JP3438478B2 - Spindle drive - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an equipment provided with a spindle connected to a load member such as a machining tool, for example, a spindle driving device incorporated in a turret device or the like.

[0002]

2. Description of the Related Art Automotive parts are manufactured through various processes such as a press working process and a mechanical working process, but in order to improve production efficiency, a turret device has been frequently used in the mechanical working process.

This turret device is one of the equipment provided with a main shaft connected to a load member such as a machining tool, and is provided on a drum rotatably mounted on a non-rotating post and on the circumference of the drum. And a plurality of gear heads. A cutting tool is provided on each gear head, and the desired gear head suitable for the purpose of machining is indexed to a machining position facing the workpiece out of a plurality of gear heads by rotating the drum, and sequentially performing predetermined machining. Has become.

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 the clutch mechanism. As a result, the cutting tool rotates, and the workpiece is subjected to predetermined machining such as tapping (see Japanese Patent Publication No. 63-9923 and Japanese Patent Publication No. 63-47003).

In recent years, some turrets are rotationally indexed by the power of a spindle drive motor.

[0006]

In equipment equipped with a spindle such as a turret device, when the load acting on the spindle is large, for example, when accelerating and decelerating, the acceleration / deceleration performance of the spindle is determined by the spindle drive motor. Most of the rising time of the spindle, that is, the acceleration time and the falling time of the spindle, that is, the deceleration time are determined based on the relationship between the rotor inertia of the motor and the torque.

For this reason, when the output of the spindle drive motor increases, the rotor inertia of the motor also increases accordingly, and the acceleration time and deceleration time increase. Further, if the load-side inertia of a load member such as a cutting tool connected to the spindle is increased, the acceleration / deceleration time is further lengthened. If the spindle acceleration time and deceleration time are long as described above, there is a problem that individual machining time such as tap machining by the turret device and a cycle time of a series of machining by the turret device become long.

The present invention has been made in order to solve the problems associated with the above-mentioned prior art, and when the high load is applied to the spindle, the torque of the spindle is supplemented to speed up the work to be performed by the equipment. An object of the present invention is to provide a drive device for a spindle, which can shorten the cycle time of equipment.

[0009]

In order to achieve the above object, a first aspect of the present invention is a drive device for a spindle, which is incorporated in equipment equipped with a spindle connected to a load member such as a machining tool. a driving means for rotationally driving the spindle, complement
It constitutes an assisting means and uses the energy of compressed air as a rotational force.
Pneumatic motor that can be converted and converted to rotate in both forward and reverse directions
In order to rotate the pneumatic motor forward or reverse.
Flow path switching valve for switching the air supply path to the pneumatic motor
And the pneumatic motor accelerates the spindle or
Is connected to the spindle during high load such as deceleration
Add torque to the main shaft and synchronize with the high load
It is a drive device for a main shaft, which is characterized in that

In this spindle driving device, at the time of high load such as acceleration of the spindle, the spindle constitutes auxiliary power means connected to the spindle in addition to the rotational force by the driving means.
Rotational force is also applied from the pneumatic motor to rotate the motor . Therefore, the output of the drive means is assisted to compensate for the torque shortage at high load, and the acceleration time of the spindle is shortened. Therefore, the acceleration of the spindle is improved, and the time required for the 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 pneumatic motor applies the rotational force, so that the acceleration time can be prevented from becoming long.

[0011]

Further, in the high load such as when decelerating the spindle, spindle, the braking force from the pneumatic motor connected to the spindle is decelerated is added, the deceleration time of the spindle is reduced. Therefore, the deceleration of the spindle is improved, and the time required for the work to be performed on the load member and the cycle time of the equipment are shortened. Also, increase the output of the driving means,
Even if the load side inertia of the load member increases, the air pressure
Since the motor applies the braking force, it is possible to prevent the deceleration time from increasing.

[0013]

Further , since the pneumatic motor operates only at the time of a high load requiring assistance such as acceleration or deceleration of the main shaft, wasteful consumption of compressed air for driving the pneumatic motor is suppressed.

[0015]

Further, the advantages of the pneumatic motor that is compact and light in comparison with the electric motor of the same output, small auxiliary power unit, through weight reduction, entire spindle of the driving device becomes smaller ones lightweight.

Further, in the invention according to claim 2 , the compressed air supplied to the pneumatic motor is obtained from a compressed air supply source provided in the facility.

With such a structure, it is not necessary to separately provide a compressed air supply source for driving the pneumatic motor or a complicated piping system, and the structure of the main shaft drive device becomes simple.

Further, in the invention described in claim 3 , the pneumatic motor is freely rotatable independently of the main shaft except when the main shaft is under the high load.

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

[0021]

According to the spindle drive device of the first aspect of the present invention, when the spindle is accelerated or decelerated at a high load, the pneumatic motor constituting the auxiliary power means assists the output of the drive means to increase the output. the lack of torque at the time of load or Tsu complement, the main shaft
Since the torque for braking the rotation of the spindle is added , the acceleration and deceleration of the spindle are improved, and the time required for the work to be performed by the load member and the cycle time of the equipment can be shortened. Also, increase the output of the driving means,
Even if the load side inertia of the load member increases, the air pressure
Since the motor adds a torque can be suppressed pressurized decrease deceleration time becomes long.

[0022]

Further, the air pressure is synchronized with the high load of the spindle.
Since the motor is operated, wasteful consumption of compressed air for driving the pneumatic motor can be suppressed.

Moreover , because of the advantage of the pneumatic motor that it is smaller and lighter than the electric motor of the same output, the overall weight and size of the drive unit for the spindle can be reduced by making the auxiliary power means smaller and lighter. Is possible.

According to the second 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, and the structure of the drive device for the spindle is simple. Can be realized.

According to the third aspect of the invention, it is possible to operate the pneumatic motor only when the load on the main spindle is high, and to suppress wasteful consumption of compressed air for driving the pneumatic motor.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

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

As one of the equipment provided with a spindle connected to a load member such as a working 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 attached to a non-rotating post 11 and a plurality of gear heads 13 provided on the circumference of the drum 12. There is. Each gear head 13
A cutting tool 14 is provided in the machine, and the drum 12 is swiveled to index a desired gear head 13 suitable for a machining purpose from a plurality of gear heads 13 to a machining position facing a workpiece, and sequentially perform predetermined machining. It is like this.
The turret device 10 is provided with a spindle system including a spindle 21 connected to the cutting tool 14 of the gear head 13 indexed to a machining position, and a spindle drive device 70 is incorporated to rotate the spindle 21. 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 main 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 project in a direction orthogonal to the inclined surface of the main body 17. A boss portion 12 a of the drum 12 is inserted into the post 11 and is rotatably supported by the post 11 via a bearing 18. The rotation indexing of the gear head 13 is performed by the indexing motor M1 attached to the unit main body 17.
(See FIG. 1), the drum 12 is driven to rotate in 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 the four indexing surfaces on the conical surface. 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 drive shaft 20 and the spindle system horizontally supported in the unit main body 17 have the same axial center. To do.
The main shaft system includes a main shaft 21 and a clutch shaft 21 a that is movable back and forth only in the axial direction with respect to the main shaft 21 and rotates together with the main shaft 21.
It has and. A clutch mechanism 22 is provided between the clutch shaft 21a and the drive shaft 20, and a sleeve 23 that rotatably holds the clutch shaft 21a moves back and forth with respect to the drive shaft 20 to move the main shaft 21 and the drive shaft 20 together. Are connected or disconnected. The sleeve 23 is connected to the cylinder 25 via a shifter 24,
Moves back and forth by the action of. Spindle drive device 70 described later
Driving force is transmitted from the main shaft system to the gear head 13 via the clutch mechanism 22, whereby the cutting tool 14 rotates and a predetermined machining such as tapping is performed on the work.

The fluid distributor 15 comprises four gear heads 1.
Fluids such as cutting oil, air and lubricating oil are distributed to the drum 3, and the rotary joint 30 is attached to the drum 11 and rotates together with the drum 11. The rotary joint 30 has a hollow cylindrical shape, and an inner peripheral surface of the rotary joint 30 is slidably fitted to an outer peripheral surface of the post 11 having a cylindrical shape. Each fluid is supplied to the gear head 13 via a plurality of pipes P connected to the rotary joint 30, but cutting oil is supplied only to the gear head 13 indexed to the machining position, and air and lubricating oil are supplied to the non-machining position. It is always supplied to a 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 that communicates with the cutting oil distribution port 31 for the gear head 13 that is indexed to the processing position. In addition, the post 11 has a first air supply port 44, a second air supply port 45, which are in constant 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 is formed. 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 air supply means 48 through the pipe P6, and the first air supply port 47 and the second air supply port 47, respectively.
It communicates with an air supply port (not shown). Further, the lubricating oil supply hole 46 is provided with the lubricating oil supply means 50 through the pipe P7.
Is connected to the lubricating oil supply port 51 connected to.

Then, when the desired gear head 13 is indexed to the processing position by turning the drum 12, the gear head 13 is rotated.
Cutting oil distribution port 31 for communication with the cutting oil supply hole 32,
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 generate each air. It is supplied to the gear head 13. Lubricating oil is similarly supplied to each gear head 13.

As described above, the drive force of the spindle drive device 70 is transmitted to the gear head 13, but the spindle drive device 70 of this embodiment drives the drive means 7 for rotating the spindle 21.
1 and auxiliary power means 72 that is connected to the main shaft 21 and applies a rotational force to the main shaft 21 when the load is high such as when accelerating the main shaft 21. The auxiliary power means 72 is provided when the load is high such as when the main shaft 21 is decelerated.
It is connected to the main shaft 21 and applies a braking force to the main shaft 21.

More specifically, the driving means 71 is
It is composed of 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 its output shaft 26. As shown in an enlarged manner in FIG. 3, the main shaft 21 is firmly connected to the output shaft 26 by a tightening ring 73 provided at the end of the main shaft 21.

As shown in the enlarged view of FIG. 3, the auxiliary power means 72 is composed of a pneumatic motor M3 which converts the energy of 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 which is in sliding contact with the inner peripheral surface of the cylinder portion formed in the housing 74 is provided on the input shaft 76. The input shaft 76 is provided with respect to the main shaft 21 via a bearing 77. Are held relatively freely rotatable.

Two air systems, an A port 78 and a B port 79, are formed in the housing 74, the unit body 17, etc. 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 connects the pneumatic motor M3.
Air is supplied to.

The pneumatic motor M3 is driven to rotate in both forward and reverse directions. When the pneumatic motor M3 rotates in the same rotation direction as the rotation direction of the main shaft 21, the A port 78 outputs the normal rotation. 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 the port 79 and exhausted from the A port 78. In order to selectively supply air from the A port 78 or the B port 79 corresponding to the desired rotation direction of the pneumatic motor M3, a flow passage switching valve (not shown) for switching the air supply passage is provided. Furthermore, the A and B ports 78 and 79 are
Flow rate control solenoid valves 80, 81 for controlling the amount of air supplied to the pneumatic motor M3 are provided.

A plurality of planets, which are sandwiched between the outer peripheral surface of the base end of the input shaft 76 and the inner peripheral surface of the housing, and which are planetary-moved around the input shaft 76 as the input shaft 76 rotates. A roller 82 is arranged. The input shaft 76
The outer peripheral surface of the base end may be the sun gear, the inner gear may be formed on the inner peripheral surface of the housing, and the planetary roller 82 may be the planetary gear.
A collet type rotor 84 connected to the planetary roller 82 via a pin 83 is arranged adjacent to the input shaft 76 in the axial direction. The collet type rotor 84 is formed with 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 into a lock ring 85 whose inner circumference is a tapered surface, and when the lock ring 85 is moved rightward in the drawing along the axial direction, the collet portion 84b is fastened to the main shaft 21,
The torque of the input shaft 76 is transmitted to the main shaft 21 via the planetary roller 82, the pin 83, and the collet type rotor 84. When the lock ring 85 is moved to the left in this state from this state, the tightening of the collet portion 84b is released, and the torque transmission from the input shaft 76 to the main shaft 21 is cut off. 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.

For the above-mentioned movement control of the lock ring 85,
The lock ring 85 is made 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 leftward in the figure, and the input shaft 76 is in a rotation-free state. On the other hand, when the coil is de-energized, the magnetic lock ring 8
No. 5 is attracted to the permanent magnet 86 and moves rightward in the drawing, and 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 set to the main shaft 21.
The rotation of the pneumatic motor M3 is controlled so as to be synchronized with the rotation speed of. This rotation control is performed by adjusting the amount of air supplied to the pneumatic motor M3.
The air supply amount is adjusted by the flow rate controlling solenoid valves 80 and 81 provided on the valve 9.

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

FIG. 4A shows the torque change of the main shaft 21,
(B) is a time chart showing a speed change of the main shaft 21, (C) a speed change of the feed shaft, (D) a port switching state, and (E) an on / off state of the electromagnet 87. . In addition, in FIGS. 9A and 9B, the change in the case of the present embodiment including the auxiliary power means 72 is shown by a solid line,
The change in the case of the comparative example in which the auxiliary power means 72 is not operated is shown by a dotted line. Further, in FIG. 7A, the torque region supplemented by the auxiliary power means 72 is shown by hatching.

In this embodiment, FIG. 4 (A) (D) (E)
As shown in FIG. 5, the air supply (ON) / air supply stop (OFF) operation and the electromagnet 87 ON / OFF operation by opening and closing the flow control solenoid valves 80 and 81 are performed by the upper limit set value a and the lower limit of the torque of the main shaft 21. It is designed to be synchronized with the timing beyond the range determined by the set value b. Spindle drive motor M2
The torque fluctuation can be monitored based on the current value applied to the motor M2, but it may be monitored by separately providing a detection unit such as a torque sensor.

Further, the 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. It is performed based on the position of the feed shaft to be advanced, and when the feed shaft is in the backward limit position, the A port 78
Is used as the air supply path, and when the feed shaft reaches the forward limit position, the B port 79 is switched to serve as 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 gear head 13 suitable for the purpose of machining is indexed by rotating the drum 12, as shown in FIG. 2, the sleeve 23 moves forward by the operation of the cylinder 25, so that the main shaft 21 becomes the clutch shaft. It is connected to the drive shaft 20 of the gear head 13 via 21 a and the clutch mechanism 22.

Before starting the spindle drive motor M2, as shown in 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 attracted to the electromagnet 87 is attracted to the permanent magnet 86 and moves rightward in FIG. 3, and the collet portion 84b 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. When the current value sharply increases with the start of the spindle drive motor M2, as shown in FIG. By operating the flow path switching valve, the A port 78 serves as the air supply system and the B port 79 serves as the exhaust system,
The flow control solenoid valve 80 of the A port 78 is opened to start (turn on) air supply. The pneumatic motor M3 rotates normally in accordance with the air supply from the A port 78 (the same direction as the rotation direction of the main shaft 21).
However, the torque of the input shaft 76 in the pneumatic motor M3 is
It is transmitted to the main shaft 21 via the planetary roller 82, the pin 83 and the collet type rotor 84.

Then, as shown in FIG. 4 (A), the main shaft 21 is rotationally driven by adding the torque transmitted from the pneumatic motor M3 in addition to the torque of the main shaft drive motor M2 itself. 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 such as acceleration of the main shaft 21, as shown in FIG.
As shown in (B), the rising time (t1-0) until the spindle speed reaches the predetermined speed V0 is determined by the auxiliary power means 72.
Is shorter than that of the comparative example in which is not operated.

When accelerating the spindle speed to reach the predetermined speed V0, the pneumatic motor M3 operates so that the rotation speed of the collet type rotor 84 is synchronized with the rotation speed of the spindle 21 by A.
Rotation is controlled while the amount of air supply is adjusted by a flow control solenoid valve 80 provided in the port 78.

When the spindle speed reaches the predetermined speed V0, it becomes unnecessary to assist the rotational drive of the spindle 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 is in the stable range, the flow rate control solenoid valve 80 is closed and the air supply from the A port 78 is stopped (turned off). Further, the coil of the electromagnet 87 is energized (turned on). As a result, the magnetic lock ring 85 attracted by the permanent magnet 86 is attracted by 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 the predetermined speed V0, the gear head 1 is driven by the driving force from the spindle driving motor M2.
The cutting tool 14 of No. 3 is rotationally driven and is sent toward the forward limit, and machining such as tapping is performed on the work.

When the feed of the cutting tool 14 reaches the forward limit (time t2 in FIG. 4C), the backward 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
Because the rotor part of No. 2 is rotated by inertial force,
1 is still spinning. When the current value suddenly decreases due to the stop of the main shaft drive motor M2, the coil of the electromagnet 87 is deenergized (OFF) again, and the collet portion 84b is fastened to the main shaft 21, as shown in FIG. 4 (E). Further, as shown in FIG. 4 (D), the flow path switching valve is operated to set the B port 79 as the air supply system and the A port 78 as the 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 due to the air supply from the B port 79 (direction opposite to the rotation direction of the main shaft 21).
However, the torque of the input shaft 76 in the pneumatic motor M3 is
It is transmitted to the main shaft 21 via the planetary roller 82, the pin 83 and the collet type rotor 84. At this time, the reversely rotating pneumatic motor M3 becomes a rotational resistance of the main shaft 21.

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

When the main shaft 21 is decelerated, the flow rate control solenoid valve 81 appropriately adjusts the supply air amount so that a sudden braking force is not applied to the main shaft 21.

When the spindle speed becomes zero (time t4), there is no need to assist the rotation stop of the spindle 21, so the operation of the auxiliary power means 72 is stopped. That is, the flow control solenoid valve 81 is closed to stop (OFF) the air supply from the B port 79, and the coil of the electromagnet 87 is energized (ON). As a result, the collet portion 84b formed by the magnetic lock ring 85
Is released, and the input shaft 76 of the pneumatic motor M3 is released.
Is in a rotation-free state.

The exhaust from the B port 79 at the time of acceleration of the main shaft 21 and the exhaust from the A port 78 at the time of deceleration are blown to the cutting tool 14 through a port, piping, etc., not shown, while being silenced by a silencer, not shown,
It is used as cooling air for the cutting tool 14 so that the air is not wasted.

As described above, in the present embodiment, the pneumatic motor M3 as the auxiliary power means 72 compensates for the torque shortage 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 is lowered, torque for braking the rotation of the spindle 21 is added, so that the deceleration time of the spindle 21 is shortened. Therefore, the accelerating and decelerating properties of the spindle 21 are improved, the individual machining time such as tap machining by the turret device 10 and the cycle time of a series of machining by the turret device 10 are shortened, and machining efficiency can be improved. 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.

Further, the flow path switching valve and the flow control solenoid valves 80 and 81 are valve-controlled while monitoring the torque fluctuation of the main spindle drive motor M2, and the pneumatic motor M3 is synchronized with a high load such as acceleration and deceleration of the main spindle 21. Since the air pressure motor M3 is operated only when the assistance is required, it is possible to suppress unnecessary consumption of power for driving the air pressure motor M3, that is, compressed air.

Further, since the pneumatic motor is generally advantageous in that it is smaller and lighter than an electric motor of the same output, the auxiliary power means 72 is smaller and smaller than the case where an electric motor is used as an auxiliary drive source. Through weight reduction, it is possible to reduce the weight and size of the main spindle drive device 70 as a whole.

Further, since the air supplied to the pneumatic motor M3 is taken from the air supply means 48 provided in the turret device 10, it is not necessary to separately provide an air supply source or a complicated piping system. Therefore, it is possible to simplify the configuration of the spindle drive device 70.

Further, since the pneumatic motor M3 can freely rotate independently of the main shaft 21 when the main shaft 21 is not under a high load, the pneumatic motor M3 is operated only when the main shaft 21 is under a high load. It is possible to suppress wasteful consumption of.

The embodiment in which the spindle drive device 70 according to the present invention is incorporated into the turret device 10 has been described. However, the present invention is not limited to the turret device 10 as long as the equipment includes a spindle connected to a load member. It goes without saying that it can also be applied to.

[Brief description of drawings]

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

FIG. 2 is a main-portion cross-sectional view schematically showing the internal structure of the turret device.

FIG. 3 is a cross-sectional view showing a main part of a drive device for a spindle.

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

[Explanation of symbols]

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 means, 72 ... Auxiliary power means) 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)

Continuation of the front page (56) Reference JP-A-7-250403 (JP, A) JP-A-5-70917 (JP, A) JP-A-1-286792 (JP, A) JP-A-56-101063 (JP , A) Actual Kaihei 3-107147 (JP, U) Actual Kaihei 3-47143 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) B23Q 5/04 B23Q 5/06 B23B 19/02 B23B 47/04 B24B 47/10

Claims (3)

(57) [Claims] 1. A drive device for a spindle, which is incorporated in equipment equipped with a spindle connected to a load member such as a processing tool, comprising a drive means for rotationally driving the spindle and an auxiliary power means, and compressed air. The energy of
Pneumatic motor that can be converted into
In order to rotate the pneumatic motor forward or reverse.
A flow path switching valve that switches the air supply path to the pneumatic motor,
And, when the pneumatic motor accelerates or decelerates the spindle,
When the load is high such as when the
A drive device for a main shaft, characterized in that, when a load is added, the drive device operates in synchronization with the high load . 2. Compressed air supplied to the pneumatic motor
The drive device for the main shaft according to claim 1 , wherein is taken from a compressed air supply source provided in the facility . 3. The pneumatic motor is characterized in that the height of the spindle is high.
When not under load, rotate freely separately from the main shaft
The drive device for a spindle according to claim 1 or 2, wherein the drive device is free .