JPH0743007B2 - Automatic balance device for eccentric rotation device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Purpose of the Invention (1) Field of Industrial Application The present invention is directed to a cylindrical revolution spindle supported on a fixed frame body so as to be rotatable about its axis and parallel to the revolution spindle. A cylindrical housing having a different axis and arranged in the revolution spindle allows eccentricity from a concentric position coaxial with the revolution spindle axis and allows the revolution spindle to swing about a swing axis parallel to the axis. The present invention relates to an automatic balance device for an eccentric rotation device, which is movably supported and in which a rotation spindle coaxially arranged in the housing is supported so as to be rotatable about an axis.

(2) Conventional Technology This eccentric rotation device can change the trajectory of the rotation spindle by changing the amount of eccentricity of the housing with respect to the revolution spindle. The cutting diameter can be easily changed by attaching a cutting tool to the rotation spindle. The present applicant has proposed a rotation processing device that can be used.

(3) Problems to be Solved by the Invention However, when the housing and the rotating spindle are eccentric with respect to the revolution spindle, uneven wear of the bearing occurs, rattling noise is generated, and machining accuracy is increased. Adversely affect.

The present invention has been made in view of the above circumstances, and provides an automatic balance device for an eccentric rotation device that automatically performs weight distribution corresponding to the eccentricity of the housing and the rotation spindle to solve the above problems. The purpose is to provide.

B. Configuration of the Invention (1) Means for Solving Problems According to the present invention, a support arm projecting from the revolution spindle on the side opposite to the swing axis with respect to the axis of the revolution spindle surrounds the revolution spindle. And a second diameter of the revolution spindle which is connected to a balance weight formed in an annular shape via a shaft parallel to the swing shaft and is orthogonal to a first diameter line of the revolution spindle passing through the axis of the swing shaft. An intermediate portion of a link mechanism provided between the housing and the balance weight is linearly connected to the revolution spindle via a pin having an axis parallel to the swing axis, and the link mechanism is connected to the revolution spindle of the housing. To move the balance weight closer to or away from the pin on the second diameter line according to the proximity or separation of the housing from the pin due to the eccentric operation. Is configured as possible.

(2) Action When the housing and the rotation spindle are eccentric with respect to the revolution spindle, the balance weight is rotated in the direction opposite to the eccentric direction about the axis of the support arm by the action of the link mechanism. The weight distribution is symmetrical with respect to the axis of the revolution spindle.

(2) Example Hereinafter, one example in which the present invention is applied to a rotary processing apparatus will be described with reference to the drawings. First, in FIG. 1, FIG. 2 and FIG. 3, the rotary processing apparatus is fixed. Frame 1, revolving spindle 2, housing 3, rotating spindle 4, cutter 5 as a cutting tool, a pair of swing arms 6, a first pulley 7, a pair of second pulleys 8, and a second
A pair of links 9 connecting between the pulley 8 and the swing arm 6, a rotation drive motor 11 connected to the rotation spindle 4 via a universal joint 10, and a first pulley 7 via a first transmission mechanism 12. Revolution drive motor 13 and first transmission mechanism
The second transmission mechanism 14 connected in the middle of 12 and the second pulley 8
A third transmission mechanism 15 connected to the second transmission mechanism 15, a differential gear mechanism 16 connected to the second and third transmission mechanisms 14 and 15, and a differential gear mechanism 1
6 and a stepping motor 17 connected thereto.

The frame body 1 is fixed on a base plate 18. The frame body 1 is provided with a revolving spindle 2 having a basically cylindrical shape, with both ends projecting laterally, with bearings 19 and 20 interposed therebetween. It is rotatably supported around a horizontal axis.

In the revolution spindle 2, a cylindrical housing 3 is arranged with its axes parallel to each other, and the housing 3 is eccentric in the revolution spindle 2. A rotation spindle 4 is rotatably supported on the housing 3 via a pair of bearings 21 and 22 and sealing members 23 and 24 about the same axis, and the tip of the rotation spindle 4 protruding from the housing 3 (first The cutter 5 is attached to the left end of the drawing. Further, one end of the universal joint 10 is connected to the rear end (right end in FIG. 1) of the rotation spindle 4 protruding from the housing 3. On the other hand, a rotation drive motor 11 having an output shaft 26 parallel to the rotation spindle 4 is fixed to a support frame 25 fixed on the base 18 at the rear of the frame 1 (on the right side in FIG. 1). A transmission shaft 27 rotatably supported by a support frame 25 below the rotation drive motor 11 and the output shaft 26 are connected via pulleys 28 and 29 and an endless belt 30. Moreover, the transmission shaft
27 is connected to the rotation spindle 4 via a universal joint 10. Therefore, according to the operation of the rotation drive motor 11, the rotation spindle 4 rotates about the axis, and the eccentricity of the housing 3, that is, the rotation spindle 4 in the revolution spindle 2 is also allowed by the universal joint 10.

Both swinging arms 6 are arranged at both ends of the housing 3, and one end of each swinging arm 6 is arranged parallel to the axis of the housing 3 on a swinging shaft 31 planted in the revolution spindle 2 and a bearing 32. Each is supported through. Therefore, each swing arm 6 is rotatable about an axis parallel to the axis of the rotation spindle 4, and one end of the swing arm 6 is supported by the revolution spindle 2.
Fixedly connected to.

The first pulley 7 is concentrically fixed to the rear end of the revolution spindle 2. On the other hand, the second pulley 8 is formed to have the same diameter as the first pulley 7, and the bearings 33 are provided at both ends of the revolution spindle 2.
It is installed via each. Therefore, the first pulley 7 and the pair of second pulleys 8 are relatively rotatable.

Each second pulley 8 is provided with a pin 34 in parallel with its axis, and the other end of each swing arm 6 is provided with a pin 35 in parallel with the pin 34. The link 9 connects the other end of the swing arm 6 and the second pulley 8 via the pins 34 and 35.

With such a configuration of the swing arm 6 and the link 9,
When the revolution spindle 2 and the second pulley 8 are displaced relative to each other, as shown in FIG. 2, from the concentric position where the axes of the housing 3 and the rotation spindle 4 coincide with the axis of the revolution spindle 2, as shown in FIG. As shown, the axes of the housing 3 and the rotation spindle 4 deviate from the axis of the revolution spindle 2, and the housing 3 and the rotation spindle 4 are eccentric in the revolution spindle 2.

At the top of the frame 1, the output shaft 36 parallel to the revolution spindle 2
The orbital drive motor 13 having is fixed. The output shaft 36 of the revolution drive motor 13 and the first pulley 7 form the first transmission mechanism 12
Are connected via.

The first transmission mechanism 12 includes a third pulley 37 that is rotatably supported by the frame 1 around an axis parallel to the first pulley 7, and a revolution drive pulley 38 that is fixed to the output shaft 36. An endless first toothed belt 39 wound around the first pulley 7, the third pulley 37 and the revolution driving pulley 38, and the first toothed belt between the revolution driving pulley 38 and the third pulley 37. 39 is also wound around a tension pulley 40 rotatably supported by the frame body 1.

The third pulley 37 is fixed to one end of a cylindrical first rotating shaft 41, and the rotating shaft 41 allows the third pulley 37 to project outward so that a pair of bearings 42 is provided. It is rotatably supported by the frame body 1 through.

The frame 1 has a second rotary shaft 43 parallel to the first rotary shaft 41.
Is rotatably supported by bearings 44 and 45, and the first gear 46 rotatable about the axis of the second rotating shaft 43.
And is fixed to the inner end of the first rotating shaft 41 and
With the second gear 47 that meshes with the gear 46, the second transmission mechanism 14
Is configured.

A fourth pulley 51 is fixed to both ends of a third rotary shaft 48 supported by the first rotary shaft 41 via a bearing 49 and supported by the frame 1 via a bearing 50. 4th pulley 51, each 4th pulley 51 and each 2nd pulley 8
A pair of endless second toothed belts 52 wound around, a third gear 53 rotatable around the axis of the second rotating shaft 43, and a third gear 53 fixed to an intermediate portion of the third rotating shaft 48. The third transmission mechanism 15 is configured by the fourth gear 54 meshing with the third gear 53.

The pair of fourth pulleys 51 are formed to have the same diameter as the third pulley 37. The fourth gear 54 is formed to have the same diameter as the second gear 47 and the same number of teeth. Furthermore, the third gear 53
Has a slightly larger number of teeth than the first gear 46, for example, the first gear
When the number of teeth of the gear 46 is 100, the number of teeth of the third gear 53 is 101.

The differential gear mechanism 16 is a conventionally known one and has a second rotary shaft.
An elliptical cam 55 fixed to 43, a pair of ball bearings 56 fitted to the outer circumference of the cam 55, and a thin metal elastic member having teeth on the outer circumference and fitted to the outer ring of the ball bearing 56. It comprises a ring 57 and first and second rings 58, 59 having internal teeth which mesh with the external teeth of the elastic ring 57. The metal elastic ring 57 has an elliptical shape when fitted to the ball bearing 56, and the first and second rings 58 and 59 mesh with the metal elastic ring 57 at two points on one diameter line thereof. Moreover, a metal elastic ring
The outer teeth of 57 and the inner teeth of the first ring 58 have the same number of teeth, and the number of inner teeth of the second ring 59 is set to be slightly larger. For example, when the number of inner teeth of the first ring 58 and the number of outer teeth of the metal elastic ring 57 is 200, the number of inner teeth of the second ring 59 is 202.

The differential gear mechanism 16 decelerates the power of the second rotary shaft 43 when the second rotary shaft 43 is rotationally operated, and reduces the power of the first and second rings 58,5.
9, the rotation speed of the second ring 59 is the first ring 58.
Slightly later than.

A first gear 46 having bearings 60 and 61 interposed between the first ring 58 and the second rotating shaft 43 and the cam 55 is fixedly mounted, and a second ring 59 includes the second rotating shaft 43 and the cam 55. Bearings between 62,6
The third gear 53 with 3 interposed is fixed. Therefore, the rotation of the second rotary shaft 43 causes the differential gear mechanism 16 and the second transmission mechanism 14 to rotate.
While being transmitted to the first pulley 7 via the first transmission mechanism 12 and transmitted to both the second pulleys 8 via the differential gear mechanism 16 and the third transmission mechanism 15, the first pulley 7, that is, the revolution. The angular displacement speed of the spindle 2 is slightly higher than the angular displacement speed of the second pulley 8. That is, in FIG. 2, when the second rotating shaft 43 rotates, the first and third gears 46 and 53 also rotate in the same direction, and the third pulley 37 is angularly displaced around the first rotating shaft 41. At the same time, the fourth pulley 51 is angularly displaced by a smaller angular displacement amount. In response to this, the first pulley 7 and the revolution spindle 2 are angularly displaced by an angular displacement amount α, and the second pulley 8 is angularly displaced by an angular displacement amount β smaller than the angular displacement amount α. Therefore, the revolution spindle 2
A relative angular displacement amount γ is generated between the second pulley 8 and the second pulley 8. The swing arm 6 is rotated by the link 9 in accordance with the relative angular displacement, and as shown in FIG. Is eccentric from the axis of the revolution spindle 2 by a displacement amount ε.

By the way, when the revolution spindle 2 rotates while the second rotating shaft 43 is stopped, power is transmitted from the second transmission mechanism 14 to the second pulley 8 via the differential gear mechanism 16 and the third transmission mechanism 15. However, the combination of the number of meshing teeth of the transmission mechanisms 14 and 15 and the differential gear mechanism 16 is set so that the revolution speeds of the revolution spindle 2 and the second pulley 8 at this time are the same.

The stepping motor 17 has an output shaft parallel to the second rotation shaft 43.
It has 64 and is fixed to the upper part of the frame 1. Moreover, the output shaft
An adjustment drive pulley 65 is fixedly installed on the frame 64, and the frame 1
The fifth pulley 66 fixed to the end of the second rotary shaft 43 protruding from the second drive shaft 65 and the adjustment drive pulley 65 have an endless third
The toothed belt 67 is wound around.

By the way, when the orbiting spindle 4 is rotated while the orbiting spindle 2 is being rotated in a state of being eccentric in the orbiting spindle 2, the bearings 19 and 20 are unevenly worn, rattling noise is generated, and machining accuracy is increased. An automatic balancing device 70 is arranged between the housing 3 and the revolution spindle 2 as it has a negative effect.

In FIG. 5, an automatic balancer 70 includes an annular balance weight 71 surrounding the revolution spindle 2, a link mechanism 72 connecting the housing 3, the revolution spindle 2 and the balance weight 71, the revolution spindle 2 and the balance weight. 71 and a supporting arm 73 that connects the 71 to each other.

The balance weight 71 is formed in the shape of a thick short cylinder surrounding the revolution spindle 2. Further, the support arm 73 passes through the axis line of the swing shaft 31 supporting the swing arm 6 when the housing 3 and the rotation spindle 4 are concentric with respect to the revolution spindle 2, and the first rotation spindle 2 of the revolution spindle 2.
On the diameter line C ₁ , the revolution spindle 2 is projected outward from the outer surface on the side opposite to the swing shaft 31 with respect to the axis of the revolution spindle 2, and the outer end of the support arm 73 is the revolution spindle. 2 is connected to the balance weight 71 via a shaft 74 having an axis parallel to 2.

The link mechanism 72 includes a support projection 75 provided on the housing 3 so as to project therefrom.
First connecting rod 77, one end of which is connected to the tip of the pin via a pin 76
An intermediate portion pivotally supported by the revolving spindle 2 via a pin 78 and a swing rod 80 having one end connected to the other end of the first connecting rod 77 via a pin 79; The second connecting rod 83 is connected to the other end of the swing rod 80 via the other end and is also connected to the balance weight 71 via the other end or the pin 82.

The pins 76, 78, 79, 81, 82 are parallel to the axis of the rotation spindle 4 and pivotally support the rocking rod 80 on the revolution spindle 2.
Is the second of the orbiting spindle 2 orthogonal to the first diameter line C ₁ .
It is arranged on the revolution spindle ₂ on the diameter line C ₂ . The swing rod 80 is formed in a substantially V shape, and the bent portion thereof has a pin 78.
It is pivotally supported by the revolution spindle 2 via.

The balance weight 71 and the revolution spindle 2 are provided with openings 84 and 85 for allowing the operation of the link mechanism 72. Further, the balance weight 71 allows the support arm 73 to rotate about the balance weight 71. An opening 86 is provided for this purpose.

In such an automatic balancer 70, as shown in FIG. 6, when the housing 3 and the rotation spindle 4 rotate around the swing shaft 31 and become eccentric from the revolution spindle 2, the link weight 72 causes the balance weight 71 to move to the second diameter. The balance weight 71 is pushed on the line C ₂ in the direction opposite to the eccentric direction, and the balance weight 71 rotates around the shaft 74 at the tip of the support arm 73. Therefore,
When the housing 3 and the rotation spindle 4 are eccentric with respect to the revolution spindle 2, the balance weight 71 is automatically eccentric in the direction opposite to the eccentric direction. As a result, the weight is distributed symmetrically with respect to the axis of the revolution spindle ₂ on the second diameter line C ₂ .

Next, the operation of this embodiment will be described. When the hole corresponding to the cutter 5 is machined, the rotation drive motor is in a concentric position where the axis of the revolution spindle 2 is aligned with the axis of the housing 3, that is, the rotation spindle 4. Only activate 11. Then, the rotation spindle 4 supported by the housing 3 rotates while keeping the axis line constant, and the cutter 5 drills holes.

Then, when processing a hole having a diameter larger than that of the cutter 5, the stepping motor 17 is operated for a predetermined time. Then, by the action of the differential gear mechanism 16 and the second and third transmission mechanisms 14 and 15, the revolution spindle 2 and the second pulley 8 are angularly displaced while being relatively angularly displaced,
Due to the functions of the link 9 and the swing arm 6, the housing 3
And the rotation spindle 4 rotates about the swing shaft 31 and deviates from the axis of the revolution spindle 2 to be eccentric.

In this state, with the stepping motor 17 stopped,
The rotation drive motor 11 and the revolution drive motor 13 are operated. Then, the rotation spiddle 4 rotates about its axis via the universal joint 10, and the revolution spindle 2 is driven to rotate about the axis by the revolution drive motor 13 via the first transmission mechanism 12. Moreover, the third pulley 8 also rotates at the same speed as the revolution spindle 2.

As a result, as shown in FIG. 7, the cut 5 revolves along a revolution orbit 87 determined by the eccentricity ε of the revolution spindle 4 from the revolution spindle 2 while rotating around its axis. Therefore, the hole 88 having a diameter larger than that of the cutter 5 can be processed.

When changing the machining diameter of the hole 88, the eccentricity amount ε, that is, the relative angular displacement amount γ between the revolution spindle 2 and the second pulley 8 may be changed, and the relative angular displacement amount γ and the operation time of the stepping motor 17 may be changed. If they are associated in advance, it is possible to cope with the change in the machining diameter very easily, and it becomes unnecessary to replace the cutter 5.

Even if the rotation spindle 4 is eccentric with respect to the revolution spindle 2, the weight is symmetrically distributed with respect to the axis of the revolution spindle 2 by the function of the automatic balancing device 70, which causes uneven wear and rattling of the bearings 19 and 20. Prevents the generation of sound,
The processing accuracy can be improved.

C. Effects of the Invention As described above, according to the present invention, the support arm projecting from the revolution spindle on the side opposite to the swing axis with respect to the axis of the revolution spindle is formed in an annular shape surrounding the revolution spindle. A balance weight connected to the revolving spindle through a shaft parallel to the oscillating shaft, and the revolving spindle on the second diameter line of the revolving spindle orthogonal to the first diametrical line of the revolving spindle passing through the axis of the oscillating shaft. An intermediate portion of a link mechanism provided between the housing and the balance weight is connected via a pin having an axis parallel to the swing axis,
The link mechanism includes a proximity of the housing to the pin due to an eccentric operation of the housing with respect to a revolution spindle,
Since the balance weight can be moved toward and away from the pin on the second diameter line according to the separation, when the housing and the spinning spindle are eccentric with respect to the revolution spindle, the balance weight is It rotates in the direction opposite to the eccentric direction, and as a whole, symmetrical weight distribution is automatically made with respect to the axis of the revolution spindle, preventing uneven wear of the bearing and rattling noise, and attaching a cutting tool to the rotation spindle. The processing accuracy at the time of processing can be improved.

[Brief description of drawings]

The drawings show an embodiment in which the present invention is applied to a rotary machining apparatus. FIG. 1 is a longitudinal sectional view of the entire development, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. Is III-III in Fig. 1
A line sectional view, FIG. 4 is a partial view of FIG. 2 showing a state where the rotation spindle is eccentric, FIG. 5 is a cross-sectional view taken along line VV of FIG. 1, and FIG. 6 is a state where the rotation spindle is eccentric. 5 is a cross-sectional view corresponding to FIG. 5, and FIG. 7 is an explanatory view showing the locus of the cutter. 1 ... frame, 2 ... revolution spindle, 3 ... housing, 4 ... spindle, 31 ... swing axis, 70 ... automatic balancer, 71 ... balance weight, 72 ... link mechanism, 73 …… Support arm, 74 …… axis, 78 …… pin, C ₁ …… first diameter line, C ₂ …… second diameter line

Claims (1)

[Claims] 1. A cylindrical revolution spindle (2) is rotatably supported on a fixed frame (1) so as to be freely rotatable about its axis, and has an axis parallel to the revolution spindle (2). A cylindrical housing (3) arranged in (2) enables eccentricity from a concentric position which is coaxial with the axis of the revolution spindle (2), and allows the revolution spindle (2) to swing shaft (parallel to the axis). 31) An eccentric rotation, which is rotatably supported around and a rotation spindle (4) coaxially arranged in the housing (3) is rotatably supported on the housing (3). Revolving spindle (2)
A balance weight (71) formed by a support arm (73) projecting from the revolving spindle (2) on the side opposite to the swing shaft (31) with respect to the axis of the revolving spindle (2) in an annular shape. ) Via a shaft (74) parallel to the swing shaft (31) and is orthogonal to the first diameter line (C ₁ ) of the revolution spindle (2) passing through the axis of the swing shaft (31). On the second diameter line (C ₂ ) of the revolution spindle (2), the revolution spindle (2) has an intermediate portion of a link mechanism (72) provided between the housing (3) and the balance weight (71). A pin (7 having an axis parallel to the swing axis (31)
8), and the link mechanism (72) responds to proximity and separation from the pin (78) of the housing (3) due to eccentric operation of the housing (3) with respect to the revolution spindle (2). An automatic balance device for an eccentric rotation device, characterized in that the balance weight (71) can be moved toward and away from the pin (71) on the second diameter line (C ₂ ).