JP2007065464A - Image shake correcting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an image shake correcting device capable of preventing damage of a shake correction driving mechanism with a simple and compact structure. <P>SOLUTION: The image shake correcting device includes a guide means movably guiding a shake correction optical element in a direction orthogonal to a photographing optical axis and a drive means moving the shake correction optical element along the guide means, according to the level and direction of shake applied to an optical system. In the image shake correcting device, the drive means includes a first moving element moved in the guide direction of the guide means by a drive source; a second moving element capable of transferring a moving force of the first moving element to the holding member of the shake correction optical element; and a mutual guiding means which couples the first and the second moving elements to allow the first and the second moving elements to move relative to each other in the guide direction of the guide means. The mutual guiding means includes at least, two first slidable portions provided at different positions in a direction orthogonal to the guide direction of the guide means, respectively; and one second slidable portion provided at a position different from the positions of the two slidable portions in the guide direction of the guide means. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an image blur correction device mounted on an optical apparatus such as a camera or binoculars.

  The image shake correction device suppresses the shake of the subject image at the focal plane position by driving a part of the optical system to be displaced with respect to the optical axis in accordance with the magnitude and direction of the shake applied to the optical device. is there. However, since the optical element for shake correction needs to be driven at high speed with good response, the driving mechanism is likely to be loaded. That is, the shake correction optical element that operates at high speed is likely to reach the mechanical moving end when the shake is large, or the movement is limited for some other reason. When a driving force is further applied in such a movement restricted state, a stress is applied to the mechanism that transmits the driving force, and there is a possibility that a weak portion may be damaged. In addition, when the optical element for shake correction is supported so as to be always movable, if a strong external force is applied, such as dropping an optical device, the optical element is moved even though the drive source is stopped. There is a possibility that. In this case as well, the driving force transmission mechanism is stressed.

  For example, when a feed screw type motor is used as a drive source for shake correction, the smaller the feed screw lead (pitch), the higher the movement accuracy (resolution) can be. If it is made small, it will be disadvantageous in strength. For this reason, when a lead with a small lead and a high-precision feed screw is used and the stress as described above is applied, the feed screw portion may be damaged (such as biting of the screw). In order to prevent this, the movable range is increased so that the shake correction optical element does not easily reach the moving end, or the shake correction optical element is mechanically locked when shake correction is not performed. It can be considered. However, in the former measure, there is a possibility that the image shake correction apparatus is enlarged due to the expansion of the movable range, and in the latter measure, the structure may be complicated by providing an independent locking mechanism.

  SUMMARY OF THE INVENTION An object of the present invention is to provide an image blur correction apparatus capable of preventing damage to a shake correction drive mechanism with a simple and small structure.

  The present invention guides a shake correction optical element so as to be movable in a direction perpendicular to the photographing optical axis, and moves the shake correction optical element along the guide means according to the magnitude and direction of shake applied to the optical system. In the image shake correction apparatus having the drive means for driving, the drive means of the shake correction optical element shakes the first moving body moved in the guide direction of the guide means by the drive source and the moving force of the first moving body. A second moving body capable of transmitting to the holding member of the correction optical element, and a mutual guide means for coupling the first moving body and the second moving body in a guide direction of the guide means so as to be relatively movable, The mutual guide means is at least two first sliding portions provided at different positions in a direction orthogonal to the guide direction of the guide means, and is positioned in the guide direction of the guide means with respect to the two slide portions. One second sliding part provided with different It is characterized in that it is.

  For example, each sliding part is good to comprise by the pin formed in one of the 1st moving body and the 2nd moving body, and the hole part which is formed in the other and this pin fits so that sliding is possible. More preferably, the pin and the hole are formed integrally with the first moving body and the second moving body. Moreover, you may make the shape of a pair of hole part which comprises a 1st sliding part mutually differ.

  Further, either one of the two first sliding portions and the second sliding portion may be positioned on the same straight line in the guiding direction of the guiding means.

  The first moving body and the second moving body are provided with a movement restricting portion that engages with each other to restrict the relative movement between the first moving body and the second moving body, and the movement restricting portion engages. A first urging means for urging the first moving body and the second moving body in a direction, and a second urging force for urging the second moving body in a direction opposite to the first urging means. If the means is provided and the first urging means is disposed between the first sliding portion and the second sliding portion, the space efficiency is good.

  A pair of movement restricting portions are provided in each of the first moving body and the second moving body so as to be separated from each other in the guiding direction of the guide means, and a first sliding portion is provided in one of the pair of movement restricting portions, and the other It is preferable to provide a second sliding portion.

  In the image shake correction apparatus of the present invention, a plurality of guide means are provided so that the shake correction optical element can be moved straight in a plurality of different directions on a plane perpendicular to the photographing optical axis, and the shake correction optics along each guide means. A plurality of driving means for moving the element may be provided. In this case, it is preferable that each of the plurality of driving means includes a first moving body and a second moving body.

  According to the image shake correction apparatus of the present invention described above, it is simple and small without expanding the movable range of the shake correction optical element or providing a locking mechanism for mechanically locking the shake correction optical element. With this structure, damage to the shake correction drive mechanism can be prevented. In particular, the mutual guide means of the first and second moving bodies are arranged with respect to the two first sliding portions whose positions are different in the direction perpendicular to the guiding direction of the guiding means, and the first sliding portion. The first and second moving bodies can be made with high accuracy while having a simple and small structure by being constituted by one second sliding portion provided at a different position in the guiding direction of the guiding means. It can be operated.

  FIG. 1 shows the appearance of a digital camera 200 equipped with an image blur correction apparatus according to the present invention. A zoom lens barrel 201, an optical viewfinder 203, and a strobe 204 are provided on the front of the camera body 202, and a shutter button 205 is provided on the upper surface of the camera body 202.

  The zoom lens barrel 201 of the digital camera 200 whose side cross section is shown in FIGS. 2 and 3 is extended from the camera body 202 to the subject side as shown in FIG. 2 at the time of shooting, and as shown in FIG. 3 when shooting is not performed. The body 202 is accommodated (collapsed). In FIG. 2, the zoom lens barrel 201 shows a photographing state in which the upper half section is the wide end and the lower half section is the tele end. As shown in FIGS. 5 and 6, the zoom lens barrel 201 includes a second group straight guide ring 10, a cam ring 11, a third feed cylinder 12, a second feed cylinder 13, a straight guide ring 14, and a first feed cylinder 15. A plurality of substantially concentric annular (cylindrical) members such as a helicoid ring 18 and a stationary ring 22 are provided, and a common central axis of these annular members is shown as a lens barrel central axis Z0 in FIGS.

  The imaging optical system of the zoom lens barrel 201 includes a first lens group LG1, a shutter S and an aperture A, a second lens group LG2, a third lens group LG3, a low-pass filter 25, and a CCD (shake correction optical element) in order from the object side. 60. Each optical element from the first lens group LG1 to the CCD 60 is located on a common photographing optical axis (common optical axis) Z1 in the photographing state. The photographing optical axis Z1 is parallel to the lens barrel central axis Z0 and is eccentric downward with respect to the lens barrel central axis Z0. Zooming is performed by moving the first lens group LG1 and the second lens group LG2 along a photographing optical axis Z1 along a predetermined locus, and focusing is performed by moving the third lens group LG3 in the same direction. In the following description, the “optical axis direction” means a direction parallel to the photographing optical axis Z1, and the subject side is the front and the image plane side is the rear. In the plane perpendicular to the photographing optical axis Z1, the vertical direction is the Y axis, and the horizontal direction is the X axis.

  The fixed ring 22 is fixed in the camera body 202, and a fixed holder 23 is fixed to the rear part of the fixed ring 22. The fixed holder 23 is provided with a CCD 60 and a low-pass filter 25 so as to be movable in the X-axis direction and the Y-axis direction via a Y stage (second moving body) 71 and an X stage (shake correction optical element holding member) 21. It is supported. An LCD 20 that displays images and shooting information is provided at the rear of the fixed holder 23.

  The third group lens frame 51 that holds the third lens group LG3 is guided straight in a direction parallel to the photographic optical axis Z1 via the guide shafts 52 and 53, and is urged forward by the third group frame urging spring 55. Has been. The third group lens frame 51 is abutted with an AF nut 54 guided in a straight line in the optical axis direction, and the AF nut 54 is screwed to a feed screw formed on the peripheral surface of the drive shaft of the focus motor 160. When the AF nut 54 is moved backward in accordance with the rotation of the drive shaft of the focus motor 160, the third group lens frame 51 is pressed by the AF nut 54 and moved backward. Conversely, when the AF nut 54 is moved forward, the third group lens frame 51 is moved forward following the AF nut 54 by the biasing force of the third group frame biasing spring 55. With the above structure, the third group lens frame 51 can be moved back and forth in the optical axis direction.

  As shown in FIG. 4, a zoom motor 150 is supported on the fixed ring 22. The driving force of the zoom motor 150 is transmitted to the zoom gear 28 (FIG. 5) via the reduction gear mechanism. The zoom gear 28 is pivotally attached to the fixed ring 22 by a zoom gear shaft 29 parallel to the photographing optical axis Z1.

  A helicoid ring 18 is supported inside the fixed ring 22. The helicoid ring 18 is rotationally driven by a zoom gear 28, and the helicoid ring 18 rotates in the direction of the optical axis while rotating through the helicoid mechanism from the housed state in FIG. 3 to the photographing state in FIG. 2 (and vice versa). In the imaging state of FIG. 2 (between the wide end and the tele end), the helicoid ring 18 is rotated at a fixed position without moving in the optical axis direction. The first feeding cylinder 15 is coupled with the helicoid ring 18 so as to rotate and move in the optical axis direction.

  A straight guide ring 14 is supported inside the first feeding cylinder 15 and the helicoid ring 18. The rectilinear guide ring 14 is linearly guided in the optical axis direction through a linear groove formed in the fixed ring 22, and relative rotation is possible with respect to the first feeding cylinder 15 and the helicoid ring 18 in the optical axis direction. They are engaged so as to move together.

  As shown in FIG. 5, the linear guide ring 14 has a through guide groove 14 a penetrating the inner peripheral surface and the outer peripheral surface. The penetrating guide groove 14 a has a lead groove portion that is inclined with respect to the photographing optical axis Z <b> 1 and a circumferential groove portion that is centered on the lens barrel central axis Z <b> 0, and is provided on the outer peripheral surface of the cam ring 11. The outer diameter protrusion 11a is slidably fitted. The outer diameter protrusion 11a is further engaged with a rotation transmission groove 15a formed on the inner peripheral surface of the first feeding cylinder 15 and parallel to the photographing optical axis Z1, and the cam ring 11 is rotated together with the first feeding cylinder 15. . When the outer diameter protrusion 11a is engaged with the lead groove portion of the penetrating guide groove 14a, the cam ring 11 is advanced and retracted in the optical axis direction while rotating by receiving the guide of the lead groove portion, and the circumferential direction of the penetrating guide groove 14a. When the outer diameter protrusion 11a is engaged with the groove portion, it rotates in a fixed position without moving in the optical axis direction. Similar to the helicoid ring 18, the cam ring 11 is rotated and retracted between the retracted state of FIG. 3 and the shooting state of FIG. 2 (and vice versa), and in the shooting state of FIG. 2 (between the wide end and the tele end) The ring 11 is rotated in place.

  The rectilinear guide ring 14 linearly guides the second group rectilinear guide ring 10 and the second feeding cylinder 13 in the optical axis direction by linear grooves formed on the inner peripheral surface thereof and parallel to the photographing optical axis Z1. The second group rectilinear guide ring 10 linearly guides the second group lens moving frame 8 supporting the second lens group LG2 in the optical axis direction, and the second feeding cylinder 13 supports the third feeding cylinder supporting the first lens group LG1. 12 is guided straight in the direction of the optical axis. The second group rectilinear guide ring 10 and the second feeding cylinder 13 are supported so as to be relatively rotatable with respect to the cam ring 11 and to move integrally in the optical axis direction.

  A second group cam follower 8 a provided on the outer peripheral surface of the second group lens moving frame 8 is engaged with the second group guide cam groove 11 b formed on the inner peripheral surface of the cam ring 11. Since the second group lens moving frame 8 is guided linearly in the optical axis direction via the second group linear guide ring 10, when the cam ring 11 rotates, the second group lens moving frame 8 follows the shape of the second group guide cam groove 11 b. Moves along a predetermined locus in the optical axis direction.

  As shown in FIG. 6, the second group lens frame 6 that holds the second lens group LG <b> 2 is supported on the inner side of the second group lens moving frame 8 so as to be rotatable about the retraction rotation shaft 33. The retraction rotation shaft 33 is an axis parallel to the photographing optical axis Z1, and the second lens group LG2 is moved to the photographing position (FIG. 2) on the photographing optical axis Z1 when the second group lens frame 6 swings. It is moved to the retracted position (FIG. 3) retracted above the optical axis Z1. The second group lens frame 6 is urged toward the photographing position by a torsion spring 39, and the second holder lens frame 6 is moved against the torsion spring 39 when the second group lens moving frame 8 is retracted to the fixed holder 23. A retracting cam projection 23a is provided for rotating to the retracted position.

  The second delivery cylinder 13 guided linearly in the optical axis direction by the second group linear guide ring 10 further guides the third extension cylinder 12 in the optical axis direction. The third feeding cylinder 12 has a first group cam follower 31 projecting in the inner diameter direction, and the first group cam follower 31 is slidably fitted in a first group guide cam groove 11 c formed on the outer peripheral surface of the cam ring 11. is doing. The first group lens frame 1 is supported in the third feeding cylinder 12 via the first group adjustment ring 2. The first group lens frame 1 holds the first lens group LG1.

  A shutter unit 100 having a shutter S and a diaphragm A is supported between the first lens group LG1 and the second lens group LG2. The shutter unit 100 is fixed inside the second group lens moving frame 8.

  The zoom lens barrel 201 having the above structure operates as follows. When the main switch 101 (FIG. 25) provided on the outer surface of the digital camera 200 is turned on in the lens barrel storage state of FIG. 3, the zoom motor 150 is driven in the lens barrel feeding direction under the control of the control circuit 102 (FIG. 25). . The zoom gear 150 is rotationally driven by the zoom motor 150, and the helicoid ring 18 and the first feeding cylinder 15 are rotated forward by the helicoid. The rectilinear guide ring 14 moves straight forward together with the first feeding cylinder 15 and the helicoid ring 18. At this time, the cam ring 11 to which the rotational force is applied from the first feeding cylinder 15 has a lead structure (penetration guide groove) provided between the linear movement of the linear guide ring 14 forward and the linear guide ring 14. The combined movement of the lead groove portion of 14a and the feeding portion by the outer diameter projection 11a) is performed. When the helicoid ring 18 and the cam ring 11 are drawn out to a predetermined position in front, the functions of the respective rotary feeding structures (helicoid, lead) are canceled and only the circumferential rotation about the lens barrel central axis Z0 is performed. become.

  When the cam ring 11 rotates, on the inner side, the second group lens moving frame 8 guided linearly through the second group linear guide ring 10 is in the optical axis direction due to the relationship between the second group cam follower 8a and the second group guide cam groove 11b. Is moved along a predetermined trajectory. 3, the second group lens frame 6 in the second group lens moving frame 8 is held at a retracted position away from the photographing optical axis Z1 by the action of the retracting cam projection 23a protruding from the fixed holder 23. The second group lens frame 6 is separated from the retracting cam projection 23a while the second group lens moving frame 8 is extended to the zoom region, and the optical axis of the second lens group LG2 is moved by the urging force of the torsion spring 39. It is rotated to a photographing position (FIG. 2) that coincides with Z1. Thereafter, the second group lens frame 6 is held at the photographing position until the zoom lens barrel 201 is moved again to the storage position.

  Further, when the cam ring 11 rotates, the third feeding cylinder 12 guided linearly through the second feeding cylinder 13 on the outside of the cam ring 11 is related to the first group cam follower 31 and the first group guiding cam groove 11c. Is moved along a predetermined locus in the optical axis direction.

  That is, the former positions of the first lens group LG1 and the second lens group LG2 with respect to the imaging surface (CCD light-receiving surface) are respectively the forward movement amount of the cam ring 11 with respect to the fixed ring 22, and the third position with respect to the cam ring 11. The sum is determined as the sum of the cam feed amount of the feed cylinder 12 and the latter is the sum of the forward movement amount of the cam ring 11 relative to the fixed ring 22 and the cam feed amount of the second group lens moving frame 8 relative to the cam ring 11. Determined. Zooming is performed by moving the first lens group LG1 and the second lens group LG2 on the photographing optical axis Z1 while changing the air interval between them. When the lens barrel is extended from the storage position of FIG. 3, first, the wide end extended state shown in the upper half section of FIG. 2 is obtained, and when the zoom motor 150 is further driven in the lens barrel extending direction, the lower half section of FIG. As shown in FIG. As can be seen from FIG. 2, in the zoom lens barrel 201 of the present embodiment, the distance between the first lens group LG1 and the second lens group LG2 is large at the wide end, and the first lens group LG1 and the second lens at the tele end. The group LG2 moves in the direction of mutual approach, and the interval is reduced. Such a change in the air gap between the first lens group LG1 and the second lens group LG2 is given by the locus of the second group guide cam groove 11b and the first group guide cam groove 11c. In the zoom region between the tele end and the wide end, the cam ring 11, the first feeding cylinder 15, and the helicoid ring 18 perform only the above-mentioned fixed position rotation, and do not advance or retreat in the optical axis direction.

  When the zoom lens barrel 201 is ready to shoot from the wide end to the tele end, the third lens group LG3 (third group) is driven by driving the AF motor 160 according to the subject distance information obtained by the distance measuring means. The lens frame 51) moves along the photographing optical axis Z1 to perform focusing.

  When the main switch 101 is turned off, the zoom motor 150 is driven in the lens barrel storage direction, and the zoom lens barrel 201 performs a retracting operation opposite to the above-described feeding operation, resulting in the retracted state of FIG. In the middle of the movement to the storage position, the second group lens frame 6 is rotated to the retracted position by the retracting cam projection 23 a and retracts together with the second group lens moving frame 8. When the zoom lens barrel 201 is moved to the storage position, the second lens group LG2 is stored at the same position as the third lens group LG3, the low-pass filter 25, and the CCD 60 in the optical axis direction (in the radial direction of the barrel). Overlap). Due to the retracting structure of the second lens group LG2 at the time of storage, the storage length of the zoom lens barrel 201 is shortened, and the thickness of the camera body 202 in the left-right direction in FIG. 3 can be reduced.

  The digital camera 200 includes an image shake correction device. This image shake correction apparatus moves the CCD 60 along a plane perpendicular to the photographing optical axis Z1 in accordance with the magnitude and direction of shake (hand shake) applied to the digital camera 200, and shakes the subject image picked up by the CCD 60. The control is performed by the control circuit 102 (FIG. 25). 7 to 9 show the shake correction unit IS including the CCD 60, and FIGS. 10 to 23 show a state in which the whole or a part of the shake correction unit IS is disassembled.

  The fixed holder 23 is provided with a pair of Y guide rods 73 and 79 in the Y-axis direction (vertical direction). The Y guide rods 73 and 79 have a guide hole 71a and a guide groove 71b ( FIG. 16) is movably supported. A pair of X guide rods 72 and 74 are provided on the Y stage 71 in the X-axis direction orthogonal to the Y guide rod 73, and the guide holes 21 a of the X stage 21 are provided in the X guide rods 72 and 74. The guide groove 21b (FIGS. 11 and 12) is supported movably. A CCD 60 and a low-pass filter 25 are fixed on the X stage 21. Therefore, the CCD 60 is supported by the fixed holder 23 through the Y stage 71 and the X stage 21 so as to be movable in two orthogonal directions on a plane perpendicular to the photographing optical axis Z1. The movable range of the X stage 21 in the X axis direction is restricted by the inner peripheral surface of the Y stage 71, and the movable range of the Y stage 71 in the Y axis direction is restricted by the inner peripheral surface of the fixed holder 23.

  An X stage biasing spring (second biasing means) 87x is stretched between a spring hooking protrusion 21v provided on the X stage 21 and a spring hooking protrusion 23vx provided on the fixed holder 23. The X stage biasing spring 87x is a tension spring that biases the X stage 21 to the right when viewed from the front (front) of the zoom lens barrel 201 and to the left when viewed from the back. A Y stage biasing spring (second biasing means) 87 y is stretched between the spring hooking protrusion 71 v provided on the Y stage 71 and the spring hooking protrusion 23 vy provided on the fixed holder 23. The Y stage urging spring 87y is a tension spring and urges the Y stage 71 downward.

  As shown in FIGS. 16 and 17, a Y moving member (first moving body) 80 is supported on one side of the Y stage 71. The Y moving member 80 is a member that is long in the Y-axis direction, and has position restricting flanges (movement restricting portions) 80a and 80b in the vicinity of the upper and lower ends thereof. A guide pin (second sliding portion) 80c projects downward from the lower position regulating flange 80a, and a pair of guide holes (first sliding portion) 80d is provided in the upper position regulating flange 80b. Is formed. The Y moving member 80 is further provided with a nut abutting portion 80e and a rectilinear groove 80f (FIG. 16) at a position adjacent to the position restricting flange 80b, and a linear portion between the position restricting flange 80a and the position restricting flange 80b. A spring hooking projection 80g is provided. The rectilinear groove 80f is a groove facing in the Y-axis direction.

  The Y stage 71 has a position restricting flange (movement restricting portion) 71c facing the position restricting flange 80a and a position restricting flange (movement restricting portion) 71d facing the position restricting flange 80b, and the position restricting flange 71c has a guide. A guide hole (second sliding portion) 71e into which the pin 80c is slidably fitted is formed, and a pair of guide pins (first slide) slidably fitted into the pair of guide holes 80d in the position regulating flange 71d. 1 sliding portion) 71f is projected. A spring hooking projection 71g is provided in a linear portion between the position restriction flange 80a and the position restriction flange 80b.

  Due to the relationship between the guide hole 71e and the guide pin 80c, and the guide pin 71f and the guide hole 80d, the Y stage 71 and the Y moving member 80 guide and support each other so as to be relatively movable in the Y-axis direction. A tension coupling spring (first biasing means) 81y is stretched between the spring latching projection 71g of the Y stage 71 and the spring latching projection 80g of the Y moving member 80. The biasing force of the tension coupling spring 81y is as follows. The position restricting flange 80a and the position restricting flange 71c and the position restricting flange 80b and the position restricting flange 71d are brought into contact with each other, that is, the Y stage 71 is acted upward and the Y moving member 80 is acted downward.

  In addition to the X guide rods 72 and 74 that guide and support the X stage 21, the fixed holder 23 is provided with a pair of X guide rods 77 and 78 that face in the X-axis direction. A first X moving member (second moving body) 75 is movably supported. As shown in FIGS. 14 and 15, the first X moving member 75 is a member that is long in the X-axis direction, and position restricting flanges (movement restricting portions) 75a and 75b are provided in the vicinity of both sides thereof. A pair of guide holes 75c through which the X guide rod 77 is inserted are formed so as to penetrate both the position restricting flanges 75a and 75b, and only one guide hole 75d through which the X guide rod 78 is inserted is formed in the position restricting flange 75a. The The position restriction flange 75a is formed with a pair of guide holes (first sliding portions) 75e positioned between the guide hole 75c and the guide hole 75d, and the position restriction flange 75b is separated from the guide hole 75c. A guide pin (second sliding portion) 75f that projects in the X-axis direction protrudes. The first X moving member 75 is further provided with an interlocking protrusion 75g below the position restricting flange 75a, and a spring hooking protrusion 75h at a linear portion between the position restricting flange 75a and the position restricting flange 75b.

  The second X moving member (first moving body) 76 has position restricting flanges (movement restricting portions) 76a and 76b that are separated in the X-axis direction. One position restricting flange 76a has a guide for the first X moving member 75. A pair of guide pins (first sliding portions) 76c that are slidably fitted into the holes 75e are projected, and the guide pins 75f of the first X moving member 75 are slidably fitted to the other position regulating flange 76b. A round guide hole (second sliding portion) 76d is formed. The second X moving member 76 is further provided with a nut contact portion 76e and a rectilinear groove 76f at a position adjacent to the position restricting flange 76a, and a spring hooking protrusion 76g on a linear portion between the position restricting flange 76a and the position restricting flange 76b. Is provided. The rectilinear groove 76f is a groove facing the X-axis direction.

  Due to the sliding relationship between the guide pin 76c and the guide hole 75e and between the guide hole 76d and the guide pin 75f, the first X moving member 75 and the second X moving member 76 guide and support each other so as to be relatively movable in the X-axis direction. A tension coupling spring (first biasing means) 81x is stretched between the spring hooking protrusion 75h and the spring hooking protrusion 76g, and the biasing force of the tension coupling spring 81x is determined by the position restriction flange 75a and the position restriction flange. 76a, acting in the direction in which the position regulating flange 75b and the position regulating flange 76b are brought into contact with each other.

  The interlocking protrusion 75g of the first X moving member 75 is in contact with a transmission roller 21c (FIGS. 12 and 13) provided on the X stage 21, and the X-axis from the first X moving member 75 to the X stage 21 by this contact portion. Directional moving force is transmitted. The transmission roller 21c is rotatably supported by an axis parallel to the photographing optical axis Z1, and when the X stage 21 moves in the Y axis direction together with the Y stage 71, the transmission roller 21c moves on the contact surface of the interlocking protrusion 75g. Roll. Since the roller contact surface on the interlocking projection 75g side is a flat surface facing the Y-axis direction, the X stage 21 can be moved without applying a force in the Y-axis direction to the first X moving member 75 by rolling the transmission roller 21c. It can be moved in the Y-axis direction.

  As shown in FIG. 11, an X-axis drive motor 170x that is a drive source in the X-axis direction and a Y-axis drive motor 170y that is a drive source in the Y-axis direction are motor brackets 23bx and 23by provided in the fixed holder 23. It is fixed to. Both the X-axis drive motor 170x and the Y-axis drive motor 170y are stepping motors, and feed screws 171x and 171y are formed on the drive shafts. An X drive nut 85x is screwed to the feed screw 171x, and a Y drive nut 85y is screwed to the feed screw 171y. The X drive nut 85x is linearly guided in the X-axis direction by the rectilinear groove 76f of the second X moving member 76, and abuts against the nut abutting portion 76e. The Y drive nut 85y is linearly guided in the Y-axis direction by the rectilinear groove 80f of the Y moving member 80, and abuts against the nut abutting portion 80e. The nuts 85x and 85y can be detached by releasing screwing from both ends of the corresponding feed screws 171x and 171y. Nut biasing springs 89x and 89y are arranged between the X drive nut 85x and the X axis drive motor 170x and between the Y drive nut 85y and the Y axis drive motor 170y. Each of the nut biasing springs 89x and 89y is a compression coil spring, and when the nuts 85x and 85y are disengaged from the corresponding feed screws 171x and 171y toward the drive motors 170x and 170y, the biasing force for re-engaging them. Is given. When the nuts 85x and 85y are disengaged from the corresponding distal ends of the feed screws 171x and 171y (opposite to the drive motors 170x and 170y), the biasing force of the X stage biasing spring 87x and the Y stage biasing spring 87y Thus, an urging force in the re-threading direction is applied.

  The structure of the above shake correction unit IS is schematically shown in FIG. In FIG. 24, the shake correction unit IS is viewed from the back side of the digital camera 200. 24, part of the positional relationship between the X guide rod 78 and the guide pin 76c is different from that in FIGS. As can be seen from this schematic diagram, in the drive mechanism in the X-axis direction, the first X moving member 75 and the second X moving member 76 have the position restricting flange 75a abutting against the position restricting flange 76a and the position restricting flange 75b being the position restricting flange. In the state of abutting on 76b, it is elastically coupled by the urging force of the tension coupling spring 81x. The urging force of the X stage urging spring 87x acts on the first X moving member 75 via the transmission roller 21c that contacts the interlocking protrusion 75g. The urging force of the X stage urging spring 87x acts on the left in FIG. 24, that is, in the direction in which the position restricting flanges 75a and 75b are separated from the position restricting flanges 76a and 76b. Is set stronger than the biasing force of the X stage biasing spring 87x. Therefore, the first X moving member 75 and the second X moving member 76 maintain the elastic coupling state in which the position restricting flange 75a and the position restricting flange 76a, and the position restricting flange 75b and the position restricting flange 76b are in contact with each other, and the X stage as a whole. The biasing spring 87x is biased leftward in FIG. Then, the movement of the second X moving member 76 to the left in FIG. 24 is restricted by the nut abutting portion 76e coming into contact with the X driving nut 85x. Therefore, the position of the X driving nut 85x is the first in the X axis direction. This is the reference position for the 2X moving member 76 and the first X moving member 75.

  When the drive shaft of the X-axis drive motor 170x is rotationally driven, the X drive nut 85x screwed with the feed screw 171x is linearly moved in the X-axis direction, and the X-axis direction positions of the second X moving member 76 and the first X moving member 75 are moved. Change. For example, when the X drive nut 85x is moved to the right in FIG. 24, the X drive nut 85x presses the nut contact portion 76e, and against the X stage biasing spring 87x, the second X moving member 76 and the first The 1X moving member 75 is moved integrally to the right in the figure. When the first X moving member 75 is moved to the right in FIG. 24, the interlocking protrusion 75g presses the transmission roller 21c, and the X stage 21 is also moved to the right in FIG. Conversely, when the X drive nut 85x is moved to the left, the second X moving member 76 and the first X moving member 75 follow the X drive nut 85x and are integrated to the left by the biasing force of the X stage biasing spring 87x. Moved to. At this time, the X stage 21 is moved to the left in the figure following the first X moving member 75 by the biasing force of the X stage biasing spring 87x. The interlocking protrusion 75g and the transmission roller 21c are always kept in contact with each other by the biasing force of the X stage biasing spring 87x.

  In the drive mechanism in the Y-axis direction, the Y stage 71 and the Y moving member 80 are tensioned in a state where the position restricting flange 71c is in contact with the position restricting flange 80a and the position restricting flange 71d is in contact with the position restricting flange 80b. It is elastically coupled by a coupling spring 81y. The Y stage 71 is urged downward in FIG. 24 by the Y stage urging spring 87y, that is, in a direction in which the position restricting flanges 71c and 71d are separated from the position restricting flanges 80a and 80b. The force is set stronger than the biasing force of the Y stage biasing spring 87y. Therefore, the Y stage 71 and the Y moving member 80 maintain the elastic coupling state in which the position restricting flange 71c and the position restricting flange 80a and the position restricting flange 71d and the position restricting flange 80b are in contact with each other, and the Y stage biasing spring as a whole. It is biased downward by 87y. Since the downward movement of the nut abutting portion 80e against the Y drive nut 85y is restricted, the position of the Y drive nut 85y is the reference position of the Y moving member 80 and the Y stage 71 in the Y axis direction. It becomes.

  When the drive shaft of the Y-axis drive motor 170y is rotationally driven, the Y drive nut 85y screwed with the feed screw 171y is linearly moved in the Y-axis direction, and the Y-axis position of the Y moving member 80 and the Y stage 71 changes. For example, when the Y drive nut 85y is moved upward in FIG. 24, the nut contact portion 80e is pressed against the Y drive nut 85y, and the Y moving member 80 and the Y stage 71 are resisted against the Y stage biasing spring 87y. Are integrally moved upward in FIG. Conversely, when the Y drive nut 85y is moved downward, the urging force of the Y stage urging spring 87y causes the Y moving member 80 and the Y stage 71 to move integrally downward following the Y drive nut 85y.

  When the Y stage 71 moves in the Y axis direction, the X stage 21 supported on the Y stage 71 also moves in the Y axis direction. On the other hand, since the first X moving member 75 with which the transmission roller 21c provided on the X stage 21 abuts does not move in the Y-axis direction, when the X stage 21 moves up and down together with the Y stage 71, the transmission roller 21c and the interlocking projection 75g The contact location changes. As described above, at this time, the transmission roller 21c rolls on the contact surface of the interlocking protrusion 75g, and the X stage 21 is moved in the Y axis direction without applying a moving force in the Y axis direction to the first X moving member 75. Can be made.

  From the above structure, by driving the X-axis drive motor 170x forward and backward, the X stage 21 can be moved forward and backward in the X-axis direction, and by driving the Y-axis drive motor 170y forward and backward, The Y stage 71 and the X stage 21 supported by the Y stage 71 can be moved forward and backward in the Y-axis direction.

  As shown in FIGS. 14 and 15, the first X moving member 75 is provided with a plate-like position detector 75 i in the vicinity of the position restricting flange 75 a. Further, as shown in FIG. 16, the Y stage 71 is provided with a plate-like position detecting portion 71h in the vicinity of the position restricting flange 71c. As shown in FIGS. 18 and 19, the photo interrupter 103 capable of detecting the passage of the position detector 75 i provided in the first X moving member 75 and the passage of the position detector 71 h provided in the Y stage 71 are detected. A photo interrupter 104 is provided. By detecting the passage of each position detector 75i, 71h by the photo interrupters 103, 104, the first X moving member 75 (that is, the X stage 21) in the X axis direction and the initial position of the Y stage 71 in the Y axis direction are detected. can do.

  As shown in the block diagram of FIG. 25, the digital camera 200 includes an X gyro sensor (angular velocity sensor) 105 and a Y gyro sensor (angular velocity sensor) 106 for detecting a moving angular velocity around the X axis and the Y axis. The speed (size) and direction of the shake are detected by the gyro sensors 105 and 106. Subsequently, the control circuit 102 obtains a moving angle by time-integrating the angular velocities in the X- and Y2-axis directions detected by the X gyro sensor 105 and the Y gyro sensor 106, and determines the moving angle from the moving angle (imaging surface of the CCD 60). The X stage 21 (the first X moving member 75 and the second X moving member 76) and Y for each axial direction for calculating the amount of movement of the image in the X axis direction and the Y axis direction and canceling the image shake are calculated. The drive amount and drive direction (drive pulses of the X-axis drive motor 170x and the Y-axis drive motor 170y) of the stage 71 (Y moving member 80) are calculated. Based on this calculated value, the X-axis drive motor 170x and the Y-axis drive motor 170y are driven and controlled. Thereby, the shake of the subject image picked up by the CCD 60 is suppressed. The image blur correction mode can be entered by turning on the shooting mode changeover switch 107 (FIG. 25). When the shooting mode changeover switch 107 is turned off, the image blur correction function is stopped and normal shooting can be performed. . The shooting mode changeover switch 107 further operates in the first follow-up mode in which the X-axis drive motor 170x and the Y-axis drive motor 170y are always driven to perform shake correction in the image shake correction mode, and the photometry switch 108 and the release switch 109 are operated. The second follow-up mode in which the shake correction is performed by driving each X-axis drive motor 170x and Y-axis drive motor 170y only at times can be selected. Note that the photometry switch 108 is turned on when the shutter button 205 is half-pressed, and the release switch 109 is turned on when the shutter button 205 is fully pressed.

  In the above image blur correction apparatus in the digital camera 200, the driving force transmission mechanism from each of the drive motors 170x and 170y to the CCD 60 (X stage 21) to be driven absorbs a load and an impact and feed screws 171x and 171y. It has a structure that prevents damage. This damage prevention structure is constituted by a first X moving member 75 and a second X moving member 76 that are spring-coupled in the drive mechanism in the X-axis direction, and a Y-stage 71 that is spring-coupled in the drive mechanism in the Y-axis direction. And the Y moving member 80.

  For example, when the X drive nut 85x is driven to the right in FIG. 24 by the X axis drive motor 170x, the X stage 21 comes into contact with the Y stage 71 to reach the movement restriction end, or the X stage 21 moves due to other causes. The first X moving member 75 and the second X moving member 76, which normally move together, resist the urging force of the tension coupling spring 81x, and the position restricting flanges 75a and 76a and the position restricting flanges 75b and 76b. Move relative to each other in the direction of separating them. Specifically, the second X moving member 76 can move alone to the right in FIG. 24 with respect to the first X moving member 75 that is prevented from moving together with the X stage 21. As a result, even if the X stage 21 becomes immovable, the X drive nut 85x can move along the feed screw 171x, so that an excessive load is not applied and the screwed portion is bitten. There is no risk of damage to other power transmission parts. When the X drive nut 85x is driven to the left in FIG. 24 by the X axis drive motor 170x, the X drive nut 85x moves in a direction away from the nut contact portion 76e. No motor driving force acts on the 1X moving member 75, and even if the movement of the X stage 21 is hindered, no excessive force is applied to the driving force transmission mechanism.

  The drive mechanism in the Y-axis direction has the same function. For example, when the Y drive nut 85y is driven upward in FIG. 24 by the Y axis drive motor 170y, the Y stage 71 comes into contact with the fixed holder 23 to reach the movement restricting end, or the Y stage 71 (or X When the movement of the stage 21) is hindered, the Y moving member 80 and the Y stage 71, which normally move together, resist the biasing force of the tension coupling spring 81y, and the position restriction flanges 71c, 80a and the position restriction flange 71d. , 80b are moved relative to each other in the direction of separating them. Specifically, the Y moving member 80 can move alone upward in FIG. 24 with respect to the Y stage 71 whose movement is prevented. As a result, even if the Y stage 71 cannot move, the Y drive nut 85y can move along the feed screw 171y, so that an excessive load is not applied and the screwed portion is bitten. There is no risk of damage to other power transmission parts. Note that when the Y drive nut 85y is driven downward in FIG. 24 by the Y axis drive motor 170y, the Y drive nut 85y moves in a direction away from the nut abutting portion 80e, and therefore the Y moving member 80 and the Y stage 71 are moved. No motor driving force is applied to the driving force transmission mechanism, and even if the movement of the Y stage 71 is hindered, no excessive force is applied to the driving force transmission mechanism.

  As described above, the moving end of the X stage 21 in the X axis direction is determined by the inner peripheral surface of the Y stage 71, and the moving end of the Y stage 71 in the Y axis direction is determined by the inner peripheral surface of the fixed holder 23. Ideally, when the X stage 21 reaches the left and right moving ends, the driving force transmission from the feed screw 171x to the X drive nut 85x is interrupted, and when the Y stage 71 reaches the up and down moving ends, the feed screw It is preferable that transmission of the driving force from 171y to the Y driving nut 85y is cut off, but such an ideal relationship is not always obtained in consideration of the accuracy error of components. For example, when the X stage 21 (or Y stage 71) has reached the mechanical moving end and the screwing length of the drive nut 85x (85y) and the feed screw 171x (171y) is still sufficient, as described above. If the damage prevention structure is not provided, a load is applied by further motor driving, and the drive nut 85x (85y) and the feed screw 171x (171y) may be bitten. As a measure to prevent this, a sufficient margin is provided for the movable amount so that the X stage 21 and the Y stage 71 do not easily reach the moving end, and drive nuts are provided at both ends of the feed screw 171x (171y). It is conceivable that the drive nut 85x (85y) is configured to drop off when the screw thread engagement is released when 85x (85y) reaches. However, in this configuration, the movable range of the X stage 21 and the Y stage 71 must be increased more than necessary, and the entire apparatus may be increased in size. In addition, when the X stage 21 or the Y stage 71 has a movement failure at an intermediate position unrelated to the moving end, a large load is applied to the screwed portion regardless of the movable range of the X stage 21 or the Y stage 71. It will take. On the other hand, in the image shake correction apparatus of the present embodiment, the movement amount is reduced by the relative movement of the intermediate members (first X moving member 75 and second X moving member 76, Y stage 71 and Y moving member 80) provided in the drive mechanism. Since the error is absorbed, it is not necessary to increase the movable range of the X stage 21 and the Y stage 71 more than necessary. Further, as described above, even if the X stage 21 and the Y stage 71 become immovable at an intermediate position unrelated to the moving end, the relative movement of this intermediate member causes the movement amount of the drive nut 85x (85y) to Since the difference is absorbed, no load is applied to the screwed portion. In the present embodiment, the relative movement amount of the first X moving member 75 and the second X moving member 76 can absorb the position error regardless of the positional relationship between the X drive nut 85x and the X stage 21 in the respective movable ranges. Is set to Similarly, the relative movement amount of the Y stage 71 and the Y moving member 80 is set so that the position error can be absorbed regardless of the positional relationship between the Y drive nut 85y and the Y stage 71 in the respective movable ranges. Yes.

  The reason why a load is applied to the driving force transmission mechanism is not limited to the movement of the X stage 21 and the Y stage 71. The CCD 60, which is an optical element for shake correction, is supported so as to be movable in the X-axis and Y-axis directions. Therefore, when the digital camera 200 is dropped and a large external force is momentarily applied, it is driven by the motors 170x and 170y. Although no force is applied, the moving force may act on the X stage 21 holding the CCD 60 and the Y stage 71. The image blur correction apparatus according to the present embodiment can reliably absorb a load and an impact even in such a case.

  For example, when the X stage 21 is moved leftward in FIG. 24 by an external force other than the motor driving force, the first X moving member 75 is pressed in the same direction via the transmission roller 21c. Since this pressing direction is a direction in which the position restricting flanges 75a and 75b are separated from the position restricting flanges 76a and 76b, the first X moving member 75 can move independently while resisting the urging force of the tension coupling spring 81x. it can. At this time, only the elastic tensile force by the tension coupling spring 81x acts on the second X moving member 76, and the first X moving member 75 does not mechanically press the second X moving member 76. An excessive force is not applied from the second X moving member 76 to the X drive nut 85x. Further, when the X stage 21 is moved rightward in FIG. 24 by an external force, the transmission roller 21c moves in a direction away from the interlocking protrusion 75g, so that the first X moving member 75 and the second X moving member 76 are moved. In any case, the moving force of the X stage 21 is not affected. In other words, even if the X stage 21 moves in either the forward or reverse direction by an external force or the like with the X-axis drive motor 170x stopped, an unreasonable force is applied to the screwed portion of the X drive nut 85x and the feed screw 171x. There is no.

  Further, when the Y stage 71 is moved downward in FIG. 24 by an external force other than the motor driving force, the pressing direction is a direction for separating the position restricting flanges 80a and 80b from the position restricting flanges 71c and 71d. The stage 71 can move alone while resisting the urging force of the tension coupling spring 81y. At this time, only the elastic tensile force by the tension coupling spring 81y acts on the Y moving member 80, and the Y stage 71 does not mechanically press the Y moving member 80. An excessive force is not applied to the Y drive nut 85y that is in contact with. In addition, when the Y stage 71 is moved upward in FIG. 24 by an external force, the Y moving member 80 is pressed upward by the contact relationship between the position restricting flanges 80a and 80b and the position restricting flanges 71c and 71d. This moving direction is a movement in a direction in which the nut abutting portion 80e moves away from the Y drive nut 85y, so that no moving force is applied to the Y drive nut 85y. In other words, even if the Y stage 71 moves in the forward or reverse direction due to an external force or the like with the Y-axis drive motor 170y stopped, an unreasonable force is applied to the threaded portion of the Y drive nut 85y and the feed screw 171y. There is no.

  As described above, in the image shake correction apparatus of the present embodiment, the X stage 21 and the Y stage 71 move unexpectedly due to an external force or the like when there is a movement failure of the X stage 21 or the Y stage 71 when the motor is driven. In any case, the moving force can be absorbed to prevent the drive mechanism from being damaged. In particular, since the load is not applied to the screwed portions of the drive nuts 85x and 85y and the feed screws 171x and 171y, the screw screwed portion is highly effective in preventing damage. Although the X stage 21 and the Y stage 71 can be driven with high accuracy by reducing the lead of the feed screws 171x and 171y, reducing the lead of the feed screw is disadvantageous in terms of strength. However, according to the configuration of the present embodiment, there is no possibility that a load is applied to the screwed portion, so that the leads of the feed screws 171x and 171y can be reduced.

  In this embodiment, the first X moving member 75 and the second X moving member 76, which are two moving bodies in the X axis direction, are coupled to each other so as to be relatively movable in the X axis direction by three sliding portions. . Specifically, each of the first X moving member 75 and the second X moving member 76 includes two first sliding portions including a pair of guide holes 75e and a pair of guide pins 76c fitted therein, and one guide. One second sliding portion including a hole 76d and one guide pin 75f fitted in the hole 76d is provided. The first sliding part (guide hole 75e and guide pin 76c) and the second sliding part (guide hole 76d and guide pin 75f) are positioned at both ends of the first X moving member 75 and the second X moving member 76. Thus, the positions are different from each other in the X-axis direction. By providing the first and second sliding portions at positions separated in the X-axis direction as described above, the first X moving member 75 and the first sliding member 75 can be compared with the structure in which the sliding portion is provided only at one position in the X-axis direction. The 2X moving member 76 can be supported and guided with high accuracy. Further, since the pair of guide holes 75e and the pair of guide pins 76c constituting the first sliding portion are provided at different positions in the Y-axis direction orthogonal to the X-axis, the first X movement with respect to the X-axis is performed. The collapse of the member 75 and the second X moving member 76 can be effectively prevented.

  As shown in FIG. 15, one (upper in the drawing) guide hole 75e-B of the pair of guide holes 75e is in the Y-axis direction compared to the other (lower in the drawing) guide hole 75e-A. It has a long hole. The guide hole 75e-A is a circular hole having substantially the same diameter as the guide pin 76c, and the guide hole 75e-A and the guide hole 75e-B have the same diameter (same width) in the direction parallel to the photographing optical axis Z1. . With this configuration, the guide hole 75e-B and the guide pin 76c fitted therein function as rotation restricting means, and relative rotation does not occur between the guide hole 75e-A and the guide pin 76c fitted therein. ing. In addition, by forming only the guide hole 75e-B in the Y-axis direction, even if there is a slight positional error in the Y-axis direction, the guide pins 75e-A and 75e corresponding to both the guide pins 76c, respectively. -Since it can be securely inserted into B, it is easy to assemble and can be slid smoothly without rattling.

  The guide pins 75f and 76c and the guide holes 75e and 76d constituting the sliding portion in the X-axis direction are integrally formed with the first X moving member 75 and the second X moving member 76, respectively. Therefore, the structure of the sliding part is simple and excellent in strength. In particular, the guide pins 75f and 76c and the guide holes 75e and 76d are formed in the position restricting flanges 75a, 75b, 76a and 76b of the first X moving member 75 and the second X moving member 76, respectively. That is, the position restricting flanges 75a, 75b, 76a, and 76b are a movement restricting portion that restricts the relative moving ends of the first X moving member 75 and the second X moving member 76, and guide pins 75f and 76c that are sliding portions and guide holes. It also serves as a formation region for 75e and 76d, and the structure can be simplified.

  Further, the tension coupling spring 81x is positioned between the guide hole 75e and the guide pin 76c as the first sliding part and the guide hole 76d and the guide pin 75f as the second sliding part in the X-axis direction. is doing. As described above, the relative movement accuracy of the first X moving member 75 and the second X moving member 76 can be improved by arranging the first sliding portion and the second sliding portion apart from each other in the X direction. However, by arranging the tension coupling spring 81x between the first sliding portion and the second sliding portion separated in the X-axis direction, the space efficiency can be further improved and the mechanism can be downsized. it can.

  Similarly to the first X moving member 75 and the second X moving member 76 which are two moving bodies in the X-axis direction, the Y stage 71 and the Y moving member 80 which are two moving bodies in the Y-axis direction are also provided at three positions. The moving parts are coupled to each other so as to be relatively movable in the Y-axis direction. Specifically, the Y stage 71 and the Y moving member 80 are provided with two first sliding portions including a pair of guide holes 80d and a pair of guide pins 71f fitted therein, and one guide hole 71e. One second sliding portion made of one guide pin 80c fitted to this is provided. The first sliding portion (guide hole 80d and guide pin 71f) and the second sliding portion (guide hole 71e and guide pin 80c) are located near the upper and lower ends of the Y stage 71 and the Y moving member 80. Thus, they are provided with different positions in the Y-axis direction. Thus, by providing the first and second sliding parts at positions separated in the Y-axis direction, the Y stage 71 and the Y-moving member are compared with the structure in which the sliding part is provided only at one place in the Y-axis direction. 80 can be supported and guided with high accuracy. Further, since the pair of guide holes 80d and the pair of guide pins 71f constituting the first sliding portion are provided in different positions in the X-axis direction orthogonal to the Y-axis, the Y stage 71 with respect to the Y-axis is provided. And the fall of the Y moving member 80 can be effectively prevented.

  Of the pair of guide holes 80d, one (the entire side shown in FIG. 16) guide hole 80d-B is longer in the X-axis direction than the other (right side) guide hole 80d-A. ing. The guide hole 80d-A is a circular hole having substantially the same diameter as the guide pin 71f, and the guide hole 80d-A and the guide hole 80d-B have the same diameter (same width) in the direction parallel to the photographing optical axis Z1. . With this configuration, the guide hole 80d-B and the guide pin 71f fitted therein function as rotation restricting means, and relative rotation does not occur between the guide hole 80d-A and the guide pin 71f fitted therein. ing. Note that by forming only the guide hole 80d-B in the X-axis direction, even if there is a slight positional error in the X-axis direction, both guide pins 71f are connected to the corresponding guide holes 80d-A, 80d. -Since it can be securely inserted into B, it is easy to assemble and can be slid smoothly without rattling.

  Further, the one guide hole 80d-A and the guide pin 71f fitted therein are positioned in the same straight line as the guide hole 71e and the guide pin 80c which are the second sliding portions in the Y-axis direction. In this manner, either one of the first sliding portions provided at two places and the second sliding portion provided at one place may be positioned on the same straight line in the relative sliding guide direction.

  The guide pins 71f and 80c and the guide holes 71e and 80d that constitute the sliding portion in the Y-axis direction are integrally formed with the Y stage 71 and the Y moving member 80, respectively. Therefore, the structure of the sliding part is simple and excellent in strength. In particular, the guide pins 71f and 80c and the guide holes 71e and 80d are formed on the Y stage 71 and the position regulating flanges 71c, 71d, 80a and 80b of the Y moving member 80, respectively. That is, the position restricting flanges 71c, 71d, 80a and 80b are a movement restricting portion for restricting the relative moving ends of the Y stage 71 and the Y moving member 80, and guide pins 71f and 80c which are sliding portions and guide holes 71e and 80d. The structure can be simplified, and the structure can be simplified.

  Further, the tension coupling spring 81y is positioned between the guide hole 80d and the guide pin 71f as the first sliding part and the guide hole 71e and the guide pin 80c as the second sliding part in the Y-axis direction. Has been. As described above, the relative movement accuracy between the Y stage 71 and the Y moving member 80 can be improved by arranging the first sliding portion and the second sliding portion apart from each other in the Y direction. By disposing the tension coupling spring 81y between the first sliding portion and the second sliding portion that are separated in the Y-axis direction, the space efficiency can be further improved and the mechanism can be miniaturized.

  26 to 28 show another embodiment of the shake correction unit IS. In FIG. 26 to FIG. 28, the same reference numerals are given to members common to the above embodiments. This other embodiment is different from the above embodiment only in that one end of the X stage biasing spring 87x is engaged with the Y stage 71 instead of the fixed holder 23. That is, the X stage biasing spring 87 x is stretched between the spring hooking protrusion 21 v of the X stage 21 and the spring hooking protrusion 71 w of the Y stage 71. In this aspect, the same effect as the first embodiment can be obtained.

  FIG. 29 shows still another embodiment of the shake correction unit IS. In FIG. 29, a sliding portion that couples the first X moving member 75 and the second X moving member 76 so as to be relatively movable in the X axis direction, and a Y stage 71 and the Y moving member 80 are joined so as to be relatively movable in the Y axis direction. The configuration of the sliding portion is different from that of the previous embodiment shown in FIG. Specifically, with respect to the first X moving member 75 and the second X moving member 76, one of the pair of sliding portions (first sliding portions) provided on the position regulating flanges 75a and 76a is as shown in FIG. The guide pin 76c and the guide hole 75e (75e-A) are the same as the guide pin 75j, and the other is a guide pin 75j protruding from the position restricting flange 75a in the direction opposite to the guide pin 76c, and the position restricting flange. The guide hole 76h is formed in 76a. The guide hole 76h is formed as a long (wide) hole in the Y-axis direction, like the guide hole 75e-B in the form of FIG. The sliding portions (second sliding portions) provided on the position restricting flanges 75b and 76b are guide pins 76i protruding from the position restricting flange 76b instead of the guide pins 75f and 76d in FIG. The guide hole 75k is formed in the position regulating flange 75b. As for the Y stage 71 and the Y moving member 80, one of the pair of sliding portions (first sliding portions) provided on the position restricting flanges 71d and 80b is the same as in FIG. 24, the guide pin 71f and the guide hole 80d. (80d-B). The other is a guide pin 80i projecting from the position restricting flange 80b in a direction opposite to the guide pin 71f, and the guide pin 80i formed on the position restricting flange 71d is slid. The guide hole 71j is movably fitted. The guide hole 71j is a circular hole having substantially the same diameter as the guide pin 80i, like the guide hole 80d-A in the form of FIG. Further, the sliding portions (second sliding portions) provided on the position regulating flanges 71c and 80a are guide pins 71i protruding from the position regulating flange 71c instead of the guide pins 80c and the guide holes 71e in FIG. The guide hole 80h is formed in the position regulating flange 80a.

  As can be seen from the form of FIG. 29, in the present invention, in which of the first and second moving bodies the pin and the hole constituting the sliding portion are provided, and in which direction the pin protrudes. The point can be arbitrarily set. For example, in FIG. 29, instead of the guide pin 76c, a pin similar to the guide pin 75j is provided in the first X moving member 75, and the guide hole into which this pin is fitted is replaced with the second X in place of the guide hole 75e (75e-A). It can also be provided on the moving member 76 side. Similarly, in FIG. 29, instead of the guide pin 71f, a pin similar to the guide pin 80i is provided in the Y moving member 80, and the guide hole into which this pin fits is replaced with the guide hole 80d (80d-B) by the Y stage. It may be provided on the 71 side.

  As mentioned above, although this invention was demonstrated based on illustration embodiment, this invention is not limited to this. For example, although the above embodiment is applied as an image shake correction apparatus for a digital camera, the image shake correction apparatus according to the present invention can be applied to various optical devices such as binoculars in addition to a camera.

  In the above embodiment, the CCD 60 is supported so as to be linearly movable in two directions of the X axis and the Y axis. However, the drive mode (drive direction) of the shake correction optical element is not limited to this. For example, the present invention can also be applied to an image shake correction apparatus that drives a shake correction optical element only in at least one of the X axis and the Y axis.

  In the embodiment, the image blur correction is performed by driving the CCD 60. However, the optical element that is driven at the time of image blur correction may be a lens group or the like.

  In the illustrated embodiment, the first X moving member 75 and the second X moving member 76, and the Y stage 71 and the Y moving member 80 are coupled to each other so as to be relatively movable. Are two places and the second sliding part is one place). As described above, by providing three sliding portions, a highly accurate operation can be performed at the time of image blur correction while having a small and simple structure. However, if there is enough space, it is possible to provide a total of four or more sliding parts by providing three or more first sliding parts or two or more second sliding parts. It is.

It is a front view of a digital camera provided with an image blur correction device to which the present invention is applied. It is a sectional side view in the imaging state of the digital camera. FIG. 2 is a side cross-sectional view of the digital camera in a lens barrel storage state. It is a perspective view of the zoom lens barrel in the stored state. It is a disassembled perspective view of a part of zoom lens barrel. It is a disassembled perspective view of a different part of a zoom lens barrel. It is a front perspective view of a shake correction unit constituting the image shake correction apparatus. It is a back perspective view of a shake correction unit. FIG. 9 is a rear perspective view of a shake correction unit having a different angle from FIG. 8. It is a disassembled perspective view of a shake correction unit. It is the disassembled perspective view which expanded and showed the fixed holder vicinity in a shake correction unit. It is a front perspective view of X stage. It is a back perspective view of X stage. It is a front perspective view which shows the decomposition | disassembly state of a 1st X moving member and a 2nd X moving member. It is a back perspective view showing the disassembly state and assembly state of the 1st X movement member and the 2nd X movement member. It is a front perspective view which shows the decomposition | disassembly state of a Y moving member and a Y stage. It is a back perspective view which shows the decomposition | disassembly state and assembly state of a Y moving member and a Y stage. It is a front perspective view of the state where the fixed holder is removed from the shake correction unit. It is the back perspective view. FIG. 4 is a front perspective view of a state in which a drive motor, a photo interrupter, and an urging spring are further removed from the shake correction unit. It is the back perspective view. It is a front perspective view of a state where the second X moving member and the Y moving member are further removed from the shake correction unit. It is the back perspective view. It is a figure which shows typically the structure of a shake correction unit. It is a block diagram which shows the main electric circuit structures of the digital camera of FIG. 1 thru | or FIG. It is a front perspective view which shows another embodiment of a shake correction unit. It is the back perspective view. It is a figure which shows typically the shake correction unit of another form of FIG.26 and FIG.27. It is a figure which shows typically the shake correction unit of a form further different from FIG. 24, FIG.

Explanation of symbols

8 Second group lens moving frame 10 Second group linear guide ring 11 Cam ring 12 Third feed cylinder 13 Second feed cylinder 14 Straight guide ring 15 First feed cylinder 18 Helicoid ring 20 LCD
21 X stage (holding member for shake correction optical element)
21a Guide hole 21b Guide groove 21c Transmission roller 21v Spring hook projection 22 Fixed ring 23 Fixed holder 23a Retraction cam projection 23bx 23by Motor bracket 23vx 23vy Spring hook projection 25 Low pass filter 28 Zoom gear 60 CCD (shake correction optical element)
71 Y stage (second moving body)
71a Guide hole 71b Guide groove 71c 71d Position restriction flange (movement restriction part)
71e Guide hole (second sliding part)
71f Guide pin (first sliding part)
71g 71v 71w Spring hooking protrusion 71h Position detection part 71i Guide pin (second sliding part)
71j Guide hole (first sliding part)
72 74 77 78 X guide rod 73 79 Y guide rod 75 First X moving member (second moving body)
75a 75b Position restriction flange (movement restriction part)
75c 75d Guide hole 75e (75e-A, 75e-B) Guide hole (first sliding part)
75f guide pin (second sliding part)
75g Interlocking protrusion 75h Spring hooking protrusion 75i Position detection part 75j Guide pin (first sliding part)
76k guide hole (second sliding part)
76 2nd X moving member (1st moving body)
76a 76b Position restriction flange (movement restriction part)
76c Guide pin (first sliding part)
76d guide hole (second sliding part)
76e Nut abutting portion 76f Straight groove 76g Spring hooking projection 76h Guide hole (first sliding portion)
75i guide pin (second sliding part)
80 Y moving member (first moving body)
80a 80b Position restriction flange (movement restriction part)
80c Guide pin (second sliding part)
80d (80d-A, 80d-B) Guide hole (first sliding part)
80e Nut contact portion 80f Straight groove 80g Spring hooking projection 80h Guide hole (second sliding portion)
80i guide pin (first sliding part)
81x 81y tension coupling spring (first biasing means)
85x X drive nut 85y Y drive nut 87x X stage biasing spring (second biasing means)
87y Y stage biasing spring (second biasing means)
89x 89y Nut biasing spring 100 Shutter unit 101 Main switch 102 Control circuit 103 104 Photo interrupter 105 X gyro sensor 106 Y gyro sensor 107 Shooting mode switch 170x X axis drive motor 170y Y axis drive motor 171x 171y Feed screw 200 Digital camera 201 Zoom lens barrel 202 Camera body IS Shake correction unit LG1 First lens group LG2 Second lens group LG3 Third lens group Z0 Lens barrel central axis Z1 Shooting optical axis

Claims (8)

Guide means for guiding the shake correction optical element to be movable in a direction perpendicular to the photographing optical axis, and drive means for moving the shake correction optical element along the guide means in accordance with the magnitude and direction of the shake applied to the optical system. In the image blur correction apparatus having
The driving means includes a first moving body that is moved in the guiding direction of the guiding means by a driving source, and a second movement that can transmit the moving force of the first moving body to the holding member of the shake correcting optical element. A body and mutual guide means for coupling the first movable body and the second movable body in a guide direction of the guide means so as to be relatively movable,
The mutual guiding means includes at least two first sliding portions provided at different positions in a direction orthogonal to the guiding direction of the guiding means, and guidance of the guiding means with respect to the two sliding portions. An image blur correction apparatus comprising: one second sliding portion provided at a different position in a direction. 2. The image blur correction apparatus according to claim 1, wherein each sliding portion includes a pin formed on one of the first moving body and the second moving body, and a hole formed on the other in which the pin is slidably fitted. An image blur correction device including a unit. 3. The image blur correction device according to claim 2, wherein the pin and the hole are formed integrally with the first moving body and the second moving body. 4. The image blur correction device according to claim 2, wherein a pair of holes constituting the two first sliding portions have different shapes. 5. The image blur correction device according to claim 1, wherein one of the two first sliding portions and the second sliding portion are the same straight line in the guiding direction of the guiding means. An image blur correction device located on a line. 6. The image blur correction apparatus according to claim 1, wherein the first moving body and the second moving body are provided on the first moving body and the second moving body and engaged with each other. , A first urging means for urging the first moving body and the second moving body in a direction in which the movement restricting portion engages, and the first urging means. Second urging means for urging the second moving body in a direction opposite to the means;
An image blur correction device in which the first urging means is provided between the first sliding portion and the second sliding portion. 7. The image blur correction device according to claim 6, wherein a pair of the movement restricting portions are provided on each of the first moving body and the second moving body so as to be separated from each other in the guiding direction of the guiding means. An image blur correction apparatus in which the first sliding portion is provided on one of the regulating portions, and the second sliding portion is provided on the other. The image shake correction apparatus according to any one of claims 1 to 7, wherein a plurality of guide means for guiding the shake correction optical element so as to be linearly movable in different directions on a plane perpendicular to the photographing optical axis, respectively. An image blur correction apparatus comprising a plurality of drive means for moving the shake correction optical element along the guide means, and each of the plurality of drive means including the first moving body and the second moving body.

Images