JP3269260B2 - Operating force adjustment device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an operating force adjusting device.

[0002]

2. Description of the Related Art FIG. 10 is a principle view showing a first conventional brake device, and a cylindrical member 1 driven from the outside of the device.
And a band-shaped member 27 fixed at one end and arranged so as to wind around the cylindrical member 1.

Now, by pulling an end (free end) of the band-like member 27 which is not fixed (a free end) in a downward direction in FIG. 10, the band-like member 27 is pressed against the peripheral surface of the cylindrical member 1, and A frictional force is generated by the contact between the mold member 1 and the band-shaped member 27, and acts as a braking torque.

FIG. 11 is a perspective view showing a second conventional brake device in which the braking torque is proportional to the rotation speed and the braking torque is variable. In this brake device, a circular plate member 29 connected to a rotating shaft 28 is arranged in a Newtonian fluid 2 sealed in a container 33, and when the rotating shaft 28 is rotated from outside the device, an adjustment provided in parallel with the rotating shaft 28 is performed. The Newtonian fluid 2 between the semi-circular plate member 31 and the circular plate member 29 of the shaft 32 is subjected to shear deformation, thereby generating a braking torque on the rotating shaft 28 in proportion to the rotation speed.

Further, the magnitude of the braking torque at a certain number of rotations is proportional to the area where the circular plate member 29 and the semicircular plate member 31 overlap when viewed from the rotation axis direction. Then, it can be adjusted by changing the area.

In this brake device, a braking torque is generated by a resistance force of the Newtonian fluid 2 in which a shearing force is generated in proportion to a shearing speed. Therefore, the braking torque acts so as to be proportional to a rotation speed. For this reason, FIG. 12 shows the torque-rotation speed characteristics together with a general prime mover. As can be seen from the comparison between the characteristics of FIG. 12 and the torque-rotation speed characteristics of the prime mover of the first conventional example shown in FIG. 13, compared with the first conventional example shown in FIG. The difference between the slopes of the graphs of FIG.

Therefore, the above configuration greatly improves the constant speed of the entire system without a speed detector or feedback means. Further, since the operating speed is the intersection of the braking torque-rotation speed characteristic of the brake device and the driving torque-rotation speed characteristic graph of the prime mover, the braking torque-rotation speed of the braking device is changed by changing the angle of the adjustment shaft 32. It is possible to operate at an arbitrary speed by changing the proportionality coefficient of the characteristic. That is, the brake device functions as speed control means.

[0008]

However, the first conventional example has the following problems because the braking force generation source is caused by friction between solids of the cylindrical member and the band-shaped member.

(1) Not suitable for constant speed rotation.

FIG. 13 shows the torque-rotational speed characteristics of the brake device of the first conventional example and a prime mover outside the device connected to the brake device. As shown in FIG.
In the brake device, since the braking torque is generated by the friction between the fixed members, a constant braking torque is generated regardless of the rotation speed.

On the other hand, a general prime mover such as a motor has a characteristic that the generated torque slightly decreases as the rotational speed increases due to internal loss.

A case where the brake device and the prime mover are connected will be considered. Now, the braking device and the prime mover when the rotating at a rotational speed V ₁ as shown in FIG. 13, deceleration will be towards the braking torque of the braking device is above the driving torque of the prime mover. On the other hand, when rotating at the rotation speed V _2, the drive torque exceeds the braking torque.

Therefore, when the brake device and the prime mover are connected to each other, the rotational speed of the prime mover is set to a rotational speed V _{0 at} which the driving torque of the prime mover and the braking torque of the brake device are balanced. At this time, as the difference in the inclination of the brake characteristics and motor characteristics shown in Figure 13 is large, restored from a certain rotational speed the torque for restoring the rotational speed V ₀ increases, even if disturbance is applied to the rotation speed V ₀ near Will be
It can be said that it is suitable for constant speed rotation.

However, in the brake device of the first conventional example, since the braking torque does not depend on the rotation speed in principle, the difference between the gradient of the brake characteristic and the inclination of the prime mover characteristic shown in FIG. In many cases, resilience to rotation is insufficient. Therefore, in a machine that is required to operate at a constant speed, it is generally practiced to change the torque-speed characteristic of the prime mover by electric feedback instead of the brake device of the first conventional example. However, expensive rotational speed detecting means and feedback means are required. In addition, since the magnitude of the feedback signal becomes small at low speed, the feedback signal is not accurately transmitted due to noise when the feedback means is electrical, and due to backlash when it is mechanical, and the constant speed is insufficient. Become.

In applications where a constant speed is required to be maintained by human operation, such as a zoom operation of a zoom lens, it is difficult to improve the torque-rotation speed characteristic of the operating force of the operator corresponding to the prime mover. This is equivalent to imposing a burden on the operator. For this reason, there is no other way to improve the operability other than the improvement of the constant speed by improving the characteristics of the brake device, and there is a demand for a brake device in which the braking torque increases as the rotation speed increases.

Further, in the above-described first conventional brake device using solid friction, stick-slip is likely to occur in low-speed operation, and the constant speed is significantly deteriorated.

(2) It is not suitable for an operation section requiring high operability and good operability.

An operation section such as a zoom operation section of a zoom lens for a television camera, which requires high operability and a good operation feeling, has not been realized with a variable operation force. In the operation section where the operating force is fixed, although the operability and operability are evaluated as excellent by the sensory test, the torque-rotation speed characteristics of the operating force are measured, and the torque increases in proportion to the rotation speed. are doing. From this, it is considered that the operation force needs to increase in proportion to the operation speed in order to realize high operability and good operation feeling. As explained in (1) above, it is considered that the constant speed of the system combining the operation unit having this characteristic and the human greatly affects the operability and the operational feeling. In the above conventional example, the operation force is variable, but the operation force is almost constant regardless of the operation speed, so that the operability and the operational feeling are not good. This was supported by the results of the sensory test.

(3) Abrasion of the member occurs Since a braking torque is generated by friction between the solids of the cylindrical member and the band-like member, wear occurs on both the shaft and the band-like member. For this reason, regular maintenance and replacement of parts are required.

The second conventional example has the following problems.

(4) Requires a sealing mechanism.

In the second conventional example, since the structure is such that a Newtonian fluid is sealed in a container, in order to prevent leakage of the Newtonian fluid, seal mechanisms 30, 34 are provided around the rotation axis and the adjustment axis.
Need. Since a general sealing mechanism has a structure in which a shaft is pressed into a flexible member, large solid friction is generated. Since the solid friction is the same as in the first conventional example, the braking torque does not depend on the rotation speed. Therefore, the characteristic that the braking torque of the brake body is proportional to the rotation speed is impaired, and it is difficult to reduce the braking torque by a certain amount or more. The small torque side of the adjustment width is limited. This corresponds to the fact that the braking torque when the number of revolutions is 0 is displayed relatively large as shown in FIG.

(5) The structure is complicated The structure of the second conventional example is more complicated than that of the first conventional example.
This leads to an increase in manufacturing costs. Further, when bubbles are generated in the Newtonian fluid, the braking torque is reduced. However, since the structure is complicated, it is difficult to prevent the generation of bubbles during assembly.

According to the present invention, the braking torque is increased in proportion to the rotation speed, and the proportion of the braking torque is changed.
It is an object of the present invention to realize an operating force adjusting device that can adjust the operating force by changing the braking torque at the same rotation speed.

[0025]

According to a first aspect of the present invention, there is provided an operating force adjusting apparatus comprising: a cylindrical member having a cylindrical surface coated with Newtonian fluid; a member in contact with the cylindrical surface; A spacer for changing a contact area of the member, and an operating force corresponding to the contact area is obtained by rotating the cylindrical member, and the operating force is changed by changing the contact area by the spacer. Is adjustable.

According to a second aspect of the present invention, there is provided an operating force adjusting device comprising: a cylindrical member having a cylindrical surface coated with Newtonian fluid;
A member that is in contact with the cylindrical surface, and a spacer for changing a contact area of the member with the cylindrical surface, and according to the contact area by rotating the spacer and the contacted member. It is characterized in that the operating force can be adjusted by obtaining the operating force and changing the contact area by the spacer.

According to the first and second aspects of the present invention, the position of the spacer is changed to change the contact area between the thin plate connected to the operating ring and the Newtonian fluid, thereby making the braking force variable. It can be operated with a light operating force when quick operation is intended, and can be operated with an appropriate operating force when intended to operate slowly and at a constant speed, such as zoom operation of a zoom lens. At the same time, it is easy to operate at a constant speed.

[0028]

[Embodiment 1] Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a drawing that best illustrates the features of the present invention, and is a cross-sectional view of a part of a brake device of the operating force adjusting device of the present invention, which is cut perpendicular to a rotation axis.

1 is a cylindrical member, and 2 is a Newtonian fluid applied to the cylindrical surface of the cylindrical member 1. The Newtonian fluid 2 is a viscous liquid such as oil. When it is difficult to hold the cylindrical surface with the Newtonian fluid 2 alone, it is desirable to use a Newtonian fluid having a paste-like shape and having an increased holding force. Grease is a specific example of the paste-like substance.

In FIG. 1, reference numeral 3 denotes a thin plate as a member disposed around the cylindrical surface. One end of the thin plate 3 is fixed and the other end is fixed via a flexible member 5. Examples of the flexible member 5 include a spring and rubber.
Further, by using a flexible material such as rubber as the thin plate 3, it is possible to replace the flexible member 5 and the thin plate 3 with one member.

Reference numeral 4 denotes a spacer which is rotatably held around the center of the cylindrical member 1 without contact with the cylindrical member 1 and the Newtonian fluid 2.

In the illustrated example, the spacer 4 is rotatably held around the center of the cylindrical member 1.
If the contact area between the fluid and the Newtonian fluid 2 can be changed, the way of holding the fluid is free. In addition, thin plate 3
Is not necessarily required to be thin as long as it can be wound around the cylindrical member 1.

As shown in FIG. 1, when the cylindrical member 1 is rotated from the outside while a part of the thin plate 3 is in contact with the Newtonian fluid 2, the Newtonian fluid 2 undergoes shear deformation. At this time, a force proportional to the rate of shear deformation is generated between the cylindrical member 1 and the thin plate 3 due to the properties of the Newtonian fluid 2. Since the speed of the shearing deformation is proportional to the rotation speed of the cylindrical member 1, as a result, the brake device generates a braking torque proportional to the rotation speed of the cylindrical member 1.

Further, by rotating the spacer 4 around the center of the cylindrical member 1 and moving the thin plate 3 away from the cylindrical surface of the cylindrical member 1, the contact area between the Newtonian fluid 2 and the thin plate 3 changes. At this time, from the properties of the Newtonian fluid 2,
The braking torque of the brake changes in proportion to the contact area. The flexible member 5 is for absorbing the extra length of the thin plate 3 generated when the contact area is changed.

In FIG. 1, it is described that the cylindrical member 1 is rotating and the thin plate 3 arranged around the cylindrical surface is stationary, but in the state where the cylindrical member 1 is stationary. The same effect can be obtained even when the surrounding member 3 rotates.
Further, even when both the cylindrical member 1 and the surrounding member 3 move, the same effect can be obtained as long as the relative rotational movement occurs between them.

FIG. 2 is a perspective view showing a reference example of the present invention. In FIG. 2 in which the same parts as those in FIG. 1 are denoted by the same reference numerals and duplicate explanation is omitted, 101 is a brake having the structure shown in FIG. Device, 104 is a prime mover, and both are shafts 105
Are connected by It should be noted that in FIG.
Although the motor and the motor 104 are directly connected, they may be connected via a power transmission means such as a speed reducer. The motor is a motor, an engine, a turbine, or the like.

FIG. 3 shows the torque-rotational speed characteristic of the prime mover. The rotational speed of the intersection between the straight line representing the characteristic of the braking torque of the brake device and the characteristic of the drive torque of the prime mover is the rotational speed of the shaft 105. . In the brake device 101, by changing the contact area between the Newtonian fluid 2 and the member 3 arranged on the outer periphery of the cylindrical member 1, the inclination of the straight line representing the torque-rotation speed characteristic can be changed in FIG. The number of rotations of 105 can be changed.

At this time, the brake device 101 is
Since the braking torque proportional to the rotation speed of the engine 04 is generated, the same effect as when the negative feedback is applied to the prime mover 104 is obtained. Therefore, not only the control of the rotation speed but also the control of the rotation angle of the shaft 105 is possible. In addition, since no sealing mechanism is provided, the braking torque at a rotational speed of 0 is smaller when FIG. 11 and FIG. 3 showing the characteristics of the second conventional example are compared.
In addition, since there is no portion where solid friction occurs, stick-slip which impairs operability particularly at low speed is less likely to occur.

Embodiment 2 FIG. FIG. 4 is a perspective view showing an embodiment of the invention. In FIG. 4, reference numeral 101 denotes a brake device having the configuration shown in FIG.
Reference numeral 6 denotes a knob for operating the device. This operation knob 10
By connecting 6 to the brake device 101, not only the operating force can be adjusted according to the application and the operator, but also a good operational feeling can be obtained because the characteristics of the brake device 101 are proportional to the braking torque and the operating speed. At the same time, as described above, an effect similar to that obtained by applying feedback on the operation speed is obtained, so that accurate operation can be performed.

Embodiment 3 FIG. FIG. 5 is a longitudinal sectional view showing an embodiment of the invention, and FIG.
FIG. 2 is a cross-sectional view along the line A, in which the brake device having the configuration shown in FIG. 1 is applied to an operation unit of a cylindrical lens such as a handy lens for a television camera.

5 and 6, 2 is a Newtonian fluid,
Numeral 3 is a thin plate, 4 is a spacer, 5 is a spring, 6 is an operating ring connected to the thin plate 3 and at the same time as the optical system, and 7 is an operating force setting ring, which holds the spacer 4 and operates the operating ring. By changing the angular relationship with 6,
The spacer 4 moves around the center of the operation ring 6. Reference numeral 8 denotes a frame of a lens called a middle cylinder (lens barrel). The operation ring 6 and the operation force setting ring 7 are rotatably held around the middle cylinder 8.

FIGS. 5 and 6 correspond to the case where the cylindrical member 1 in FIG. 1 is fixed and the other members are rotated, and the middle cylinder 8 in FIGS. 5 and 6 corresponds to the cylindrical member 1 in FIG. I do. Now, by rotating the operating ring 6 and the operating force setting ring 7 together, a braking torque proportional to the rotation speed is generated in the operating ring 6 due to the properties of the Newtonian fluid 2. Further, by changing the angular relationship between the operating force setting ring 7 and the operating ring 6, the positional relationship between the thin plate 3 and the spacer 4 changes, and the contact area between the Newtonian fluid 2 and the thin plate 3 changes. Therefore, the braking torque changes.

Embodiment 4 FIG. FIG. 7 is a longitudinal sectional view showing another embodiment of the present invention.
This is applied to the operation unit of the axis 2 operation zoom lens.

In FIG. 7, 9 is a focusing lens group for focusing, 10 is a variator lens group for zooming in a zoom system, 11 is a compensator lens group for correction in a zoom system, and 12 is a relay lens group for imaging. The lens groups 9 to 12 are supported by a lens body 13. One end of the holding lens barrel of the focusing lens group 9 has a helicoid 1
4 is provided with a female screw 9a which engages with the male screw 14a, and the other end is provided with a rotating member 9b which engages with a linear groove 13a provided in the lens body 13, and linear movement in the optical axis direction by rotation of the helicoid 14. I do.

Further, a variator lens group 1 of a zoom system
Rotating members 10a and 11a that engage with cam grooves 15a and 15b provided on the cylindrical cam 15 based on an optical relationship are provided at one end of the holding barrel of the compensator lens group 11 and the lens body 13 at the other end. The rotary members 10b and 11b which are engaged with the linear grooves 13b provided in the optical disk drive are mounted, and perform linear motion in the optical axis direction in accordance with the rotation of the cylindrical cam 15.

Rotating members 17b and 17c are provided on a shaft 17a provided perpendicularly to the sliding shaft 17,
b is a linear groove 18 provided in the rotary cylinder 18 in parallel with the sliding shaft.
a, and the rotating member 17c has a cylindrical groove 19a provided in a sliding body 19 having an inner diameter engaged with the outer diameter of the rotating cylinder 18.
Is engaged. In order to prevent rotation, the sliding member 19 is used.
Is engaged with the shaft 20 by a hole 19b, and wires 21 attached to both ends of the shaft 20 change pulleys 22a, 22b,
It is wound around the drum 102a via 23c.

In the above configuration, the linear motion of the sliding shaft 17 connected to one end of the operating rod 16 in the direction of the arrow is transmitted to the sliding body 19 via the rotating member 17c,
Drives the drum 102a integrated with the cylindrical member 1 of the zoom brake device 102.

On the other hand, the rotation of the drum 102a is controlled by the belt pulley 10 connected to the zoom brake device 102.
The cylindrical cam 15 is driven through the belt 2b, the belt 24, and the belt pulley 15c.

The rotational movement of the sliding shaft 17 is transmitted to a belt pulley 18b provided on the rotary cylinder 18 via a rotating member 17b, and the belt pulley 14b is driven by the timing belt 23. Drive.

With the above configuration, in the one-axis two-operation zoom lens, the grip 16a of the operation rod 16 is pushed (Tele).
Pull (Wide) for zooming, clockwise (infinity)
Operate focusing by rotating counterclockwise (closest). Therefore, the zoom brake device 102 having the same configuration as the brake device shown in FIG. 1 is connected to the cylindrical cam 15, and the focus brake device 103 is connected to the helicoid 14, so that it can be selected according to the operator's preference and shooting conditions. The operability of zoom and focus is made variable, and the operability changes in accordance with the operation speed, so that good operability is obtained.

Embodiment 5 FIG. FIG. 8 is a cross-sectional view along a rotating shaft showing another brake device. In FIG. 8, 1 is a cylindrical member, 2 is a Newtonian fluid applied to the cylindrical surface of the cylindrical member, 25 is a cylindrical flexible member, which is arranged on the outer periphery of the cylindrical member 1. It is constrained in the axial direction. This flexible member 25
Examples include rubber. 4 is a spacer,
It is supported between the cylindrical member 1 and the cylindrical flexible member 25 so as to freely move in the direction along the axis without contacting the cylindrical member 1. Note that the spacer 4 in the fifth embodiment may be arc-shaped or cylindrical.

As shown in FIG. 8, the cylindrical flexible member 25
When the cylindrical member 1 is rotated from the outside while a part of the Newtonian fluid 2 is in contact with the Newtonian fluid 2, the Newtonian fluid 2 undergoes shear deformation. At this time, a braking force proportional to the speed of the shear deformation is generated between the cylindrical member 1 and the cylindrical flexible member 25 due to the properties of the Newtonian fluid 2. Since the speed of this shearing deformation is proportional to the rotation speed of the cylindrical member 1, as a result,
This brake device generates a braking torque proportional to the rotation speed of the cylindrical member 1. Further, by moving the spacer 4 along the axis of the cylindrical member 1, the cylindrical flexible member 25 is moved.
Of the cylindrical member 1 changes, and the contact area between the Newtonian fluid 2 and the cylindrical flexible member 25 changes. At this time, the braking torque of the brake device is proportional to the contact area due to the properties of the Newtonian fluid 2.

In the fifth embodiment, the first embodiment is not symmetric with respect to the rotation direction of the cylindrical member 1, but has a symmetric shape. For this reason, a difference in characteristics depending on the rotation direction of the cylindrical member 1 is unlikely to occur.

In the fifth embodiment, the members are arranged on the outer periphery of the cylindrical surface.
, A member in which a member is arranged inside a cylinder can also be realized.

FIG. 9 shows a reference example of the present invention, and is a cross-sectional view taken perpendicularly to a rotation axis.

In FIG. 9, 1 is a cylindrical member, 2 is a Newtonian fluid applied to the cylindrical surface of the cylindrical member, 26 is a contact member, and one or a plurality of members are arranged on the outer periphery of the cylindrical member 1. Are constrained in the circumferential direction of the outer periphery of the cylindrical member. When the cylindrical member 1 is rotated from the outside in a state where a part of the contact member 26 is in contact with the Newtonian fluid 2, a shear deformation occurs in the Newtonian fluid 2.

At this time, a braking force proportional to the speed of the shearing deformation is generated between the cylindrical member 1 and the contact member 26 due to the properties of the Newtonian fluid 2. Since the speed of the shearing deformation is proportional to the rotation speed of the cylindrical member, as a result, the brake device generates a braking torque proportional to the rotation speed of the cylindrical member 1. Further, by changing the distance between the contact member 26 and the cylindrical member 1, the contact between the contact member 26 and the outer periphery of the cylindrical member can be improved.
Non-contact is selected. Therefore, the total contact area of the cylindrical member 1 changes. At this time, the braking torque of the brake device is proportional to the total contact area due to the properties of the Newtonian fluid 2.

In the third and fifth embodiments, a spacer is required between the cylindrical member 1 and the members 25 and 26 disposed on the outer periphery thereof. However, the spacer is not required in this embodiment. Further, while the setting of the operating force is performed continuously in the third and fifth embodiments, the setting can be performed stepwise in this reference example.

[0059]

As described above, according to the first and second aspects of the present invention, it is possible to obtain an operating force adjusting device for various devices having excellent operability.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part showing a brake device according to a first embodiment of the present invention.

FIG. 2 is a main part configuration diagram showing a control device related to the present invention.

FIG. 3 is a characteristic explanatory diagram of the embodiment of FIG. 2;

FIG. 4 is a main part configuration diagram showing an operation force adjusting device according to a second embodiment.

FIG. 5 is a main part configuration diagram showing an optical device according to a third embodiment of the present invention.

FIG. 6 is a transverse sectional view taken along line AA of FIG. 5;

FIG. 7 is a main part configuration diagram showing an optical device according to a fourth embodiment of the present invention.

FIG. 8 is a sectional view of a main part showing a brake device according to a fifth embodiment of the present invention.

FIG. 9 is a sectional view of a main part of a brake device according to a reference example of the present invention.

FIG. 10 is a sectional view of a main part of a first conventional example.

FIG. 11 is a characteristic explanatory diagram of the first conventional example.

FIG. 12 is a perspective view of a second conventional example.

FIG. 13 is a diagram illustrating characteristics of a second conventional example.

[Explanation of symbols]

 Reference Signs List 1 cylindrical member 2 Newtonian fluid 3 thin plate 4 spacer 5 flexible member 6 operating ring 7 operating force setting ring 8 middle cylinder (lens barrel) 9 focusing lens group 9b rotating member 10 variator lens group 10a, 10b rotating member 11 compensator lens Group 11a, 11b rotating member

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F16D 57/00 F16D 35/00 G02B 7/08 G05G 1/08 G05G 5/00 H02K 7/102

Claims (2)

(57) [Claims] A cylindrical member having a cylindrical surface coated with Newtonian fluid, a member in contact with the cylindrical surface, and a spacer for changing a contact area of the member with the cylindrical surface; An operating force adjusting device characterized in that an operating force according to the contact area is obtained by rotating a cylindrical member, and an operating force can be adjusted by changing the contact area by the spacer. A cylindrical member having a cylindrical surface coated with Newtonian fluid, a member in contact with the cylindrical surface, and a spacer for changing a contact area of the member with the cylindrical surface; An operating force adjusting device, wherein an operating force according to the contact area is obtained by rotating a spacer and the contacted member, and the operating force can be adjusted by changing the contact area by the spacer.