JPH08300251A - Wheel type grinder - Google Patents

Abstract

PURPOSE: To keep the peripheral velocity of a wheel constant irrespective of the decreased status of a wheel diameter by installing a constant peripheral speedizing means to control a variable speed motor driving means so as to have a motor speed varied in an inversely proportional manner in relation to a diametral size in the wheel. CONSTITUTION: After a diametral decrement value Dn out of a wheel diameter decrement arithmetic circuit 126 in a wheel diameter detecting means 121 is inputted into a wheel diameter arithmetic circuit, each time this diametral decrement value Dn is inputted, a value made up of subtracting the diameter decrement value Dn from the value of a wheel diameter R (n-1) calculated last time is calculated as the new wheel diameter Rn. In succession, a constant peripheral speedizing means 122 controls the extent of output frequency (f) of an inverter circuit of a variable speed motor driving means 120 by an equation of f=K1/Rn on the basis of the value of the wheel diameter Rn calculated in this wheel diameter operational means. Here, K1 is a constant. Like this, the speed of a motor 39 is increased in an inverselt proportional manner in response to the decrement of the wheel diameter, thereby keeping the wheel peripheral velocity to be constant.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wheel type polishing machine for polishing a work by rotating a wheel having an outer peripheral surface as a polishing surface by a motor.

[0002]

2. Description of the Related Art A wheel type polishing machine of this type comprises a conveyer for horizontally conveying a work and a wheel arranged above the conveyer and rotationally driven by a motor. In such a wheel type polishing machine, since the workpiece to be polished is made of a hard material such as metal, the abrasion of the polishing surface progresses in a relatively early stage, and the wheel diameter decreases accordingly. To go. If the wheel rotation speed remains constant despite the wheel diameter becoming smaller, the peripheral speed of the grinding surface will slow down,
In order to continue uniform polishing, it is necessary to increase the rotation speed of the wheel. Also, when the wheel diameter becomes smaller,
The state of contact with the workpiece by the wheel's abrasive surface changes,
There is a risk that the polishing state on the work will not be uniform. Therefore, "cutting" is performed in which the wheel is moved in the direction of approaching the work according to the wear amount of the grinding surface.

[0003]

Conventionally, as a method for accelerating the rotation speed of a wheel when the wheel diameter becomes small, the operator visually checks the reduction of the wheel diameter and, based on the degree of decrease, the operator Had to make an appropriate decision to adjust the wheel rotation speed. Therefore, there is a problem that the peripheral speed of the wheel cannot be kept constant with high accuracy, and the work cannot be uniformly polished.

When cutting the wheel as the diameter of the wheel becomes smaller, the operator visually observes the reduction of the diameter of the wheel in the same manner as described above, and based on the degree of reduction, the wheel is adjusted to an appropriate size. Was supposed to move. Therefore, there is a problem that the contact state of the wheel with the work is not constant, and the work cannot be evenly polished.

The present invention was devised in view of the above circumstances, and its object is to make the peripheral speed of the wheel constant regardless of the reduction condition of the wheel diameter. The purpose is to set an appropriate cutting amount in the cutting operation.

[0006]

As a means for solving the above problems, the invention of claim 1 polishes a work by bringing a wheel having an outer peripheral surface into a grinding surface into contact with the work while being rotated by a motor. In such a configuration, the variable speed motor driving means for driving the motor for driving the wheel so that the rotation speed can be adjusted, the wheel diameter detecting means for detecting the diameter dimension of the wheel, and the diameter of the wheel detected by the wheel diameter detecting means. It is characterized in that it is provided with a constant peripheral speed increasing means for controlling the variable speed motor driving means so that the rotation speed of the motor changes in inverse proportion to the size.

According to a second aspect of the present invention, a wheel having an outer peripheral surface as a grinding surface is rotationally driven by a motor, and the work is polished by bringing the wheel into contact with the work on the processing table. A gap adjusting mechanism that adjusts the gap between the outer peripheral surface and the machining table, a wheel diameter detecting unit that detects the diameter of the wheel, and a gap adjusting mechanism according to the diameter of the wheel detected by the wheel diameter detecting unit are provided. It is characterized in that it is configured to include a constant gap forming means for adjusting the gap by driving.

The invention of claim 3 relates to claim 1 or claim 2.
In the invention, the wheel diameter detecting means includes a polishing number counting means for counting the polishing number of the work, and the value obtained by multiplying the polishing number of the work counted by the polishing number counting means by a constant is the initial diameter of the wheel. It is characterized in that it is configured to detect the diameter of the wheel by subtracting from it.

According to a fourth aspect of the invention, in the invention of the third aspect, the distance from the origin set on the displacement path of the wheel in the contacting / separating direction to the workpiece during the polishing operation to the measurement reference surface provided on the displacement path. The reference distance detection means for detecting the reference distance and the displacement amount detection means for detecting the amount of displacement from the position where the axis of the wheel coincides with the origin to the position where the outer peripheral surface abuts the measurement reference surface. It is characterized in that the initial radial dimension of the wheel is detected by setting the dimension obtained by subtracting the displacement detected by the displacement detection means from the distance detected by the means as the radius of the wheel. .

[0010]

According to the invention of claim 1, when the diameter of the wheel becomes smaller due to the abrasion of the grinding surface, the speed of the motor increases in inverse proportion to the decrease in the diameter of the wheel, whereby the peripheral speed of the wheel is increased. Is kept constant.

According to the second aspect of the present invention, when the wheel surface becomes worn and the wheel diameter becomes small, the gap adjusting mechanism operates in accordance with the diameter dimension of the wheel, and the outer peripheral surface of the wheel is properly adjusted to the work. Get in touch.

According to the third aspect of the invention, for example, the number of workpieces to be polished is set in advance, and each time the set number of workpieces to be polished is counted, the initial number of wheels is multiplied by the number to be polished. The values are sequentially subtracted, and each value is detected as the wheel radial dimension.

In the invention of claim 4, the initial diameter of the wheel is detected by moving the wheel on the displacement path during the polishing operation.

[0014]

According to the first aspect of the present invention, even if the wheel diameter changes, the rotational speed of the wheel is adjusted to keep the wheel peripheral speed constant, so that it is uniform and good for all workpieces. Polishing is performed.

According to the second aspect of the present invention, even if the diameter of the wheel is reduced, the state in which the abrasive surface is in proper contact with the workpiece is maintained, so that good polishing can be continued.

According to the third aspect of the present invention, when the diameter of the wheel is detected, it is not necessary to move the wheel from the polishing position or remove it from the polishing machine, which is efficient. Since the operator does not measure it by himself but calculates it based on the number of polished workpieces, it is possible to save labor.

According to the invention of claim 4, when the initial diameter of the wheel is detected, it is only necessary to move the wheel on the displacement path during the polishing operation, and it is not necessary to remove the wheel from the polishing machine. The detection work can be performed easily and quickly.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. In FIG. 1, a base 1 has an endless conveyor belt 4 between a pair of rolls 3 and 3.
A belt conveyor 2 is provided so as to bridge the workpieces, and the belt conveyor 2 is configured to convey a work in a horizontal direction from right to left in FIG.

As shown in FIG. 13, at the position on the starting end side of the belt conveyor 2 in the conveying direction, in order to prevent the work from entering a polishing area by a polishing mechanism which will be described later in a state where two or more workpieces overlap each other. The overlapping prevention means 5 is provided. The overlap preventing means 5 is formed by screwing a male screw pin 7 onto a bracket 6 supported along the conveying surface of the belt conveyor 2 with its axis lined up and down, and when the male screw pin 7 is rotated, its sharp lower end. The height from the transport surface of the can be adjusted. This male screw pin 7
By setting the height of the workpiece to be larger than the thickness of one work and smaller than the thickness of two works, the passage of two or more works is regulated.

Further, the bracket 6 supporting the male screw pin 7 is provided with a proximity switch 8 located closer to the terminal end in the carrying direction than the male screw pin 7.
The proximity switch 8 is set to a height such that a space slightly larger than the thickness of the work is provided between the downward detection surface 8A and the conveyance surface. Such proximity switch 8
Detects this every time a metal work passes under it. The height of the wheel 13 is adjusted based on the detection signal from the proximity switch 8, that is, the number of polishing processes of the work, as described later.

A frame 10 having an operation panel 11 on its outer surface is provided above the belt conveyor 2. In the following description, the state viewed from the direction toward the conveyance direction of the belt conveyor 2 (right side in FIG. 1) is referred to as the front,
Therefore, the surface shown in FIG. 1 will be referred to as the left side surface.

The frame 10 is provided with a pair of polishing mechanisms 12 and 12 for polishing a work, with a space in the transport direction. Since the pair of polishing mechanisms 1 and 12 are symmetrical in the transport direction, the left side of FIG. 1 will be described in the following description, and the right side will not be described.

As shown in FIG. 3, the polishing mechanism 12 rotates a wheel 13 for polishing the work by bringing the outer peripheral polishing surface into contact with the work, and for moving the wheel 13 up and down above the work. The wheel displacement mechanism 14, the dresser 15 for dressing when the abrasive surface of the wheel 13 is clogged or crushed and the sharpness of the abrasive grains becomes dull, and the dresser 15 is raised and lowered above the wheel 13. The dresser displacement mechanism 16 of FIG.

<Wheel Displacement Mechanism 14> An elevating guide 17 having a dovetail groove extending in the vertical direction is fixed to the frame 10 (see FIG. 4), and a plate-like wheel side elevating slider 18 is attached to the elevating guide 17. Is fitted so that it can move up and down freely. At the lower end of the wheel side lift slider 18,
A female screw body 19 with its axis oriented in the vertical direction is used for the lifting guide 17
Is mounted so as to be integrally movable with the wheel-side lifting slider 18 at a position substantially right under (see FIGS. 2 and 3). On the other hand, on the support plate 20 provided on the frame 10, a wheel-side male screw rod 21 whose axis is oriented in the up-down direction is supported by bearings so that it cannot move vertically and is freely rotatable. A female screw body 19 fixed to the elevating slider 18 is screwed. When the wheel-side male screw rod 21 rotates, the wheel-side elevating slider 18 is raised or lowered integrally with the female screw body 19 by a distance proportional to the rotation angle (rotation amount).
A relief recess 22 is formed at the lower edge of the elevating guide 17 to avoid interference when the female screw body 19 is raised. With the above, the wheel displacement mechanism 14 is configured, and the wheel displacement mechanism 14 is operated by the drive mechanism described later.

<Horizontal Reciprocating Oscillation Mechanism of Wheel 13> The surface of the wheel side lifting slider 18 opposite to the lifting guide 17 is horizontal and is a guide in a direction orthogonal to the conveying direction of the belt conveyor 2. 23 is fixed,
A horizontal slider 24 is fitted in the guide 23 so as to be freely movable. A driven shaft 25 having its axis oriented vertically is rotatably supported by bearings 26, 26 on the horizontal slider 24. Further, on the side of the driven shaft 25, the drive shaft 27 whose axis is oriented in the vertical direction is provided with the bearing 2
An eccentric shaft 29, which is rotatably supported by the wheel-side elevating slider 18 and is decentered from its axis, is integrally and rotatably attached to the drive shaft 27 (see FIG. 7). Through holes (not shown) formed at both ends of a plate-shaped arm 30 are fitted in the eccentric shaft 29 and the driven shaft 25 so as to be rotatable relative to each other.

Furthermore, a driven pulley 31 is integrally rotatably attached to the upper end of the drive shaft 27, which projects from the upper bearing 28, and an output shaft 33 of a wheel swinging motor 32 fixed to the wheel side lift slider 18. A drive pulley 34 is integrally rotatably attached to the drive pulley 34, and an endless belt 35 is stretched between the drive pulley 34 and the driven pulley 31.

When the wheel swing motor 32 is driven,
The rotational force is transmitted to the drive shaft 27 and the eccentric shaft 29 via the drive pulley 34, the belt 35, and the driven pulley 31.
Then, as the eccentric shaft 29 eccentrically rotates about the shaft center of the drive shaft 27, the rotational force is transmitted to the driven shaft 25 via the arm 30 as a pushing / pulling force, so that the horizontal slider 24 is moved. The eccentric shaft 29 is reciprocally driven by the eccentric dimension.

<Rotary Driving Mechanism of Wheel 13> A bearing 36 having an axis line parallel to the moving direction of the horizontal slider 24 is fixed to the horizontal slider 24, and a wheel rotating shaft 37 is attached to the bearing 36. It is rotatably supported with its both ends protruding. The wheel 13 is integrally rotatably attached to one end of the rotary shaft 37. The wheel 13 and the belt conveyor 2 are located directly above the work transfer area.

A driven pulley 38 is integrally rotatably attached to the end of the rotary shaft 37 opposite to the wheel 13. A drive pulley 40 attached to a wheel drive motor 39 fixed to the lower end of the wheel-side lift slider 18 is arranged directly below the driven pulley 38, and is disposed between the driven pulley 38 and the drive pulley 40. An endless belt 41 is stretched around. When the wheel drive motor 39 is driven, the rotational force of the wheel drive motor 39 is generated.
9, the rotation shaft 37 via the belt 41 and the driven pulley 38
The wheel 13 is driven to rotate integrally with the rotary shaft 37.

As described above, the wheel 13 is supported by the horizontal slider 24 and reciprocates in the horizontal direction (axial direction of the wheel 13) with respect to the wheel drive motor 39. Since this reciprocating amount is a relatively small size corresponding to the eccentric amount of the eccentric shaft 29, the amount by which the belt 41 tilts is also small. Therefore, there is no fear that the rotational speed will be changed in the transmission of the rotational force from the wheel driving motor 39 to the wheel 13 and the like.

<Dresser Displacement Mechanism 16> A lifting guide 17 to which the above wheel-side lifting slider 18 is fitted.
A plate-shaped dresser-side lifting slider 42 is fitted vertically above the wheel-side lifting slider 18 so as to be vertically movable. On the rear surface of the dresser-side lifting slider 42, the axis line is arranged in the vertical direction, that is, the female screw body 19 on the wheel 13 side.
The female screw body 43 oriented parallel to the vertical direction penetrates through the vertically long opening 44 formed in the lifting guide 17, and the lifting guide 17
Of the dresser-side lifting slider 42 while protruding to the rear side of the
It is attached so that it can move together with. On the other hand, on the support plate 20 supporting the wheel side male screw rod 21, a dresser side male screw rod 45 having an axis lined in the vertical direction is rotatably supported by a bearing so as not to be vertically movable. The screw rod 45 and the female screw body 43 fixed to the dresser-side lift slider 42 are screwed together. When the dresser-side male screw rod 45 rotates, the dresser-side elevating slider 42 ascends or descends integrally with the female screw body 43 by a distance proportional to the rotation angle (rotation amount). With the above, the dresser displacement mechanism 16 is configured,
The dresser displacement mechanism 16 is operated by a drive mechanism 62 described later.

<Driving Mechanism of Dresser 15> FIGS. 8 to 1
As shown in 0, a slender bracket 46 is horizontally fixed to the dresser-side elevating slider 42. The bracket 46 has a guide 47 extending in a direction parallel to the axial direction of the wheel 13 until it reaches above the wheel 13.
Is attached, and the horizontal slider 4 is attached to the guide 47.
8 is movably fitted. This horizontal slider 4
8 is a female screw body 49 with its axis parallel to the guide 47.
Is attached to the horizontal moving slider 48 so as to be movable integrally therewith while being positioned below the bracket 46 through an L-shaped auxiliary bracket 50.

On the other hand, a bearing 51 consisting of a ball screw is attached to the lower surface of the bracket 46 with its axis aligned with the female thread 49, and a male threaded rod 52 is immovable and free to rotate in this axial direction. The male screw rod 52 is screwed into the female screw body 49. Further, an output shaft (not shown) of a dresser horizontal drive motor 53 is connected to the male screw rod 52 via a speed reducer 54. When the male screw rod 52 is rotated by the drive of the dresser horizontal drive motor 53, the horizontal slider 48 moves integrally with the female screw body 49 in the axial direction of the wheel 13.

Further, the bracket 46 has two sensors 55, which detect the approach of the right end in FIG. 8 when the horizontal slider 48 is located at both ends of the allowable movement range.
55 is attached. When the sensor 55 detects the horizontal slider 48, the rotation direction of the dresser horizontal drive motor 53 is switched, so that the horizontal slider 48 reciprocates within the allowable movement range. The allowable range of movement of the horizontal slider 48 varies depending on the position of the sensor 55, and in this embodiment,
The dresser 15 to be described later is set so as to move within a range that covers the entire width of the wheel 13.

The base end portion of the horizontal slider 48 (the end portion on the side closer to the dresser horizontal drive motor 53 in FIG. 8)
A dresser rotation drive motor 56 is fixed to the drive shaft, and a drive pulley 57 with its axis oriented in the up-down direction is attached to the output shaft of the drive motor so as to be integrally rotatable. On the other hand, at the tip of the horizontal slider 48, a rotary shaft (not shown) whose axis is oriented in the vertical direction is rotatably supported via a bearing 59. A driven pulley 60 having the same height as the drive pulley 57 is integrally rotatably attached to the upper end of the rotary shaft.
An endless belt 61 is stretched between the driven pulley 60 and the drive pulley 57.

Further, a dresser 15 is integrally rotatably attached to a lower end portion of the rotary shaft which projects from a bearing 59, and a high hardness dressing material such as diamond attached to a lower end surface of the dresser 15 is attached to a grinding surface of the wheel 13. On the other hand, it can be contacted from above. Then, when the dresser rotation drive motor 56 is driven, the rotational force of the drive pulley 57,
It is transmitted to the rotary shaft via the belt 61 and the driven pulley 60, and the dresser 15 is rotationally driven with the lower surface of the dressing member kept horizontal. The rotational driving of the dresser 15 can be performed simultaneously with the movement of the wheel 13 in the axial direction, or independently of this.

<Drive Mechanism 62> The drive mechanism 62 drives the wheel displacement mechanism 14 and the dresser displacement mechanism 16 up and down, and includes a lift drive motor (not shown), a wheel-side transmission mechanism 63, Dresser side transmission mechanism 6
4 and a clutch mechanism 65.

First, the wheel side transmission mechanism will be described. A bearing 66 for supporting the wheel-side male screw rod 21 is attached to the bracket 10 to which the lifting guide 17 is fixed, and a gear box 67 is integrally formed with the bearing 66 so as to project downward. ing. In the gear box 67, a worm wheel (not shown) fixed to the lower end of the wheel-side male screw rod 21 and a worm (not shown) are engaged.

A driven shaft 68 is integrally rotatably fixed to the worm. The driven shaft 68 projects leftward (leftward in FIG. 11) from the gear box 67, and a sprocket 69 is fixed to the projecting end thereof. Further, the base 1 is rotatably supported by the bearings 71, 71 on a drive shaft 70 that is laterally offset in parallel with the driven shaft 68 and extends leftward from the driven shaft 68. . A sprocket 72 having the same pitch diameter as the sprocket 69 of the driven shaft 68 is fixed to the right end of the drive shaft 70, and a chain 73 is stretched between the two sprockets 69, 72. Therefore, the drive shaft 70 and the driven shaft 68 rotate at the same speed (by the same angle). Further, at a position near the left end of the drive shaft 70, a sprocket 73 for interlocking rotation with the drive rotor 96 on the wheel 13 side is fixed. Further, a handle 74 for performing a manual rotation operation is fixed to the left end of the drive shaft 70.

Next, the dresser-side transmission mechanism 64 will be described. Bracket 1 to which lifting guide 17 is fixed
A bearing 75 for supporting the dresser-side male screw rod 45 is attached to 0, and a gear box 76 is integrally formed with the bearing 75 so as to project downward.
In the gear box 76, the male threaded rod 4 on the dresser side
Worm wheel fixed to the lower end of 5 (not shown)
And a worm (not shown) are engaged. A driven shaft 77 is integrally rotatably fixed to the worm. The driven shaft 77 extends leftward from the gear box 76 in parallel with the driven shaft 70 and the drive shaft 68 on the wheel 13 side. A left end portion of the driven shaft 77 penetrates a clutch mechanism 65, which will be described later, and is rotatably supported by the base 1 by a bearing 78. The left end of the driven shaft 77 is used for a manual rotation operation. The handle 79 of is fixed.
The dresser-side transmission mechanism 64 is configured as described above.

In both of the transmission mechanisms 63 and 64, comparing the reduction ratio due to the meshing of the worm wheel on the dresser 15 side with the reduction ratio due to the meshing of the worm wheel on the wheel 13 side, When the driven shafts 68 and 77 have the same rotation amount, the rotation amount of the dresser-side male screw rod 45 is set to be twice the rotation amount of the wheel-side male screw rod 21. Further, the thread pitches of the male threaded rod 21 on the wheel side and the male threaded rod 45 on the dresser side are the same.
Therefore, when both driven shafts 68 and 77 have the same amount of rotation, the amount of elevation of the dresser-side elevating slider 42 is twice that of the wheel-side elevating slider 18.

A clutch mechanism 65 is provided on the dresser-side transmission mechanism 64. As shown in FIG. 12, in the clutch mechanism 65, the driven rotor 81 made of a magnetic material, the spacer 82, the bearing 83, and the spacer 84 are fitted in the small diameter portion 80 of the driven shaft 77 in order from right to left. Then, these fitting members are fastened in the axial direction by the lock nut 86 screwed to the male screw portion 85 of the driven shaft 77, so that the driven rotor 81, the spacer 82, the bearing 83, and the spacer 84 are Driven shaft 77
It is possible to rotate together with.

The driven rotating body 81 has a brim-shaped portion 87 at its left end edge.
On the right side of the collar-shaped portion 87, the electromagnet 8 housed in a ring-shaped housing 88 made of a magnetic material.
9 is fixed to the base 1 via an arm 90 so as not to rotate. A bearing 91 is provided between the inner circumference of the electromagnet 89 and the outer circumference of the driven rotor 81.
The driven rotating body 81 can smoothly rotate with respect to the electromagnet 89.

The collar-shaped portion 87 has a driven shaft 77 to the left thereof.
A plurality of guide pins 92 projecting in parallel with the axis of are attached at appropriate intervals in the circumferential direction. The guide pin 92 is fitted with a guided hole 94 of an annular clutch plate 93 made of a magnetic material and arranged on the left side of the flange 87. As a result, the clutch plate 93 causes the driven rotor 8 to move.
It is supported so as to be integrally rotatable with respect to No. 1 and relatively movable in a direction parallel to the axis of the driven shaft 77. The clutch plate 93 is urged to the left (in the direction away from the driven rotor 81) by the compression coil spring 95 attached to the driven rotor 81.

The bearing 8 mounted on the driven shaft 77
A drive rotating body 96, which is composed of a plurality of members and has a flange portion 97 and a sprocket 98, is fitted to the member 3 so as to be rotatable relative to the driven shaft 77. The flange portion 97 of the drive rotor 96 is located so as to be adjacent to the clutch plate 93 in the axial direction.
A friction pad 99 that faces 3 is integrally rotatably fixed. Between the friction pad 99 and the clutch plate 93, the clutch plate 93 is constantly pressed by the friction pad 99 due to the urging of the compression coil spring 95, and a large frictional resistance is generated between the friction pad 99 and the clutch plate 93. 81 and the driving rotator 96 are in a state of being integrally rotatable. Also,
When the electromagnet 89 is excited by energization, the clutch plate 93 is pulled toward the driven rotor 81 side to separate from the friction pad 99, and thus the driven rotor 81 and the drive rotor 96 can rotate independently of each other. Becomes

Further, the sprocket 98 of the driving rotary member 96
Are arranged side by side at the same position in the axial direction with respect to the sprocket 73 fixed to the drive shaft 70 on the wheel 13 side, and both sprockets 73 and 98 have the same pitch diameter. Further, below these both sprockets 73 and 99, drive sprockets (not shown) are arranged so as to be lined up at the same position in the axial direction with respect to these sprockets. It is fixed to the output shaft of a motor (not shown). A chain 100 is stretched between these three sprockets, and when a lifting drive motor is driven, the sprockets 73 of the driven shaft 70 are driven.
And the sprocket 98 of the driving rotor 96 rotate in the same direction at the same speed (by the same angle).

A procedure for setting the height of the wheel 13 and the height of the dresser 15 according to the thickness of the work in the drive mechanism 62 having the above structure will be described. At this time, the drive of the lifting drive motor is stopped and the sprocket is allowed to rotate freely, thereby cutting off the transmission of the rotational force from the lifting drive motor to the wheel 13 side and the dresser 15 side, and the clutch mechanism 65. The electromagnet 89 is energized to interrupt the transmission of the rotational force from the driving rotary body 96 on the dresser 15 side to the driven rotary body 81, so that the wheel-side male screw rod 21 and the dresser-side male screw rod 45 are independent of each other. Be ready to rotate.

In this state, the handle 7 on the wheel 13 side
When 4 is rotated, its drive shaft 70, chain 73,
The wheel-side male screw rod 21 is rotated through the driven shaft 68 and the worm and the worm wheel in the gear box 67, and the wheel-side elevating slider 18 is moved up and down. As a result, the height of the wheel 13 is adjusted so that the grinding surface properly contacts the upper surface of the work.

When the drive shaft 70 on the wheel 13 side rotates, the sprockets 73, 98 and the chain 100 are rotated.
The drive rotating body 96 on the dresser 15 side also rotates in conjunction with the drive rotating body 9 via the clutch mechanism 65.
Since the transmission of the rotational force from 6 to the driven rotary body 81 is cut off, the dresser-side male screw rod 45 does not rotate.

After the height of the wheel 13 is adjusted, the height of the dresser 15 is adjusted. When the handle 79 on the dresser 15 side is rotated, the dresser-side male screw rod 45 is rotated via the driven shaft 77 and the worm and the worm wheel in the gear box 76, and the dresser-side lifting slider 42 is moved up and down. As a result, the height of the dresser 15 is adjusted so that the dressing surface of the dresser 15 is the wheel 13
Make proper contact with the grinding surface.

When the driven shaft 77 on the dresser 15 side is rotated, the driven rotary body 81 of the clutch mechanism 65 also moves integrally, but the rotational force is transmitted between the driven rotary body 81 and the drive rotary body 96. Is cut off. Therefore,
The drive rotor 96 connected to the drive shaft 70 on the wheel 13 side by the chain 100 does not rotate, and the wheel 13 whose height has been adjusted does not move up and down by operating the handle on the dresser 15 side.

In this way, the wheel 13 and the dresser 1
After adjusting the height of 5, the electromagnet 89 of the clutch mechanism 65
To the driven rotor 81 from the drive rotor 96.
Allows the transmission of rotational force to. This allows the wheel 13 side and the dresser 1 to be driven when the lifting drive motor is driven.
Both driven shafts 68 and 77 on the fifth side rotate in the same direction by the same amount of rotation.

<Elevating position detecting means for the wheel 13 and the dresser 15> In this embodiment, the wheel 13 and the dresser 15 are arranged.
Means are provided for detecting the up and down position of the. In FIG. 3, a lower limit position detection proximity switch 102 is provided at the lower end position on the left outer surface of the elevating guide 17, and an origin position detection proximity switch 10 is provided at a position approximately at an intermediate height.
3 is at the position immediately above the origin position detecting proximity switch 103, and the wheel side upper limit position detecting proximity switch 1 is provided.
04, and a dresser-side upper limit position detection proximity switch 105 is provided at the upper end position.

On the other hand, on the outer left side surface of the wheel side lift slider 18, the wheel side lower limit position detection proximity switch 10 is provided.
A lower limit detection dock 106 disposed above 2 and an upper limit detection dock 107 disposed below the wheel side upper limit position detection proximity switch 104 are attached. When the wheel side elevating slider 18 moves up and down to reach the lower limit of the ascending and descending range, and when the upper limit of the same range is reached, the lower limit position detection proximity switch 102 or the upper limit position detection detecting the approach of the docks 106 and 107 is detected. The drive of the lifting drive motor is stopped based on the detection signal from the vehicle proximity switch 104, and the transmission of the rotational force to the wheel side male screw rod 21 and the dresser side male screw rod 45 is cut off.

On the outer left side surface of the dresser-side lifting slider 42, the dresser-side upper limit position detection proximity switch 10 is provided.
An upper limit detection dock 108 arranged below 5 is attached. When the dresser-side elevating slider 42 rises and reaches the upper limit of the ascending / descending allowable range, based on a detection signal from the dresser-side upper limit position detection proximity switch 105 that detects the approach of the upper limit detection dock 108, the clutch mechanism 65 is activated. Electricity is applied to the electromagnet 89, so that
Only the transmission of the rotational force from the lifting drive motor to the dresser side male screw rod 45 is blocked.

Further, an approach prevention proximity switch 109 is attached to the lower end of the dresser-side elevation slider 42, while the wheel-side elevation slider 18 has a slider proximity detection corresponding to the slider proximity detection proximity switch 109. Dock 110 is attached. Lift sliders 1 on both the wheel 13 side and the dresser 15 side
8 and 42 are fitted to the same elevating guide 17, but when both elevating sliders 18 and 42 come close to each other, the slider approach detecting proximity switch 109 and the slider approach detecting dock 110 approach each other. Then, the proximity switch 109 performs detection.

Then, when detection is made by the slider approach detection proximity switch 109 in a state in which both the wheel side elevation slider 18 and the dresser side elevation slider 42 are descending, the electromagnet 89 of the clutch mechanism 65 is energized and the dresser is energized. Transmission of the rotational force to the side male screw rod 45 is cut off. Since the amount of elevation of the dresser-side elevating slider 42 at this time is twice that of the wheel-side elevating slider 18, as will be described later, if the descent of the dresser-side elevating slider 42 is stopped, both elevating sliders 18 and 42 collide. Is avoided. In this case, in addition to energizing the clutch mechanism 65, driving of the lifting drive motor may be stopped.

When the worn wheel 13 is replaced, the lifting drive motor is driven to raise both the wheel 13 and the dresser 15. As described above, the amount of rise of the dresser 15 is larger than that of the wheel 13. Since it is doubled, the dresser 15 may reach the upper limit position of the ascending / descending allowable range before the wheel 13. In this case, the transmission of the rotational force to the dresser 15 side is blocked by energizing the electromagnet 89 of the clutch mechanism 65, so that only the wheel 13 is raised. As a result, the wheel 13 has a sufficient space between it and the belt conveyor 2, while avoiding an unnecessarily large space between the wheel 13 and the dresser 15.

Further, for example, the wheel side lifting slider 1
If both lift sliders 18 and 42 are lowered while the wheel 13 is removed from the wheel 8, the dresser-side lift slider 42 may catch up with the wheel-side lift slider 18 and collide. 1
When the proximity switch 109 for detecting the slider approach detects that the 8 and 42 approach each other, the electromagnet 89 is energized and the descent of the dresser 15 is stopped. Therefore, both lift sliders 18 and 42 are prevented from colliding.

<Wheel Peripheral Velocity Consistency Means> In this embodiment, means is provided for stabilizing the circumferential speed of the wheel 13 when the diameter of the wheel 13 becomes small due to abrasion of the grinding surface. There is. As shown in FIG. 17, this means includes a variable speed motor drive means 120 for adjusting the rotation speed of the wheel drive motor 39, and a wheel 1.
Wheel diameter detection means 121 for detecting the diameter of 3;
Constant speed increasing means 1 for controlling the variable speed motor driving means 120
22 and 22. The variable speed motor drive means 120 is composed of an inverter circuit, and the wheel drive motor 39 is rotationally driven at a rotation speed proportional to the frequency of the alternating current flowing through this inverter circuit.

As shown in FIG. 17, the wheel diameter detecting means 121 includes a polishing number counting means 123, a polishing number setting means 124, a wheel initial diameter dimension detecting means 125, a wheel diameter reduction amount calculating circuit 126, and a wheel. And a diameter calculation circuit 127. The polishing number counting means 124 comprises the proximity switch 8 provided on the belt conveyor 2, and the count value (Gn) from the polishing number counting means 124 is input to the wheel diameter reduction amount calculation circuit 126. The polishing number setting means 123 sets a predetermined polishing number (Gn) by a digital switch provided on the operation panel 11, and the set value in this polishing number setting means 123 is set in the wheel diameter reduction amount calculation circuit 126. To be done. In this wheel diameter decrease amount calculation circuit 126, a value obtained by multiplying the number of count values (Gn) by a predetermined constant (k) on condition that the count value has reached a set value is a wheel diameter decrease amount (Dn). ) And outputs the calculated diameter reduction value (Dn) to the wheel diameter calculation circuit 127.

In the wheel diameter calculation circuit 127, the value (Ro) of the wheel initial diameter dimension is directly calculated as the wheel diameter when starting the first operation after newly replacing the wheel 13. Further, the diameter reduction value (Dn) from the wheel diameter reduction amount calculation circuit 126 is the wheel diameter calculation circuit 1
After being input to 27, each time the diameter reduction value (Dn) is input, a value obtained by subtracting the diameter reduction value (Dn) from the value of the wheel diameter (R (n-1)) calculated last time is calculated. It is calculated as a new wheel diameter (Rn).

The constant peripheral speed increasing means 122 is based on the value of the wheel diameter (Rn) calculated by the wheel diameter calculating means 127, and is based on the following equation (1).
The output frequency f of the 20 inverter circuits is controlled. f = k1 / Rn (k1 is a constant) (1) FIG. 15 is a graph showing the relationship between the wheel diameter (Rn) and the frequency (f). Since the wheel drive motor 39 is rotationally driven at a rotational speed proportional to the value of the frequency (f), the relationship between the rotational speed (N) of the wheel 13 per unit time and the frequency (f) at this time. Is expressed by the following equation (2). N = k2f (k2 is a constant) = k1k2 / Rn ... (2) That is, in the present embodiment, the rotation speed (Rn) is set with respect to the wheel diameter value (Rn). N) is controlled so as to change in inverse proportion. By the way, the relationship between the rotational speed (N) and the peripheral speed (V) of the wheel 13 is represented by the following expression (3). V = 2πRn · N (3) Substituting the above equation (2) into the above equation gives V = 2πRn · k1 · k2 / Rn = 2πk1 · k2. It is clear that the peripheral velocity of is constant.

Further, the wheel initial diameter dimension detecting means 125
As shown in FIG. 16, it comprises a reference distance detecting means 128, a displacement amount detecting means 129 and a wheel initial diameter calculating circuit 130. First, the reference distance detecting means 128 will be described. Wheel side upper limit detection proximity switch 104
An origin position detection proximity switch 103 is provided immediately below the position of the origin position detection proximity switch 103.
3 detects the approach of the upper limit position detection dock 107 provided on the wheel side lift slider 18, and the detection signal from the origin position detection proximity switch 103 stops the driving of the wheel lift drive motor. The operation flow at this time will be described with reference to FIG. 18. When a switch for returning to the origin (not shown) is turned on in the operation panel 11, the lifting drive motor is activated in step 1 and the wheel 13 is raised. Starts and waits for output of a detection signal from the origin position detection proximity switch 103 in step 2, and when the detection signal is output, driving of the lifting drive motor is stopped in step 3 and lifting of the wheel 13 is stopped. .

The height from the upper surface of the belt conveyor (processing table) 2 to the axis P of the wheel 13 in the state where the origin position detection proximity switch 103 is detected.
(X) is predetermined (see FIG. 14). A test piece 131 whose thickness (Z) has been measured in advance is placed on the belt conveyor 2.
The distance (X) from the belt conveyor 2 to the origin O and the thickness (Z) of the test piece 131 are the wheel initial diameter calculation circuit 13
A value obtained by subtracting the thickness dimension (Z) from the distance (X) is calculated as the reference distance.

The displacement amount detecting means 129 is an encoder 101 for detecting the amount of rotation of the wheel side male screw rod 21 described above.
And a displacement amount calculation circuit 133 for calculating the displacement amount of the wheel 13 based on the pulse signal from the encoder 101.
Composed of and. From the state where the wheel 13 is positioned with the axis P at the origin O, the grinding surface at the lower end of the outer circumference is tested.
Encoder 101 when descending until it abuts 31
Based on the pulse signal from, the displacement amount calculation circuit 133 calculates the descending amount (Y) or (y) of the wheel 13,
This calculated value is output to the wheel initial diameter calculation circuit 130.

In the wheel initial diameter calculation circuit 130, from the reference distance obtained by subtracting the thickness dimension (Z) of the test piece 131 from the distance (X) from the origin O to the belt conveyor 2, the origin O of the wheel 13 is further calculated. The value obtained by subtracting the displacement amount (Y) from the contact with the test piece 131 is calculated, and this is the initial diameter dimension (Ro) of the wheel 13 as shown in the following equation (4). Ro = (X−Z) −Y The flow of the wheel initial diameter detection operation described above will be described with reference to FIG. 19. When a switch (not shown) for starting wheel initial diameter detection is turned on in the operation panel 11. ,
In step 11, the test piece 131 is placed on the operation panel 11.
Wait until the thickness dimension (Z) is set, and when this thickness dimension is set, the value is read in step 12. Then, in step 13, the control panel 11 waits until the descending amount of the wheel 13 is set, and when this descending amount is set, the value is read in step 14. Then, in step 15, the wheel initial diameter calculation circuit 1
The initial wheel diameter (Ro) is calculated at 30 and the value of the initial wheel diameter is stored in a memory (not shown) at step 16. The stored value of the wheel initial diameter dimension is used in the above-mentioned means for keeping the circumferential speed of the wheel 13 constant and in the means for adjusting the gap between the wheel 13 and the belt conveyor 2 described later.

<Gap Adjusting Means Between Wheel 13 and Belt Conveyor 2> In this embodiment, when the diameter of the wheel 13 becomes small due to abrasion of the grinding surface, the wheel 13 is brought into proper contact with the work. Means are provided for maintaining the condition. As shown in FIG. 17, this means is composed of the wheel diameter detecting means 121, the gap adjusting mechanism 135, and the constant gap forming means 136.

The gap adjusting mechanism 135 includes a wheel-side lifting slider 18 on which the wheel 13 described above is supported.
It is composed of a lifting drive motor (not shown) for lifting and lowering.
The constant gap forming means 136 is composed of an encoder 101 that detects the amount of rotation of the wheel side male screw rod 21, and a control circuit 137 that controls the drive of the lifting drive motor. In the control circuit 137, the value (Dn) of the wheel diameter reduction amount calculated by the wheel diameter reduction amount calculation circuit 126.
And the pulse signal from the encoder 101, the rotation amount of the lifting drive motor is controlled. As a result, the wheel 13 descends by the same distance as the wheel diameter reduction amount (Dn).

Next, the flow of the polishing operation by the polishing machine of this embodiment will be described with reference to FIG. Here, it is assumed that the height of the wheel 13 is adjusted in advance, the initial diameter dimension (Ro) of the wheel 13 is read into the memory, and the number of polishing pieces is set on the operation panel 11. When a switch (not shown) for starting the operation is operated on the operation panel 11 from this state, the wheel initial diameter dimension (Ro) stored in the memory is read in step 21, and step 22
At (3), the constant peripheral speed conversion means 122 calculates the frequency (f) of the current passed through the inverter circuit of the variable speed motor drive means 120, and in step 23, the drive of the wheel rotation drive motor 39 is started. Along with this, the wheel swing motor 32, the dresser horizontal drive motor 53, and the dresser rotation drive motor 56 are activated.

Next, in step 24, the conveyance of the work by the belt conveyor 2 is started, and the number of conveyances of the work, that is, the number of polishing is counted by the polishing number counting means 124 (proximity switch 8). In step 25, the process waits until the number of counted polishing reaches the preset polishing number set on the operation panel 11.

During this time, the work is polished by the wheel 13. At this time, the wheel 13 reciprocates in the axial direction of the wheel 13 to come into contact with the work over a wide area of the grinding surface, thereby preventing uneven wear of the grinding surface. In addition, dressing by the dresser 15 is applied to the grinding surface of the wheel, which is clogged or crushed by polishing and whose abrasive grains are not sharp. At this time, the dresser 15 reciprocates in the axial direction over a region that covers the entire width of the wheel 13, while rotating on its axis about the vertical axis. This allows
The sharpening on the grinding surface is performed uniformly over the entire width of the wheel 13.

When the number counted by the polishing number counting means 124 reaches the set number, the conveyance of the work is stopped in step 26, and the wheel diameter reduction amount Dn is calculated in step 27. Then, in step 28, the lifting drive motor is started, the wheel 13 is lowered by the reduction amount Dn of its diameter, and the dresser 15 is also lowered. While the wheel 13 and the dresser 15 are descending, in step 29, the descending amount of the wheel 13 is reduced by the wheel diameter decrease value Dn based on the pulse signal from the encoder 101.
When the descending amount of the wheel 13 reaches the decreasing amount of the wheel diameter, the ascending / descending motor is stopped in step 30, and the descending of the wheel 13 and the dresser 15 is stopped.

When the wheel 13 and the dresser 15 are lowered, the lower end position of the wheel 13 has the same size as the wear amount on the grinding surface, whereas the lower end position of the wheel 13 lowers the wear amount on the grinding surface. Therefore, the upper end position of the wheel, that is, the contact position with the dresser is lowered by an amount twice the lowering amount of the wheel. However, the reduction ratio due to the engagement of the worm and the worm wheel in the gearbox is 1: 2.
Since the descending amount of the dresser 15 is twice the descending amount of the wheel 13,
And when the dresser 15 stops descending, the dresser 1
5 is in a state of properly contacting the upper end of the wheel 13.

Then, in step 31, a new wheel diameter (Rn) is detected based on the wheel diameter initial size (Ro) and the wheel diameter reduction value (Dn).
Based on (Rn), return to step 22 and select the wheel diameter
A new inverter frequency (f) is calculated according to (Rn). Hereinafter, by repeating the above-described operation, the height of the wheel 13 and the dresser 15 and the wheel peripheral speed are adjusted, and the work is polished intermittently.

As described above, according to this embodiment,
As the wheel diameter decreases, the rotation speed of the wheel 13 increases, so that the peripheral speed of the wheel 13 is kept constant with high accuracy. As a result, it is possible to uniformly and satisfactorily polish all the works.
Further, since the wheel 13 is lowered as the diameter of the wheel is decreased, the contact state of the grinding surface with the work is properly maintained. Therefore, the grinding of the work can be performed uniformly and satisfactorily. You can do it.

[Brief description of drawings]

FIG. 1 is a left side view showing an entire embodiment of the present invention.

FIG. 2 is a front view

[Figure 3] Left side view

FIG. 4 is a partially enlarged plan view.

FIG. 5 is a partially enlarged front view.

[Figure 6] Left side view

FIG. 7 is a partially enlarged plan view showing a horizontal drive mechanism of a dresser.

FIG. 8 is a partially enlarged front view showing a horizontal drive mechanism of the dresser.

FIG. 9 is an enlarged left side view of a portion showing a contact portion between the dresser and the wheel.

FIG. 10 is a partially enlarged plan view showing a horizontal drive mechanism of a dresser.

FIG. 11 is a partially enlarged plan view showing a lifting drive mechanism for a wheel and a dresser.

FIG. 12 is a partially cutaway enlarged plan view of the clutch mechanism.

FIG. 13 is an enlarged left side view showing work overlapping prevention means.

FIG. 14 is an explanatory view showing an operation of detecting an initial diameter dimension of a wheel.

FIG. 15 is a graph showing a relationship between a change in wheel diameter dimension and a corresponding change in frequency of an inverter circuit.

FIG. 16 is a block diagram showing a configuration of a wheel diameter dimension detecting means.

FIG. 17 is a block diagram showing a configuration of means for keeping the peripheral speed of the wheel constant and means for adjusting the gap between the wheel and the work.

FIG. 18 is a flowchart showing the operation of returning the wheel to the original position when detecting the initial wheel diameter dimension.

FIG. 19 is a flowchart showing the operation of detecting the initial wheel diameter dimension.

FIG. 20 is a flowchart showing an operation of polishing a work by a wheel, an operation of making a circumferential speed of the wheel constant, and an operation of adjusting a gap between the wheel and the work.

[Explanation of symbols]

 13 ... Wheel 39 ... Wheel driving motor 120 ... Variable speed motor driving means 121 ... Wheel diameter detecting means 122 ... Constant speed increasing means 124 ... Polishing number counting means 128 ... Reference distance detecting means 129 ... Displacement amount detecting means 135 ... Gap Adjusting mechanism 136 ... Constant gap forming means

Claims (4)

[Claims] 1. A wheel polishing machine, wherein a wheel having an outer peripheral surface as an abrasive surface is rotated by a motor and brought into contact with the workpiece to polish the workpiece. The motor for driving the wheel can be driven so that the rotation speed can be adjusted. Variable speed motor driving means, wheel diameter detecting means for detecting the diameter dimension of the wheel, and the rotation speed of the motor inversely proportional to the diameter dimension of the wheel detected by the wheel diameter detecting means. A wheel-type polishing machine, comprising: a constant peripheral speed increasing means for controlling a variable speed motor driving means. 2. A wheel in which an outer circumference is a grinding surface is rotationally driven by a motor, and the work is abraded by bringing the wheel into contact with a work on a machining table. A gap adjusting mechanism for adjusting a gap between the processing table, a wheel diameter detecting means for detecting a diameter dimension of the wheel, and the gap adjusting mechanism according to the diameter dimension of the wheel detected by the wheel diameter detecting means. A wheel-type polishing machine, comprising: a constant gap forming means for adjusting the gap by driving. 3. The wheel diameter detecting means comprises a polishing number counting means for counting the polishing number of the work, and a value obtained by multiplying the polishing number of the work counted by the polishing number counting means by a constant is used as an initial value of the wheel. The wheel-type polishing machine according to claim 1 or 2, wherein the wheel-type polishing machine is configured to detect the diameter of the wheel by subtracting it from the diameter. 4. A reference distance detecting means for detecting a distance from an origin set on a displacement path of a wheel in a contacting / separating direction to a workpiece during a polishing operation to a measurement reference surface provided on the displacement path, and the wheel. Is provided with a displacement amount detecting means for detecting an amount of displacement from a position where its axis coincides with the origin to a position where the outer peripheral surface is brought into contact with the measurement reference surface, and the distance detected by the reference distance detecting means. The initial diameter dimension of the wheel is detected by setting the dimension obtained by subtracting the displacement amount detected by the displacement amount detection means from the above as the radius dimension of the wheel. Wheel type polishing machine.