JPH08184870A - Oscillation correction device' - Google Patents

Abstract

PURPOSE: To eliminate the need of a position detection means for detecting the displacement quantity of a correction means and to make the device compact. CONSTITUTION: This device is provided with elastic means 11pa, 11py, 11ya and 11yb supporting the correction means so that it can be displaced in a two-dimensional direction, driving means 79p, 79y, 712p and 712y giving force to resist against the elastic force of the elastic means and a control means allowing the driving means to input a driving target value balanced with the elastic force of the elastic means in order to displace the correction means to a position where image blurring can be corrected. Taking notice that relation between the elastic force of the elastic means and the displacement quantity of the correction means can be previously recognized so that the driving force corresponding to the elastic force of the elastic means required for displacing the correction means to the position where the image blurring can be corrected is given to the driving means.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a shake correction device which detects a low frequency vibration generated in the device and corrects an image shake.

[0002]

2. Description of the Related Art In the current camera, all the important operations for photographing such as exposure determination and focusing are automated, so that even a person unskilled in the operation of the camera has a very low possibility of photographing failure.

Further, recently, a line-of-sight input focus adjustment means for focusing on a place (subject) in which a photographer gazes in a viewfinder has been developed, and a system for preventing camera shake applied to a camera has been studied. The factors that cause shooting mistakes are almost gone.

Here, a system for preventing camera shake will be briefly described.

The camera shake at the time of photographing is usually a vibration of 1 Hz to 12 Hz as a frequency. However, at the time of shutter release, it is possible to take a photograph without image shake even if such a camera shake occurs. As a basic idea, it is necessary to detect the vibration of the camera due to the hand shake and displace the correction lens according to the detected value. Therefore, in order to achieve the ability to take a picture without causing image shake even if camera shake occurs, first, it is necessary to accurately detect the camera vibration and secondly correct the optical axis change due to camera shake. Will be needed.

In principle, this vibration (camera shake) is detected by a vibration sensor for detecting angular acceleration, angular velocity, angular displacement, etc., and an output signal of the sensor is integrated electrically or mechanically to determine the angle. This can be done by mounting a camera shake detection unit that outputs displacement on the camera. Then, based on this detection information, the correction optical mechanism that decenters the photographing optical axis is driven to suppress the image blur.

Here, an outline of the vibration isolation system using the vibration detection means will be described with reference to FIG.

The example of FIG. 25 is a diagram of a system for suppressing image shake caused by camera vertical shake 81p and camera horizontal shake 81y in the direction of arrow 81 in the figure.

In the figure, 82 is a lens barrel, 83p, 83
y is a vibration detecting means for detecting the camera vertical shake angular displacement and the camera horizontal shake vibration, respectively.
p, 84y. 85 is a correction means (86p, 8
6y is a coil for applying thrust to the shake correction means 85, 8
7p and 87y are position detecting elements for detecting the position of the correcting means 85, and the correcting means 85 is provided with a position control loop described later, and is driven with the outputs of the angular displacement detecting means 83p and 83y as target values, The stability on the image plane 88 is secured.

Next, FIG. 26 is an exploded perspective view showing the structure of the correction means suitably used for such purpose.

A bearing 73y is press-fitted into a support frame 72 in which the lens 71 is crimped. A support shaft 74y is supported by the bearing 73y so as to be slidable in the axial direction. The recess 74ya of the support shaft 74y is fitted into the claw 75a of the support arm 75. The bearing 7 is also attached to the support arm 75.
3p is press-fitted, and the support shaft 74p is supported slidably in the axial direction.

Incidentally, FIG. 26 also shows a rear view of the support arm 75 and a partial front view for clearly showing the claws 75a.

Projector mounting holes 72pa, 72 of the support frame 72
Light projecting elements 76p and 76y such as IRED are bonded to ya, and the terminals are soldered to lids 77p and 77y (bonded to the support frame 72) that also serve as connection boards. Further, the support frame 72 is provided with slits 72pb and 72yb so that the light projecting elements 76p and 76y project light through the slits 72p.
It is incident on PSDs 78p and 78y described later through b and 72yb. Coils 79p and 79y are also bonded to the support frame 72, and terminals are soldered to the lids 77p and 77y.

Supporting balls 711 are fitted into the lens barrel 710 (at three positions), and a claw portion 710a into which the recess 74pa of the support shaft 74p is fitted is provided.

Yokes 712p ₁ , 712p ₂ , 712p
₃ , the magnet 713p is laminated and adhered, and similarly, the yokes 712y ₁ , 712y ₂ , 712y ₃ and the magnet 7 are attached.
13y is also laminated and adhered. In addition, the polarity of the magnet is the arrangement of arrows 713pa and 713ya.

The yokes 712p ₂ and 712y ₂ are lens barrels 71.
It is screwed into the 0 recessed portions 710pb and 710yb.

Position detecting elements 78p and 78y such as PSD are adhered to the sensor seats 714p and 714y (714y is not shown), the sensor masks 715p and 715y are covered, and the terminals of the position detecting elements 78p and 78y are soldered to the flexible substrate 716. Attached. The convex portions 714pa and 714ya (714ya are not shown) of the sensor seats 714p and 714y are fitted into the mounting holes 710pc and 710yc of the lens barrel 710, and the flexible board 716 is mounted at the flexible board stay 717.
Is screwed to the lens barrel 710. Flexible board 71
The ear portions 716pa and 716ya of the sixth member 6 pass through the holes 710pd and 710yd of the lens barrel 710, respectively, and the yokes 712p ₁ and 7
12y ₁ is screwed on, and the coil terminals and the light emitting element terminals on the lids 77p and 77y are the land portions 716pb and 7 of the ear portions 716pa and 716ya of the flexible substrate 716, respectively.
16yb and polyurethane copper wire (three twisted wires) are connected.

A plunger 719 is screwed to the mechanical lock chassis 718, the plunger 719 is fitted to a mechanical lock arm 721 charged with a spring 720, and is rotatably screwed to the mechanical lock chassis 718 by a shaft screw 722.

The mechanical lock chassis 718 is screwed to the lens barrel 710, and the terminal of the plunger 719 is soldered to the land portion 716b of the flexible substrate 716.

The spherical adjusting screw 723 (three places) is threadedly penetrated into the yoke 712p ₁ and the mechanical lock chassis 718, and the adjusting screw 723 and the supporting ball 711 support the supporting frame 72.
The sliding surface (hatched portion 72c) is sandwiched. Adjustment screw 72
3 is screwed and adjusted so as to face the sliding surface with a slight clearance.

The cover 724 is adhered to the lens barrel 710 and covers the above-mentioned correction means.

FIG. 27 is a diagram for explaining the drive control system of the correction means shown in FIG.

The outputs of the position detecting elements 78p and 78y are amplified by the amplifier circuits 727p and 727y to be coils 79p and 79y.
When input to y, the support frame 72 is driven and the outputs of the position detection elements 78p and 78y change. Coil here 79
The drive direction (polarity) of p and 79y is the position detection element 78p,
When the output of 78y is set to be small (negative feedback), the driving force of the coils 79p and 79y causes the support frame 7 to be at a position where the outputs of the position detection elements 78p and 78y become substantially zero.
2 is stable. The adder circuits 731p and 731y are circuits that add the output from the position detection elements 78p and 78y and the command signals 730p and 730y from the outside, and the compensating circuits 728p and 728y are circuits that further stabilize the control system. Circuits 729p and 729y are coils 79p and 79
It is a circuit that supplements the current applied to y.

A command signal 7 is externally supplied to the system of FIG.
When 30p and 730y are given via the adder circuits 731p and 731y, the support frame 72 causes the command signals 730p and 730y.
Driven extremely faithfully.

The method of controlling the coil by negatively feeding back the position detection output as in the control system of FIG. 27 is called a position control method.
When the shake amount is given as the command signals 730p and 730y, the support frame 72 is driven in proportion to the shake amount.

FIG. 28 is a circuit diagram showing the details of the drive control system of the correction means shown in FIG. 27. Here, only the pitch direction 725p will be described (yaw direction 726y.
Is also the same).

Current-voltage conversion amplifiers 732pa and 732
pb is photocurrents 78i ₁ and 78i generated in the position detecting element 78p (composed of resistors R1 and R2) by the light projecting element 76p.
₂ is converted into a voltage, and the differential amplifier 733p calculates the difference between the current-voltage conversion amplifiers 732pa and 732pb (the output proportional to the position of the support frame 72 in the pitch direction 725p). Above, the current-voltage conversion amplifier 732pa, 7
32pb, the differential amplifier 733p, and the resistors R3 to R10 form the amplifier 727p in FIG.

The command amplifier 734p adds the command signal 730p input from the outside to the difference signal of the differential amplifier 733p, and the resistors R11 to R14 form the adder circuit 731p of FIG.

Resistors 738p and 739p and capacitor 7
40p is a known phase advance circuit, which corresponds to the compensation circuit 728p in FIG.

The output of the adder circuit 731p is the compensation circuit 7
It is input to the drive amplifier 735p via 28p, the drive signal of the pitch coil 79p is generated here, and the correction means is displaced. The drive amplifier 735p, the resistor 737p, and the transistors 736pa and 736pb form a drive circuit 729p in FIG.

The adding amplifier 741p is the sum of the outputs of the current-voltage converting amplifiers 732pa and 732pb (the position detecting element 7).
Then, the drive amplifier 742p receiving this signal drives the light projecting element 76p accordingly. As described above, the adding amplifier 741p, the driving amplifier 742p,
A drive circuit for the light projecting element 76p is configured by the resistors R18 to R24 and the capacitor C1 (not shown in FIG. 27).

The light projecting element 76p is extremely unstable in temperature and the like, and its projecting amount changes, and accordingly the differential amplifier 73p.
Although the position sensitivity of 3p changes, if the light projecting element 76p is controlled by the drive circuit so that the total amount of received light is constant as described above, the change in position sensitivity is reduced.

Here, the support frame 7 shown in FIG. 26 and FIG.
The locking means for locking 2 will be described.

The mechanical lock chassis 7 described with reference to FIG.
18, the plunger 719, the spring 720, the mechanical lock arm 721, and the shaft screw 722 constitute a locking means, and the locking means is viewed from the direction of the arrow 718a in FIG.
29 (a), and a sectional view of the plunger 719 is shown in FIG. 29 (b).

In FIG. 29B, the plunger 719
Is a slider 719a, a stator 719b, a coil 719c provided on the stator 719b, and a permanent magnet 71.
It is composed of 9d. Then, as shown in FIG. 29A, the slider 719a is hooked in a hole 721b of a mechanical lock arm 721 rotatably supported by a shaft 722, and the mechanical lock arm 721 is rotated by a spring 720 in a direction of an arrow 720a. It is energized. Therefore, the force F with which the slider 719a is pulled out from the stator 719b is
Always receive out. However, since the slider 719a is in contact with the permanent magnet 719d, its attractive force is large and is not moved by the force of the spring 720 (Fmg> Fou).
t: Fmg is the attractive force of the permanent magnet). In this state, the projection 721a at the tip of the mechanical lock arm 721 is fitted in the hole 72d of the support frame 72, and the support frame 72 is locked.

Next, when a current is applied to the coil 719c in a desired direction, the flow of magnetic flux in the magnetic circuit formed by the permanent magnet 719d, the slider 719a and the stator 719b changes, and the slider 719a and the permanent magnet 719d are attracted. The power weakens. Then, the mechanical lock arm 7 is driven by the force of the spring 720.
21 rotates in the direction of arrow 720a, the protrusion 721a is separated from the hole 72d of the support frame 72, and the locking is released (Fout.
> Fmg-Fi Fi is current repulsive force). At this time, the slider 719a is also pulled out of the stator 719b at the same time, and a gap δ is generated between the slider 719a and the permanent magnet 719d.

As is well known, since the attraction force is inversely proportional to the square of the distance between the permanent magnet 719d and the opposing object, the attraction force becomes extremely small due to the gap δ. Therefore, the coil 71
Even if the power supply to 9c is cut off, the support frame 72 is pressed by the urging force of the spring 720.
The unlocked state of can be maintained.

Next, when a current is applied to the coil 719c in the opposite direction, the resultant force of the absorption force of the slider 719a and the attraction force of the permanent magnet 719d by this current becomes larger than the force of the spring 720, and the slider 719a moves into the stator 719b. Pulled in (Fmg + Fi> Fout) Once the slider 719a begins to be pulled into the stator 719b, the absorption force of the permanent magnet 719d increases at an accelerated rate due to the decrease in the gap δ, and the slider 719a abuts the permanent magnet 719d. Along with the protrusion 7
21a enters the hole 72d of the support frame 72, and again the support frame 72
Will be locked.

As described above, a current is passed through the plunger 719 only at the time of locking and unlocking, so that a bistable structure for holding each state is realized, and a compact and power-saving locking means is realized. ing.

FIG. 30 is a block diagram showing the outline of the image stabilization system.

In FIG. 30, reference numeral 91 denotes the vibration detecting means 83p and 83y shown in FIG. 25. The shake detecting sensor detects the angular velocity of the vibration gyro and the DC of the shake detecting sensor output.
It is composed of sensor output calculation means for obtaining the angular displacement by integrating after cutting the component.

The angular displacement signal from the vibration detecting means 91 is input to the target value setting means 92. This target value setting means 9
2 is a variable differential amplifier 92a and a sample hold circuit 9
2b, and a sample hold circuit 92b
Is always being sampled, the two signals inputted to the variable differential amplifier 92a are always equal and the output thereof is zero. However, when the sample-hold circuit 92b is brought into the hold state by the output from the delay means 93 which will be described later, the variable differential amplifier 92a sets the time to zero and starts outputting continuously.

The amplification factor of the variable differential amplifier 92a is variable by the output of the image stabilization sensitivity setting means 94. The reason is that the target value signal of the target value setting means 92 is a target value (command signal) that causes the correction means to follow, but the correction amount (anti-vibration sensitivity) of the image plane with respect to the drive amount of the correction means is
This is because it changes depending on the optical characteristics based on the change in focus such as focus, and thus compensates for the change in the image stabilization sensitivity. Therefore, the image stabilization sensitivity setting unit 94 receives the zoom focal length information from the zoom information output unit 95 and the focus focal length information based on the distance measurement information of the exposure preparation unit 96, and sets the image stabilization sensitivity based on the information. The target value setting means 9 extracts the image stabilization sensitivity information preset based on the calculation or the information.
The gain of the variable differential amplifier 92a of No. 2 is changed.

The correction drive means 97 is the drive control circuit shown in FIG. 28, and the target values from the target value setting means 92 are input as command signals 730p and 730y.

The correction starting means 98 is the driving circuit 7 of FIG.
29p, 729y and the coils 79p, 79y are connected to each other.
By connecting it to 8c, both ends of each of the coils 79p and 79y are short-circuited, and when the signal of the logical product means 99 is input, the switch 98a is connected to the terminal 98b and the correction means 910 is in the control state (still Although shake correction is not performed, power is supplied to the coils 79p and 79y, and the position detection elements 78p and
The correction means 910 is stabilized at the position where the 78y signal becomes substantially zero). At the same time, the output signal of the logical product means 99 is also input to the locking means 914, whereby the locking means unlocks the correction means 910.

The correcting means 910 is the position detecting element 7
Input the position signals of 8p and 78y to the correction driving means 97,
Position control is performed as described above.

The logical product means 99, when both the release half-press SW1 signal of the release means 911 and the output signal of the image stabilization switching means 912 are input, the AND gate 99a, which is a component thereof, outputs the signal.

That is, when the photographer operates the anti-vibration switch of the anti-vibration switching means 912 and the release means 911 presses the release half-way, the correction means 910 is unlocked and enters the control state.

The SW1 signal of the release means 911 is input to the exposure preparation means 96 to perform photometry, distance measurement, and lens focusing drive, and as described above, output focus focal length information to the image stabilization sensitivity setting means 94. .

The delay means 93 receives the output signal of the logical product means 99, outputs it after one second, for example, and causes the target value setting means 92 to output the target value signal as described above.

Although not shown, the vibration detecting means 91 also starts to operate in synchronization with the SW1 signal of the release means 911. As described above, the sensor output calculation including a large time constant circuit such as an integrator requires a certain amount of time from the start to the stable output.

The delay means 93 plays a role of outputting a target value signal to the correction means 910 after waiting until the output of the vibration detection means 91 stabilizes, and prevents vibration after the output of the vibration detection means 91 stabilizes. It is configured to start.

The exposure means 913 performs the mirror-up by the release push-off SW2 signal input of the release means 911, opens and closes the shutter at the shutter speed obtained based on the photometric value of the exposure preparation means 96 to perform the exposure, and the mirror-down. Then, the shooting ends.

After the photographing, the photographer releases the shutter 911.
When the hand is released and the SW1 signal is turned off, the logical product means 99 stops the output, the sample hold circuit 92b of the target value setting means 92 enters the sampling state, and the output of the variable differential amplifier 92a becomes zero. Therefore, the correction means 91
0 returns to the control state in which the correction drive is stopped.

Since the output of the logical product means 99 is turned off, the locking means 914 locks the correction means 910, and then the switch 98a of the correction starting means 98 is connected to the terminal 98c, and the correction means 910 becomes Get out of control.

The vibration detecting means 91 continues to operate for a fixed time (for example, 5 seconds) after the operation of the release means 911 is stopped by a timer (not shown), and then stops.
This is because it is complicated for the photographer to continuously perform the release operation after stopping the release operation. Therefore, it is possible to prevent the vibration detection means 91 from being activated each time at such a time, and to shorten the waiting time until the output is stabilized. Vibration detection means 9
When 1 is already activated, the vibration detecting means 91 sends an activated signal to the delay means 93 to shorten the delay time.

[0057]

26 to 28.
The shake correction apparatus (comprising a correction means and its drive control system) described in 1. has a means for detecting the position of the correction means,
Since the correction means is driven and controlled by the output, there is an advantage that accurate shake correction drive can be performed, but as means for detecting the position, the light projecting elements 76p and 76y and the position detecting elements 78p and 78y, and further It is necessary to provide one drive control system for each of the correction drive directions in FIG. 27 and FIG. 28, resulting in an increase in size and power for position detection (projection element
6p, 76y driving and control circuit driving are also required, and a more compact and power saving correcting means has been desired.

(Object of the Invention) A first object of the present invention is to provide a shake correction device which can eliminate the position detecting means for detecting the amount of displacement of the correcting means and can be made compact. is there.

A second object of the present invention is to use a spring as the elastic means to accurately obtain the relationship between the displacement of the correcting means and the elastic force, and improve the expected position control by using a porous elastic material. In the case where rubber is used to reduce the driving load, braking near the drive stroke end of the correction means can be made effective, so that controllability can be stabilized, and shake correction can be achieved. It is to provide a device.

A third object of the present invention is to provide a shake correction device capable of improving the controllability of the correction means.

A fourth object of the present invention is to reliably apply the braking in the driving direction of the correction means when the viscous means is oil, and to easily apply the braking when the friction generating member is used. It is an object of the present invention to provide a shake correction device that can effectively improve the controllability of the correction unit.

A fifth object of the present invention is to provide a shake compensating device which can surely apply the braking of the compensating means in the driving direction regardless of the use environment.

A sixth object of the present invention is to use a metal provided in a magnetic field as the electromagnetic means so that braking in the driving direction of the correction means can be easily effected, and a short-circuit coil is used. Is to provide a shake correction device capable of obtaining a high braking force and improving the controllability of the correction means.

A seventh object of the present invention is to provide a shake correction apparatus which can improve the controllability of the correction means without providing any special means.

An eighth object of the present invention is to provide a shake compensating device capable of enhancing the controllability of the compensating means by making the compensating means braking in the driving direction with a simple circuit.

A ninth object of the present invention is to provide a shake correction device capable of improving the controllability of the correction means.

A tenth object of the present invention is to provide a shake correction device capable of widening the shake correction band and improving the shake prevention accuracy.

An eleventh object of the present invention is to provide a shake correction device capable of widening the shake correction band and improving the shake prevention accuracy.

A twelfth object of the present invention is to provide a shake compensating device capable of preventing the compensating means from swinging largely with respect to disturbance vibration.

A thirteenth object of the present invention is to provide a shake compensating device in which the compensating means is less likely to be displaced to the drive stroke end and the vibration sensation can be improved.

A fourteenth object of the present invention is to provide a shake correction device which can always stabilize the controllability of the correction means regardless of the environment of use.

A fifteenth object of the present invention is to provide a shake correction device capable of reducing the noise when the correction means collides with the end of the driving stroke and improving the vibration proof feeling.

A sixteenth object of the present invention is to provide a shake compensating device capable of achieving compactness of the device.

A seventeenth object of the present invention is to provide a shake correction device which can smoothly drive the correction means and can improve the vibration isolation accuracy.

An eighteenth object of the present invention is to provide a shake compensating device capable of eliminating twisting and rattling at the time of displacement of a support frame and improving vibration damping accuracy.

The nineteenth object of the present invention is to improve the slidability of the support frame with respect to the base plate, and when resin balls are used, it is possible to prevent a trace from being left on the base plate upon impact. An object is to provide a shake correction device.

A twentieth object of the present invention is to provide a shake compensating device capable of preventing rattling within the holding interval between the support frame and the main plate.

A twenty-first object of the present invention is to provide a shake correction device capable of increasing the mounting accuracy of the correction means and improving the vibration isolation accuracy.

[0079]

In order to achieve the first object, the present invention according to claim 1 provides elastic means for supporting the correcting means so as to be displaceable in a two-dimensional direction, and elasticity of the elastic means. A drive unit for applying a force against the force and a control unit for inputting a drive target value balanced with the elastic force of the elastic unit to the drive unit in order to displace the correction unit to a position where the image blur can be corrected are provided. Focusing on the fact that the relationship between the elastic force of the correction means and the displacement amount of the correction means can be known in advance, a driving force corresponding to the elastic force of the elastic means, which is displaced by the correction means to a position where image blur correction can be performed, is applied to the drive means. I am trying to give.

In order to achieve the second object,
According to the second aspect of the present invention, the elastic means is composed of a spring, a porous elastic material, or rubber.

Further, in order to achieve the third object,
According to the third aspect of the present invention, the viscous means for exerting the braking effect on the driving direction of the correction means is provided, and the viscous means exerts the braking effect on the driving direction of the correcting means.

In order to achieve the above-mentioned fourth object,
The present invention according to claim 4 uses oil or viscous means as the viscous means.
The viscous effect of the friction generating member is used.

In order to achieve the fifth object,
In the present invention according to claim 5, an electromagnetic means is used as the viscous means. .

In order to achieve the sixth object,
According to the sixth aspect of the present invention, a metal provided in a magnetic field or a short-circuit coil is used as the electromagnetic means.

In order to achieve the seventh object,
According to the seventh aspect of the present invention, the counter electromotive force induced in the coil, which is a constituent element of the driving means, is utilized so that the braking of the correcting means in the driving direction is effective.

In order to achieve the above eighth object,
According to the present invention of claim 8, the electromagnetic means is a means for performing negative feedback so that when the impedance of the coil, which is a component of the driving means, becomes high, the voltage applied to the coil is made low or high. The back electromotive force induced in the coil is extracted by detecting the impedance change of the coil, which is a component of the driving means.

In order to achieve the above ninth object,
According to the present invention as set forth in claim 9, near the natural frequency of the correcting means (obtained by the elastic constant of the elastic means and the mass of the correcting means), the correcting means over-responds, so that the prospective control with a small drive target value is performed. I am trying.

In order to achieve the tenth object, the present invention according to claim 10 corrects the frequency characteristic deterioration of the correction means on the input target value side.

In order to achieve the eleventh object, according to the present invention as set forth in claim 11, the correction means inputs at least near its natural frequency (obtained from the elastic constant of the elastic means and the mass of the correction means). However, since the phase is delayed, the phase of the target value input is advanced in advance.

In order to achieve the twelfth object, the present invention according to claim 12 is characterized in that the elastic force of the elastic means is
It is non-linear.

In order to achieve the twelfth object, the present invention according to claim 13 provides the elastic force of the elastic means,
In consideration of the large displacement of the correction means, the elastic force works more than linearly.

In order to achieve the above ninth object,
According to the fourteenth aspect of the present invention, the drive target value input to the correction means is made non-linear.

Further, in order to achieve the above thirteenth object, the present invention according to claim 15 is such that when the correcting means is largely displaced, the input is made smaller than the target value input corresponding thereto.

In order to achieve the above ninth object,
According to a sixteenth aspect of the present invention, when the correcting means is slightly displaced,
Since the correction means may not move due to friction, the value is set larger than the target value input to overcome friction and allow displacement.

In order to achieve the fourteenth object, the present invention according to claim 17 is such that the elastic force of the elastic means changes according to the environmental temperature in which the device is used. I am trying to change.

In order to achieve the fifteenth object of the present invention, the elastic stopper means absorbs the impact force when the correction means reaches the end of its driving stroke. There is.

In order to achieve the above ninth object,
According to the nineteenth aspect of the present invention, the elastic means is precharged in advance so that the elastic force is applied over the entire driving stroke of the correction means.

Also in order to achieve the above ninth object,
According to the present invention as set forth in claim 20, one end side of the elastic means is arranged in the drive means, and the center of the elastic force of the elastic means coincides with the center of the drive force of the drive means.

Further, in order to achieve the sixteenth object, the present invention according to claim 21 is such that one end of the elastic means is provided in an empty space (in the magnetism) in the drive means constituting the closed magnetic circuit. The side is arranged.

In order to achieve the seventeenth object, the present invention according to claim 22 provides a support frame and a base plate for holding a correction lens for correcting image blur with high dimensional accuracy, and The sphere is designed to be clamped with a sphere that can be accurately set.

In order to achieve the eighteenth object, the present invention according to the twenty-third aspect is such that a support frame holding a correction lens for correcting image blur and a base plate are sandwiched by a plurality of spherical bodies. In addition, the sandwiching flatness is improved.

In order to achieve the seventeenth object, the present invention according to claim 24 is for arranging a plurality of spheres so as to be in contact with each other even if the sandwiching interval is wide, thereby correcting the image blur. The base frame and the support frame that holds the correction lens are sandwiched.

Further, in order to achieve the eighteenth object, the present invention according to claim 25 is such that a plurality of sets of a support frame and a base plate holding a correction lens for correcting image blur are formed of a plurality of spheres. The sandwiching is performed so that the sandwiching flatness is good.

In order to achieve the nineteenth object, the present invention according to claim 26 is such that the sphere is formed of a metal sphere or a resin sphere.

Further, in order to achieve the twentieth object, according to the present invention of claim 27, the sphere is made of rubber or a porous elastic material.

In order to achieve the twenty-first object, the present invention according to claim 28 is characterized in that the base plate is attached to a holding frame for holding the base plate so as to be adjustable in angle or position with respect to each other.
The inclination and the positional deviation of the sandwiching surface of the correction means with respect to the main plate can be adjusted between the main plate and the holding frame.

In order to achieve the 21st object, the present invention according to claim 29 is such that a correction lens or a lens barrel for supporting the correction lens is attached to a support frame so as to be adjustable in angle or position. The inclination and the positional deviation of the holding surface of the correction means with respect to the main plate can be adjusted between the support frame and the correction lens or the lens barrel.

Further, in order to achieve the above ninth object,
According to the thirtieth aspect of the present invention, the base plate and the sphere are slidable with respect to each other so that the sphere does not become a driving load of the correction means even if the sphere does not rotate.

Also in order to achieve the above ninth object,
According to a thirty-first aspect of the present invention, the number of spheres forming a set is an even number, and when the plurality of spheres rotate with respect to the main plate, the rotation directions of the spheres do not become a load on the contact surfaces. There is.

[0110]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below based on the illustrated embodiments.

FIGS. 1 to 5 are views relating to the shake correcting apparatus in the first embodiment of the present invention. Parts having the same functions as those in the conventional example of FIGS. I will omit the explanation.

FIG. 1 is a front view of the shake correcting apparatus, FIG. 2 is a sectional view of the shake correcting apparatus and its drive control system, and FIG. 3 is a perspective view of the shake correcting apparatus and its drive control system.
The difference from the conventional shake correction apparatus shown in FIGS. 26 to 28 is that the light projecting elements 76p and 76y forming the position detecting means are
The position detecting elements 78p, 78y are omitted, and the compression coil springs 11pa, 11pb, 11y are elastic means.
a, 11yb (not shown) are provided, and the support arm 75 is omitted. Instead, the support shafts 74p, 74y are L-shaped.
Forming a support shaft 74 in the shape of a letter, one side of which is slidably fitted with the bearing portion 710d of the lens barrel 710, and the other side thereof is the bearing portion 72 of the support frame 72.
It is slidably fitted with d. Further, the lens barrel 710 is provided with a stopper 12 (formed of rubber or the like) that elastically restricts the displacement, and elastically receives when the support frame 72 is displaced by a certain amount or more. Therefore, the correction means will not be damaged even when a large disturbance vibration occurs.

The metal sphere 13 is attached to the support frame 72 as shown in FIG.
The projection 72e of the lens barrel 710 and the projection 72 of the cover 724 (see also FIG. 2).
It is sandwiched by 4a. Conventionally, the support frame 7 is adjusted by the ball 711 and the adjusting screw 723 (see FIG. 26).
No. 2 is clamped without looseness, but the adjustment process is complicated for that reason. However, without adjustment, the support frame 72
The sliding play 72c (see FIG. 26) has a pinching play corresponding to the dimension error in the thickness direction.

Therefore, instead of using the sliding surface 72c, the sphere 13 is embedded in the support frame 72, and both surfaces of the sphere 13 are mounted on the lens barrel 710 (base plate).
The backlash is reduced by the cover 724 (base plate). This is possible because the dimensional error of the spherical body 13 is extremely smaller than the dimensional error of the sliding surface 72c. Specifically, the dimensional error of the sliding surface 72c is ± 0.
Compared to the limit of 03 mm, the sphere 13 is ± 0.003 mm
The accuracy of the place is obtained. Therefore, when the method of FIG. 4A is used, the pinching backlash can be reduced.

It should be noted that the mounting position deviation between the spherical body 13 and the support frame 72 is caused by the fitting and mounting error of the spherical body 13 to the supporting frame 72, which is not the holding backlash but the plane of the supporting frame 72 with respect to the lens barrel 710. Appears as a tilt error. Therefore, the lens barrel 7
By fitting 10 (base plate) into the holding frame 14 and turning the eccentric pin 14 a, the tilt of the lens barrel 710 with respect to the holding frame 14 can be adjusted. In this way, the tilt of the support frame 72 is adjusted with respect to the holding frame 710, and the tilt error is corrected.

That is, in the conventional example shown in FIG. 26 and the like, the adjustment pin needs to be adjusted. Depending on this adjustment process, the support frame 72 may rattle, or the holding force may be strong, and a shake correction load may be generated. Compared to being complicated, the lens barrel 710
The inclination adjustment of the (base plate) and the holding frame 14 can be easily performed while observing the optical state, and the adjustment process can be simplified.

A coil spring 11pb is attached to the projection 710f (see FIGS. 1 to 3) of the lens barrel 710, and the support shaft 74
And the coil spring 11 is attached to the support frame 72.
pa is attached and pushes up the yoke 712p.
That is, the support frame 72 is elastically charged and sandwiched in the pitch direction 725p by the lens barrel 710 and the yoke 712p. The coil spring 11pa is actually a yoke 712p.
Although it is not visible in the magnetic path formed by, the yoke 7 in FIG.
Only 12p is shown in a sectional view, and FIG. 2 is also a side sectional view showing that the coil spring 11pa is provided between the support frame 72 and the yoke 712p.

When a coil spring is provided in the magnetic path in this way,
Not only can the space be made compact by effective use of the extra space, but also the center of the drive thrust (the direction of the generated force of the coil 79p) and the spring force of the coil spring 11pa can be made to coincide with each other. Prevent things.

Similarly, the support frame 72 has a coil spring 11y.
b is provided, a repulsive force is generated with respect to the support shaft 14, and a coil spring 11ya having the same configuration as the coil spring 11pa is provided, though it is not visible because it is hidden by the yoke 712y, and the support frame 72 supports the yoke 712y. The shaft 74 is elastically charged and sandwiched in the yaw direction 726y.

As described above, the support frame 72 is elastically supported by the lens barrel 710 in the shake correction direction.

The above coil springs 11pa, 11pb, 1
The elastic force of 1ya and 11yb is, as shown in FIG.
The support frame 72 is composed of a linear portion (a straight portion) and a non-linear portion (a portion where the strength is large even if the displacement is small), and the support frame 72 is linearly displaced from the central portion thereof up to a constant displacement amount (for example, 1 mm), and more. Becomes non-linearly displaced (because the elastic force becomes stronger). This prevents the support frame 72 from colliding with the correction stroke end at a high speed and generating a collision sound when an excessively large shake or disturbance vibration is input.

In the above structure, the voltage (electric power) input to the drive coils 79p and 79y of the correction means is a target value input for shake correction and is an output from the vibration detection means. Here, the coil springs 11pa, 11pb, 11
Since ya and 11yb are linear up to a certain drive range, and the relationship of the thrust of the coils 79p and 79y with respect to the input target value (voltage) is also linear, the elastic constant (elastic force for displacement) of the coil spring and the coil If the thrust constant (thrust against the input voltage) is known in advance, the desired displacement value can be given to the correction means by adjusting the input voltage, and no special position detection means is required.

The outline of the frequency characteristic of the correction means supported by the spring is, as shown in the Bode diagram of FIG. 5B, its natural frequency f ₀ (determined by the spring constant and the weight of the correction means). The gain is attenuated at the above frequencies. That is, the driving amount of the correction means becomes smaller than the target value. This natural frequency f
_{The value} of ₀ is set higher than the normal camera shake band A so that the attenuation region (the region where the shake cannot be corrected) does not overlap the shake correction band.

However, in actual shooting, there is also shake of a higher frequency than the normal shake correction band such as shock of the quick return mirror and shutter. Since such a shake is generally small, it does not cause a problem at the time of photographing, but when the shake is detected by the vibration detecting means and is inputted to the correcting means as a target value, the following problems occur.

As shown in FIG. 5B, the natural frequency f ₀
With the above, not only the gain is reduced, but also its phase is delayed. That is, a response delay in driving the correction means with respect to the target value input also occurs. When the delay amount is large, the movement of the correction means does not correct the shake, but moves in the direction of increasing the shake. That is, although it is actually desired to move the correction means so as to cancel the shake (crush the peak of the shake at the valley of the correction means operation), the correction means moves to increase the shake (the correction means operates on the shake peak). Mountain). Therefore, the shake due to the impact of the click return mirror and the shutter becomes larger when the shake correction is performed than when the shake correction is not performed, which may cause image deterioration.

Therefore, the filter of the Bode diagram shown in FIG. 5C (which reduces the target value gain of the natural frequency f ₀ or more) is connected to the target value output, and the shake due to the impact of the click return mirror or the shutter is shaken. And the correction means itself also reduces this shake as shown in FIG. 5 (b), so that the correction means does not respond to the shake due to the impact of the click return mirror or the shutter at all, and the above image deterioration is caused. Can be prevented.

In order to realize the above, as shown in FIG. 2, the target values 15p and 15y from the vibration detecting means (not shown) are used.
(The output of the shake angle in the shake directions 725p and 726y) is input to the calculation means 16p and 16y, and the target value suitable for the correction is changed. As described above, the calculation means 16p and 16y change the target value to an amount that gives a coil voltage suitable for the displacement amount (spring force) of the correction means, and also the shake correction amount associated with the zoom and focus of the camera. The change is also performed (generally, when the focal length changes, the shake correction amount on the image plane with respect to the displacement amount of the correction unit changes, so this correction is performed).

Further, the temperature detecting means 17 detects the ambient temperature and changes the calculation amount of the calculating means 16p, 16y. This is because the magnetic flux density of the magnetic circuit, the resistance value of the coil, and the spring constant are subtly changed due to the temperature change, so that the relationship of the displacement amount of the correction means with respect to the coil input voltage is corrected. . Then, after that, the filters 18p and 18y
At, the shake caused by the quick return mirror and the shutter included in the target value is attenuated by the characteristic shown in FIG. The signal that has passed through the filters 18p and 18y is input to the driving means 19p and 19y, where the voltage applied to the coil is generated (a sufficient current is applied to the voltage input to the coil). Here, the driving means 19p, 19y
Is output to the coils 79p and 79y via the resistance value detecting means 110p and 110y. The resistance value detecting means 110p and 110y detect the current value flowing in this coil and are also input. The driving voltage is the driving means 19
coil 79p, 79 because it is known from p, 19y
The resistance value of y is obtained.

FIG. 5D shows the frequency characteristic of the resistance value (impedance) of the coils 79p and 79y, which is large near the natural frequency f ₀ . In FIG. 5B, the outline of the frequency characteristic of the correction means is shown, but in reality, as shown in FIG. 5E, the gain is large (resonant) near the natural frequency f _0. Therefore, the driving speed of the correction means is high,
The counter electromotive voltage generated in the coils 79p and 79y becomes high, and the impedance rises as shown in FIG. 5 (d). When such a vibration of this frequency is input, such a resonance phenomenon causes an excessive response and is not preferable. Therefore, it is necessary to collapse the resonance phenomenon as shown by the constant chain line in FIG. 5 (e).

Here, when resonance occurs, FIG. 5 (d)
Paying attention to the fact that the impedance of the coil increases as shown by, the resistance value detecting means 110p and 110y are
The resistance value (impedance) of p and 79y is used as the negative feedback means 1
11p, 111y, and negative feedback means 111p, 11y
1y determines that resonance occurs when the resistance of the coils 79p and 79y exceeds a certain value, and the input voltage to the coils 79p and 79y of the driving means 19p and 19y is reduced to prevent resonance.

The above is the circuit block of the drive control system of the correction means, but in order to reduce the lifting near the natural frequency of FIG. 5 (e), the groove 112 of each bearing 710d, 72d is shown in FIG. As shown in b), the viscous oil 113 is filled, and damping (braking) is given to the sliding with the support shaft 74.

As described above, the following advantages are produced in the first embodiment of the present invention.

1) Since the elastic stopper 12 is provided, the impact noise can be reduced when the correcting means uses up its stroke when a large disturbance vibration is applied, and the damage due to the impact can be avoided.

2) Since both sides of the sphere 13 are sandwiched by the ground plane, the sandwiching interval can be set with high precision (sphere 13
Since the dimensional accuracy is high), the vibration isolation accuracy is improved.

3) A support frame 72 holding a plurality of spheres 13 therebetween.
Since the flat surface is provided, the accuracy of the sandwiching surface is high, and thus the accuracy of the plane can be increased.

4) Since the inclination error of the plane (the mounting error between the spherical surface and the support frame) can be adjusted by the eccentric pin 14a, the mounting accuracy of the correction means is increased and the vibration isolation accuracy is improved.

5) Since the sphere 13 is a metal sphere, the slidability is improved.

6) Since the correction means is elastically biased in the shake correction direction and the position is determined by applying a thrust force commensurate with the elastic force, no position detection means such as a sensor is required and the apparatus is compact. Can be achieved.

7) Apply the elastic bias to the coil springs 11pa and 11pa.
pb, 11ya, and 11yb are used, so
The temperature and stability over time increase, the linearity is good, and the vibration isolation accuracy is improved.

8) Coil springs 11pa, 11pb, 11
Since the ya and 11yb are provided in the surplus space in the magnetic path, the device can be made compact and the generation of the twisting force can be eliminated, so that the correction driving accuracy is improved.

9) Coil springs 11pa, 11pb, 11
When ya and 11yb have large displacements of the correction means, they generate a spring force that is more than linear, so that the correction means rarely collide with the stroke end during disturbance vibration or large shake.

10) Since the filters 18p and 18y for attenuating the target value are provided in the area where the shake of the corrector or higher than the natural frequency is inversely corrected, the inverse correction can be prevented.

11) Since the drive target value of the correction means is changed (by the calculation means 16p, 16y and the temperature detection means 17) according to the focal length and the temperature, the vibration isolation accuracy can be always improved.

12) The impedance of the coils 79p and 79y is calculated and negative feedback is performed to the coils (negative feedback means 1
11p and 111y, resistance value detection means 110p and 110y
Therefore, since the damping is applied, the controllability is improved.

13) Support shaft 74 and bearing portions 710d, 72
Since d is filled with oil and damping is applied, controllability is improved.

(Second Embodiment) The above 1) to 5), 8),
The effects of 9), 11), and 13) are not limited to the shake control device of the prospective control method that balances the spring force as in the first embodiment, and the position as described with reference to FIG. The same can be obtained in the control type shake correction apparatus. An example is shown in FIGS.

FIG. 6 is a front view of the shake correcting apparatus according to the second embodiment of the present invention, FIG. 7 is a sectional view of the shake correcting apparatus and its drive control system, and FIG. 8 is a perspective view of the shake correcting apparatus and its driving. It is a figure which shows a control system.

In FIG. 6, the outputs of the magnetic sensors 21p and 21y such as Hall elements and MR elements provided on the support frame 72 change depending on the distances to the yokes 712p and 712y, respectively (the yokes 712p and 712y are magnetized). Because). That is, the position detecting means changes its output according to the displacement of the support frame 72. Then, as shown in the circuit block of FIG. 7, the same position control as in FIG. 27 is performed.

Even when the control method similar to the conventional one is performed in this way, the above-mentioned 1) to 5), 8), 9), 1
It has the advantages of 1) and 13) and can improve the vibration isolation accuracy.

(Third Embodiment) FIGS. 9 to 11 are views according to a third embodiment of the present invention. FIG. 9 is a front view of a shake correction apparatus,
FIG. 10 is a diagram showing a cross section of the shake correction apparatus and a drive control system thereof, and FIG. 11 is a perspective view of the shake correction apparatus and a drive control system thereof. The difference from the first embodiment is the configuration of the elastic means. is there.

In the first embodiment, the compression coil spring is used as the elastic means, but in the third embodiment, the bending elasticity of the coil spring is utilized to reduce the gap of the elastic means. .

In FIG. 9, a hole 31 is provided in the support frame 72, and as shown in FIG. 10B, the small hole 31 of the hole 31.
The protruding pin 32a of the coil spring 32 is fitted in the portion a. The coil spring 32 is fixed to the lens barrel 710. Therefore, when the support frame 72 is displaced, the coil spring 32 is bent and an elastic force is generated.

With such a structure, the space of the coil spring is provided in the optical axis direction, which is a surplus space, and the space can be effectively used. Further, in the first embodiment, the coil spring 1 is provided independently of the pitch 725p and the yoke 26y direction.
Although 1pa, 11pb, 11ya, and 11yb are provided, the springs can be directly urged to the support frame 72 to reduce the number of springs as shown in FIGS.

(Fourth Embodiment) FIGS. 12 to 14 are views relating to a fourth embodiment of the present invention. FIG. 12 is a front view of a shake correction apparatus, and FIG. 13 is a cross section of the shake correction apparatus and its drive control. FIG. 14 is a diagram showing a system and FIG. 14 is a diagram showing a perspective view of a shake correction device and a drive control system thereof. What is different from the first embodiment is a biasing method of a spring which is an elastic means.

In FIGS. 13 and 14, one end of the metal leaf spring 41p is attached to the support frame 72 and the other end is attached to the support ring 42. The support frame 72 leaves the support ring 42 only in the pitch direction 725p. Since the spring 41p can be displaced by bending, and the supporting ring 42 is connected to the lens barrel 710 by the same plate spring 41y, the supporting ring 42 bends the plate spring 41y with respect to the lens barrel 710 and moves in the yaw direction. 726
It can be displaced only in y. Therefore, the support frame 72 is the lens barrel 710.
On the other hand, it can be displaced in the pitch direction 725p and the yaw direction 726y.

In this way, the support frame 72 has the leaf springs 41p and 41p.
Since it is attached by y to the optical axis direction and rotation around the optical axis without rattling, means for clamping as in the first to third embodiments (the base plate clamps the support frame by a spherical body or the like). Therefore, it is not necessary to suppress the play in the optical axis direction) and the support shaft 74 for regulating the rotation of the optical axis is not required, so that sliding friction can be eliminated and the driving accuracy can be improved.

The support frame 7 is not attached due to a mounting error of the metal spring.
The plane 2 and the plane of the lens barrel 710 may not be parallel to each other, but this can be easily eliminated by adjusting the inclination with the holding frame 14.

(Fifth Embodiment) FIGS. 15 to 19 are views relating to a fifth embodiment of the present invention. FIG. 15 is a front view of a shake correcting apparatus, and FIG. 16 is a cross section of the shake correcting apparatus and its driving. FIG. 17 is a diagram showing a control system, and FIG. 17 is a perspective view of a shake correction device and a drive control system thereof.

The difference from the first embodiment is that the elastic means is not the coil springs 11pa, 11pb, 11ya, 11yb but the rubber balls 51pa, 51pb, 51ya, 5ya.
1yb (in FIG. 15, 51ya is hidden by the yoke 712y and cannot be seen. Also, the yoke 712p and the coil 79p.
Is cross section).

When rubber is used as the elastic means instead of the coil spring, damping is effective, so that the controllability is enhanced as described in the first embodiment. The ball may be a porous elastic material (sponge), in which case the driving load can be reduced.

Further, the support shaft 74 and the bearings 710d, 72
In the sliding of d, the groove 112 of the bearing 710d (72d)
As shown in FIG. 18B, an O-ring 52 is enclosed, and friction is generated between the O-ring 52 and the support shaft 74 to perform damping, and controllability is similarly enhanced.

Further, in order to increase the damping, on the back side of the coils 79p and 79y, as shown in FIG. 18 (c),
Non-magnetic metal plates 53p and 53y, such as copper plates, are attached, and magnetic damping is added in association with the magnets 713y ₁ and 713y ₂ .

As described above, the controllability is improved by the damping by the rubber ball, the O-ring and the metal plate, and the resistance value detecting means 110y and the negative feedback means 11 used in the first embodiment are used.
1y is eliminated and the circuit is made smaller.

Further, as shown in FIG. 18A, a small metal sphere 54a is embedded in the support frame 72, a sphere 54b is fitted in contact with the sphere 54a, and the surface of the sphere 54a is covered with a cover 724. To contact the sphere 54b and the base plate 710e to sandwich the support frame 72.
Since the spheres 54a and 54b have extremely high dimensional accuracy, even if a plurality of spheres 54a and 54b are stacked and used, a clamping error does not occur. Sphere 5 like this
By using a plurality of 4a and 54b, each sphere can be made smaller and the sphere holding portion can be made smaller.

Also, the balls 51pa, 5 which are elastic means.
1pb, 51ya, 51yb are as in the first embodiment,
As shown in FIG. 19, which has no nonlinearity [FIG. 5 (a)],
The target value itself may be smaller than linear at the time of large displacement. This eliminates the need for setting the elastic means with high precision.

As the spheres, not only metal spheres but also resin spheres (resin spheres with high dimensional accuracy are commercially available) may be used, and in this case, the clamping parts (base plate 710e and cover 724a) due to impact or the like. It is possible to prevent dents from being left on.

When a plurality of spheres are used, the number of them is preferably an even number. Because, when the support frame 72 moves relative to the main plate (lens barrel 710) and the cover 724, not only the sphere slides but also rotation occurs. This is because at this time, the directions of the tangential force of the sphere at the contact points of the spheres are aligned so that the rotation directions of the spheres do not hinder the rotation of the other spheres.

It goes without saying that the above-mentioned mechanism can also be used for the position control correction means described in the second embodiment.

In the fifth embodiment described above, by using rubber or sponge as the elastic means, damping can be increased, controllability can be improved, or driving load can be reduced. Also, O
It is possible to improve the controllability by increasing friction by adding friction using a ring or magnetic damping using a metal plate. Furthermore, by using multiple spheres in a stack, sphere 1
The size of each one can be reduced and the whole can be made compact and lightweight. Also, durability can be improved by using resin balls as the spheres.

(Sixth Embodiment) FIGS. 20 to 24 are views according to a sixth embodiment of the present invention. FIG. 20 is a front view of a shake correcting apparatus, and FIG. 21 is a cross section of the shake correcting apparatus and its driving. 22 is a diagram showing a control system, and FIG. 22 is a diagram showing a perspective view of the shake correction apparatus and a drive control system thereof.

The difference from the fifth embodiment is that the method of adding damping and the filter 18p, described in the first embodiment,
18y is a configuration and an inclination adjusting method.

In FIG. 20, the lens barrel 61 holding the lens 71 is separate from the support frame 72.
As shown in (b), the spring washer 62 is attached to the flange portion 61a.
It is fixed to the support frame 72 with screws 63 via. Therefore, the lens barrel 61 can be finely adjusted with respect to the support frame 72 and the displacement in the optical axis direction depending on how the screw 62 is tightened, and the above-described fine adjustment of the holding frame 14 and the lens barrel 710 can be performed, so that the adjustment can be performed more accurately. You can Of course, the holding frame 14 and the lens barrel 71
The tilt adjustment may be performed only between the lens barrel 61 and the support frame 71 by omitting the adjustment of 0.

Further, the ball 5 shown in the fifth embodiment described above.
Instead of the elastic means composed of 1pa, 51pb, 51ya, 51yb, as shown in FIG. 20, rubber columns 64pa, 64p
b, 64 pa, 64 pb may be embedded in the support frame 72 or the lens barrel 710.

The outer periphery of the coils 79p and 79y is shown in FIG.
As shown in (a), the coil 65 is short-circuited.
p and 65y are respectively wound, and magnets 713p ₁ and 71
In addition to the above-mentioned magnetic damping of the metal plates 53p and 53y due to the relation with 3p ₂ , 713y ₁ and 713y ₂ ,
The controllability is improved by obtaining a more damping effect.

In the first embodiment described above, the filters 18p and 18y have the characteristic of attenuating the natural frequency or more as shown in FIG. 5C, and the correcting means for the shock of the quick return mirror and the shutter is provided. Was trying not to respond. This is because the shake due to the impact of the quick return mirror and the shutter is at a high frequency, and therefore the correction means delays the response and prevents the shake from being inversely corrected.

In the sixth embodiment, in order to eliminate the response delay of the correction means with respect to the shake of the high frequency and to make it possible to correct the shake caused by the quick return mirror and the shutter, FIG. As shown, the natural frequency f
The target value gain of ₀ or more is increased to cancel the deterioration of the frequency characteristic of the correction means [see FIG. 23 (b)].

Compensation for increasing the gain as shown in FIG. 23 (a) is generally called phase advance compensation. The phase of the target value is advanced in this band to cancel the phase delay (response delay) of the correction means. The quick return mirror shutter shake can also be corrected.

In the sixth embodiment, the tilt and the position can be adjusted between the lens barrel and the support frame to improve the optical performance and the vibration isolation accuracy.

Further, since the short-circuit coils 65p and 65y are provided around the coils 79p and 79y to enhance the magnetic damping, the controllability can be improved.

Furthermore, a phase advance filter may be added to the target value so that vibration of high frequency such as quick return mirror and shutter can be accurately prevented.

(Correspondence between Invention and Embodiment) In this embodiment, the coil springs 11pa, 11pb, 11ya and 11y are used.
b, coil spring 32, balls 51pa, 51pb, 51
ya, 51yb, rubber columns 64pa, 64pb, 64y
a and 64yb correspond to the elastic means of the present invention, and the filter 1
8, 18y corresponds to the compensation means of the present invention, and the O-ring 5
2. The resistance value detecting means 110p, 110y and the negative feedback means 111p, 111y correspond to the viscous means of the present invention, and the metal plates 53p, 53y and the short-circuit coils 65p, 65y correspond to the electromagnetic means of the present invention.

The above is the correspondence relationship between each configuration of the embodiments and each configuration of the present invention, but the present invention is not limited to the configurations of these embodiments, and the functions or embodiments shown in the claims or the embodiments It goes without saying that any structure may be used as long as it can achieve the function of.

(Modification) Although the present invention has been described as applied to a camera such as a single lens reflex camera, a lens shutter camera, a video camera, etc., other optical devices and other devices,
Furthermore, it can be applied as a constituent unit.

Furthermore, the present invention may be constructed by appropriately combining the above-described embodiments or their techniques.

[0185]

As described above, according to the present invention, attention is paid to the fact that the relationship between the elastic force of the elastic means and the displacement amount of the correction means can be known in advance, and the correction means can correct image blur. A driving force that is displaced to a position and is commensurate with the elastic force of the elastic means is applied to the driving means.

Therefore, the position detecting means for detecting the displacement amount of the correcting means is not required, and the size can be reduced.

Further, according to the present invention, the elastic means is composed of a spring, a porous elastic material, or rubber.

Therefore, when the elastic means is a spring,
The relationship between the displacement of the correction means and the elastic force can be accurately obtained, and the improvement of expected position control can be achieved by using a porous elastic material to reduce the driving load, and by using rubber, the correction means can be driven. Since the braking can be applied near the stroke end, the controllability can be stabilized.

Further, according to the present invention, the viscous means for exerting the braking in the driving direction of the correcting means is provided, and the viscous means exerts the braking in the driving direction of the correcting means.

Therefore, it becomes possible to improve the controllability of the correction means.

Further, according to the present invention, as the viscous means,
Oil or the viscous effect of the friction generating member is used.

Therefore, when oil is used as the viscous means, braking of the correction means in the driving direction can be surely effected,
When the friction generating member is used, braking can be easily applied and the controllability of the correction means can be improved.

Further, according to the present invention, the electromagnetic means is used as the viscous means.

Therefore, it is possible to reliably apply the braking in the driving direction of the correction means regardless of the use environment.

Further, according to the present invention, as the electromagnetic means,
A metal provided in the magnetic field or a short-circuit coil is used.

Therefore, when the electromagnetic means is a metal provided in a magnetic field, braking in the driving direction of the correction means can be easily effected, and when a short-circuit coil is used, a high braking force is obtained. Therefore, the controllability of the correction means can be improved.

Further, according to the present invention, the electromagnetic means is a means for extracting the counter electromotive force induced in the coil which is a constituent element of the driving means and negatively feeding it back to the driving means. The back electromotive force induced in a certain coil is used to exert braking in the driving direction of the correction means.

Therefore, the controllability of the correction means can be improved without providing any special means.

Further, according to the present invention, the means for performing negative feedback in the electromagnetic means is such that when the impedance of the coil which is a component of the driving means becomes high, the voltage applied to the coil is made low or high. Then, the counter electromotive force induced in the coil is extracted by detecting the impedance change of the coil, which is a component of the driving means.

Therefore, it becomes possible to enhance the controllability of the correction means by applying braking in the drive direction of the correction means with a simple circuit.

Further, according to the present invention, the drive target value is set to a value that can be attenuated above the natural frequency of the correction means,
In the vicinity of the natural frequency of the correction means (obtained by the elastic constant of the elastic means and the mass of the correction means), the correction means over-responds, so that the prospective control with a small drive target value is performed.

Therefore, the controllability of the correction means can be improved.

Further, according to the present invention, the driving target value is input to the driving means through the compensating means for compensating the frequency characteristic of the correcting means, and the deterioration of the frequency characteristic of the correcting means is corrected on the input target value side. I am trying to do it.

Therefore, it is possible to widen the shake correction band and improve the shake prevention accuracy.

According to the present invention, the compensating means is a means for compensating the phase so that the phase advances when the frequency input exceeds the natural frequency of the drive target value, and the correcting means has its natural frequency (of the elastic means). The phase of the target value input is advanced in advance because the phase is delayed with respect to the input above the vicinity (determined from the elastic constant and the mass of the correction means).

Therefore, it becomes possible to widen the shake correction band and improve the shake prevention accuracy.

Further, according to the present invention, the elastic force of the elastic means is made non-linear.

Therefore, the correcting means is prevented from swinging largely with respect to the disturbance vibration.

Further, according to the present invention, the elastic force of the elastic means is made to work linearly or more in consideration of the large displacement of the correcting means.

Therefore, it becomes possible to prevent the correcting means from swinging largely with respect to the disturbance vibration.

Further, according to the present invention, the drive target value input of the correction means is made non-linear.

Therefore, the controllability of the correction means can be improved.

Further, according to the present invention, when the correcting means is largely displaced, the input is made smaller than the corresponding target value input.

Therefore, the correction means is less likely to be displaced to the drive stroke end, and the vibration proof feeling can be improved.

Further, according to the present invention, when the correction means is slightly displaced, the correction means may not move due to friction. Therefore, the value is set larger than the target value input to enable displacement overcoming the friction.

Therefore, the controllability of the correction means can be improved.

Further, according to the present invention, since the elastic force of the elastic means changes according to the environmental temperature in which the apparatus is used, the target value is changed depending on the temperature.

Therefore, the controllability of the correction means can always be made stable regardless of the use environment.

Further, according to the present invention, the elastic stopper means for restricting the displacement of the correcting means at the time of the large displacement of the correcting means is provided, and the impact force when the correcting means reaches the end of its driving stroke is elasticized. It is designed to be absorbed by the stopper means.

Therefore, it is possible to reduce the noise when the correction means collides with the drive stroke end and to improve the vibration sensation.

Further, according to the present invention, the elastic means is precharged in advance so that the elastic force is applied over the entire driving stroke of the correction means.

Therefore, it becomes possible to improve the controllability of the correction means.

Further, according to the present invention, one end side of the elastic means is arranged in the drive means, and the center of the elastic force is made to coincide with the center of the drive force of the drive means.

Therefore, it becomes possible to improve the controllability of the correction means.

Further, according to the present invention, in the vacant space (in the magnetism) in the driving means forming the closed magnetic circuit,
One end side of the elastic means is arranged.

Therefore, it is possible to achieve compactness of the device.

Further, according to the present invention, the support frame for holding the correction lens for correcting the image blur and the base plate are sandwiched by the spheres with high dimensional accuracy and the sandwiching interval can be accurately set. I am trying to do it.

Therefore, the correction means can be driven smoothly, and the vibration isolation accuracy can be improved.

Further, according to the present invention, the supporting frame for holding the correction lens for correcting the image blur and the base plate are sandwiched by a plurality of spheres, and the sandwiching flatness is improved.

Therefore, it is possible to eliminate the twisting and rattling when the support frame is displaced, and to improve the vibration isolation accuracy.

Further, according to the present invention, a plurality of spheres are arranged so as to be in contact with each other even if the sandwiching interval is wide so that the support frame holding the correction lens for correcting the image blur is sandwiched by the base plate. ing.

Therefore, the correction means can be driven smoothly, and the vibration isolation accuracy can be improved.

Further, according to the present invention, the supporting frame for holding the correction lens for correcting the image blur and the base plate are sandwiched by a plurality of sets of a plurality of spheres, so that the sandwiching flatness is improved. I am making it.

Therefore, it is possible to eliminate the twisting and rattling when the support frame is displaced, and to improve the vibration isolation accuracy.

Further, according to the present invention, the sphere is formed of a metal sphere or a resin sphere.

Therefore, the slidability of the support frame with respect to the base plate can be improved, and when a resin ball is used, it is possible to prevent a trace from being left on the base plate at the time of impact.

According to the present invention, the sphere is made of rubber or a porous elastic material.

Therefore, it is possible to prevent rattling within the holding interval between the support frame and the ground plane.

Further, according to the present invention, the base plate is attached to the holding frame for holding the base plate so that the angle or the position of the base plate can be adjusted with respect to each other. It is adjustable between and.

Therefore, the accuracy of mounting the correction means is increased,
It is possible to improve the vibration isolation accuracy.

Further, according to the present invention, the correction lens or the lens barrel for supporting the correction lens is attached to the support frame so that the angle or the position of the correction lens can be adjusted with respect to each other. Is adjustable between the support frame and the correction lens or the lens barrel.

Therefore, the accuracy of mounting the correction means is increased,
It is possible to improve the vibration isolation accuracy.

Further, according to the present invention, the base plate and the sphere are slidable with respect to each other so that the correction load does not become a driving load even if the sphere does not rotate.

Therefore, the controllability of the correction means can be improved.

Further, according to the present invention, when the number of spheres forming a set is an even number and a plurality of spheres rotate with respect to the ground plane,
The rotation directions of the two spheres are set so as not to exert a load on the contact surfaces.

Therefore, it becomes possible to improve the controllability of the correction means.

[Brief description of drawings]

FIG. 1 is a front view of a shake correction apparatus according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a cross section of a shake correction apparatus and a drive control system thereof in the first embodiment of the present invention.

FIG. 3 is a diagram showing a perspective view of a shake correction apparatus and a drive control system thereof according to the first embodiment of the present invention.

FIG. 4 is a sectional view showing a detailed structure of a main part of FIG.

5 is a diagram showing characteristics of the coil spring and the like in FIG.

FIG. 6 is a front view of a shake correction device according to a second embodiment of the present invention.

FIG. 7 is a diagram showing a cross section of a shake correcting apparatus and a drive control system thereof in a second embodiment of the present invention.

FIG. 8 is a diagram showing a perspective view of a shake correction device and a drive control system thereof in a second embodiment of the present invention.

FIG. 9 is a front view of a shake correction device according to a third embodiment of the present invention.

FIG. 10 is a diagram showing a cross section of a shake correction device and a drive control system thereof in a third embodiment of the present invention.

FIG. 11 is a diagram showing a perspective view of a shake correction device and a drive control system thereof in a third embodiment of the present invention.

FIG. 12 is a front view of a shake correction device according to a fourth embodiment of the present invention.

FIG. 13 is a diagram showing a cross section of a shake correction device and a drive control system thereof in a fourth embodiment of the present invention.

FIG. 14 is a diagram showing a perspective view of a shake correction apparatus and a drive control system thereof in a fourth embodiment of the present invention.

FIG. 15 is a front view of a shake correction device according to a fifth embodiment of the present invention.

FIG. 16 is a diagram showing a cross section of a shake correction device and a drive control system thereof in a fifth embodiment of the invention.

FIG. 17 is a diagram showing a perspective view of a shake correction device and a drive control system thereof in a fifth embodiment of the invention.

18 is a sectional view showing a detailed structure of a main part of FIG.

FIG. 19 is a diagram showing characteristics of a ball which is the elastic means of FIG.

FIG. 20 is a front view of a shake correction device according to a sixth embodiment of the present invention.

FIG. 21 is a diagram showing a cross section of a shake correction device and a drive control system thereof in a sixth embodiment of the present invention.

FIG. 22 is a diagram showing a perspective view of a shake correction device and a drive control system thereof in a sixth embodiment of the present invention.

23 is a cross-sectional view showing the detailed structure of the main part of FIG.

24 is a diagram showing the characteristics of the elastic means and the frequency characteristics of the correction means in FIG.

FIG. 25 is a mechanism diagram showing an outline of a conventional vibration isolation system.

FIG. 26 is an exploded perspective view showing a specific configuration example of the correction means in FIG. 25.

27 is a diagram showing a drive control system of the correction means in FIG. 26.

28 is a circuit diagram showing a specific configuration example of each circuit in FIG. 27. FIG.

FIG. 29 is a view showing the structure of the locking means shown in FIG. 27.

FIG. 30 is a block diagram showing a schematic configuration of a conventional image stabilization camera.

[Explanation of symbols]

11pa, 11pb, 11ya, 11yb Coil spring 13, 54a, 54b Sphere 18p, 18y filter 32 Coil spring 51pa, 51pb, 51ya, 51yb Rubber ball 52 O-ring 53p, 53y Metal plate 64pa, 64pb, 64ya, 64yb65 Rubber column 65p Short-circuit coil 110p, 110y Resistance value detection means 111p, 111y Negative feedback means 113 Oil 721p, 712y Yoke

Claims (31)

[Claims] 1. A shake correction apparatus having a correction means for correcting image blur, wherein an elastic means for supporting the correction means so as to be displaceable in a two-dimensional direction and a force against the elastic force of the elastic means are provided. Drive means for giving the correction means and control means for inputting to the drive means a drive target value balanced with the elastic force of the elastic means in order to displace the correction means to a position where image blur correction is possible. Shake correction device. 2. The elastic means is a spring, a porous elastic material,
The shake correction apparatus according to claim 1, wherein the shake correction apparatus is one of rubber. 3. The shake correction apparatus according to claim 1, further comprising a viscous means for exerting a braking effect on the driving direction of the correction means. 4. The shake correction device according to claim 3, wherein the viscous means is oil or a friction generating member. 5. The shake correction apparatus according to claim 3, wherein the viscous means is an electromagnetic means. 6. The electromagnetic means is a metal provided in a magnetic field, or a short-circuit coil.
The shake correction device described. 7. The electromagnetic means is means for extracting a counter electromotive force induced in a coil, which is a component of the driving means, and feeding it back negatively to the driving means. Shake correction device. 8. The electromagnetic means is means for performing negative feedback so that the voltage applied to the coil is lowered or increased when the impedance of the coil, which is a constituent element of the driving means, increases. The shake correction apparatus according to claim 7, wherein the shake correction apparatus is a shake correction apparatus. 9. The shake correction apparatus according to claim 1, wherein the drive target value is attenuated above a natural frequency of the correction means. 10. The shake correction apparatus according to claim 1, wherein the drive target value is input to the drive means via a compensating means for compensating the frequency characteristic of the correcting means. 11. The shake correcting apparatus according to claim 10, wherein the compensating means is a means for compensating the phase so that the phase of the frequency input above the natural frequency of the drive target value is advanced. 12. The shake correction apparatus according to claim 1, wherein the elastic force of the elastic means is non-linear. 13. The shake correction apparatus according to claim 12, wherein the elastic force of the elastic means works linearly or more in accordance with the displacement of the correcting means. 14. The shake correction apparatus according to claim 1, wherein the drive target value input is non-linear. 15. The shake correction apparatus according to claim 14, wherein the drive target value input is smaller than a linear target value input according to the displacement when the correcting means is largely displaced. 16. The shake correction apparatus according to claim 14, wherein the drive target value input is larger than a linear target value input according to the displacement when the correction unit is slightly displaced. 17. The shake correction apparatus according to claim 1, wherein the drive target value is changed according to temperature. 18. The shake correcting apparatus according to claim 1, further comprising an elastic stopper means for limiting the displacement of the correcting means when the correcting means is largely displaced. 19. The shake correction apparatus according to claim 1, wherein the elastic means is precharged in advance. 20. The elastic means has a center of elastic force at a position which coincides with a center of driving force of the driving means.
The shake correcting apparatus according to claim 1, wherein one end side thereof is arranged in the driving means. 21. The shake correction apparatus according to claim 20, wherein the drive means is a means forming a closed magnetic circuit, and the elastic means has one end side thereof arranged in the magnetic field. 22. A shake correction apparatus comprising a correction unit for correcting image shake, wherein the correction unit holds a support frame for holding a correction lens for correcting image shake, a base plate, and
A shake correction device comprising a sphere that is sandwiched between the base plate and the support frame and that allows the support frame to be displaced in two dimensions with respect to the base plate. 23. The shake correction apparatus according to claim 22, wherein the spheres are provided at a plurality of positions in a plane parallel to the driving direction of the support frame. 24. A shake correction apparatus comprising a correction means for correcting image shake, wherein the correction means holds a support frame for holding a correction lens for correcting image shake, a base plate, and
A shake correction characterized by comprising a plurality of spheres that are sandwiched between the main plate and the support frame, arranged in contact with each other, and capable of displacing the support frame in the two-dimensional direction with respect to the main plate. apparatus. 25. The shake correction apparatus according to claim 24, wherein the plurality of spheres forming a set are provided at a plurality of positions in a plane parallel to the driving direction of the support frame. 26. The shake correction apparatus according to claim 22, wherein the sphere is either a metal sphere or a resin sphere. 27. The shake correction device according to claim 22, wherein the sphere is an elastic sphere. 28. The shake correction apparatus according to claim 22, wherein the base plate is attached to a holding frame that holds the base plate so that the base plate can be adjusted in angle or position. 29. The correction lens or a lens barrel for supporting the correction lens is attached to the support frame so as to be adjustable in angle or position with respect to each other.
Alternatively, the shake correction device according to 24. 30. The shake correction device according to claim 22, wherein the base plate and the sphere are configured to be slidable with respect to each other. 31. The shake correction device according to claim 24, wherein the plurality of spheres forming a set is an even number.