JPH0650393A - Positional displacement controller - Google Patents

Abstract

PURPOSE: To simplify a structure by changing rotation speed of a main gear to change rotation load for a driven gear of a load device and changing an offset turn angle of a control drive shaft on the same shaft as the main gear under the conditions in which it is balanced with a balance spring. CONSTITUTION: A main gear 27 and a driven gear 35 rotate by the rotation of a motor 22, the rotation is transmitted to an large-diameter intermediate gear 25 integral with a small-diameter intermediate gear 26, and a load gear 41 of a load device 40 rotates. Two centrifugal forces act on mass members 44a, 44b by this rotation, friction occurs in a friction circular column 42 and friction rings 45a, 45b, and rotation load for the driven gear 35 is generated in the load device 40. A shaft base 33 turns with offsetting and a control drive shaft 30 turns with offsetting under the conditions in which rotation load for the driven gear 35 and a balance spring 34 are balanced due to the fluctuation of rotation speed of the main gear 27. In this way, a positional displacement controller is pulled or interlocked due to a turn amount of the control drive shaft 30 by changing rotation speed of the motor 22, thereby controlling the other controlled device.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a positional deviation control device applied to, for example, a direction control mechanism for toys and a speedometer.

[0002]

2. Description of the Related Art Conventionally, a position shift control device generally used for a computer printer uses a stepping motor to generate a position shift amount. In the position shift control by the stepping motor, a large number of coil members provided in the inside of the stepping motor cause a rotation of a specific angle in accordance with the external control pulse signal. The structure is complicated, the control circuit requires control that causes a large number of control pulses and time sequence, the necessary control mechanism is also complicated, the product price is high, and the position deviation control device capable of simple position deviation control is provided. Was required.

Further, for example, as a direction control device for a toy, there is known a device that uses a servo mechanism to control the amount of positional deviation, but this device usually applies an independent power mechanism. Supplying the necessary power to the servo mechanism,
Furthermore, the structure is such that the rotation shaft is pulled by the movement of the servo mechanism to obtain an appropriate change in the amount of positional deviation.

[0004]

The position shift control mechanism using the servo mechanism described above is not only large in size due to the complex structure of the power mechanism and the servo mechanism, but also requires high precision and complicated transmission. However, there is a problem in the structure and manufacturing of the servo mechanism, which makes maintenance difficult, and it is difficult to make a simple structure in the position displacement driving device using the servo mechanism. It has the same problem as the displacement control device.

The present invention has been made in view of the above problems of the prior art, and has a structure in which the control drive shaft is rotated in an offset direction due to a change in the rotation speed of the drive source, and the offset angle and the offset rotation amount are simple. It is an object of the present invention to provide a positional deviation control device that does not require a complicated control circuit and does not require high accuracy.

[0006]

According to another aspect of the present invention, there is provided a position shift control apparatus, wherein a main drive gear that rotates by the power of a drive source, a driven gear that meshes with the main drive gear, and both of these gears are rotatable. A supported headstock, a load device that changes the rotational load on the driven gear in accordance with a change in the rotation speed of the main gear, and a direction in which the headstock is rotated by the load of the load device. A balance drive spring biased in the opposite direction, and a control drive shaft provided on the headstock coaxially with the rotation shaft of the main drive gear, and by changing the rotation speed of the main drive gear, Under the condition that the rotational load on the driven gear of the load device is changed to balance with the elastic force of the balance spring, the control drive shaft on the headstock is offset on the same axis as the rotational shaft of the main drive gear. It is intended to be of.

According to a second aspect of the present invention, there is provided the positional shift control device according to the first aspect, wherein the load device for changing the rotational load of the driven gear transmits the power of the drive source to the driven gear via the intermediate gear. It is what is done.

According to a third aspect of the present invention, there is provided a positional deviation control device according to the second aspect, wherein the load device includes a load gear rotated by rotation of a driven gear and a centrifugal force mechanism provided in the load gear. It is composed by.

[0009]

In the position shift control device according to the first aspect, when driven by the power of the drive source of the main gear, the driven gear also rotates. By changing the rotational speed of the main drive gear, the rotational load on the driven gear of the load device is changed, and the headstock is rotated in a direction opposite to the biasing direction of the balance spring. Rotate until equilibrium with elasticity. Then, the control drive shaft on the headstock is turned on the same axis as the rotary shaft of the main drive gear, and the angle of the offset is an angle according to the rotational speed of the main drive gear.

In the position shift control device according to the second aspect, the power of the drive source is transmitted to the load device to the driven gear meshed with the driving gear via the intermediate gear.

In the position shift control device according to the third aspect, the load device is composed of a centrifugal force mechanism, and a large load change can be obtained for the driven gear with respect to a change in the rotational speed of the driving gear.

[0012]

EXAMPLE An example of the present invention will be described below. First, the principle of rotation of the present invention will be described prior to the description of specific embodiments of the present invention. As shown in FIG. 5, the main gear 1 and the driven gear 2 are mainly in mesh with each other, and the centers of the gears 1 and 2 are freely rotatable by the rotary shafts 1a and 2a to one headstock, for example, the link 3. Is supported by. When the driving gear 1 receives a driving force from an electric motor or the like and rotates clockwise, the driven gear 2 is rotated counterclockwise.

As shown in FIG. 6, when the driven gear 2 receives a rotational load F from another device in its rotation, that is, the rotational load F of the driven gear 2 is smaller than the torque of the main driving gear 1. When the driving gear 1 receives the rotational load F of the driven gear 2 under the condition that the driving gear 1 continuously rotates, a reaction force K that the rotation of the driven gear 2 receives the load F and is transmitted to the driving gear 1 is generated. . This reaction force K causes a biasing force in the driven gear 2 in the clockwise direction about the rotation shaft 1a of the driving gear 1, and the link 3 receives the biasing force of the driving gear 2 to cause the link 3 to rotate in the rotation shaft 1a of the driving gear 1. Center around.

Then, as shown in FIG. 7, the link 3
Is located near the driven gear 2 and has a balance spring 4
Of the balance spring 4 is fixed to the fixing point 5. Offset state of the link 3 by the balance spring 4 is continued until take equilibrium of offset and the elastic force of the balance spring 4, as shown in FIG. 8, the deviation force of the driven gear 2 by the rotational load F ₁ Is larger, the biasing force of the link 3 is larger.

Next, as shown in FIG. 9, a wind resistance load device 6 is provided in the device shown in FIG. 5 as a load device for the driven gear 2 to generate a rotational load F of the driven gear 2 by the rotation of the driven gear 2. It is provided. The wind resistance load device 6 has a load gear 7 that meshes with the driven gear 2. The load gear 7 meshes with the driven gear 2 on the link 3 and rotates on a straight line connecting the rotary shafts 1a, 2a. It is rotatably supported by the shaft 7a.

Further, as shown in FIGS. 9, 11 and 12, the load gear 7 of the wind resistance load device 6 is provided with wind resistance blades 8 symmetrically positioned on a straight line passing through the rotary shaft 7a. .
As the rotational speed of the driven gear 2 increases due to the wind resistance load device 6, as shown in FIG.
The rotational load F with respect to is increased, and the amount of offset rotation of the link 3 is increased.

As described above, the rotational speed of the driven gear 2 is changed by controlling the change of the rotational speed of the main driving gear 1, and the resistance load F of the wind resistance load device 6 is changed.
By utilizing the change in the rotation speed of the driven gear 2 and the change in the resistance load F, the amount of offset rotation of the link 3 can be controlled.

Then, the amount of one-sided rotation of the link 3 is
According to the relationship between the rotational load F of the wind resistance load device 6 and the offset amount of the link 3, the configuration that can change the rotational load F of the driven gear 2 and the elastic coefficient of the balance spring 4 determine the wind to the driven gear 2. The resistance load device 6 is
For example, the centrifugal loading device 10 shown in FIGS. 13 and 14 can be replaced.

The wind resistance load device 6 and the centrifugal load device 10 both have rotational speeds of the main gear 1 and the driven gear 2.
And the rotational speed of the driven gear 2 is faster, the load devices 6 and 10 are also rotated faster, and the rotational load F acting on the driven gear 2 is larger, but with the same change in rotational speed, the centrifugal load is increased. The device 10 has a larger load change than the wind resistance load device 6.

As shown in FIGS. 13 and 14, this centrifugal load device 10 is constituted by a friction column 12 fixed to the center of a load gear 11 and a centrifugal force mechanism 13.
It is composed of a pair of mass members 14a and 14b, friction rings 15a and 15b fitted to the friction cylinder, and connecting members 16a and 16b for connecting the mass members 14a and 14b to the friction rings 15a and 15b. The bodies 16a and 16b are prevented from rotating by stoppers 17a and 17b protruding from the load gear 11.

When the centrifugal load device 10 rotates, two centrifugal forces act on the respective mass members 14a and 14b to cause friction between the friction column 12 and the friction rings 15a and 15b, and the centrifugal load device. A rotational load F is generated on the driven gear 2 at 10, and this rotational load F is proportional to the rotational speed.

Next, the structure of an embodiment of the position shift control device of the present invention will be described with reference to FIG. The drive control unit 20 is provided in the main body 21 of the apparatus and is provided in the main body 21 of the apparatus. This electric motor 22 is driven by a single electric motor 22 that is a driving source.
One end of the rotary shaft 23 of the bearing is a bearing provided at the bottom of the device body 21.
The shaft 24 is rotatably supported by the shaft 24. One end of the rotary shaft 23 is projected from the bottom of the device main body 21 to supply necessary power to the driven device.

A large-diameter intermediate gear 25 and a small-diameter intermediate gear 26 that rotates integrally with the large-diameter intermediate gear 25 are rotatably provided at the other end of the rotary shaft 23 of the electric motor 22. There is. Further, a drive gear 27 is fixed to the other end of the rotary shaft 23.

Further, the rotary shaft is provided on the upper part of the apparatus main body 21.
A control drive shaft 30 is rotatably supported by a bearing 28 on the same axis as the control shaft 23, and an upper end of the control drive shaft 30 is projected from an upper portion of the apparatus main body 21.

A head 33 is mounted on the control drive shaft 30 so as to be positioned inside the apparatus main body 21, and an upper end of the rotary shaft 23 is rotatably fitted to a lower surface of the head 33. There is.
The other end of the balance spring 34, one end of which is fixed to the headstock 33, is connected to the apparatus main body 21. Also, this headstock
On the lower surface side of 33, the driving gear 27 and the small-diameter intermediate gear 26
A driven gear 35 meshing with and is rotatably provided on a shaft 36.

Further, a vertical fixed shaft 37 is provided in the device body 21, and a load device 40 is provided on the fixed shaft 37. The load device 40 is rotatably supported by the fixed shaft 37 and meshes with the large-diameter intermediate gear 25.
The load gear 41 includes a friction column 42 fixed to the center of the load gear 41 and a rotatable centrifugal force mechanism 43. The centrifugal force mechanism 43 includes two sets of mass members 44a, 44.
b and friction rings 45a and 45b fitted to the friction column 42
And the mass members 44a and 44b and the friction rings 45a and 45b.
It is composed of connecting bodies 46a and 46b for connecting with, and these connecting bodies 46a and 46b are stoppers 47a and 47 protruding from the load gear 41.
The rotation is blocked by b and.

Next, the operation of this embodiment will be described.

The driving gear 27 is rotated by the rotating shaft 23 that is rotated by the drive of the electric motor 22, and the driven gear 35 that meshes with the driving gear 27 is rotated. The rotational power of the driven gear 35 is the intermediate gear 26 of small diameter. It is transmitted to the large-diameter intermediate gear 25 that rotates integrally, and the rotation of the large-diameter intermediate gear 25 causes the load device 40 to rotate.
The load gear 41 of is rotated. By the rotation of the load gear 41, two centrifugal forces are applied to the respective mass members 44a and 44b to cause friction between the friction cylinder 12 and the friction rings 45a and 45b, and the centrifugal load device 40 receives a rotational load against the driven gear 35. F
And the rotational load F is proportional to the square of the rotational speed.

The headstock 33 corresponds to the link 3 in FIG. 11 and FIG. 12, the load device 40 becomes the rotational load F of the driven gear 35, and the main drive gear 27 by the rotation of the rotary shaft 23 of the electric motor 22.
Under the condition that the rotational load F on the driven gear 35 and the elastic force of the balance spring 34 are balanced due to the fluctuation of the rotational speed of the headstock 33, the headstock 33 rotates to one side, and the control drive shaft 30 having the same axis as the rotary shaft 23 of the electric motor 22. Is rotated to one side.

As described above, when the rotation speed of the motor 22 is controlled by changing the resistance value of the variable resistor to control the rotation speed of the driving gear 27, the head 33 rotates the driving gear 27. The controlled rotation of the control drive shaft 30 causes an offset rotation of a rotation amount according to the speed, and the rotation of the headstock 33 shifts the position of the headstock 33. To control.

Next, the construction of another embodiment of the positional deviation control device of the present invention will be explained with reference to FIGS.

The structure of this embodiment is the same as the structure of the embodiment shown in FIG. 1 except that the large-diameter intermediate gear 25 is used as the rotary plate 50.
The rotating plate 50 is configured to directly rotate the load device 51 that rotates about the rotating shaft 23. This load device 51
The centrifugal force mechanism 53 includes a friction ring 55 supported by a support arm 54 in the apparatus main body 21, mass members 56a, 56b and a mass member 56a, which are brought into centrifugal contact with the inner peripheral surface of the friction ring 55,
Support arm 57a, 57b for supporting 56b on the inner peripheral surface of said friction ring 55 so as to be freely contactable and separable, and said support arm
57a and 57b are formed in a substantially L shape, and support arms 57a
57b are projected from the lower surface of the rotary plate 50. The mass members 56a, 56b supported by the support arms 57a, 57b are held at symmetrical positions on a straight line passing through the rotary shaft 23.

Next, the operation of this embodiment will be described.

When the driving gear 27 is rotated by the driving of the electric motor 22, the driven gear 35 is rotated, and the rotational power of the driven gear 35 is transmitted to the rotary plate 50 which rotates integrally with the small-diameter intermediate gear 26,
The rotation of the rotating plate 50 causes the friction ring 55 of the load device 40 to rotate. By the rotation of the rotary plate 50, two centrifugal forces act on the respective mass members 56a, 56b, so that the mass members 56a, 5b
6b rubs against the friction ring 55 to generate friction, which causes the centrifugal load device 51 to generate a rotational load F on the driven gear 35,
Moreover, this rotation load F is proportional to the rotation speed.

Then, under the condition that the fluctuation of the rotational speed of the main driving gear 27 balances the rotational load F on the driven gear 35 and the elastic force of the balance spring 34, the headstock 33 pivots to one side, and the control drive shaft 30 shifts to one side. It is rotated.

This position displacement control device can change the traveling direction of a toy, for example, in an automobile toy by interlocking the rotation direction control device with an interlocking mechanism connected to the control drive shaft 30. Then, one end of the rotary shaft 23 of the electric motor 22 is connected to a wheel drive device of an automobile toy so that the toy can be run.

The positional deviation control device is not limited to toys, and various machines that do not require high precision,
It is generally applicable to instrument control and tachometers such as speedometers.

[0038]

According to the present invention, the control drive shaft is pivoted by the change of the rotational speed of the drive source, and the offset angle and the offset rotation amount can be obtained with a simple structure. It is not necessary, does not require high precision, and can be obtained at low cost.

[Brief description of drawings]

FIG. 1 is a cross-sectional plan view of a misalignment control device showing an embodiment of the present invention.

FIG. 2 is a cross-sectional plan view of a positional deviation control device showing another embodiment of the present invention.

FIG. 3 is a plan view of the same load device.

FIG. 4 is a front view of the same load device.

FIG. 5 is a diagram illustrating the principle of the positional deviation control device of the present invention.

FIG. 6 is an explanatory view of the principle of the one-sided rotation state in which a load is applied to the same.

FIG. 7 is an explanatory view of the principle in which a balance spring for maintaining the balance with the load is provided.

FIG. 8 is a principle explanatory diagram showing a state in which the elastic force of the balance spring and the load are kept in equilibrium.

FIG. 9 is an explanatory view of the principle in which the same load device is provided.

FIG. 10 is an explanatory view of the principle in the state where the load of the same load device and the elastic force of the balance spring are kept parallel to each other.

FIG. 11 is a plan view of the same load device.

FIG. 12 is a front view of the same.

FIG. 13 is a plan view of another load device of the above.

FIG. 14 is a front view of the same.

[Explanation of symbols]

 1 Driving gear 2 Driven gear 3 Shaft base 22 Drive source motor 23 Rotating shaft 25, 26 Intermediate gear 30 Control drive shaft 33 Shaft base 34 Balance spring 40, 51 Load device 43, 53 Centrifugal force mechanism

Claims (3)

[Claims] 1. A drive gear that rotates by the power of a drive source, a driven gear that meshes with the drive gear, a headstock that rotatably supports both gears, and a rotational load for the driven gear. A load device that changes according to a change in the rotation speed of a gear; a balance spring that urges the headstock in a direction opposite to a direction in which the headstock rotates one-sidedly by the load of the load device; The balance drive spring is provided with a control drive shaft provided coaxially with the rotation shaft of the main drive gear, and changing the rotational speed of the main drive gear to change the rotational load on the driven gear of the load device. The position deviation control device for changing the angle of one-sided rotation of the control drive shaft on the headstock on the same axis as the rotation shaft of the main drive gear under the condition of being balanced with the resilience. 2. The positional deviation control device according to claim 1, wherein the load device for changing the rotational load of the driven gear transmits the power of the drive source to the driven gear via the intermediate gear. 3. The positional deviation control device according to claim 2, wherein the load device is constituted by a load gear rotated by rotation of a driven gear and a centrifugal force mechanism provided on the load gear.