stopper 24 according to the cutting dimension, receives an arrival signal confirming that the pinch roller 20 has reached a predetermined position, and then the pinch roller 20 Is reduced to such an extent that it does not slip with respect to the bar S, and the bar S is held and fixed (see FIGS. 6B, 6C, and 6D).

  The control means receives the swing start signal on the condition that the arrival signal has been received, drives the swing drive source 16, and moves the pressurizing surface 5c of the swing head 5 up and down the orbit of the pressure receiving portion of the movable blade 2. (See FIG. 6A.) Thereafter, the slider 3 starts a cutting operation, pushes down the pressure surface 5c of the oscillating head 5 to a position where it contacts the pressure receiving portion of the movable blade 2 (see FIG. 6B), and further cuts the movable blade 2. Push down to the completion position (see FIG. 6C). The control means detects, with the eccentric shaft sensor, the phase (180 degrees) when the direction in which the eccentric disk 13b is swung is directly below, and the movable blade 2 has reached the cutting completion position, and the cutting operation has been completed. To detect.

  In this example, when the direction in which the eccentric disk 13b swings is the horizontal direction, the pressing surface 5c of the oscillating head 5 is set so as to be in contact with the movable blade 2 at the return position. When the swinging direction of the core 13b is directly below, the pressure surface 5c of the swing head 5 is at a position that is lowered by a certain length (60 mm in this example) from the position of the pressure receiving portion of the movable blade 2 at the return position. It is set so as to exist (see FIGS. 1, 3A, and 6A).

  The slider 3 which has completed the cutting operation starts to rise, and the movable blade 2 pushed down by the slider 3 is raised to the return position by the return mechanism 4 such as an air damper.

  The control means receives an oscillating start signal and retreats the pressurizing surface 5c of the oscillating head 5 to the outside of the elevating orbit of the pressure receiving unit until another operation such as stopping the cutting machine is performed as described above. And the control which repeats a series of operation | movement which starts to the operation | movement which supplies the rod S is performed.

The bar cutting machine according to the present invention has the same basic structure as the frame 10, slider 3, reciprocating mechanism 12, die set 7, etc., but does not employ a structure in which the swing head 5 is provided at the tip of the slider 3, It is possible to employ an intermittent drive mechanism having a structure provided in the movable blade 2.
In this embodiment, the slider 3 includes a pressure surface 5c at the tip. The movable blade 2 that receives pressure from the slider 3 includes a swing head at the upper end thereof.

  The oscillating head 5 is supported on an oscillating shaft 5 a supported on the upper end portion of the movable blade 2 so that the oscillating head 5 can stand or tilt, and the oscillating shaft 5 a can be adjusted in angle from an oscillating drive source 16 via a shaft 15. Receive a strong rotational force. The mode of the shaft 15 that connects the rocking shaft 5a and the rocking drive source 16 is the same as that of the above-described embodiment.

  The oscillating head 5 can transmit the lifting / lowering motion of the slider 3 to the movable blade 2 on the condition that the oscillating head 5 is in a posture standing in the vertical direction.

1 fixed blade, 1a cut end, 1b round hole,
2 movable blade, 2a cutting end, 2b movable blade body, 2c die holder, 2d round hole,
3 Slider, 3a Moving bearing, 3b Guide hole,
4 return mechanism, 5 oscillating head, 5a oscillating shaft, 5b head body, 5c pressure surface,
6 abutments, 7 die sets, 8 cutting guides, 9 through holes,
10 frame, 11 lifting guide, 12 reciprocating mechanism,
13 reciprocating drive source, 13a eccentric shaft, 13b eccentric disk, 13c support shaft,
14 shock absorber,
15 shaft, 16 swing drive source, 17 universal joint,
18 sensors, 19 transmission arms,
20 pinch rollers, 21 feeding means,
22 retraction mechanism, 23 intermittent drive mechanism, 24 stopper,
S bar,

Claims (2)

A fixed blade (1) and a movable blade (2) for cutting the bar (S);
A reciprocating motion mechanism (12) for causing the slider (3) to generate a lifting motion to be applied to the movable blade (2);
An intermittent drive mechanism (23) for transmitting the lifting and lowering movement of the slider (3) to the movable blade (2);
A feeding means (21) for supplying a bar (S) to be cut;
Control means for controlling the movement of the intermittent drive mechanism (23) based on the supply status of the bar (S),
The intermittent drive mechanism (23) includes a swing head (5) that pressurizes the movable blade (2) at the lower end of the slider (3),
The control means sets the posture of the oscillating head (5) to an effective phase in which the movable blade (2) is pressurized or an invalid phase in which the movable blade (2) is not pressurized based on the supply state of the bar (S). Bar cutting machine that switches selectively. A fixed blade (1) and a movable blade (2) for cutting the bar (S);
A reciprocating motion mechanism (12) for causing the slider (3) to generate a lifting motion to be applied to the movable blade (2);
An intermittent drive mechanism (23) for transmitting the lifting and lowering movement of the slider (3) to the movable blade (2);
A feeding means (21) for supplying a bar (S) to be cut;
Control means for controlling the movement of the intermittent drive mechanism (23) based on the supply status of the bar (S),
The intermittent drive mechanism (23) includes an oscillating head (5) that receives pressure from the slider (3) at the upper end of the movable blade (2),
The control means determines the posture of the swing head (5) based on the supply state of the bar (S), the effective phase of receiving pressure from the slider (3), or the invalidity not receiving pressure from the slider (3). Bar cutting machine that selectively switches to phase.

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