JPS5924954A - High speed barrel grinding device - Google Patents

Abstract

PURPOSE:To efficiently perform barrel grinding work with a barrel grinding device for polishing a work, by forming the shape of a barrel tank in that of vessel of small size with an internal diameter of about 600mm. or less and driving the barrel tank to be rotated at a high speed of about 80rpm or more. CONSTITUTION:A barrel tank 14 with internal diameter of about 600mm. or less is rotatably supported by a rotary shaft 16, tilted by about 30 deg., and driven to be rotated at about 80rpm or more by a driving motor 24 provided with 32 poles, the number of effective ones of which may be switched as required, through a gear type speed reduction gear 20 and a V-belt 22. This barrel tank 14, being of low inertia due to its small diameter, can eliminate the necessity for a one-way clutch further solve the problem of deflection of the center, and the life of a bearing device can be increased together with reduction of the waiting time, then work efficiency can be improved. In addition, the barrel tank, being rotated at a high speed, can eliminate the necessity for using a worm reduction gear, and rapid braking and reversible rotary driving are easily performed.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a barrel processing device that polishes a workpiece by rotationally driving the barrel tank while holding the workpiece in media housed in the barrel tank. This invention relates to a high-speed barrel processing device that eliminates mechanical and operational problems caused by the inertia of the barrel tank and the use of a reducer with a high reduction ratio by reducing the diameter of the barrel and driving the barrel at a high rotational speed. .

1. A rotatably supported rotating shaft; a container-shaped barrel containing media and fixed to the upper end of the rotating shaft; 1. There is a barrel processing apparatus that includes a rotation drive device operatively connected to the rotating shaft and rotationally drives the barrel tank, and polishes the workpiece by rotationally driving the barrel i while holding the workpiece in a medium. For example, there is a so-called gyro-type barrel processing device shown in FIG.

In the figure, a rotatably supported vertical rotating shaft 1
At the upper end of 00, there is a barrel tank 1 having a cylindrical shape with a large diameter and a bottom.
02 is fixed, and the lower ends of the rotating shafts 1, JO are connected to a drive motor (not shown) via a worm reducer 104.
is designed to be rotationally driven. Further, in such an apparatus, a holding device 10 for holding the workpiece 106 is provided.
8 can be inserted into the barrel tank 102,
It is generally formed to have a large inner diameter of about 1500+ nm, and in order to maintain the circumferential speed of the media for polishing the workpiece 106 at a predetermined speed, the rotating shaft 100 is rotated by 2°r, p,
It is designed to be rotated at a speed of about 1,000 m.

However, such conventional barrel processing equipment has various disadvantages as described below. That is, (1) Since the barrel tank 102 has a large diameter, it is difficult to process it with high precision, which causes an increase in the cost of the equipment, and also causes the center of gravity to shift from the center of rotation, causing vibration during rotation. Bearing device 1 that easily supports a rotating shaft 100
This caused 10 malfunctions.

(2) The rotation speed of the barrel tank 102 is 2 Or, p,
m, it is preferable to use the worm reducer 104 which can obtain a large reduction ratio when using a normal electric motor. However, since the diameter of the barrel tank 102 is large and the inertia is large, The sprockets 114 and 116 or the chain 118 that connect the output shaft 112 of the worm reducer 104 and the rotating shaft 100 are easily damaged.

(3) Therefore, in order to allow the rotation caused by the inertia of the barrel tank 102 independently of the worm reducer 104, a one-way clutch 120 as shown in FIGS. 6 and 7 is used.
is being installed. However, the one-way clutch 120 is frequently damaged because a large force is applied each time the barrel tank 102 is started or stopped, which is one of the causes of lowering the reliability of the barrel processing apparatus.

(4) Furthermore, since the one-way clutch 120 allows the barrel tank 102 to rotate according to its inertia, a waiting time of about 5 to 10 seconds is required until the rotation of the barrel tank 102 stops, reducing barrel processing efficiency. Was.

The present invention was made against the background of the above circumstances, and its purpose is to provide a high-speed barrel machining device that eliminates the mechanical and operational problems caused by the inertia and low rotational speed of the barrel tank. It is about providing.

In order to achieve such an object, the present invention provides a barrel tank having a small diameter container shape with an inner diameter of approximately 600 mm or less, and a barrel tank having a rotation speed of approximately 8Qr, p, rri or more in a rotational drive device. It is characterized by being driven to rotate at high speed.

In this way, the diameter of the barrel tank is made small and the inertia is greatly reduced, so processing of the barrel tank becomes easy and the barrel tank can be manufactured at a low cost. can be significantly improved. In addition, a one-way clutch is not required, making the device simpler and
Troubles caused by one-way clutches are completely eliminated.

Barrel machining work becomes more efficient.

In addition, in order to maintain the circumferential speed of the media in the part that holds the workpiece at a predetermined speed, the barrel tank is driven to rotate at high speed, so a speed reducer with a relatively small reduction ratio such as a gear reducer or chain reducer is used. Since the one-way clutch is eliminated, it is possible to quickly start and stop the barrel tank by the drive motor, and by such a drive method, <
It also has the effect of effectively stirring the media in the tank.

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described in detail below based on the drawings.

In FIGS. 1 and 2, a tilting table 12 whose upper surface is inclined approximately 30 degrees with respect to the horizontal is fixed on the base lO, and the upper surface of the tilting table 12 has a vertical A barrel tank 14 is provided so as to be driven to rotate around an axis inclined at approximately 30 degrees with respect to the line. That is, on the inclined table 12,
A rotating shaft 16 inclined approximately 30 degrees with respect to the vertical line is rotatably supported by a bearing device 18, and a barrel tank 14 having a container shape with an open top is fixed to the upper end of the rotating shaft 16. has been done. The lower end of the rotating shaft 16 is connected to the 32
It is connected to a drive motor 24 having a pole and the number of poles can be changed, and the barrel tank 14 is driven to rotate around a rotation axis inclined at approximately 30 degrees with respect to the vertical line by the drive motor 24. It has become. Therefore, reducer 2
0 and the drive motor 24 form a rotary drive.

The reducer 20 is fixed to the lower end of the bearing device 18, and the rotation transmitted to the V pulley fixed to the input shaft of the reducer 20 via the V belt 22 is reduced at a ratio of approximately 11:1. Rotation #h 16 is transmitted. The rotating shaft 16 passes through the reducer 20, and the rotating shaft 16 directly serves as the output shaft of the reducer 20. In addition, V
The pulley 25 has a diameter approximately twice that of the pulley fixed to the output shaft of the drive motor 24, and the rotation speed of the drive motor 24 is eventually reduced to 1/22, so that the rotation shaft 16 is rotationally driven. It has become. Therefore, when the drive motor 24 has four poles and rotates at a speed of about 170 Or, p, m, the barrel tank 14 rotates at a speed of about 8 Or, p, +n.

It is designed to be rotationally driven.

As shown in FIG. 3, the barrel tank 14 has a rotating shaft 16
A disc-shaped flange portion 26 fixed to the upper end with mounting bolts 27, a frame portion 28 projecting upward at equal intervals in the circumferential direction on the outer periphery of the flange portion 26, and a frame portion 26.
Inner diameter 600 m supported by frame 28 inscribed in 8
It is composed of a container-shaped tank main body 30 of about m. The tank body 30 includes a cylindrical portion 32, a tapered portion 34 whose diameter decreases downwardly following the cylindrical portion 32 and forms an inclination of approximately 30 degrees with respect to the flange portion 26, and an upper end of the cylindrical portion 32. and an opening edge 36 facing inward. Therefore, the mounting bolt 27 can be easily removed between the tapered portion 34 and the flange portion 26, and the barrel tank 14 can be quickly attached and detached.

On the inclined table 12 located below the barrel tank 14, the barrel tank 1
A container 38 for receiving the coolant and media slag flowing out from the container 4 is tilted and fixed, and the coolant and the like collected at one end of the container 38 pass through the tilted receiving gutter 40 and are stored in a tank (not shown). A cover 44 that covers the barrel tank 14 and has a top plate 42 that is spaced apart from the opening edge 36 of the barrel tank I4 by a small gap is fitted into the container 88. Coolant and the like are blocked by the cover 44 and collected in the container 38.

Note that the container 38 includes a first partial container 46 that is approximately U-shaped;
The second partial container 48 has a hook between its U-shaped tips.
By removing the second partial container 48, the first partial container 46 can be pulled out in a direction perpendicular to the rotating shaft 16 without removing the barrel tank 14. Further, a nozzle 50 for discharging coolant is provided at the U-shaped tip of the first partial container 46, so that media slag and the like are swept away by the coolant into the first partial container 46 to prevent the media slag from sticking. It has become.

The upper surface plate 42 of the cover 44 has a through hole 56 that allows a holding device 54 that is elongated in the vertical direction, is driven in the vertical direction, and holds a workpiece 52 at its lower end to be inserted into the barrel tank 14. is formed, and the workpiece 52 is held in the media contained in the barrel tank 14 by the holding device 54. Further, on the top plate 42, a workpiece 52 which has been slightly pulled out of the media in the barrel tank 14 and
A perforated member 5 provided in the cylindrical part 32 located at the upper part of the
8, nozzles 60 and 62 that inject coolant toward
is installed.

The center part of the upper surface of the seven rungs 26 and the upper end surface of the rotating shaft 16 form the bottom surface inside the barrel tank 14, and the discharge passage 64 formed through the axis of the rotating shaft 16 is located at the center of the bottom surface. It is opened to the public. The opening of the discharge passage 64 into the barrel tank 14 has a large number of openings that block the passage of normal-sized media but allow the passage of particles smaller than a predetermined size. A perforated member 66 having a hole is removably attached. Perforated member 66
is formed into a cone shape with an apex angle of about 90 degrees by a so-called punched metal plate material in which a large number of predetermined holes are punched, and the center part thereof extends upward along the rotation axis of the barrel tank 14. It is removably fixed so as to protrude and the seven rungs 68 at the base are in close contact with the periphery of the opening of the discharge passage 64.

Returning to FIGS. 2 and 3, a gate-shaped seven frame 70 is erected on the base 1o, and a vertical drive device 72 is provided for vertically driving the holding device 54 that holds the workpiece 52. It is being That is, the vertical drive device 72 includes a pair of guide rods 74 fixed inside the gate-shaped frame 7o, a vertical frame 76 supported movably in the vertical direction by the guide rods 74, and an upper end of the gate-shaped frame 7o. It is fixed to a horizontal part and includes an upper and lower cylinder 78 with a rod fixed to an upper and lower frame 76, and is narrated so as to be driven in the vertical direction by the upper and lower cylinders 78. The holding device 54 is fixed to the upper and lower frames 76, and the workpiece 52 held by the holding device 54 is inserted into the barrel tank 14 together with the lower end of the holding device 54 by the upper and lower cylinders 78. be.

The holding device 20 is constructed in substantially the same manner as the workpiece holding device described in Utility Model Registration Application No. 98602 filed in 1982 by the present applicant. That is, its upper end is connected via a chain to a rotating motor 80 fixed to the upper and lower frames 76, and the rotating motor 80 rotates the workpiece 52 around a vertical axis, and the upper end of the gate-shaped frame 70 Opening/closing cylinder 8 fixed on the horizontal part
When the upper end of the holding device 54 is pressed downward by the holding device 2', a chuck for gripping the workpiece 52 provided at the lower end of the holding device 54 is opened and closed.

On the other hand, as shown in FIG. 2, the operation/detector 84 detects the position state of each movable part such as the position of the upper and lower frames 76, and the operation state of an operating device such as a push button or a foot switch. A state signal SJ representing the positional state of the controller and the operating state of the operating device is supplied to the control drive circuit 86. The control drive circuit 86 supplies the drive motor 24 and the rotary motor 80 with power signals SDI and 8D2 for rotationally driving or braking the rotation in a predetermined rotational direction based on a predetermined program according to the status signal SJ. .

The control drive circuit 86 is constituted by a sequence circuit shown in FIG. 4, for example. Here, drive motor 2
4 and the rotary motor 80'' are a multi-pole AC induction motor and a 4-pole AC motor that can select between 32 poles and 4 poles,
88 is an electromagnetic brake unit. The electromagnetic brake unit 88 supplies a DC current to a coil for forming a rotating magnetic field in the AC motor, forms a DC magnetic field in the AC motor, and rapidly brakes the rotor of the AC motor by eddy current braking. This is a well-known method that supplies DC power to one phase of the coil of the drive motor 24 from its output terminals + and - for a certain period of time after the voltage supplied to its input terminal 0 is removed. It is configured. The electromagnetic brake unit 88 is equipped with a timer that controls the time for supplying DC power to the drive motor 24, and is kept closed at all times, but is checked to be open when DC power is being supplied. A contact AC6Q is provided.

The present invention will be explained in detail below.

As the device starts up, a circuit (not shown) causes the first
When the electrical voltage from the transformer TR1 is supplied to each group of relays in the figure, the relays Ai 84, M, and S6 are activated, and drive signals SD2 and SDI are supplied to the rotary motor 80 and the drive motor 24. Therefore, the workpiece 52 is rotationally driven counterclockwise around the vertical axis, and
The barrel tank 14 is driven to rotate clockwise, which is the opposite direction to the rotation direction of the workpiece 52. Then, when the upper and lower frames 76 are lowered according to another control circuit (not shown), the workpiece 52 is inserted into the media housed in the barrel tank 14. As a result, the workpiece 52 is polished by the media rotating together with the barrel tank 14. The workpiece 52 in FIG. 3 shows this state.

In such a state, contact 0R5 of a relay (not shown)
P, CH2F, C! A timer TRIQ, identified by l'L7F and connected in series with the contacts, begins timing the polishing state. The set time of the timer TR10 is determined corresponding to the first polishing period that is performed first. In addition, in this state, the relay MS
Since the relay MS9 is operated by the motor 6, the drive motor 24 is driven to rotate at high speed with four poles.

After the set time of timer TR1O has elapsed, timer TRIQ
When energizes for a limited time, its contacts are energized to deactivate relays MS4 and MS(3), and relay MS
5 is activated and relay MS9 is subsequently activated. Therefore, the rotary motor 80 is driven in the reverse direction immediately after the first polishing period ends. On the other hand, relays M and S
5, the voltage supplied to the input terminal 0 of the electromagnetic brake unit 880 is removed, so the electromagnetic brake unit 88 immediately supplies DC power to the drive motor 24, causing the drive motor 24 and barrel tank 14 to suddenly At the same time, the confirmation contact AC60 is released to open the time limit contact of the timer TR16X.

In such a state, the centrifugal force that had been acting on the media in the barrel tank 14 disappears, and at the same time it flows toward the center, it also flows in the direction of rotation due to inertial force.
Further, since the inclination of the barrel tank 14 causes the polishing material to flow toward the lower part of the barrel tank 14, the fluid is stirred extremely efficiently by the dominant flow, and the polishing efficiency is suitably maintained.

- After a certain period of time has elapsed, the DC output of the electromagnetic brake unit 88 is stopped, and at the same time, the confirmation contact AC60 is closed and the timer TR16X starts timing. timer TR
After a very short set time of 15X has passed, timer TR16
When the time limit contact of X is closed, relay MS7 is activated. Therefore, the power signal SDI for driving the drive motor 24 to rotate in the direction opposite to the rotation direction of the first polishing period is supplied to the drive motor 24, and the barrel tank 14 is rotated counterclockwise. As a result, the workpiece 52 is polished again, and the second polishing period begins. In this state, the relay MS
The second polishing period continues until the TR 13, which started the timing operation at the same time as step 5, operates for a limited time. Timer TR1
3 operates for a limited time, the time limited contact activates the relay MS.
9 is deactivated and relay MS8 is activated. Therefore, the drive motor 24 is driven to rotate with 32 poles, and drives the barrel tank 14 at about ⅛ the rotation speed compared to the first and second polishing periods. Therefore, barrel tank 1
The media in the barrel tank 14 is fluidly stirred together with the inclination of the barrel tank 14, and media slag and the like are efficiently discharged by the coolant injected from the nozzles 60 and 62, and the activity of the media is suitably maintained.

Thereafter, when the power to the group of relays shown in FIG. 4 is cut off by a timer (not shown), the low-speed rotation period ends and one machining cycle ends.

In this way, according to this embodiment, the diameter of the barrel tank 14 is reduced to about 600 mm compared to the conventional 1500 mm, so the inertia of the barrel tank 14 is made extremely small, a one-way clutch is not required, and the barrel Failures caused by the inertia of the tank 14 and the one-way clutch are completely eliminated. Further, since the diameter of the barrel tank 14 is small, the runout of the barrel tank 14 is eliminated, the life of the bearing device is greatly improved, and the barrel tank 14 is easy to manufacture, making the device inexpensive. Furthermore, since the inertia of the barrel tank 14 is small and a one-way clutch is not required,
The waiting time due to rotation of the barrel tank 14 due to inertia is almost eliminated, and work efficiency is suitably improved.

Moreover, since the barrel tank 14 is rotated at a high speed several times (80 r, p, m,) compared to the conventional 2 Or, p, m, it is difficult to reduce the speed of gear reducers, etc., which are inherently strong. A speed reducer with a relatively small ratio can be used in place of the worm speed reducer with its output shaft directly connected to the barrel tank 14, and failures caused by the worm speed reducer can be completely eliminated, and This has the advantage that braking and forward/reverse driving are possible. Furthermore, during such sudden braking and forward/reverse driving, the belt 22 slips appropriately and functions as a torque limiter, which has the advantage of absorbing mechanical shocks and preventing failures.

Further, according to this embodiment, the workpiece 52 and the barrel tank 14 are rotated in the opposite direction during the first polishing period, and in the subsequent second polishing period, they are each driven in the opposite direction to the previous period, so that the workpiece 52 and the barrel tank 14 are extremely uniformly rotated. It has the advantage that polishing can be performed with high efficiency.

Further, according to this embodiment, the tapered portion 34 is provided in the barrel tank 14.
, the weight of the media is reduced and the inertia of the barrel tank 14 is further reduced.

Although one embodiment of the present invention has been described above in detail based on the drawings, the present invention can also be applied to other aspects.

For example, the barrel tank 14 in the above embodiment has a diameter of 6.
However, according to experiments conducted by the present inventors, when the diameter of the barrel tank is set to about 800 mm, the inertia of the barrel tank 14 can be further reduced and the rotation drive device can be rotated at higher speeds without straining. It was capable of rotational driving, rapid forward/reverse driving, and rapid braking. In such a case, the circumferential speed of the media near the workpiece 52 should be increased to 150 Hl.
/min, if a general two-pole AC motor is used, the reduction ratio of the gear reducer may be about 11:1 (the reduction ratio between the pulleys at this time is 2:1). However, if a 4-pole motor is used, the reduction ratio between the pulleys may be 1:1. Also, depending on the reduction ratio between the mouth pulleys and the type of drive motor, the reduction ratio of the reduction gear 20 is between 521 and 15:
It can be selected within a range of 1.

Further, in the above-mentioned embodiment, the barrel tank 14 is driven to rotate around an axis inclined at approximately 30 degrees with respect to the vertical line, but it goes without saying that the angle of inclination can be selected from various values including zero degrees. .

[Brief explanation of drawings]

FIG. 3 is a cross-sectional view showing the main parts of the embodiment. FIG. 4 is a diagram showing a control drive circuit provided in the embodiment of FIG. 1. FIG. 5 is a longitudinal sectional view showing a conventional barrel processing device, and FIGS. 6 and 7 are a plan view and a sectional view showing a one-way clutch provided in the device shown in FIG. 14: Barrel tank 16: Rotating shaft 20: Reducer 1 (rotary drive device) 24: Drive motor Applicant Toyota Motor Corporation Kyoho Seisakusho Co., Ltd.

Claims (4)

[Claims] (1) A rotatably supported rotary shaft, a container-shaped barrel containing media and fixed to the upper end of the rotary shaft, and a barrel operably connected to the rotary shaft to hold the barrel. A barrel processing device comprising a rotary drive device that rotates and polishes a workpiece by rotationally driving the barrel tank while holding the workpiece in the media, wherein the barrel tank has an inner diameter of approximately 600 Inm or less. In addition to having a small diameter container shape, the rotary drive device has approximately 8 Q r,
1. A high-speed barrel machining device characterized by being driven to rotate at a high speed of more than 100 pm. (2) The rotary drive device has a reduction ratio of 115 to 1/1.
5. The high-speed barrel processing apparatus according to claim 1, further comprising a gear type reducer of 5, and rotationally driving the barrel tank via the reducer. (3) The high-speed barrel processing apparatus according to claim 2, wherein the output shaft of the gear type reducer is directly connected to the lower end of the rotating shaft. (4) The rotational drive device includes a multipolar AC motor, and the barrel tank is driven to rotate at a low speed following the high speed rotation by switching the number of poles of the multipolar AC motor. The high-speed barrel machining device according to any one of items 1 to 3.