JPH1034477A - Main spindle driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten the cycle time of a device by suplementing the torque of a main spindle to accelerate the work to be performed by the device when a high load is applied to the main spindle. SOLUTION: A main spindle driving device 70 has a main spindle driving motor M2 (driving means 71), which is incorporated in a turret device provided with a main spindle 21 to be connected to a cutting tool and drives the rotation of the main spindle 21, and a pneumatic motor M3 (auxiliary power means 72), which is connected to the main spindle 21 to compensate the torque of the main spindle when a high load is applied for accelerating the main spindle 21. In addition, this pneumatic motor M3 is connected to the main spindle 21, when a high load is applied to the main spindle 21 in reducing the speed of the main spindle 21, adding braking force to the main spindle 21. The pneumatic motor M3 is supplied with air from the air supply means provided on the side of the turret device and operates by synchronizing with a high load when the main spindle 21 is accelerated and decelerated.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device for a spindle which is incorporated in a facility having a spindle connected to a load member such as a working tool, for example, a turret device.

[0002]

2. Description of the Related Art Automobile parts are manufactured through various processes such as a pressing process and a machining process. In order to increase production efficiency, a turret device has been frequently used in the machining process.

[0003] This turret device is one of equipments having a main shaft connected to a load member such as a processing tool, and includes a drum rotatably mounted on a non-rotating post, and a turret device provided on the circumference of the drum. And a plurality of gear heads. Each gear head is provided with a cutting tool, and rotates the drum to index a desired gear head for a machining purpose from among a plurality of gear heads to a machining position facing the workpiece, so as to sequentially perform predetermined machining. Has become.

[0004] The turret device is provided with a spindle system having a spindle connected to a cutting tool of a gear head indexed to a machining position, and one spindle composed of a spindle motor for rotating the spindle. A drive motor is provided. Generally, the power of the spindle drive motor is transmitted from the spindle system to the gear head via a clutch mechanism. As a result, the cutting tool rotates, and predetermined machining such as tapping is performed on the work (see Japanese Patent Publication No. 63-9,923 and Japanese Patent Application Laid-Open No. 63-47,003).

[0005] In recent years, some turrets are indexed for rotation by the power of a spindle drive motor.

[0006]

In equipment having a main shaft such as a turret device, when a load acting on the main shaft is large, for example, when accelerating and decelerating, the acceleration / deceleration performance of the main shaft is determined by a main shaft drive motor. The rise time of the spindle, ie, the acceleration time, and the fall time of the spindle, ie, the deceleration time, are mostly determined based on the relationship between the rotor inertia and the torque of the motor.

[0007] For this reason, when the output of the spindle drive motor increases, the rotor inertia of the motor also increases, which increases the acceleration time and the deceleration time. Further, if the load-side inertia of a load member such as a cutting tool connected to the main shaft increases, the acceleration / deceleration time further increases. If the acceleration time and the deceleration time of the spindle are long, there is a problem that individual processing times such as tapping by the turret device and a cycle time of a series of machining operations by the turret device become long.

SUMMARY OF THE INVENTION The present invention has been made to solve the problems associated with the above-mentioned prior art, and aims to supplement the torque of the main spindle when a high load acts on the main spindle, thereby increasing the speed of work to be performed in the equipment. It is another object of the present invention to provide a spindle drive device capable of achieving a reduction in equipment cycle time.

[0009]

According to a first aspect of the present invention, there is provided a driving device for a main shaft which is incorporated in equipment having a main shaft connected to a load member such as a machining tool. A driving unit that rotationally drives the main shaft, and an auxiliary power unit that is connected to the main shaft and applies a rotational force to the main shaft during a high load such as when accelerating the main shaft,
A driving device for a spindle, comprising:

In this drive device for a spindle, when the spindle is accelerated or when a high load is applied, the spindle receives not only the torque from the drive means but also the torque from the auxiliary power means connected to the spindle. It is driven to rotate. For this reason, the output of the driving means is assisted, and the shortage of torque at the time of high load is compensated, so that the acceleration time of the main shaft is shortened. Therefore, the acceleration of the spindle is improved, and the time required for work to be performed on the load member and the cycle time of the equipment are shortened. Further, even if the output of the driving unit is increased or the load-side inertia of the load member is increased, the auxiliary power unit applies the rotational force, so that the acceleration time is suppressed from becoming long.

Further, in the invention described in claim 2, the auxiliary power means is connected to the main shaft and applies a braking force to the main shaft at a time of high load such as when the main shaft is decelerated. I do.

In such a configuration, when the main shaft is decelerated and the load is high, for example, the main shaft is decelerated by the application of the braking force from the auxiliary power means connected to the main shaft, so that the deceleration time of the main shaft is shortened. Therefore, the deceleration of the spindle is improved, and the time required for the work to be performed by the load member and the cycle time of the equipment are shortened. In addition, even if the output of the driving means is increased or the load-side inertia of the load member is increased, the braking force is added by the auxiliary power means, so that a longer deceleration time can be suppressed.

According to a third aspect of the present invention, the auxiliary power unit operates in synchronization with the high load of the main shaft.

In such a configuration, the auxiliary power means operates only at a high load requiring assistance such as acceleration or deceleration of the main shaft, so that wasteful consumption of power for driving the auxiliary power means is suppressed.

According to a fourth aspect of the present invention, the auxiliary power means is constituted by a pneumatic motor which converts the energy of the compressed air into a rotational force and is rotatable in both forward and reverse directions.

In this configuration, the advantage of the pneumatic motor, which is smaller and lighter than an electric motor of the same output, makes it possible to reduce the size and weight of the auxiliary power means so that the whole drive unit of the main shaft is lighter and smaller. Become.

In the invention described in claim 5, the compressed air supplied to the pneumatic motor is obtained from a compressed air supply source provided in the facility.

With this configuration, it is not necessary to separately provide a compressed air supply source or to provide a complicated piping system for driving the pneumatic motor, and the configuration of the driving device for the main shaft is simplified.

Further, in the invention described in claim 6, the pneumatic motor is freely rotatable independently of the main shaft when the main shaft is not under the high load.

With such a configuration, the pneumatic motor can be operated only at a high load requiring assistance such as acceleration or deceleration of the main shaft, and wasteful consumption of compression power for driving the pneumatic motor is suppressed.

[0021]

According to the driving device for a spindle according to the first aspect, at a high load such as when the spindle is accelerated, the auxiliary power means assists the output of the driving means to compensate for the lack of torque at the time of a high load. For this reason, the acceleration of the spindle is improved, and the time required for the work to be performed by the load member and the cycle time of the equipment can be reduced. In addition, even if the output of the driving means is increased or the load-side inertia of the load member is increased, the auxiliary power means adds a rotational force, so that it is possible to suppress an increase in acceleration time.

According to the second aspect of the present invention, the auxiliary power means applies a braking force to the main shaft at the time of a high load such as when the main shaft is decelerated. The deceleration of the main shaft is also improved, and the time required for work to be performed on the load member and the cycle time of the equipment can be further reduced. Further, even if the output of the driving unit is increased or the load-side inertia of the load member is increased, the auxiliary power unit applies the braking force, so that it is possible to suppress the deceleration time from becoming long.

According to the third aspect of the present invention, the auxiliary power means is operated in synchronization with a high load on the main shaft, so that wasteful consumption of power for driving the auxiliary power means can be suppressed. .

According to the fourth aspect of the present invention, the advantage of the pneumatic motor, which is smaller and lighter than the electric motor of the same output, allows the overall drive of the main shaft to be reduced by reducing the size and weight of the auxiliary power means. Can be reduced in weight and size.

According to the fifth aspect of the present invention, it is not necessary to separately provide a compressed air supply source for driving the pneumatic motor or to provide a complicated piping system, thereby simplifying the configuration of the driving device for the main shaft. Can be achieved.

According to the sixth aspect of the present invention, the pneumatic motor can be operated only when the main shaft is under a high load, and wasteful consumption of compressed air for driving the pneumatic motor can be suppressed.

[0027]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 are a front view showing an external appearance of a turret device incorporating a drive device for a spindle according to the present invention and a sectional view of a main part schematically showing an internal structure. FIG. It is sectional drawing which shows a part.

As one of the equipments having a spindle connected to a load member such as a processing tool, there is a turret device as described above. As shown in FIGS. 1 and 2, the turret device 10 includes a drum 12 rotatably mounted on a non-rotating post 11, and a plurality of gear heads 13 provided on the circumference of the drum 12. I have. Each gear head 13
Is provided with a cutting tool 14, and performs predetermined machining in turn while rotating the drum 12 to index a desired gear head 13 for a machining purpose from among a plurality of gear heads 13 to a machining position facing a workpiece. It has become.
The turret device 10 is provided with a spindle system having a spindle 21 connected to the cutting tool 14 of the gear head 13 indexed to the machining position, and incorporates a spindle drive device 70 for driving the spindle 21 to rotate. ing. The turret device 10 also incorporates a fluid distribution device 15 that distributes and supplies cutting oil, air, and lubricating oil to each of the plurality of gear heads 13.

More specifically, the turret device 10 comprises:
The unit body 17 has an inclined surface (inclination angle of 45 degrees) and is fixed to the base 16, and the post 11 is attached so as to protrude from the inclined surface of the main body 17 in a direction orthogonal to the unit body 17. The boss 12 a of the drum 12 is inserted into the post 11, and the drum 12 is rotatably supported by the post 11 via a bearing 18. The rotation index of the gear head 13 is determined by the index motor M1 attached to the unit body 17.
(See FIG. 1) to rotate the drum 12 in the forward and reverse directions as appropriate.

In the illustrated turret device 10, the drum 1
2 is formed in a truncated cone shape, and a gear head 13 is attached to each of four index surfaces on the cone surface. Note that only one gear head 13 is shown, and the other three gear heads are not shown. Each gear head 13 includes a cutting tool 14 and a drive shaft 20, and at a processing position where the drive shaft 20 is horizontal, the axes of the drive shaft 20 and the spindle system horizontally supported in the unit body 17 coincide with each other. I do.
The main shaft system includes a main shaft 21 and a clutch shaft 21a that can move back and forth only in the axial direction with respect to the main shaft 21 and rotates together with the main shaft 21.
And A clutch mechanism 22 is provided between the clutch shaft 21a and the drive shaft 20. A sleeve 23 that rotatably holds the clutch shaft 21a moves forward and backward with respect to the drive shaft 20, so that the main shaft 21 and the drive shaft 20 are separated from each other. Are connected or disconnected. The sleeve 23 is connected to a cylinder 25 via a shifter 24.
Moves forward and backward by the operation of. Spindle drive 70 described later
Is transmitted from the main shaft system to the gear head 13 via the clutch mechanism 22, whereby the cutting tool 14 is rotated, and predetermined machining such as tapping is performed on the work.

The fluid distribution device 15 includes four gear heads 1
3 for distributing fluid such as cutting oil, air and lubricating oil, and has a rotary joint 30 attached to the drum 11 and rotating together with the drum 11. The rotary joint 30 has a hollow cylindrical shape, and its inner peripheral surface is slidably fitted to the outer peripheral surface of the post 11 having a cylindrical shape. Each fluid is supplied to the gear head 13 through a plurality of pipes P connected to the rotary joint 30, but the cutting oil is supplied only to the gear head 13 indexed to the processing position, and the air and the lubricating oil are supplied to the non-processing position. It is always supplied to a certain gear head.

The rotary joint 30 has a cutting oil distribution port 31 and a first air distribution port 3 for each gear head 13.
5, a second air distribution port 36 and a lubricating oil distribution port 37 are formed. The post 11 is formed with a cutting oil supply hole 32 communicating with a cutting oil distribution port 31 for the gear head 13 indexed to a processing position. The post 11 has a first air supply hole 44 and a second air supply hole 45 which are always in communication with the first air distribution port 35, the second air distribution port 36, and the lubricating oil distribution port 37 via a ring groove (not shown). And a lubricating oil supply hole 46. The cutting oil supply hole 32 communicates with a cutting oil supply port 33 connected to a cutting oil supply means 34 via a pipe P5. The first air supply hole 44 and the second air supply hole 45 are connected to the first air supply port 47 and the second air supply port 47 connected to the air supply means 48 via the pipe P6.
It communicates with an air supply port (not shown). Further, the lubricating oil supply hole 46 is connected to the lubricating oil supplying means 50 through the pipe P7.
Is connected to a lubricating oil supply port 51 connected to the lubricating oil supply port 51.

When the desired gear head 13 is indexed at the machining position by turning the drum 12, the gear head 13
Cutting oil distribution port 31 for communication with the cutting oil supply hole 32,
The cutting oil is supplied to the indexed gear head 13. Further, each first air distribution port 35 communicates with the first air supply hole 44 to supply air to each gear head 13, and each twelfth air distribution port 36 communicates with the second air supply hole 45 to allow air to flow therethrough. It is supplied to the gear head 13. Lubricating oil is similarly supplied to each gear head 13.

As described above, the driving force of the main shaft driving device 70 is transmitted to the gear head 13, and the main shaft driving device 70 of this embodiment uses the driving means 7 for driving the main shaft 21 to rotate.
1 and an auxiliary power means 72 connected to the main shaft 21 to apply a rotational force to the main shaft 21 at the time of a high load such as when accelerating the main shaft 21. This auxiliary power means 72 is used when the load is high, such as when the spindle 21 is decelerated.
It is connected to the main shaft 21 to apply a braking force to the main shaft 21.

More specifically, the driving means 71 comprises:
It comprises a spindle drive motor M2 attached to the unit body 17. The main shaft drive motor M2 is composed of a spindle motor, and the main shaft 21 is connected to an output shaft 26 thereof. As shown in an enlarged manner in FIG. 3, the main shaft 21 is firmly connected to the output shaft 26 by a fastening ring 73 provided at an end of the main shaft 21.

As shown in FIG. 3, the auxiliary power means 72 is composed of a pneumatic motor M3 which converts the energy of the compressed air into a rotational force and is rotatable in both forward and reverse directions. The pneumatic motor M3 is of a vane type, and a vane 75 is provided on the input shaft 76 for sliding contact with the inner peripheral surface of a cylinder portion formed on the housing 74. The input shaft 76 is connected to the main shaft 21 via a bearing 77. And are relatively rotatably held.

Two air systems, an A port 78 and a B port 79, are formed in the housing 74 and the unit body 17 for supplying and discharging compressed air for driving the pneumatic motor M3. The A and B ports 78 and 79 are connected to the air supply means 48 (see FIG. 2) provided in the turret device 10, and the air supply means 48 supplies air motor M3.
Is supplied to the air.

The pneumatic motor M3 is driven to rotate in both forward and reverse directions. Assuming that the same rotational direction as the rotational direction of the main shaft 21 is the normal rotation of the pneumatic motor M3, the A port 78 Air is supplied and exhausted from the B port 79. On the other hand, when the pneumatic motor M3 rotates in the reverse direction, B
Air is supplied from port 79 and exhausted from A port 78. In order to selectively supply air from the A port 78 or the B port 79 in accordance with a desired rotation direction of the pneumatic motor M3, a flow path switching valve (not shown) for switching an air supply path is provided. In addition, the A and B ports 78 and 79
Solenoid valves 80 and 81 for controlling the flow rate that control the amount of air supplied to the pneumatic motor M3 are provided.

A plurality of planets sandwiched between the base outer peripheral surface of the input shaft 76 and the inner peripheral surface of the housing by these two surfaces and planetaryly move around the input shaft 76 with the rotation of the input shaft 76. A roller 82 is provided. The input shaft 76
May be a sun gear, an inner gear may be formed on the inner circumferential surface of the housing, and the planetary roller 82 may be a planetary gear.
A collet type rotor 84 connected to the planetary roller 82 via a pin 83 is disposed adjacent to the input shaft 76 in the axial direction. The collet-type rotor 84 has a center hole 84a through which the main shaft 21 is inserted, and a collet portion 84b having a tapered outer periphery. Collet part 84b
Is inserted through a lock ring 85 having an inner periphery tapered, and when the lock ring 85 is moved rightward in the figure along the axial direction, the collet portion 84b is tightened to the main shaft 21,
The torque of the input shaft 76 is transmitted to the main shaft 21 via the planetary rollers 82, the pins 83, and the collet-type rotor 84. When the lock ring 85 is moved leftward in the drawing from this state, the tightening of the collet portion 84b is released, and the transmission of torque from the input shaft 76 to the main shaft 21 is interrupted. At this time, the input shaft 76 is in a rotation-free state. Therefore, if the movement of the lock ring 85 is controlled, the auxiliary power means 72 can be operated only when it is necessary to assist the rotational drive and braking of the main shaft 21.

To control the movement of the lock ring 85,
The lock ring 85 is formed of a magnetic material, and a strong permanent magnet 86 is arranged on the right side in the figure, and an electromagnet 87 is arranged on the left side in the figure so as to sandwich the lock ring 85 with a predetermined gap. . When the coil of the electromagnet 87 is energized, the magnetic lock ring 85 is attracted by the electromagnet 87 and moves to the left in the drawing, and the input shaft 76 is in a rotation-free state. On the other hand, when the power supply to the coil is cut off, the magnetic lock ring 8
5 is attracted by the permanent magnet 86 and moves rightward in the figure, so that the torque of the input shaft 76 is transmitted to the main shaft 21.

When a rotational force is applied from the input shaft 76 to the main shaft 21, the rotational speed of the collet-type rotor 84 is
The rotation of the pneumatic motor M3 is controlled so as to synchronize with the rotation speed of. This rotation control is performed by adjusting the amount of air supplied to the pneumatic motor M3.
The supply air amount is adjusted by the flow rate control solenoid valves 80 and 81 provided at 9.

Next, the operation of the present embodiment will be described with reference to the operation time chart shown in FIG.

FIG. 4A shows a change in torque of the main shaft 21.
(B) is a time chart showing a speed change of the main shaft 21, (C) is a speed change of the feed shaft, (D) is a port switching state, and (E) is a time chart showing the on / off state of the electromagnet 87. . In FIGS. 9A and 9B, a change in the case of the present embodiment including the auxiliary power means 72 is indicated by a solid line.
The change in the case of the comparative example in which the auxiliary power means 72 is not operated is indicated by a dotted line. Further, in FIG. 3A, the torque region supplemented by the auxiliary power means 72 is indicated by hatching.

In this embodiment, FIGS. 4A, 4D, and 4E
As shown in the figure, the air supply (on) / air supply stop (off) operation by opening and closing the flow control solenoid valves 80 and 81 and the on / off operation of the electromagnet 87 are determined by the upper limit set value a and the lower limit of the torque of the main shaft 21. This is performed in synchronization with the timing beyond the range determined by the set value b. Spindle drive motor M2
Can be monitored based on the current value applied to the motor M2, but may be monitored by separately providing a detecting means such as a torque sensor.

Switching of the air supply path by the flow path switching valve (switching between air supply from the A port 78 and air supply from the B port 79) is provided in the gear head 13 to move the cutting tool 14 back and forth. This is carried out based on the position of the feed shaft to be advanced.
Is set as the air supply path, and when the feed shaft reaches the forward limit position, the B port 79 is switched to the air supply path. Whether or not the feed shaft has reached the backward limit position and the forward limit position is detected by a limit switch or the like attached to the feed shaft.

First, when the drum 12 is turned to index the gear head 13 for the purpose of machining, as shown in FIG. 2, the operation of the cylinder 25 causes the sleeve 23 to move forward, and the main shaft 21 is moved to the clutch shaft. It is connected to the drive shaft 20 of the gear head 13 via a clutch mechanism 21a and a clutch mechanism 22.

Before starting the spindle drive motor M2, FIG.
As shown in (E), the power supply to the coil of the electromagnet 87 is cut off (turned off). As a result, the magnetic lock ring 85 that has been attracted to the electromagnet 87 is attracted to the permanent magnet 86 and moves rightward in FIG. 3, and the collet 84 b is fastened to the main shaft 21. The torque fluctuation of the spindle drive motor M2 is monitored based on the current value applied to the motor M2, and when the current value increases rapidly with the start of the spindle drive motor M2, as shown in FIG. By operating the flow path switching valve, the A port 78 is used as an air supply system, and the B port 79 is used as an exhaust system,
The flow control solenoid valve 80 at the A port 78 is opened to start (turn on) air supply. The pneumatic motor M3 rotates forward with the air supply from the A port 78 (the same direction as the rotation direction of the main shaft 21).
And the torque of the input shaft 76 in the pneumatic motor M3 is
The light is transmitted to the main shaft 21 via the planetary rollers 82, the pins 83, and the collet type rotor 84.

Then, as shown in FIG. 4A, the torque transmitted from the pneumatic motor M3 is further added to the torque of the spindle drive motor M2 itself, as shown in FIG. Become. As described above, the torque is supplemented from the pneumatic motor M3 to the main shaft 21 at the time of a high load when the main shaft 21 is accelerating.
As shown in (B), the rise time (t1-0) until the spindle speed reaches the predetermined speed V0 is equal to the auxiliary power means 72.
Is shorter than that of the comparative example in which is not operated.

When the main shaft speed is accelerated until reaching the predetermined speed V0, the pneumatic motor M3 controls the A-type motor so that the rotation speed of the collet type rotor 84 is synchronized with the rotation speed of the main shaft 21.
The rotation is controlled while the supply air amount is adjusted by a flow control solenoid valve 80 provided in the port 78.

When the main shaft speed reaches the predetermined speed V0, there is no need to assist the rotational drive of the main shaft 21, so that the operation of the auxiliary power means 72 is stopped. That is, when it is detected that the current value applied to the spindle drive motor M2 has reached the stable range, the flow control solenoid valve 80 is closed, and the air supply from the A port 78 is stopped (off). Further, the coil of the electromagnet 87 is energized (turned on). As a result, the magnetic lock ring 85 attracted to the permanent magnet 86 is attracted to the electromagnet 87 and moves leftward in FIG. 3, the tightening of the collet portion 74b is released, and the input shaft 76 of the pneumatic motor M3 is in a rotation-free state. become.

When the spindle speed reaches a predetermined speed V0, the gear head 1 is driven by the driving force from the spindle drive motor M2.
The third cutting tool 14 is fed toward the forward limit while being driven to rotate, and performs machining such as tapping on the workpiece.

When the feed of the cutting tool 14 reaches the forward limit (time t2 in FIG. 4C), the retreating movement of the cutting tool 14 is started.

When the machining is completed, the spindle drive motor M
2 is stopped (time t3), but the spindle drive motor M
2 is rotating by inertia, the main shaft 2
1 is still spinning. When the current value sharply decreases with the stop of the main shaft drive motor M2, the energization of the coil of the electromagnet 87 is again cut off (off), and the collet portion 84b is tightened to the main shaft 21, as shown in FIG. Further, as shown in FIG. 4D, the B port 79 is set to an air supply system, the A port 78 is set to an exhaust system, and
The flow control solenoid valve 81 of the port 79 is opened to start (turn on) air supply. The pneumatic motor M3 rotates in reverse with the air supply from the B port 79 (the direction opposite to the rotation direction of the main shaft 21).
And the torque of the input shaft 76 in the pneumatic motor M3 is
The light is transmitted to the main shaft 21 via the planetary rollers 82, the pins 83, and the collet type rotor 84. At this time, the pneumatic motor M <b> 3 that rotates in reverse has a rotational resistance of the main shaft 21.

Then, as shown in FIG. 4A, the torque transmitted from the pneumatic motor M3 is applied as a braking force, and the main shaft 21 stops rotating. As described above, when the main shaft 21 is decelerated and the load is high, a braking force is applied to the main shaft 21 from the pneumatic motor M3, and as shown in FIG.
Fall time from 0 to zero (stop) (t4-
t3) is shorter than the comparative example in which the auxiliary power means 72 is not operated.

When the main shaft 21 is decelerated, the amount of air supply is appropriately adjusted by the flow control solenoid valve 81 so that no sudden braking force is applied to the main shaft 21.

When the spindle speed becomes zero (time t4), there is no need to assist in stopping the rotation of the spindle 21, so that the operation of the auxiliary power means 72 is stopped. That is, the electromagnetic valve 81 for flow control is closed, the supply of air from the B port 79 is stopped (off), and the coil of the electromagnet 87 is energized (on). Thereby, the collet portion 84b by the magnetic lock ring 85
Is released, and the input shaft 76 of the pneumatic motor M3 is released.
Becomes free to rotate.

The exhaust from the B port 79 during acceleration of the main shaft 21 and the exhaust from the A port 78 during deceleration are blown to the cutting tool 14 through ports and pipes (not shown) while silencing with a silencer (not shown).
It is used as cooling air for the cutting tool 14 so that air is not wasted.

As described above, in this embodiment, the pneumatic motor M3 as the auxiliary power means 72 compensates for insufficient torque of the motor M2 when the spindle drive motor M2 is started up, so that the acceleration time of the spindle 21 is shortened. on the other hand,
When the spindle drive motor M2 falls, a torque for braking the rotation of the spindle 21 is added, so that the deceleration time of the spindle 21 is shortened. Therefore, the acceleration and deceleration of the spindle 21 are improved, and the individual machining time such as tapping by the turret device 10 and the cycle time of a series of machining by the turret device 10 are shortened, thereby improving the machining efficiency. it can. Further, even when the output of the spindle drive motor M2 is increased or the load side inertia of the load member such as the cutting tool 14 is increased, it is possible to suppress the acceleration / deceleration time from being lengthened.

The flow control valve and the flow rate control solenoid valves 80 and 81 are valve-controlled while monitoring the torque fluctuation of the spindle drive motor M2, and synchronized with the pneumatic motor M3 when a high load such as acceleration or deceleration of the spindle 21 occurs. Is operated, the pneumatic motor M3 operates only when assistance is required, so that the power for driving the pneumatic motor M3, that is, wasteful consumption of compressed air can be suppressed.

In general, a pneumatic motor has the advantage of being smaller and lighter than an electric motor of the same output, so that the size of the auxiliary power means 72 can be reduced as compared with the case where an electric motor is used as an auxiliary driving source. Through the weight reduction, it is possible to reduce the weight and size of the entire spindle drive device 70.

Since the air supplied to the pneumatic motor M3 is taken from the air supply means 48 provided in the turret device 10, there is no need to provide an additional air supply source or a complicated piping system. Thus, the configuration of the spindle drive device 70 can be simplified.

Since the pneumatic motor M3 is freely rotatable independently of the main shaft 21 except when the main shaft 21 is under a high load, the pneumatic motor M3 is operated only when the main shaft 21 is under a high load, and Wasteful consumption can be suppressed.

Although the embodiment in which the spindle drive device 70 according to the present invention is incorporated in the turret device 10 has been described, the present invention is not limited to the turret device 10 as long as the equipment has a spindle connected to a load member. Needless to say, it can also be applied to.

[Brief description of the drawings]

FIG. 1 is a front view showing the appearance of a turret device incorporating a spindle drive device according to the present invention.

FIG. 2 is a sectional view of a main part schematically showing an internal structure of the turret device.

FIG. 3 is a cross-sectional view showing a main part of a driving device of a main shaft.

FIG. 4 is an operation time chart for explaining the operation of the embodiment;

[Explanation of symbols]

REFERENCE SIGNS LIST 10 turret device (equipment) 14 cutting tool (load member) 21 spindle 48 air supply means (compressed air supply source) 70 spindle drive device (71 drive unit, 72 auxiliary power unit) 75 vane 76 ... input shaft 78, 79 ... A, B port 80, 81 ... flow control solenoid valve 82 ... planetary roller 83 ... pin 84 ... collet type rotor 85 ... lock ring 86 ... permanent magnet 87 ... electromagnet M2 ... spindle drive motor ( 71: driving means) M3: pneumatic motor (72: auxiliary power means)

Claims (6)

[Claims] 1. A drive device for a spindle incorporated in a facility having a spindle connected to a load member such as a processing tool, comprising: a drive unit for rotating and driving the spindle; and a driving device for accelerating the spindle. An auxiliary power unit that is connected to the main shaft to apply a rotational force to the main shaft when a load is applied, and a driving device for the main shaft. 2. The main shaft according to claim 1, wherein the auxiliary power unit is connected to the main shaft and applies a braking force to the main shaft when a high load is applied, such as when the main shaft is decelerated. Drive. 3. The main shaft drive device according to claim 1, wherein the auxiliary power unit operates in synchronization with the high load of the main shaft. 4. The apparatus according to claim 1, wherein said auxiliary power means comprises a pneumatic motor which converts the energy of the compressed air into a rotational force and is rotatable in both forward and reverse directions.
A drive device for a spindle according to any one of claims 1 to 3. 5. The main shaft driving device according to claim 4, wherein the compressed air supplied to the pneumatic motor is taken from a compressed air supply source provided in the facility. 6. The spindle according to claim 4, wherein the pneumatic motor is freely rotatable independently of the spindle when the spindle is not under the high load. Drive.