JP7286312B2 - vane drive - Google Patents

Description

The present invention relates to a blade drive device.

A vane driving device typified by a focal plane shutter used in a camera is incorporated inside the camera body, so it is necessary to have a size that satisfies the dimensional requirements of the camera body. In recent years, a so-called mirrorless camera has also appeared, and the camera body itself has been miniaturized. Further, in such a blade driving device, a device having a drive spring adjusting mechanism for adjusting the curtain speed has been proposed (for example, Patent Documents 1 and 2).

Japanese Patent No. 3359085 Japanese Patent No. 4948367

In the case of a mechanism for adjusting the drive spring by locking one end of the drive spring to the worm wheel and rotating the worm wheel with the worm as the drive spring adjustment mechanism, a load is applied to the worm wheel at the portion where the drive spring is locked. It takes. If the strength of the worm wheel as a whole is increased or the size of the worm wheel is increased on the basis of this load, the cost will increase, and the size reduction may not be sufficiently achieved.

In view of the above, according to the first invention,
a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
The thick portion has a first side surface on the locking portion side and a second side surface on the opposite side in the circumferential direction,
The second side surface is formed in a direction intersecting the tooth space,
There is provided a blade driving device characterized by:
According to the second invention,
a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
The thick portion includes a first thick portion on one side in the circumferential direction of the locking portion and a second thick portion on the other side,
The first thick portion has a first side surface on the locking portion side and a second side surface on the opposite side in the circumferential direction, and the second side surface extends in a direction intersecting the tooth space. is formed in
The second thick portion has a third side surface on the locking portion side and a fourth side surface on the opposite side in the circumferential direction, and the fourth side surface is formed along the tooth space. has been
There is provided a blade driving device characterized by :
According to the third invention,
a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
In the thick portion, one axial end of the worm wheel is wider in the circumferential direction than the other axial end.
There is provided a blade driving device characterized by :
According to the fourth invention,
a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The worm wheel has tooth grooves formed obliquely with respect to the axial direction of the worm wheel,
There is provided a blade driving device characterized by :
According to the fifth invention,
a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
a charging mechanism for charging the drive spring;
a cover member arranged to face the base member;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The charging mechanism includes a charging slider that moves in a predetermined direction between the base member and the cover member as the charging operation,
The worm is supported by the cover member,
the cover member has a bulging portion that avoids interference with the charge slider,
The bulging portion is formed so that the width gradually narrows in the predetermined direction,
There is provided a blade driving device characterized by :

According to the first to third aspects of the present invention, it is possible to improve the strength of the worm wheel at the engagement portion of the drive spring.

1 is a diagram showing the overall configuration of an imaging device according to an embodiment of the present invention; FIG. 1 is a perspective view of a shutter according to an embodiment of the invention; FIG. FIG. 3 is a perspective view showing an internal mechanism of the shutter of FIG. 2; FIG. 3 is a plan view showing the internal mechanism of the shutter of FIG. 2; FIG. 3 is an exploded perspective view of the shutter of FIG. 2; Explanatory drawing of a main plate. Explanatory drawing of a blade mechanism. Explanatory drawing of a blade mechanism. Explanatory drawing of a blade mechanism. Explanatory drawing of a drive mechanism. Explanatory drawing of a drive mechanism. FIG. 4 is an explanatory diagram of a driving member for the trailing curtain; FIG. 4 is a perspective view of a drive member for the front curtain; FIG. 4 is an exploded perspective view of a drive member for the front curtain; (A) and (B) are perspective views showing the structure around the worm wheel. (A) and (B) are perspective views showing the structure around the worm wheel. FIG. 3 is an exploded perspective view of the locking mechanism; The perspective view which looked at the locking lever and the control lever from two directions. Explanatory drawing of the support structure of a motor. Explanatory drawing of the support structure of a motor. (A) and (B) are perspective views of the periphery of the MG base plate. FIG. 4 is an explanatory diagram of a guide mechanism of a charge slider; FIG. 3 is a perspective view of a charge slider; FIG. 4 is a cross-sectional view taken along line III-III of FIG. 3; FIG. 4 is a sectional view taken along line IV-IV of FIG. 3; Explanatory drawing of a gear train etc. FIG. Explanatory drawing of a gear train etc. FIG. Explanatory drawing of a gear train etc. FIG. FIG. 4 is an explanatory diagram of the operation of the charging mechanism; FIG. 4 is an explanatory diagram of the operation of the charging mechanism; FIG. 4 is an explanatory diagram of the operation of the charging mechanism; Operation explanatory drawing of a bound suppression mechanism. Operation explanatory drawing of a bound suppression mechanism. (A) is a perspective view of the main plate, and (B) is a plan view of the main plate. FIG. 34(B) is a cross-sectional view taken along the line VV. FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2; FIG. 3 is an explanatory view of the operation of the shutter in FIG. 2;

Hereinafter, embodiments will be described in detail with reference to the accompanying drawings. It should be noted that the following embodiments do not limit the invention according to the claims, and not all combinations of features described in the embodiments are essential to the invention. Two or more of the features described in the embodiments may be combined arbitrarily. Also, the same or similar configurations are denoted by the same reference numerals, and redundant explanations are omitted.

<Imaging device>
FIG. 1 is a diagram showing the overall configuration of an imaging device 10 according to an embodiment of the invention. The imaging device 10 is, for example, a mirrorless camera. An imaging device 10 includes a lens unit 1 , a shutter 2 and an imaging device 3 . The lens unit 1 includes a lens group and its drive mechanism for forming an image of light from an object. The imaging element 3 is an element that photoelectrically converts an object image formed by the lens unit 1, and is, for example, a CMOS image sensor. The shutter 2 is a blade driving device that is arranged between the lens unit 1 and the imaging device 3 on the photographing optical axis 1a, and adjusts the exposure time and the like for the imaging device 3 by opening and closing a group of blades.

An analog image signal output from the imaging element 3 is converted into a digital image signal by an AFE (Analog Front End) 4 . A DSP (Digital Signal Processor) 5 performs various image processing, compression/expansion processing, and the like on the digital image signal output from the AFE 4 . A storage medium 5 a and a RAM 5 b are connected to the DSP 5 . The RAM 5b is used for temporarily storing image data, for example. The storage medium 5a is, for example, a memory card, and is used to store captured images. The display 6 is an electronic image display device such as a liquid crystal display (LCD), and displays captured images, various menu screens, and the like.

The CPU 7 controls the imaging device 10 as a whole. The CPU 7 outputs control signals based on the detection results of various sensors 7a to control various drive circuits 7b. The sensor 7a includes, for example, a sensor that detects the power supply voltage of the imaging device 10, a sensor that detects temperature, and various sensors provided in the lens unit 1 and the shutter 2. FIG. The drive circuit 7b includes, for example, a timing generator that supplies a drive signal to the imaging element 3, and a drive circuit for actuators provided in the lens unit 1, the shutter 2, and the like.

<Shutter>
The shutter 2 of this embodiment is a focal plane type shutter. The shutter 2 will be described with reference to FIG. 2 and subsequent figures. In each figure, arrows X, Y, and Z indicate directions orthogonal to each other, the Z direction is parallel to the photographing optical axis 1a, and the Y direction is parallel to the traveling direction of the blades. It should be noted that, in some drawings, constituent parts of the shutter 2 may be shown in a see-through manner or may be omitted.

<1. Overall configuration and layout>
The overall configuration of the shutter 2 and the layout of the mechanism will be described with reference to FIGS. 2 to 6. FIG. 2 is a perspective view of the shutter 2, FIGS. 3 and 4 are views showing the internal mechanism of the shutter 2, FIG. 5 is an exploded perspective view of the shutter 2, and FIG.

The shutter 2 is roughly divided into a blade portion 20 that exposes/shields subject light to the imaging element 3 and a mechanism portion 21 that operates the blades. The blade portion 20 has a rectangular shape that is thinner than the mechanism portion 21, and the shutter 2 has an L shape as a whole when viewed from the side (in the Y direction). The mechanical portion 21 has a rectangular parallelepiped shape having a thickness corresponding to the diameter of the motor 81 . Conversely, the thickness of the shutter 2 in the Z direction is approximately the diameter of the motor 81 at maximum. The accommodation space in the imaging device 10 is reduced by locating the mechanical part 21 on the side of the blade part 20 while reducing the installation space of the shutter 2 and the imaging device 3 in the optical axis direction by thinning the blade part 20. can be effectively utilized. In addition, the shutter 2 has a rectangular shape as a whole and has a compact configuration, which is advantageous for an imaging device with a narrow internal space such as a mirrorless camera.

The shutter 2 has a base plate 30, which is a plate-shaped base member, as a basic support, and each component is mounted on the base plate 30. As shown in FIG. The base plate 30 integrally has an opening forming portion 31 that constitutes the blade portion 20 and a mechanism support portion 32 that constitutes the mechanism portion 21, and is a member made of synthetic resin, for example. A plurality of shafts, such as a shaft 320 to be described later, are erected on the main plate 30. Unless otherwise specified, the axial direction of these shafts is the Z direction.

The aperture forming portion 31 is formed with an aperture 31a through which subject light passes. One side of the opening forming portion 31 is covered with a cover plate 33 , and a partition plate 34 is arranged between the opening forming portion 31 and the cover plate 33 . The cover plate 33 and the partition plate 34 are formed with an opening 33a and an opening 34a overlapping the opening 31a. The other side (subject side) of the opening forming portion 31 is also covered with the cover plate 36 . An opening 36a overlapping the opening 31a is also formed in the cover plate 36 to form an imaging opening. These openings 31a, 33a, 34a and 36a have a rectangular shape, the normal direction of which is the Z direction, and the plane direction of which is the X and Y directions. Subject light passes through the aperture 36a, the aperture 31a, the aperture 34a, and the aperture 33a in order to expose the imaging device 3. As shown in FIG. The optical axis of the aperture 36a, the aperture 31a, the aperture 34a and the aperture 33a is the imaging optical axis 1a.

The partition plate 34 divides the blade chamber between the opening forming part 31 and the cover plate 33 into two spaces in the Z direction into a space for the leading curtain and a space for the trailing curtain. The shutter 2 is provided with a blade mechanism 40 for the front curtain and a blade mechanism 50 for the rear curtain. Group 51 (rear blade) is accommodated. FIG. 4 shows a state in which the cover plate 33 and partition plate 34 are removed.

The mechanism unit 21 includes a drive mechanism 60 that drives the blade mechanisms 40 and 50, a locking mechanism 70 that can maintain the blade group 41 in an open state, a charge mechanism 80 that charges the drive mechanism 60, and the blade group 51 that bounces. A restraining mechanism 900 for restraining is arranged. Further, an MG base plate 35 that also serves as a cover member for covering these mechanisms, and a cover member 37 that covers the MG base plate 35 are provided. FIG. 3 shows a state in which the MG base plate 35 and the cover member 37 are removed. The MG base plate 35 and the cover member 37 prevent dust from entering the driving mechanism 60 , locking mechanism 70 , charging mechanism 80 and restraining mechanism 900 .

The charge mechanism 80 includes a motor 81 as its drive source, a charge slider 82 for the front curtain and a rear cam gear 855 for the rear curtain, which charge the drive mechanism 60 by the driving force of the motor 81, and further the motor 81. It includes a gear train 85 and the like that transmit driving force. In the case of this embodiment, the charging mechanism 80 includes the motor 81, but it is also possible to use a motor provided on the imaging device 10 side as the motor 81. FIG. In other words, the charging mechanism 80 may be a mechanism with its own motor, or may be a mechanism that does not have its own motor and receives driving force from another motor.

The motor 81 is arranged on the side of the opening 31a in the X direction so that its rotating shaft 81a is in the Y direction. In other words, it is arranged along one side of the peripheral edge of the rectangular opening 31a. In order to improve the operating speed of the shutter 2, a relatively high-output motor is required as the motor 81, but the size of the motor generally increases in proportion to the output. By arranging the motor 81 as in the present embodiment, when viewed in the Y direction, the body 81b of the motor 81 can be accommodated within the travel/storage range Yw (see FIG. 4) of the blade groups 41 and 51. A high-output motor can be arranged relatively compactly.

As another arrangement mode of the motor 81, for example, it is conceivable to arrange so that the rotating shaft 81a is in the Z direction. become longer. In addition, as another arrangement mode of the motor 81, it is conceivable to arrange the rotating shaft 81a in the X direction. In this case, the shutter 2 becomes longer in the X direction. In addition, since it is generally easier to secure a storage space on the left and right sides of the shutter than on the top and bottom of the shutter in a digital camera, if the motor 81 is arranged on the side of the opening 31a in the Y direction, it is disadvantageous in terms of accommodation for the imaging device 10. Sometimes. Although such other arrangement manners can be employed, the arrangement manner of the motor 81 in this embodiment is advantageous in achieving both high performance and miniaturization of the shutter 2 .

In this embodiment, the charge mechanism 80 moves the charge slider 82 in the direction (Y direction) intersecting the optical axis direction (Z direction) by the driving force of the motor 81 to move the charge slider 82 to the driving member 61 for the leading curtain. Perform charge operation. The charge slider 82 is a displacement member that is displaced for this charging operation. The driving force may be transmitted to the driving member 61 by a rotating member such as a cam. , the size of the shutter 2 can be reduced in the X direction as compared with the configuration in which the rotating member for charging is rotated. Further, the range of reciprocating movement of the charge slider 82 is within the travel/storage range Yw (see FIG. 4) of the blade groups 41 and 51, and the size of the shutter 2 is not increased in the Y direction.

The driving mechanism 60 drives the blade mechanisms 40 and 50 and receives charging operation by the charging mechanism 80 . For this reason, it is advantageous in terms of mechanism and miniaturization that the blade mechanisms 40 and 50 and the charge mechanism 80 are arranged adjacent to the drive mechanism 60 . In the case of this embodiment, the drive mechanism 60 is arranged in the region Xw (see FIG. 4) between the motor 81 and the opening 31 a , and the charge slider 82 is arranged between the motor 81 and the drive mechanism 60 . With such an arrangement, the drive mechanism 60 is arranged adjacent to the blade mechanisms 40 and 50 and the charge mechanism 80, which is advantageous in terms of mechanism. Moreover, since the rotation axis direction of the motor 81 and the movement direction of the charge slider 82 are both in the Y direction, each mechanism can be concentrated in a narrow area in the X direction, and the shutter 2 can be miniaturized.

In the case of this embodiment, a gear train 85 is arranged on one end side (rotation shaft 81a side) of the motor 81 in the Y direction, and a locking mechanism 70 is arranged on the other end side. By symmetrically arranging the locking mechanism 70 and the gear train 85 in the spaces on both sides of the body portion 81b of the motor 81 in the Y direction, the size of the shutter 2 in the Y direction can be reduced. A worm gear 81 c is provided on the rotary shaft 81 a of the motor 81 , and the worm gear 81 c meshes with the worm wheel 850 a of the gear 850 of the gear train 85 . At this portion, the rotation axis direction is changed from the Y direction (motor 81 side) to the Z direction (gear train 85 side). Since each gear of the gear train 85 has a rotation axis in the Z direction, the thickness of the mechanical portion 21 of the shutter 2 in the Z direction can be reduced.

<2. Blade mechanism>
The configuration of the blade mechanisms 40 and 50 will be described with reference to FIGS. 5, 6 and 7 to 9. FIG. 7 is an explanatory diagram of the blade mechanisms 40 and 50, and FIGS. 8 and 9 are explanatory diagrams of the blade mechanism 40. FIG. In FIG. 7, state ST1 indicates the state in which the blade group 41 is closed and the blade group 51 is in the open state, and state ST2 indicates the state in which the blade group 41 is in the open state and the blade group 51 is in the closed state. The open state is a state in which the opening 31a is not covered, and the closed state is a state in which the opening 31a is covered.

The blade mechanism 40 includes a group of blades 41, a main arm 42, a sub arm 43 and a spring 44, and constitutes a front curtain. The blade mechanism 50 includes a group of blades 51, a main arm 52, a sub arm 53 and a spring 54, and constitutes a rear curtain. In the case of this embodiment, the blade groups 41 and 51 are composed of blades 41a to 41d and 51a to 51d, respectively. However, the number of blades is not limited to four. Each blade is formed of, for example, a resin sheet (or a light-shielding material such as a metal plate or a composite material) coated with black paint. The blades 41a-41d are connected to the main arm 42 and the sub-arm 43 to form a parallel link mechanism with the Y direction as the running direction of the blades 41a-41d. The blades 51a-51d are connected to the main arm 52 and the sub-arm 53 to form a parallel link mechanism with the Y direction as the running direction of the blades 51a-51d.

As shown in FIG. 8, the main arm 42 has a shaft hole 42a and an engaging hole 42b. The shaft hole 42a and the engaging hole 42b are holes for mounting the main arm 42 on a driving member 61, which will be described later. The shaft 320 of the base plate 30 is inserted into the shaft hole 42a through the driving member 61, and the main arm 42 is rotatable about the shaft 320 together with the driving member 61. As shown in FIG.

The sub arm 43 has a shaft hole 43a. A shaft 324 of the base plate 30 is inserted into the shaft hole 43a, and the sub arm 43 is rotatable around the shaft 324. As shown in FIG. In this embodiment, the spring 44 (biasing spring) is a torsion coil spring through which the shaft 324 is inserted. The restoring force of the spring 44 urges an arm portion 610B, which will be described later, via the sub arm 43 in a direction to close the blade group 41 . As a result, rattling of the blade group 41 can be suppressed.

As another arrangement example of the spring 44, an elastic member corresponding to the spring 44 is provided between the arm portion 610B described later and the base plate 30 to bias the arm portion 610B in the direction to close the blade group 41. Configurations are also possible. Further, as another arrangement example of the spring 44, an elastic member corresponding to the spring 44 is provided between the body portion 610A and the arm portion 610B, which will be described later, and the arm portion 610B is attached in the direction in which the blade group 41 is closed. It is also possible to adopt a configuration that

In any configuration of the spring 44, the arm portion 610B may be urged in the rotating direction opposite to the rotating direction of the main body portion 610A by the driving spring 63A for the leading curtain, thereby closing the blade group 41. The arm portion 610B of the drive member 61 can be urged toward a travel start position, which will be described later. Then, the main body portion 610A can be urged toward the travel completion position by the driving spring 63A for the leading curtain.

FIG. 9 shows a state in which the drive member 61 is driven (rotated) by the charge slider 82 to rotate the main arm 42 and the sub arm 43, thereby closing the blade group 41. FIG. As will be described later, the charge slider 82 pushes the body portion 610A of the driving member 61, thereby bringing the body portion 610A into contact with the holding mechanism 66A. The arm portion 610B is rotated by the biasing force of the spring 44 so as to follow the motion. 9, the motor 81, the holding mechanism 66A, etc. are omitted.

The blade mechanism 50 has the same configuration as the blade mechanism 40 . The main plate 30 is provided with a shaft 321 and a shaft 325, the main arm 52 is provided with a shaft hole and an engagement hole (both not shown) corresponding to the shaft hole 42a and the engagement hole 42b of the main arm 42, and , the sub arm 53 is provided with a shaft hole (not shown) corresponding to the shaft hole 43 a of the sub arm 43 . The spring 54 is also attached to the base plate 30 in the same mounting manner as the spring 44 , and the spring 54 biases the blade group 51 in the direction of opening via the sub arm 53 . As a result, rattling of the blade group 51 can be suppressed.

<3. Drive Mechanism>
The drive mechanism 60 will be described mainly with reference to FIGS. 4 and 10 to 16. FIG. FIG. 10 is an explanatory diagram of the driving mechanism 60, and is a cross-sectional view taken along the line II of FIG. FIG. 11 is a partially exploded perspective view of the drive mechanism 60. FIG. FIG. 12 is an exploded perspective view of the trailing shutter drive member 62 viewed from two directions. FIG. 13 is a perspective view of the driving member 61 for the front curtain. FIG. 14 is an exploded perspective view of the driving member 61 for the front curtain. 15(A) to 16(B) are perspective views showing the structure around the worm wheel 64A.

The driving mechanism 60 includes a driving member 61, a driving spring 63A, a worm wheel 64A, a worm 65A, and a holding mechanism 66A as a mechanism for driving the blade mechanism 40, and a driving member 62 and a driving spring 63B as a mechanism for driving the blade mechanism 50. , a worm wheel 64B, a worm 65B and a holding mechanism 66B.

The drive member 62 shown in FIG. 12 includes a body member 620 , an armature 622 , a spring 623 and an armature shaft 624 . The body member 620 is, for example, a member made of synthetic resin. Body member 620 includes a tubular portion 620a extending in the Z direction. The shaft 321 of the base plate 30 is inserted through the cylindrical portion 620a shown in FIGS. The rotational position of the drive member 62 (body member 620) is detected by an optical sensor PI2 (see FIG. 2). The optical sensor PI2 is supported by the base plate 30 via the holder HD2 (see FIGS. 3 and 5) and the MG base plate 35. As shown in FIG.

12 is inserted through the shaft hole of the main arm 52 of the blade mechanism 50 (not shown, corresponding to the shaft hole 42a of the main arm 42 of the blade mechanism 40). The drive spring 63B is inserted through the opposite end of the tubular portion 620a. A worm wheel 64B is rotatably supported by a shaft 321 beyond the drive spring 63B.

Body member 620 includes a pin base 620c that projects in the Z direction. A cylindrical pin cover 621a made of metal is attached to the pin base 620c for the purpose of improving durability, and a driving pin 621 for the blade is formed. The drive pin 621 is inserted through an engagement hole (not shown. Corresponding to the engagement hole 42b of the main arm 42 of the blade mechanism 40) of the main arm 52 of the blade mechanism 50, and a guide groove formed in the base plate 30. 326B (FIG. 11). A cushioning member 326b such as rubber is provided at the moving end of the drive pin 621 in the guide groove 326B to cushion the impact when the drive pin 621 comes into contact with the peripheral wall of the guide groove 326B.

As shown in FIG. 11, the body member 620 includes an engaging portion 620b extending radially from the cylindrical portion 620a. The engaging portion 620b receives an input of an operation force from a cam provided on a rear cam gear 855 included in the charging mechanism 80 when the charging mechanism 80 performs a charging operation. In other words, the driving force of the motor 81 is transmitted. By this operating force, the driving member 62 rotates counterclockwise in FIG. 4 around the shaft 321, and the driving spring 63B is charged. In this embodiment, as shown in FIG. 12, the engaging portion 620b is composed of a shaft portion 620e erected on the body portion 620 and a rotating body (roller) 625 rotatably held on the shaft. By using the rotating body 625, the driving force can be smoothly transmitted as the rear cam gear 855 rotates.

Body member 620 also includes an armature support 620d. An armature 622 is attached by an armature shaft 624 via a spring 623 to the armature support portion 620d. The armature 622 is releasably held by the holding mechanism 66B by the magnetic force of the holding mechanism 66B.

The drive spring 63B is a torsion coil spring in this embodiment. The drive spring 63B is provided between the drive member 62 and the worm wheel 64B, and one end of the drive spring 63B is engaged with the drive member 62, and the other end thereof is engaged with the worm wheel 64B. there is A worm 65B that meshes with the worm wheel 64B is rotatably supported by the MG base plate 35 with its axial direction inclined at a predetermined angle from the Z direction. can be miniaturized in the XY plane direction. In this embodiment, the worm wheel 64B is also obliquely formed so that the worm 65B is inclined so that the angle formed with the Z direction is small. Details will be described later.

The worm 65B meshes with the worm wheel 64B, thereby fixing the rotational position of the worm wheel 64B. The charging operation causes the driving member 62 to rotate about the shaft 321 from the initial position to the charging position, but the worm wheel 64B is stationary due to engagement with the worm 65B. Therefore, the drive spring 63B is wound up and elastic energy for driving the blades is accumulated. The charged drive spring 63B exerts an urging force in the direction in which the blade group 51 is closed. The driving spring 63B and the spring 54 bias the blade group 51 in opposite directions, but the biasing force of the driving spring 63B is sufficiently stronger than that of the spring 54. As shown in FIG.

When the worm 65B is rotated by a screwdriver or the like, the phase of the worm wheel 64B in the rotational direction with respect to the shaft 321 changes. That is, the traveling speed (curtain speed) of the blade group 51 can be adjusted by adjusting the amount of elastic deformation of the drive spring 63B during charging and adjusting the biasing force thereof. The worm 65B must be rotated in order to adjust the curtain speed when the shutter 2 is completed. However, if the axis of the worm 65B faces the XY plane, the arrangement of the worm 65B is restricted. For example, in the completed state of the shutter 2, if the axial direction of the worm 65B is directed in the X direction, the motor will be an obstacle in the case of the motor 81 side, and the light beam will be blocked in the case of the opening 31a. It becomes difficult to operate the worm 65B with a screwdriver or the like. Inclining the axial direction of the worm 65B is also effective in terms of increasing the degree of freedom in design. In addition, it contributes to miniaturization of the shutter 2 in the Z direction by improving the degree of freedom in arranging other structures.

The holding mechanism 66B holds the drive member 62 at the charge position by magnetic force. FIG. 4 shows the drive member 62 held in the charging position. The holding mechanism 66B is an electromagnet including a yoke 66a and a coil 66b wound around the yoke 66a, and the yoke 66a is supported by the MG base plate 35. By energizing and de-energizing the coil 66b, the armature 622 is switched between adsorption and adsorption release. As a result, it is possible to switch between holding and releasing the driving member 62 at the charging position. Upon release, the driving member 62 is rotated clockwise by the biasing force of the driving spring 63B as shown in state ST2 in FIG. Group 51 runs to the closed state.

Next, a mechanism for driving the blade mechanism 40 will be described. The drive mechanism 60 includes a drive member 61, a drive spring 63A, a worm wheel 64A, a worm 65A, and a holding mechanism 66A as a mechanism for driving the blade mechanism 40. The mechanism for driving the blade mechanism 40 is basically the same as the mechanism for driving the blade mechanism 50, but the structure of the driving member 61 is different.

As shown in FIGS. 13 and 14, the driving member 61 includes a body member 610, an armature 612, a spring 613 and an armature shaft 614. As shown in FIG. The body member 610 has a two-member structure in which two rotating members, a body portion 610A and an arm portion 610B, are combined in the Z direction, and both are made of synthetic resin, for example. The body portion 610A includes a tubular portion 610a extending in the Z direction, and the arm portion 610B includes a tubular portion 610e coaxial with the tubular portion 610a through which the tubular portion a is inserted. The shaft 320 of the base plate 30 is inserted through the cylindrical portion 610a, and the body portion 610A and the arm portion 610B are independently rotatable around the shaft 320. As shown in FIG. A driving spring 63A is connected to the body portion 610A, and the blade group 41 is connected to the arm portion 610B.

The rotational position of the driving member 61 (arm portion 610B) is detected by an optical sensor PI1 (see FIGS. 2 and 3). The optical sensor PI1 is supported by the base plate 30 via the holder HD1 (see FIGS. 3 and 5) and the MG base plate 35. As shown in FIG.

The tubular portion 610e is inserted through the shaft hole 42a of the main arm 42 of the blade mechanism 40, and the tubular portion 610a is inserted through the drive spring 63A. The worm wheel 64A is arranged closer to the MG base plate 35 than the drive spring 63A and is rotatably supported by the shaft 320. As shown in FIG.

The arm portion 610B includes a pin base portion 610c protruding in the Z direction. A cylindrical pin cover 611a made of metal is attached to the pin base 610c for the purpose of improving durability, and a drive pin 611 for the blade is formed. The drive pin 611 is inserted through the engagement hole 42b of the main arm 42 of the blade mechanism 40 and moves within the guide groove 326A (see FIG. 6) formed in the main plate 30. As shown in FIG. A cushioning member 326a such as rubber is provided at the moving end of the drive pin 611 in the guide groove 326A to cushion the impact when the drive pin 611 comes into contact with the peripheral wall of the guide groove 326A.

Also, the arm portion 610B forms a cam portion 610i on its outer peripheral surface. The cam portion 610i is shaped so as to come into contact with a rib 744 of a locking lever 74, which will be described later.

The body portion 610A includes an engaging portion 610b extending radially from the tubular portion 610a. The engaging portion 610b receives an input of operation force from the charge slider 82 when the charging mechanism 80 performs a charging operation. In other words, the driving force of the motor 81 is transmitted. By this operating force, the body portion 610A rotates counterclockwise in FIG. 4 with the shaft 320 as the rotation center.

The body portion 610A also includes an armature support portion 610d. An armature 612 is attached to the armature support portion 610d by an armature shaft 614 via a spring 613. As shown in FIG. The armature 612 is releasably held by the holding mechanism 66A by the magnetic force of the holding mechanism 66A.

The drive spring 63A is a torsion coil spring in this embodiment. The drive spring 63A is provided between the main body portion 610A and the worm wheel 64A, and one end of the drive spring 63A is engaged with the main body portion 610A and the other end thereof is engaged with the worm wheel 64A. there is The worm 65A is rotatably supported by the MG base plate 35 with its axial direction inclined at a predetermined angle from the Z direction. It can be made smaller in any direction.

The worm 65A meshes with the worm wheel 64A, thereby fixing the rotational position of the worm wheel 64A. Due to the charging operation, the driving member 61 (main body portion 610A) rotates from the initial position to the charging position about the shaft 320, but the worm wheel 64A remains stationary due to its engagement with the worm 65A. Therefore, the drive spring 63A is wound up and elastic energy for driving the blades is accumulated. The charged drive spring 63A exerts an urging force in the direction in which the blade group 41 is in the open state. The driving spring 63A and the spring 44 bias the blade group 41 in opposite directions, but the biasing force of the driving spring 63A is sufficiently stronger than that of the spring 44. FIG.

The body portion 610A and the arm portion 610B are independently rotatable around the shaft 320, and the spring 44 is a biasing spring that biases the arm portion 610B counterclockwise via the sub arm 43. As shown in FIG. The arm portion 610B includes an engaging portion 610g that contacts the armature support portion 610d of the body portion 610A. Since the engagement portion 610g is pressed toward the armature support portion 610d by the biasing force of the spring 44, when the body portion 610A rotates clockwise due to the biasing force of the charged drive spring 63A, the arm portion 610B also moves toward the body portion 610A. are pushed and rotated integrally, and the blade group 41 travels in the open state.

In this embodiment, an engaging portion 610g is formed at the root portion of the pin base portion 610c. Since a load is applied to the pin base 610c, it is preferable that the root portion be a thick base. It can be made compact.

When the worm 65A is rotated by a screwdriver or the like, the phase of the worm wheel 64A in the rotation direction with respect to the shaft 320 changes. That is, the traveling speed (curtain speed) of the blade group 41 can be adjusted by adjusting the amount of elastic deformation of the drive spring 63A during charging and adjusting the biasing force thereof. The worm 65A must be rotated in order to adjust the shutter curtain speed when the shutter 2 is completed. For example, in the completed state of the shutter 2, if the axial direction of the worm 65A is in the X direction, the motor will be an obstacle in the case of the motor 81 side, and the light beam will be blocked in the case of the opening 31a. It becomes difficult to operate the worm 65A with a screwdriver or the like. Inclining the axial direction of the worm 65A is also effective in terms of increasing the degree of freedom in design. In addition, it contributes to miniaturization of the shutter 2 in the Z direction by improving the degree of freedom in arranging other structures.

The holding mechanism 66A holds the drive member 61 (main body portion 610A) at the charge position by magnetic holding force. State ST1 in FIG. 7 shows a state in which the drive member 61 is held at the charge position. The holding mechanism 66A is an electromagnet including a yoke 66a and a coil 66b wound around the yoke 66a, and the yoke 66a is supported by the MG base plate 35.

By energizing and interrupting the coil 66b, the armature 612 is switched between adsorption and adsorption release. As a result, it is possible to switch between holding and releasing the driving member 61 at the charging position, and by releasing the driving member 61, the biasing force of the driving spring 63A causes the driving member 61 to rotate clockwise as shown in state ST2 in FIG. Group 41 runs to the open state.

<Worm wheel>
The structure of the worm wheel 64A will be described with reference to FIGS. 15(A) to 16(B). The worm wheel 64B also has a similar structure.

The worm wheel 64A of this embodiment has a peripheral wall with gear teeth formed on the peripheral surface thereof, and a slit-shaped engaging portion 640 is formed in a part of the peripheral wall. The end of the drive spring 63A is locked by this locking portion 640. As shown in FIG. In this embodiment, the tooth trace direction or tooth groove direction of the gear is not parallel to the axial direction of the worm wheel 64A, but is inclined. By forming the tooth spaces obliquely in this manner, the inclination angle of the worm 65A with respect to the Z direction can be made smaller (closer to the Z direction).

With the demand for downsizing of the shutter 2, each mechanism member is getting smaller and thinner, but the biasing force of the drive spring 63A is not so weak as to correspond to the downsizing. In other words, it can be said that the load applied to the locking portion 640 of the worm wheel 64A that locks one end of the drive spring 63A is relatively increased due to the downsizing of the mechanism members responsible for each mechanism.

It is necessary to avoid deformation of the engaging portion 640 of the worm wheel 64A due to the force of the drive spring 63A. If the locking portion 640 is deformed, a stable spring force cannot be obtained, which affects exposure accuracy and the like. On the other hand, if the worm wheel 64A is made of a special material, the cost will increase, and if the overall size is increased, it will not be possible to meet the demand for miniaturization.

Therefore, in order to prevent this deformation while maintaining the size reduction, in the present embodiment, reinforcing portions 641A and 641B are formed on the circumferential wall of the worm wheel 64A at portions adjacent to the locking portion 640 in the circumferential direction. By partially forming the reinforcement portions 641A and 641B, the locking portion 640 can be reinforced within a necessary range, and an increase in the size and cost of the worm wheel 64A can be suppressed.

Of the reinforcing portions 641A and 641B, the reinforcing portion 641A bears the spring force when the drive spring 63A is charged. Therefore, although it is possible to employ a configuration in which the reinforcing portion 641B is not provided, the reinforcing performance of the locking portion 640 can be improved by providing the reinforcing portions 641A and 641B on both sides of the locking portion 640 in the circumferential direction.

The strength of the reinforcing parts 641A and 641B may be improved by changing the material, but this may complicate the manufacture of the worm wheel 64A. In the present embodiment, the thick portion is formed by increasing the thickness (thickness in the radial direction) of the peripheral wall of the worm wheel 64A, and the first thick portion provided on one side of the locking portion 640 in the circumferential direction. and a reinforcing portion 641B as a second thick portion provided on the other side. That is, a part of the gear tooth flank formed on the peripheral wall of the worm wheel 64A is rendered unusable as the gear tooth flank, and the tooth spaces are filled to ensure strength. The reinforcing portions 641A and 641B may be thicker than the tooth groove portion, but in this embodiment, the thickness is the same as or thicker than the tooth tip portion. Specifically, the reinforcing portion 641 is thicker than the tooth tip portion at one end (end portion 64a side) on the side of the drive spring 63A in the Z direction, and the other end (end portion 64b) on the side opposite to the drive spring 63A. side), the reinforcing portion 641 has substantially the same thickness as the tip portion.

In the case of this embodiment, the locking portion 640 is open on the side of the end portion 64a in the axial direction of the worm wheel 64A and closed on the side of the opposite end portion 64b. In terms of strength, the side of the end portion 64a tends to be weak. In the case of this embodiment, the widths of the reinforcing portions 641A and 641B in the circumferential direction are widened on the side of the end portion 64a, and have a triangular or trapezoidal shape in appearance. Thereby, the strength around the locking portion 640 can be increased on the side of the end portion 64a. The thickness (thickness in the radial direction) of the reinforcing portions 641A and 641B is also increased on the side of the end portion 64a. Thereby, the strength around the locking portion 640 can be increased on the side of the end portion 64a.

On the other hand, due to the formation of the reinforcing portions 641A and 641B, there are portions on the peripheral wall of the worm wheel 64A that cannot mesh with the worm 65A. In other words, if the rotatably supported worm wheel 64A rotates at 360 degrees, an angle at which the worm 65A cannot be meshed with the worm 65A is generated by the loss of the tooth surface of the gear to increase strength.

In this embodiment, the reinforcing portion 641A is formed close to the worm 65A in order to minimize the angle at which meshing cannot occur, in other words, so that the reinforcing portion 641A can effectively escape from the worm 65A. Specifically, the reinforcing portion 641A has a side surface 641a' on the locking portion 640 side and a side surface 641a on the opposite side in the circumferential direction. The side surface 641 a ′ forms the inner side surface of the locking portion 640 .

A side surface 641a on the worm 65A side is formed in a direction that intersects the tooth spaces of the worm wheel 64A. As a result, the side surface 641a becomes closer to the axial direction of the worm wheel 64A, and the range of interference between the reinforcing portion 641A and the worm 65A can be reduced. By inclining the side surface 641a along the axial direction of the worm 65A, the range of interference between the reinforcing portion 641A and the worm 65A can be further reduced. By matching the inclination angle of the side surface 641a and the worm 65A, it is possible to maintain a compact size, withstand the load of the drive spring 63A, and secure an angle that allows meshing with the worm 65A as much as possible. In this respect as well, tilting the worm 65A is effective.

On the other hand, the reinforcing portion 641B far from the worm 65A has a side surface 641b' on the locking portion 640 side and a side surface 641b on the opposite side in the circumferential direction. The side surface 641b is formed along the tooth space. This has molding advantages. That is, when the worm wheel 64A is made of resin and is manufactured by molding such as injection molding, when the worm wheel 64A is ejected from the mold, the worm wheel 64A rotates around its axis because the tooth spaces are oblique. discharged while At this time, since the side surface 641b is formed along the tooth groove, the reinforcing portion 641B does not interfere with the ejection of the worm wheel 64A.

<4. Locking Mechanism and Bound Suppressing Mechanism>
The locking mechanism 70 and the bounce suppression mechanism of the blade group 41 will be described. First, the locking mechanism 70 and the bounce suppression mechanism of the blade group 41 will be described mainly with reference to FIGS. 17 and 18. FIG. FIG. 17 is an exploded perspective view of the locking mechanism 70. FIG. FIG. 18 is a perspective view of the locking lever and the restraining lever viewed from two directions.

The locking mechanism 70 is a mechanism capable of maintaining the blade group 41 in the open state while maintaining the body portion 610A at the charging position. As described above, in this embodiment, the main body portion 610A and the arm portion 610B are independently rotatable around the shaft 320. As shown in FIG. When the driving member 61 is moved to the charging position by the charging operation, the locking mechanism 70 locks the arm portion 610B so that the main body portion 610A moves to the charging position while the arm portion 610B is held at the initial position. and the opening 31a can be kept open until just before the shutter is released. When the locking of the arm portion 610B by the locking mechanism 70 is released, the biasing force of the spring 44 also rotates the arm portion 610B to the traveling start position, and the blade group 41 is closed. The arm portion 610B stops at the travel start position by coming into contact with the body portion 610A held at the charge position.

The locking mechanism 70 includes a base member 71 , a cover member 72 , an actuator 73 and a locking lever 74 . A restraining lever 75 is engaged with the locking lever 74 . The base member 71 is a member that supports the actuator 73 , and the cover member 72 is a member that covers the actuator 73 . The base member 71 is attached to the base plate 30 .

The actuator 73 is a rotary solenoid type actuator in this embodiment and includes a rotor 730 and an electromagnet 731 . The rotor 730 includes a cylindrical permanent magnet 730a and an arm member 730b attached to the permanent magnet 730a. A drive pin 730c is integrally provided at the end of the arm member 730b. The electromagnet 731 includes a yoke 731a and a coil 731b wound around the yoke 731a. Yoke 731a includes a C-shaped portion into which rotor 730 is inserted. When the coil 731b is energized, the rotor 730 rotates around the axis in the Z direction. The rotating direction of the rotor 730 can be switched by switching the energization direction of the coil 731b.

The locking lever 74 includes a shaft hole 742 through which a shaft 323a (see FIG. 6) provided on the base plate 30 is inserted, and is rotatably supported by the shaft 323a. An engaging portion 740 that engages with a drive pin 730 c of the rotor 730 is formed at one end of the locking lever 74 . In this embodiment, the engaging portion 740 has a C shape. A locking portion 741 is formed at the other end of the locking lever 74 . The locking portion 741 has an L-shaped cross section and engages with the engaging portion 610f of the arm portion 610B of the driving member 61 to lock the arm portion 610B. A pin-shaped connecting portion 743 is formed on the back side of the engaging portion 741 .

A rib 744 is provided on one end face of the cylindrical portion around the shaft hole 742 of the locking lever 74 . The rib has a C-shaped shape in which a part of the cylinder is notched. The notched part has a relief shape for the driving member 61 , and the rib 744 has a shape that abuts on the driving member 61 .

The suppression lever 75 includes a shaft hole 751 through which a shaft 323b (see FIG. 6) provided on the base plate 30 is inserted, and is rotatably supported by the shaft 323b. A connecting portion 750 that engages with the connecting portion 743 of the locking lever 74 is formed at one end of the restraining lever 75 . In this embodiment, the connecting portion 750 has a C shape. A locking portion 752 is formed at the other end of the restraining lever 75 . The locking portion 752 engages with the engaging portion 610h of the arm portion 610B of the driving member 61 to suppress the bounding of the arm portion 610B, that is, the bounding of the blade group 41 .

Operations of the locking mechanism 70 and the restraining lever 75 will be described with reference to FIG. This figure is an explanatory view of the operation of the shutter 2. As shown in FIG. State ST31 indicates the case where rotor 730 is at the locked position, and state ST32 indicates the case where rotor 730 is at the released position. The energization of the coil 731b is basically set to end when the rotor 730 rotates to the locking position or the releasing position.

When the rotor 730 is at the locking position, the locking portion 741 can be engaged with the engaging portion 610f of the arm portion 610B of the driving member 61. As shown in FIG. In the state ST31, the body portion 610A is located at the charge position, but the arm portion 610B is locked at the initial position by the locking lever 74. As shown in FIG. Therefore, the blade group 41 is in an open state.

When the rotor 730 rotates from the locking position to the releasing position, the locking lever 74 rotates clockwise about the shaft 323a to release the engagement between the locking portion 741 and the engaging portion 610f. Then, the arm portion 610B is rotated to the traveling start position by the biasing force of the spring 44, and the blade group 41 is closed.

The restraining lever 75 rotates in the opposite direction to the locking lever 74 in conjunction with the locking lever 74 . That is, while the locking lever 74 rotates and transitions from the locked state (state ST31) in which the rotor 730 is in the locked position to the released state (state ST32) in which the rotor 730 is in the released position, the shaft It rotates counterclockwise around the hole 751 (shaft 323b).

When the rotor 730 is at the release position, as shown in state ST32, the locking portion 752 moves to the engaging position where it can engage with the engaging portion 610h of the arm portion 610B. This engagement suppresses bouncing of the blade group 41 in the direction from the closed state to the open state. That is, after the blade group 41 changes from the open state to the closed state by the biasing force of the spring 44, the bouncing toward the open state side is suppressed.

When the rotor 730 rotates from the release position to the locking position, the restraining lever 75 rotates the shaft 323b clockwise to move to the releasing position where the engagement between the locking portion 752 and the engaging portion 610h is released. do. As a result, the blade group 41 can be moved from the closed state to the open state by the biasing force of the drive spring 63A. The engaging portion 752 is formed so that its tip is positioned on the locus of movement when the body portion 610A moves to the charging position at the engaging position. A curved surface is formed on the contact surface of the locking portion 752 with the engaging portion 610h so that the locking portion 752 can be smoothly pushed away by the engaging portion 610h of the arm portion 610B at that time.

<5. Charge mechanism>
The charging mechanism 80 will be explained. First, the support structure of the motor 81 by the base plate 30 will be described mainly with reference to FIGS. 19 and 20. FIG. 19 and 20 are explanatory diagrams of the support structure of the motor 81, FIG. 19 is an exploded perspective view of the motor 81 and the main plate 30, and FIG. 20 is a cross-sectional view taken along line II-II of FIG.

The mechanism support portion 32 of the base plate 30 includes a motor support portion 328 that supports the motor 81 . The motor support portion 328 includes a recess 328a for receiving the body portion 81b of the motor 81, and a mounting portion 328b for fixing the body portion 81b. The mounting portion 328b protrudes in the Z direction from one Y-direction end of the recess 328a and is integrally formed with the base plate 30 . The mounting portion 328b has a mounting hole 328d for fixing the end portion of the body portion 81b of the motor 81, and a hole 328e through which the rotating shaft 81a of the motor 81 is inserted. Further, the mounting portion 328b is provided with a pin-shaped engaging portion 328f that engages with a hole formed in the end surface of the body portion 81b to restrict the rotation of the body portion 81b.

The motor 81 is arranged on the recess 328a and fixed to the mounting portion 328b. When the surface 30a around the recessed portion 328a of the opening forming portion 31 and the mechanism supporting portion 32 is used as a reference (see line L1 in FIG. 20), the motor 81 is partially embedded in the main plate 30 in the Z direction. there is As for the degree of burying, in the case of this embodiment, when viewed in the arrangement direction (X direction) of the opening 31a and the motor 81, the body portion 81b and the opening 31a overlap. In FIG. 17, it is understood that the opening 31a is located between the lines L1 and L2 and overlaps the trunk portion 81b. With this arrangement, even if a large, high-output motor is used as the motor 81, the thickness of the shutter 2 in the Z direction can be made thinner, and the size of the shutter 2 can be reduced. If the weight of the motor 81 is heavy, or if the imaging device 10 is accidentally dropped, the motor 81 may fall off the motor support portion 328. It can prevent falling off.

The thickness of the recessed portion 328a is constant, and the recessed portion 328a is recessed from the periphery of the surface 30a of the base plate 30, while the surface 30b of the opening forming portion 31 and the mechanism support portion 32 around the recessed portion 328a is recessed from the periphery of the recessed portion 328a on the opposite surface 30b side. (see line L2 in FIG. 17), it protrudes from its surroundings in a convex shape. By making the thickness of the base plate 30 substantially constant regardless of the location, the weight increase can be suppressed. For example, wasted space can be reduced by providing the cover plate 36 within the range in the Z direction where the concave portion 328a protrudes.

The recessed portion 328a extends in the Y direction, and its cross-sectional shape in the X direction has an arc shape that matches the cylindrical body portion 81b of the motor 81. As shown in FIG. Since the concave portion 328a has a curved shell shape, the weight can be reduced and the rigidity of the motor support portion 328 can be improved. In addition, since the recessed portion 328a has a shape that follows the outer shape of the body portion 81b, it is possible to reduce gaps that are wasted spaces and to enhance the function of the motor 81 as a fall-off prevention wall. The peripheral surface of the trunk portion 81b may be in contact with or slightly separated from the bottom surface of the recess 328a. The heat dissipation of the motor 81 can be improved.

As shown in FIG. 19, a motor terminal 81d is provided on the other end side of the motor 81 in the Y direction. When the motor 81 is manufactured, the motor terminal 81d is crimped while adjusting the phase between the motor terminal 81d and the motor 81. Therefore, the motor terminal 81d may rotate and be fixed with a variation of about 20 degrees around the output shaft. . On the other hand, when the motor 81 is mounted, if the terminals of the motor 81 are oriented in the positive direction of the Z-axis and the X-axis, workability can be improved. Therefore, in the present embodiment, the motor terminal member 81e is attached so as to contact the motor terminal 81d and face the terminal in the positive direction of the X axis.

That is, the motor terminal member 81e is attached to the other end side of the motor 81 so that the electrode portion 81g provided along the curved surface formed on the side surface of the motor terminal member 81e is in contact with the motor terminal 81d. It is provided so as to face the axial positive direction. Since the electrode portion 81g has a predetermined length along the circumferential direction of the body portion 81b of the motor 81, even if the motor terminals 81d vary as described above, they can be reliably brought into contact with each other. The terminal 81f can be easily fixed so as to face the positive direction of the X-axis.

The motor terminal member 81 e is positioned by fitting a hole formed in its center into a projection provided on the other end side of the motor 81 . In addition, a flat portion is provided at the end of the motor terminal member 81e on the negative side of the X axis, and a flat portion for positioning provided on a fixing jig for fixing the motor terminal member 81e to the motor 81 is provided. By abutting against the surface, the mounting angle of the motor terminal member 81e with respect to the motor 81 can be adjusted to an appropriate position.

In this embodiment, the motor support portion 328 is provided integrally with the main plate 30, but the motor support portion 328 may be a separate member from the main plate 30. For example, the motor support portion 328 may be provided on the imaging device 10 side. and a structure in which the motor 81 is provided can also be adopted.

Next, between the opening 31a and the motor 81, there are arranged mechanisms related to the operation of the blade groups 41 and 51, such as the mechanism of the drive mechanism 60, the mechanism of the charge mechanism 80 other than the motor 81, and the bounce suppression mechanism 900. there is Mechanisms related to the operation of the blade groups 41 and 51 and the body portion 81b are densely arranged in the X direction to reduce the size of the shutter 2 in the X direction.

The MG base plate 35 also functions as a cover member that covers a gap between the body portion 81 b and the mechanism involved in the operation of the blade groups 41 and 51 . In FIG. 20, the end of the MG base plate 35 protrudes toward the body portion 81b from the line L3, covering the gap between the body portion 81b and the upper portion of the charge slider . This can prevent dust from entering the mechanism through the gap.

A line L4 indicates the height (distance in the Z direction) of the MG base plate 35 from the base plate 30 excluding the bulging portion 35b described later. It is arranged at a position lower than 81b. Further, the bulging portion 35b protrudes from the outer peripheral surface of the body portion 81b at a position deviated from the end point of the body portion 81b in the X direction indicated by the line L3, so that the size in the X direction can be reduced.

A region above the MG base plate 35 can be utilized as a region for arranging the flexible substrate 38 . That is, various mechanisms, the flexible substrate 38, and the like can be accommodated within the width of the body portion 81b in the Z direction, and the size of the shutter 2 in the Z direction can be reduced. The flexible substrate 38 can include wiring for the sensor provided in the shutter 2 and wiring for energizing the coil. In particular, electric parts such as capacitors arranged on the flexible board 38 are arranged on the Z-axis positive direction side of the flexible board 38, and the electric parts arranged on the flexible board 38 are avoided by providing a cover member 37, which will be described later. The cover member 37 can be provided while suppressing the thickness in the Z direction.

An L-shaped cover member 37 is provided on the opening 31a side of the MG base plate 35 . The cover member 37 can prevent dust from entering the driving mechanism 60 in the Z direction and the X direction. The shape of the MG base plate 35 and the shape for preventing dust from entering will be described with reference to FIGS. 21(A) and 21(B). 21(A) and 21(B) are perspective views of the periphery of the MG base plate 35, in which the position of the charge slider 82 is different.

It is desirable to position the MG base plate 35 as close to the base plate 30 as possible, but to prevent dust from entering from above the charge slider 82 . Therefore, as described above, the MG base plate 35 has a part of its shape that is used as a cover member that also serves as the arrangement area 35a of the flexible substrate 38. The bulging portion 35b is formed so as to cover the upper surface of the charge slider 82, which has different heights.

Here, in this embodiment, the inclined worms 65A, 65B are arranged between the charge slider 82 and the corresponding worm wheels 64A, 65A for the purpose of miniaturization. More specifically, the worms 65A and 65B have their axial directions contained in the ZY plane, and when viewed in the Z direction,
The worms 65A, 65B extend in the Y direction and are arranged so as to overlap the corresponding drive members 61, 62 (see also FIG. 10). Such arrangement of the worms 65A and 65B contributes to miniaturization of the shutter 2 in the Z direction and in the X direction.

On the other hand, as shown in FIG. 21, the worms 65A, 65B are rotatably held by worm holding portions 35c, 35c of the MG base plate 35 formed by die-cutting and bending. If the rigidity of the worm holding portions 35c, 35c is weak, there is a possibility that the worms 65A, 65B will be disengaged from the worm wheels 64A, 64B due to dropping or vibration, and the elastic energy of the drive springs 63A, 63B will be released. There is

In the case of the present embodiment, the bulging portion 35b bulges in the Z direction by bending the plate that is the raw material of the MG base plate 35. When viewed in the Z direction, the width in the X direction gradually changes in the Y direction, with a wider width on the gear train 85 side (worm 65B side) and a narrower width on the opposite side (worm 65A side). It is said that In other words, it has a wedge shape or a triangular or trapezoidal shape.

If the bulging portion 35b has a simple stepped shape with a uniform width in the X direction along the Y direction, the bulging portion 35b is formed in a wide belt shape in order to avoid the operating range of the charge slider 82. As a result, it becomes difficult to form the worm holding portions 35c, 35c. Further, when the MG base plate 35 is processed by sheet metal, there is a possibility that the shape of the connecting portion 351 of the worm holding portions 35c, 35c cannot be expanded and cut.

In order to increase the rigidity of the worm holding portions 35c, 35c, there is a method of increasing the thickness of the material of the MG base plate 35 itself or selecting a highly rigid material, but increasing the thickness is disadvantageous for miniaturization. , there is a limit to changing to a material with high rigidity. In that case, the rigidity will be secured by the shape and processing method. For example, if the MG base plate 35 is subjected to a drawing process to form the swelling portion 35b, the joint portion 351 will also remain, and the purpose can be achieved.

Therefore, in the present embodiment, the bulging portion 35b is formed by bending a part of the MG base plate 35 along a straight line obliquely inclined from the Y-axis direction. By doing so, the bulging portion 35b can be created by a relatively simple straight bending process, and the area of the bulging portion 35b itself can be reduced to widen the arrangement region 35a, thereby increasing the worm connection. The shape of the portion 351 can also be ensured without interruption, and the rigidity of the worm portion can also be ensured.

The configuration of the charging mechanism 80 other than the motor 81 will be described mainly with reference to FIGS. 4 and 22 to 28. FIG. 22 is an explanatory view of the charge slider guide mechanism, FIG. 23 is a perspective view of the charge slider 82, FIGS. 24 to 26 are structural explanatory views of the charge mechanism 80, and FIG. 24 is a sectional view taken along line III-III in FIG. , and FIG. 25 is a cross-sectional view taken along line IV--IV of FIG. 26 to 28 are explanatory diagrams of the gear train 85 and the like.

The charge mechanism 80 is a mechanism that charges the drive springs 63A and 63B with respect to the drive mechanism 60 using the motor 81 as a drive source. The charge mechanism 80 includes a charge slider 82 for operating the drive mechanism 60, a cam gear 854 for the front curtain (front cam gear 854), a cam gear 855 for the rear curtain (rear cam gear 855), and a guide shaft 83 for guiding the movement of the charge slider 82. and 84, a gear train 85 for transmitting the driving force of the motor 81 to the front cam gear 854 and the rear cam gear 855, and a coil spring 86 for urging the charge slider 82 to the initial position.

The charge mechanism 80 includes a mechanism for charging the drive spring 63A, a mechanism for charging the drive spring 63B, and a common mechanism. Common mechanisms are motor 81 and gear train 85 . A mechanism for charging the drive spring 63A includes a front cam gear 854, a charge slider 82, guide shafts 83 and 84, and the like. The gear train 85 and the front cam gear 854 are transmission mechanisms that transmit driving force to the charge slider 82 . A rear cam gear 855 is a mechanism for charging the drive spring 63B. In this embodiment, the charging operation of the drive spring 63A is performed by a linear motion method using the linear reciprocating motion of the charge slider 82, and the charging operation of the drive spring 63B is performed by a rotating method using the rotating motion of the rear cam gear 855. .

The guide shafts 83 and 84 both extend in the Y direction and are spaced apart from each other in the Z direction. The guide shaft 84 is arranged farther from the main plate 30 than the guide shaft 83 is. The base plate 30 includes a pair of support portions 329 that support both ends of the guide shaft 84 . The support portion 329 is a columnar member erected in the Z direction and formed integrally with the base plate 30 . The length of the guide shaft 83 in the Y direction is shorter than that of the guide shaft 84, one end of which is supported by one of the pair of support portions 329, and the other end of which is different from the support portion 329 provided on the main plate 30. Supported by a support. These supports are provided with support holes into which respective ends of guide shafts 83 and 84 are fitted. The support holes into which the ends of the guide shaft 83 are fitted may be elongated holes in the Z direction. Thereby, for example, manufacturing errors can be absorbed.

The charge slider 82 includes a pair of insertion portions (here, holes) 820a through which the guide shaft 84 is inserted, and a pair of insertion portions (here, long holes) 820b through which the guide shaft 83 is inserted. The hole 820a and the elongated hole 820b are engaging portions for engaging the guide shafts 84, 83 and the charge slider 82. As shown in FIG. The hole 820a is a circular closed hole, and the hole 820b is a closed hole with a straight line in part. The linear movement of the charge slider 82 in the Y direction is guided by the guide shaft 84 passing through the pair of holes 820a. By inserting the guide shaft 83 through the pair of elongated holes 820b, the swinging of the charge slider 82 around the guide shaft 84 is restricted (rotation prevention). The pair of long holes 820b can also be notches depending on the arrangement of surrounding parts.

When two guide shafts are used to guide the movement of the charge slider 82 as in this embodiment, if the distance between the two guide shafts is fixed, the operation of the charge slider 82 is hindered due to manufacturing errors and the like. Therefore, as described above, the support hole of one of the guide shafts is elongated to reduce the influence of manufacturing errors. On the other hand, although the operating force for moving the charge slider 82 is input from the input portion 821, the input portion 821 that receives the operating force moves in the X direction, which reduces the accuracy of the straight movement of the charge slider 82. , the support hole of the guide shaft 84 adjacent to the input portion 821 is used as a hole to prevent displacement of the guide shaft 84 at the support portion.

By arranging the pair of holes 820a and the pair of elongated holes 820b apart from each other in the Y direction, the charge slider 82 can be made smaller and the friction during sliding can be reduced compared to a configuration in which continuous holes or elongated holes are provided. can be achieved. Furthermore, since the set of the pair of elongated holes 820b and the guide shaft 83 and the set of the pair of holes 820a and the guide shaft 84 are spaced apart in the Z direction, the shutter is more sensitive than the structure in which these are spaced apart in the X direction. 2 can be made smaller in the X direction.

The charge slider 82 includes a body portion 820 , an engaging portion 821 , an operating portion 822 and a restraining operating portion 824 . The body portion 820 is integrally formed of synthetic resin, for example, and includes portions forming the holes 820a and the elongated holes 820b described above. The hole 820a and the elongated hole 820b are spaced forward from the engaging portion 821 when viewed in the moving direction during the charging operation.

As shown in FIG. 24, the body portion 820 is arranged adjacent to the body portion 81b of the motor 81 and has a concave portion 82a recessed in the X direction so as to avoid the body portion 81b. The concave portion 82a is formed by slanting the portion forming the hole 820a and the elongated hole 820b toward the trunk portion 81b. In the case of this embodiment, the Z-direction central portion of the body portion 820 and the Z-direction central portion of the body portion 81 b are at substantially the same height when viewed from the surface 30 a of the base plate 30 .

For this reason, the central portion in the Z direction of the main body portion 820 is moved toward the opening 31a in the X direction, and both ends (that is, the portions forming the holes 820a and the elongated holes 820b) are moved toward the motor 81 in the X direction. , the charge slider 82 is arranged close to the motor 81 without interfering with it.

As shown in FIG. 24, the side surface of the charge slider 82 on the side of the motor 81 has a curved surface shape (arcuate surface shape) generally along an imaginary circle C1 coaxial with the body portion 81b. With such arrangement, it is possible to reduce the size of the shutter 2 in the X direction. In this embodiment, the guide shafts 83 and 84 are positioned closer to the opening 31a than the line L3, but at least one of them may be partially positioned closer to the motor 81 than the line L3. be. This makes it possible to further reduce the size of the shutter 2 in the X direction.

Also, the charge slider 82 is positioned within the range of the width (diameter) W1 of the body portion 81b of the motor 81 in the Z direction. The thickness of the shutter 2 in the Z direction can be kept substantially within the diameter of the motor 81, and the thickness of the shutter 2 can be reduced.

A coil spring 86 is provided between the base plate 30 and the body portion 820, and biases the charge slider 82 to the initial position. The guide shaft 83 passes through the coil spring 86 and also functions as a support shaft for the coil spring 86 . By using the guide shaft 83 both to guide the movement of the charge slider 82 and to support the coil spring 86, the number of parts can be reduced. Thus, the charge slider 82 moves forward by the front cam gear 854 and moves back by the biasing force due to the compression of the coil spring 86 .

The engaging portion 821 is an input portion (pressed portion) to which the driving force of the motor 81 is input via the gear train 85 and the front cam gear 854, and in the case of this embodiment, is rotatable around the axis in the Z direction. is a metal roller supported by the main body portion 820. The engaging portion 821 is arranged so as to partially overlap the guide shafts 83 and 84 in the Z direction. The engaging portion 821 is supported by the main body portion 820 via a dedicated holder 823. The main body portion 820 has only a pivotal support. It is also possible to regulate movement (dropping) to This reduces the number of parts in that the holder 823 is not required. Note that the engaging portion 821 is detachable from the main body portion 820 . It is also possible to adjust the movement stroke of the charge slider 82 by selectively using rollers with different diameters as the rollers serving as the engaging portion 821 .

Here, a virtual plane VS shown in FIG. 24 is a reference plane on the XY plane including the opening 31a of the base plate 30. As shown in FIG. In this embodiment, the distance H1 indicates the distance from the virtual plane VS to the end point of the engaging portion 821 on the main plate 30 side, and the distance H2 indicates the distance from the virtual plane VS to the end point of the guide shaft 84 on the engaging portion 821 side. is shown.

There is a relationship of H1>H2, and the engaging portion 821 is arranged at a position farther from the virtual plane VS than the guide shaft 84 is. Therefore, the space on the virtual plane VS side of the guide shaft 84 in the Z direction can be used as a space for arranging other components. In this embodiment, the rear cam gear 855 is arranged closer to the virtual plane VS than the guide shaft 84 is. A part of the rear cam gear 855 is laid out in this space so that it can enter during the rotational movement, and the rear cam gear 855 overlaps the guide shaft 84 in the Z direction during the rotational movement. By using the space between the guide shaft 84 and the base plate 30 as a space for arranging mechanical parts in this way, the size of the shutter 2 can be reduced in the Y direction, for example. Further, the guide shaft 83 is arranged closer to the virtual plane VS than the rear cam gear 855 , and in the case of this embodiment, the space between the guide shafts 83 and 84 is used as an operating space for the rear cam gear 855 . ing.

Next, the operation part 822 is a part of the drive mechanism 60 that operates the drive member 61. In the case of this embodiment, the operation part 822 is a metal roller supported by the main body part 820 so as to be rotatable around the axis in the Z direction. be. As with the engaging portion 821, the operating portion 822 is also arranged so as to partially overlap the guide shafts 83 and 84 in the Z direction. The engaging portion 821 and the operating portion 822 are portions that transmit the driving force of the motor 81, and by making them metal, the durability of the mechanism can be improved. Further, by arranging the engaging portion 821 and the operating portion 822 so as to overlap the guide shafts 83 and 84, it is possible to reduce the size of the entire unit in the XY directions.

While the engaging portion 821 is positioned farther from the virtual plane VS than the guide shaft 84 , the operating portion 822 is arranged closer to the virtual plane VS than the guide shaft 84 . As a result, the distance between the operating portion 822 and the rear cam gear 855 with respect to the virtual plane VS can be substantially the same, and the driving members 61 and 62 can be moved while the front cam gear 854 and the rear cam gear 855 are arranged at different positions in the Z direction. They can be arranged at approximately the same position in the Z direction.

In addition, although one engaging portion 821 is provided in this embodiment, the number may be two or three or more. The operation part 822 is also the same.

Rear cam gear 855 operates drive member 62 of drive mechanism 60 . The rear cam gear includes a cam portion 855a that operates the driving member 62 and a gear portion 855b that receives force from the gear train 85, and is an integrally molded synthetic resin member, for example.

The front cam gear 854 and the rear cam gear 855 each receive a force input from the gear train 85 connected from the motor 81, the front cam gear 854 operates the driving member 61 through the charge slider 82, and the rear cam gear 855 operates the driving member 62, The driving members 61 and 62 that have received the operating force rotate to charge their respective driving springs 63A and 63B.

In this embodiment, the driving member 61 is operated by the front cam gear 854 positioned farther from the virtual plane VS than the guide shaft 84, and the driving member 61 is operated by the rear cam gear 855 positioned closer to the virtual plane VS than the guide shaft 84. 62 is operated, but not limited to this, the drive member 62 is operated by a cam gear positioned far from the virtual plane VS with respect to the guide shaft 84, and driven by a cam gear positioned closer to the virtual plane VS than the guide shaft 84. It may be configured to operate the member 61 .

Gear train 85 includes gears 850-854. The main plate 30 includes Z-direction shafts 327a to 327c and 322 that rotatably support them (see FIG. 6, etc.). As shown in FIG. 27, the gear 850 comprises a worm wheel 850a and a spur gear 850b on a shaft 327a which rotate together. The worm wheel 850a meshes with the worm gear 81c attached to the rotary shaft 81a of the motor 81. As shown in FIG. Here, by changing the rotation axis direction of the driving force transmission system from the X direction to the Z direction, the thickness of the shutter 2 in the Z direction can be reduced even if the diameters of the gears 850 to 854 are large.

Gear 851 includes spur gears 851a, 851b and 851c on shaft 327b, which rotate together. The spur gear 851 a meshes with the spur gear 850 b , the spur gear 851 b meshes with the spur gear 852 described later, and the spur gear 851 c meshes with the rear cam gear 855 . As described above, charging mechanism 80 includes a charging mechanism for charging drive spring 63A and a mechanism common to the charging mechanism for charging drive spring 63B, specifically motor 81 and gear train 85. is. In particular, the motor 81 is a common drive source, and the gears 850 and 851 are common drive gears.

The gear 852 is a spur gear provided on the shaft 327c and is connected to the gear 853 so as to rotate integrally with the gear 852 on the same shaft. The front cam gear 854 is a rotating member that includes a gear portion 854b and a cam portion 854a, and these are supported on the shaft 322 so as to be integrally rotatable. The rear cam gear 855 has a gear portion 855b and a cam portion 854a, and is a rotating member supported on the same shaft 322 as the front cam gear 854 so as to be rotatable together.

The rear cam gear is arranged on the root side of the shaft 322 and the front cam gear is arranged on the tip side of the shaft 322 . In this embodiment, the gear 852, the gear 853, the front cam gear 854, and the rear cam gear 855 have a speed reduction ratio of one. A detected member 852a is also provided on the shaft 327c. The detected member 852a rotates integrally with the gear 852. As shown in FIG. The rotational position of the detected member 852a is detected by an optical sensor PI3 (only its arrangement is shown in FIG. 4). The rotational position of the gear 852 is detected by detecting the rotational position of the detected member 852a.

In the case of the present embodiment, the speed reduction ratios of the gear 852, the gear 853, the front cam gear 854, and the rear cam gear 855 are all 1. Therefore, the detected result of the rotational position of the member 852a to be detected is not converted by the speed reduction ratio. It can be used as the rotational position of the cam gear 854 and the rear cam gear 855 .

It is also possible to provide sensors that directly detect the rotational positions of the front cam gear 854 and the rear cam gear 855 . However, in this embodiment, due to the layout of the mechanism, it is difficult to secure a sensor arrangement space around each cam gear. Therefore, the rotational position of each cam gear is detected via the member 852a to be detected that rotates synchronously with each cam gear.

The Z-direction position of the detected member 852a is within the range of the Z-direction thickness of the body portion 81b of the motor 81 . This contributes to downsizing of the shutter 2 in the Z direction.

The front cam gear 854 is a member that inputs the driving force of the motor 81 to the charge slider 82 . The front cam gear 854 includes a cam portion 854 a that contacts the engaging portion 821 . In the case of this embodiment, the engaging portion 821 of the main body portion 820 linearly moves the charge slider 82 in the Y direction by being pressed by the contact of the cam portion 854a.

The rear cam gear 855 is a member that inputs driving force to the driving member 62 of the driving mechanism 60 . The rear cam gear 855 includes a cam surface 855a that contacts the engagement portion 620b of the drive member 62. As shown in FIG. In the case of this embodiment, the driving member 61 of the driving mechanism 60 performs charging operation by the operating portion of the charge slider 82 that receives driving force input from the front cam gear 854 , and the driving member 62 receives the driving force from the rear cam gear 855 . It receives the input directly and performs the charge operation.

As described above, in this embodiment, the front cam gear 854 for inputting the driving force to the charge slider 82 for operating the driving member 61 and the rear cam gear 855 for inputting the driving force for operating the driving member 62 are arranged on the same axis. In other words, the space for providing the input section for inputting each driving force is overlapped in the Z direction, so that the space can be saved.

These gears 850 to 855 are finally regulated in the Z direction by incorporating the MG base plate 35 at the tip of each rotating shaft. However, during the assembly process until the MG base plate 35 is assembled, there is a possibility that the parts may come off due to an accidental accident and come apart. Therefore, in this embodiment, in order to avoid such an accident, a regulation functioning as a safety measure for assembly is provided separately from the MG base plate 35. FIG. Specifically, a gear 852 , a gear 851 , and a gear 850 are partially overlapped in this order, and the charge slider 82 is partially overlapped with the tip of the rotation shaft of the gear 853 . Also, the end of the guide shaft 84 is arranged so as to overlap with the gear train 85 (especially the gears 850 and 851) in the Z direction.

By configuring in this manner, it becomes possible to regulate the Z-direction of the constituent gears of the gear train 85 by the guide shaft 84 and the charge slider 82 when the guide shaft 84 is incorporated. The incorporated gears 850 to 855 are not easily removed, and management of the assembling process is simple. In addition, by arranging the guide shaft 84 and the charge slider 82 so as to hold down these gear groups, in other words, by arranging them so as to weave through the gaps between the gears, they contribute to downsizing of the shutter 2 as a whole. In this embodiment, since it is difficult to regulate the spur gear 851 in the Z direction with the MG base plate 35, a separate gear cover member is arranged. Consideration is given so that the shutter 2 does not become large.

29 to 31 are explanatory diagrams of the operation of the charging mechanism 80, showing examples of the charging operation of the charging mechanism 80 with respect to the drive mechanism 60. FIG. State ST21 shows the stage at which the cam portion 854a of the front cam gear 854 begins to contact the engaging portion 821 of the charge slider 82. FIG. At this time, the cam portion 855a of the rear cam gear 855 is not in contact with the engaging portion 620b of the driving member 62 yet. Both the drive members 61 and 62 of the drive mechanism 60 are located at their initial positions.

State ST22 indicates a state in which the rotation of the front cam gear 854 and the rear cam gear 855 has progressed. The cam portion 854a presses the engaging portion 821 in the Y direction, thereby moving the charge slider 82 in the Y direction. At least at the stage of state ST22, the leading cam gear 854 overlaps the guide shaft 84 in the Z direction.

The operation portion 822 operates the driving member 61 by moving the charge slider 82 . Specifically, the operating portion 822 contacts the engaging portion 610b of the driving member 61 and presses it in the Y direction. This causes the driving member 61 to rotate counterclockwise. In state ST23, the cam portion 855a of the rear cam gear 855 is in contact with the engagement portion 620b of the drive member 62, and the drive member 61 is almost completely charged at this time. In state ST24, the cam portion 855a presses the engaging portion 620b, and the driving member 62 rotates counterclockwise. 29 to 31, the arm portion 610B is not locked by the locking mechanism 70, and the body portion 610A and the arm portion 610B of the drive member 61 are integrally rotated.

State ST25 indicates a state in which the front cam gear 854 and the rear cam gear 855 are further rotated. The engaging portion 821 continues to be pushed by the cam portion 854a of the leading cam gear 854, and the engaging portion 821 is in contact with the cam top of the cam portion 854a. Further, the cam portion 855a of the rear cam gear 855 continues to press the engaging portion 620b, and the engaging portion 620b rides on the cam top of the cam portion 855a. As a result, the operating portion 822 of the charge slider 82 rotates the driving member 61, the rear cam gear 855 rotates the driving member 62, and the driving members 61 and 62 reach the charging position.

After that, the drive members 61 and 62 are held at the charge position by driving the holding mechanisms 66A and 66B. As the rotation of the front cam gear 854 and the rear cam gear 855 further progresses, the contact between the cam portion 854a and the engaging portion 821, and the contact between the cam portion 855a and the engaging portion 620b is also dissolved, and the charge slider 82 becomes a coil spring. The drive mechanism 60 is returned to the initial position by the biasing force of 86, and the drive mechanism 60 is attracted and held by the respective holding mechanisms as in state ST26. At least at the stage of state ST26, the rear cam gear 855 overlaps the guide shaft 84 in the Z direction. In this embodiment, the reciprocating range of the charge slider 82 is within the total length YM of the motor 81 in the axial direction. As a result, the size of the shutter 2 in the Y direction can be reduced.

<Charging timing>
In order to improve continuous shooting performance, it is important to complete the charging operation in a short time after the exposure operation. To this end, it is advantageous in terms of shortening the time to charge the front curtain and the rear curtain at the same time. It may affect the captured image. In this embodiment, the gap between the front curtain and the rear curtain is prevented during the charging operation.

Referring again to FIGS. 29 to 31, regarding the engagement timing of the operation portion 822 and the rear cam gear 855 with the corresponding engagement portions 610b and 620b and the amount of rotation of the drive members 61 and 62 in the charge operation. explain.

As the charge slider 82 moves downward in the figure, first, as shown in state ST21, the peripheral surface of the operating portion 822 comes into contact with the corresponding engaging portion 610b to engage them. At this stage, the rear cam gear 855 and the corresponding engaging portion 620b are not engaged. That is, in the case of this embodiment, the engagement between the operating portion 822 and the engaging portion 610b is configured to occur earlier than the engagement between the rear cam gear 855 and the engaging portion 620b. This timing adjustment is realized by changing the contact timing of the cam portion 854a and the cam portion 855a at the initial position and the position of the operation portion 822 in the Y direction.

As the charge slider 82 moves while the operating portion 822 and the engaging portion 610b are engaged, the driving member 61 rotates counterclockwise in the figure. As a result, the blade group 41 forming the front curtain begins to shift to the closed state before the blade group 51 forming the rear curtain starts shifting to the open state. Therefore, the end portions of the blade group 41 and the blade group 51 can be reliably overlapped, and the occurrence of a gap can be prevented.

As the charge slider 82 moves further, as shown in state ST23, the cam portion 855a of the rear cam gear 855 comes into contact with the corresponding engaging portion 620b to engage them. As a result, the driving member 62 also begins to rotate counterclockwise in FIG. At this time, the blade group 41 is already just before the end of charging.

As the movement of the charge slider 82 and the rotation of the rear cam gear 855 progress further, the drive members 61 and 62 reach the charge position as shown in state ST25. At this stage, the blade group 41 forming the front curtain is in the closed state, and the blade group 51 forming the rear curtain is in the open state.

<6. Bound Suppression Mechanism>
Next, the trailing curtain bounce suppression mechanism 900 will be described with reference to FIGS. 32 and 33. FIG. 32 and 33 are explanatory diagrams of the operation of the bound suppression mechanism 900. FIG.

If the impact of the exposure operation of the driving member 62 (running operation of the blade group 51) cannot be appropriately mitigated, the blade group 51 causes re-exposure (rear curtain bound) as the driving member 62 rebounds after completing the exposure operation. will do. In order to suppress the bouncing of the blade group 51, a trailing curtain bounce suppression mechanism 900 is provided in the present embodiment.

The trailing curtain bounce suppression mechanism 900 is a mechanism for suppressing the bounce of the driving member 62 that operates the blade group 51 in order to suppress the bounce of the blade group 51 . include. The lock lever 910 and the reversing lever 920 are arranged adjacent to the charge slider 82 and the driving member 62. The lock lever 910 is attached to the lock shaft 33b erected on the cover plate 33 in the Z direction. 920 are rotatably supported by reversing shafts 33c erected on the cover plate 33 in the Z direction.

Both the lock lever 910 and the reversing lever 920 are arranged between the driving member 61 and the driving member 62 in the Y direction.

The lock lever 910 is a restraining member that can be displaced between a restraining position that restrains the bouncing of the blade group 51 via the driving member 62 and a retracted position that releases restraint. Displacement is rotation. The lock lever 910 can be displaced from the restraint position to the retracted position by operation via the reversing lever 920 by the restraint operation portion 824 provided on the charge slider 82 . That is, the displacement of the charge slider 82 during the charge operation is used to operate the lock lever 910 to release the suppression of rotation of the driving member 62 .

In the state immediately before the exposure operation, the restraining portion 910a provided on the lock lever 910 enters the operating locus of the driving member 62 as in the state ST71 of FIG. During the exposure operation, the blade group 51 is once pushed out of the operating locus of the driving member 62 by the rotation of the driving member 62 that moves the blade group 51 to the closed state (state ST72). 33, when the driving member 62 rotates to the vicinity of the travel completion position of the blade group 51, the urging force of the lock spring 930 causes the driving member 62 to enter the operating locus again. That is, the lock spring 930 is a restraining elastic member that biases the lock lever 910 to the restraining position. Thereafter, even if the driving member 62 bounces back, the restraining portion 910a of the lock lever 910 engages with the pin base portion 620c, which is the restrained portion provided on the driving member 62, and the bounce is restrained.

During charging, it is necessary to retract the lock lever 910 before the driving member 62 is charged. The engaged portion 920a of 920 is engaged. As the reversing lever 920 is rotated counterclockwise around the reversing shaft 33 c , the pushing portion 920 b of the reversing lever 920 contacts the pressed portion 910 a of the lock lever 910 . As the rotation of the reversing lever 920 continues, the lock lever 910 is rotated clockwise about the lock shaft 33 b , and the restraining portion 910 a retreats from the movement locus of the driving member 62 . After that, charging of the driving member 62 is started. The retracted lock lever 910 returns from the retracted position to the restrained position by the urging force of the lock spring 930 at the timing when the charge slider 82 retracts from the operation locus of the driving member 61 at the start of the release operation, and returns to the state ST71.

By operating the lock lever 910 and the reversing lever 920 that suppress the bounce of the drive mechanism 62 using the charge slider 82, which is a member that is not directly interlocked with the drive member 62 as in the present embodiment, both suppression and retraction are stabilized. Therefore, it is possible to configure the bounce suppression mechanism 900 that operates reliably.

Furthermore, by using the charge slider 82, which is a member for charging the leading curtain side, which is different from the rear cam gear 855 for charging the driving member 62, the driving member 62 can be restrained or retracted, and charging timing of the leading and trailing curtains can be controlled. , the number of items that must be considered for operation and phase is reduced, and the degree of freedom in design is increased. That is, the driving member 62 can be reliably restrained or retracted in accordance with the charge timing.

In the present embodiment, the charge mechanism on the front curtain side is of a linear motion type, and therefore the bounce suppression mechanism 900 is operated by the charge slider 82 that moves linearly. In that case, the bound suppressing mechanism 900 may be operated by a driving member for the front curtain that rotates.

<7. Deflection regulation of the guide shaft>
When the pair of support portions 329 that support the guide shaft 84 are separated from each other, the intermediate portion of the guide shaft 84 is likely to bend. A driving force from the front cam gear 854 acts on the guide shaft 84 via the charge slider 82 for each charge operation. The guide shaft 84 may bend toward the motor 81 side due to repeated application of the driving force. Also, the user may accidentally drop the imaging device 10 . In this case as well, the guide shaft 84 may be bent due to the impact.

If the guide shaft 84 is plastically deformed in a bent state, it becomes a factor that hinders the smooth operation of the charge slider 82 . Therefore, the present embodiment has a structure for restricting the deflection of the guide shaft 84 . 34A is a perspective view of part of the main plate 30, and FIG. 34B is a plan view of the main plate 30. FIG. FIG. 35 is a cross-sectional view taken along the line VV of FIG. 34(B) (however, the figure is rotated so that the main plate 30 is located on the lower side of the drawing.

The base plate 30 is provided with two restricting portions 30e and 30f that restrict the deflection of the guide shaft 84. As shown in FIG. The regulating portions 30e and 30f may be separate members from the base plate 30, but in the case of the present embodiment, they are formed integrally with the base plate 30, and particularly at one end in the X direction of the mounting portion 328b to which the motor 81 is mounted. integrally formed.

Both of the restricting portions 30 e and 30 f are arranged in a section between the pair of supporting portions 329 and are arranged so as to face the peripheral surface of the guide shaft 84 . The restricting portions 30e and 30f may be in contact with the peripheral surface of the guide shaft 84, but may have a minute gap (for example, about 0.1 to 0.3 mm) between them and the peripheral surface of the guide shaft 84. .

The restricting portion 30e restricts the guide shaft 84 from bending in the X direction. In the case of this embodiment, when viewed in the X direction, the front cam gear 854 is arranged on one side of the guide shaft 84, and the restricting portion 30e is arranged on the other side of the opposite side. In other words, the restricting portion 30e comes into contact with the peripheral surface of the guide shaft 84 when the guide shaft 84 is about to bend in the X direction due to the drive force acting on the guide shaft 84 from the front cam gear 854 via the charge slider 82. are arranged to suppress this deflection.

The restricting portion 30 e is arranged within the movement section of the charge slider 82 , but is arranged at a position where it does not interfere with the charge slider 82 . Specifically, the restricting portion 30e comes closest to the charge slider 82 when the charge slider 82 is at the initial position when the charge operation is started, as shown in state ST71 and the like in FIG. At this time, the restricting portion 30e does not interfere with the engaging portion 821 because it is positioned below the engaging portion 821 as shown in FIG. When the charge slider 82 is in the illustrated position, the regulating portion 30e is arranged at a position overlapping the charge slider 82 in the Z direction, which contributes to downsizing of the shutter 2. FIG. In addition, in order to prevent the operation of the charge slider 82 from being hindered by the restricting portion 30e, the position of the body portion 820 of the charge slider 82 when the charging operation is started is on the positive Y-axis side and the negative Z-axis position of the engaging portion 821 is set. Regulating portions 30e and 30f are provided so as to be positioned on the direction side.

From the viewpoint of preventing deflection of the guide shaft 84 due to the driving force of the leading cam gear 854, the restricting portion 30e is arranged on the X-direction component line of the driving force from the leading cam gear 854 to the charge slider 82 during the charging operation. It is effective to be However, in the case of this embodiment, as the charge slider 82 moves, the position of the component force line in the X direction of the driving force from the front cam gear 854 to the charge slider 82 changes. Considering these points, in the case of the present embodiment, the restricting portion 30e is a section between the engaging portion 821 and the insertion portion 820a on the side closer to the engaging portion 821 at the start of the charging operation (see FIG. 32). It is arranged so as to face the peripheral surface of the guide shaft 84 in the section SC of the state ST71.

The restricting portion 30f restricts the guide shaft 84 from bending in the Z direction. In the present embodiment, the restricting portion 30f is formed continuously with the restricting portion 30e, but may be formed at a different site. The restricting portion 30 f is also arranged at a position overlapping the charge slider 82 in the Z direction, which contributes to the size reduction of the shutter 2 . When viewed in the Z direction, the restricting portion 30f is positioned closer to the base plate 30 than the guide shaft 84, so that it does not interfere with the charge slider 82. As shown in FIG.

In this embodiment, the restricting portions 30e and 30f are provided integrally with the mounting portion 328b that fixes the body portion 81b of the motor 81. As shown in FIG. With this configuration, the end portion of the mounting portion 828b that fixes the motor 81 can be used to regulate the deflection of the guide shaft 84. This eliminates the need to provide a separate regulation portion, thereby saving space. can be done.

<8. Overall operation example>
An example of the overall operation of the shutter 2 will be described with reference to FIGS. 36 to 43. FIG. 36 to 38 are explanatory diagrams of the operation of the shutter 2, and mainly show examples of the single shooting operation of the imaging device 10. FIG.

State ST31 in FIG. 36 shows a stage in which the shutter 2 is in a standby state. The shutter 2 can selectively select between normally open and normally closed as a standby state, but the case where normally open is selected is exemplified here. Both blade groups 41 and 51 are in an open state, and the opening 31a is open. Rotor 730 of locking mechanism 70 is positioned at the locking position, and arm portion 610B is locked at the initial position by locking lever 74 . The drive members 61, 62 are held in the charging position. In the locking mechanism 70, a state in which the rotor 730 is at the locking position is called a locked state.

When the shutter operation is detected and a control signal is output from the control unit of the imaging device 10, the lock mechanism 70 is driven and the rotor 730 rotates to the release position. As a result, the engagement between the arm portion 610B and the locking lever 74 is released, and the urging of the spring 44 causes the blade group 41 to once travel to the closed state as shown in state ST32.

As the rotor 730 is rotated to the release position, the suppression lever 75 engages with the engaging portion 610h of the arm portion 610B to suppress the bouncing of the blade group 41 as described above. In the locking mechanism 70, the state in which the rotor 730 is at the released position is called the released state. Simultaneously with the operation of the locking mechanism 70, the front cam gear 854 is rotated by driving the motor 81, and the contact between the cam portion 854b and the engaging portion 821 is released. back to

As a result, the engagement portion 610b of the drive mechanism 61 is released from contact with the operation portion 822, and the drive mechanism 61 moves from the overcharge position to the position held by the holding mechanism 66A by the biasing force of the drive spring 63A. Similarly, by driving the motor 81, the rear cam gear 855 rotates to release the contact between the cam portion 855b and the engaging portion 620b, and the driving mechanism 62 is held by the holding mechanism 66B from the overcharge position together with the blade group 51. position by the biasing force of the drive spring 63B.

Note that even if the restraint lever 75 once moves out of the operation locus of the arm portion 610B due to the rotation of the arm portion 610B, it will return to the operation locus of the arm portion 610B again because the locking mechanism is energized. to suppress the bounce of the arm portion 610B. When the arm portion 610B is restrained from bounding at the standby position, the restraining lever 75 has an inclined surface at its tip so that the restraining lever 75 is not disengaged even if the restraining lever 75 is urged by the bounding action of the arm portion 610B ( An urging force is applied to the inclined surface from the arm portion 610B in a direction to rotate the suppression lever 75 counterclockwise).

Subsequently, as shown in state ST33 of FIG. 37, locking mechanism 70 is driven to return rotor 730 to the locking position. As a result, the restraining lever 75 is moved out of the rotation locus described above.

Subsequently, as shown in state ST34, the holding of the driving member 61 by the holding mechanism 66A is released, the driving member 61 is rotated clockwise by the force of the driving spring 63A, and the blade group 41 travels to the open state. , the aperture 31a is opened, and the imaging device 3 is exposed. At this time, as the body portion 610A is rotated by the driving spring 63A, the engagement portion 610g of the arm portion 610B is pushed by the armature support portion 610d, and the body portion 610A and the arm portion 610B are rotated together. move.

Here, the relationship between the drive member 61 and the locking lever 74 will be described in detail with reference to FIGS. 39-41. As described above, when the drive member 61 is released from the holding mechanism 66A, the drive member 61 rotates clockwise due to the force of the drive spring 63A. gradually open.

At the locking position, the locking lever 74 is designed such that the tip of the locking lever 74 enters the travel locus of the arm portion 610B. Then, the contact surface 741 b of the engaging portion 610 f of the arm portion 610 B contacts the engaging portion 741 of the locking lever 74 .

As the driving member 61 further rotates, the engaging portion 610f pushes away the engaging portion 741 of the locking lever 74 as shown in state ST38. It passes to the left of junction 741 . The locking lever 74 has a curved contact surface 741b, which facilitates the depression by the engaging portion 610f.

The engaging portion 741 that has been pushed down receives a counterclockwise rotational force from the rotor 730. In the meantime, the rotation of the driving member 61 progresses further, and when the blade group 41 reaches the exposed travel completion position, as shown in FIG. As shown in the state ST39 of 40, the cam portion 610i on the outer peripheral surface of the arm portion 610B comes into contact with the rib 744 of the locking lever 74 and pushes. A surface of the rib 744 provided at a position where the cam portion 610i abuts serves as a pushed portion. The locking lever 74 rotates counterclockwise about the shaft hole 742 by the energy of the rotation of the driving member 61 . In this manner, locking lever 74 is rotated to the locked position by two forces, the biasing force of rotor 730 and the force of rotation of drive member 61 applied to rib 744 of the locking lever. Here, the position of the blade group 41 immediately after the opening 31a is fully opened is defined as the exposure travel completion position, but the exposure travel completion position is not necessarily limited to this. Also good.

As the driving member 61 further rotates, the driving pin 611 collides with the cushioning member 326a provided in the guide groove 326A, and the cushioning member 326a is crushed, so that the rotation of the driving member 61 is decelerated. During this time as well, the cam portion 610i on the outer peripheral surface of the drive member pushes the rib 744 of the locking lever to rotate the locking lever 74 clockwise, as in the state ST40 of FIG.

After the driving member 61 collides with the buffer member 326a, the driving member 61 rebounds (bounds) due to the repulsive force and starts rotating counterclockwise. When a bounce occurs and the drive member 61 rotates counterclockwise, as shown in state ST41 of FIG. It catches on 741a and restricts further rotation. This restricts the blade group 41 from entering the opening 31a of the base plate.

After that, the drive member 61 rotates clockwise again under the force of the drive spring 63A, and stably stops while contacting the buffer member 326a.

As described above, the counterclockwise rotational force of the rotor 730 and the rotational force generated by the contact of the cam portion 610i on the outer peripheral surface of the arm portion 610B with the rib 744 of the locking lever cause the locking lever 74 to move. Rotate counterclockwise. Therefore, the locking lever 74 can be rotated to the locking position before the driving member 61 bounces and rebounds to the locking position by the locking lever 74 without increasing the size of the locking mechanism 70 . . In this way, the locking lever 74 can suitably suppress the bouncing of the blade group 41 after the completion of the exposed travel.

Here, in general, the cushioning member 326a is easily deformed in a high-temperature environment, and is difficult to deform in a low-temperature environment. Therefore, even if the same impact force is applied, the drive member 61 is likely to be crushed at high temperatures and the amount of rotation of the drive member 61 at the time of collision is large, and at low temperatures the drive member 61 is not easily crushed and the amount of rotation of the drive member 61 at the time of collision is small. The stop angle is sensitive to temperature. In the present embodiment, as shown in state ST40 of FIG. 40, when the driving member 61 is largely rotated, the cam portion 610i on the outer peripheral surface and the rib 744 of the locking lever do not interfere with each other. That is, when the amount of rotation of the driving member 61 increases, (part of) the cam portion 610i is separated from the rib 744. As shown in FIG. Since the locking lever 74 receives a clockwise rotational force from the rotor, a gap is formed between the cam portion 610i and the rib 744 of the locking lever, and even if the driving member 61 rotates greatly in a high-temperature environment, You can get good performance.

Return to the general description. After the leading blade group starts traveling, the holding of the driving member 62 by the holding mechanism 66B is released at a timing corresponding to the set shutter speed, and the driving member 62 is rotated clockwise by the force of the driving spring 63B. , the blade group 51 travels to the closed state as shown in the state ST35 of FIG. As a result, the opening 31a is closed, and the exposure of the imaging element 3 is completed. While the driving member 62 is running, the bounce suppression mechanism 900 on the trailing curtain side as described above functions in the same way as on the leading curtain side.

A charge operation is then performed. When the motor 81 is driven, the front cam gear 854 and the rear cam gear 855 rotate, the front cam gear 854 moves the charge slider 82, and the drive springs 63A and 63B are charged via the drive mechanism. At this time, the blade group 41 is maintained in the open state due to the engagement between the arm portion 610B and the locking lever 74, and the state ST36 in FIG. 38 is reached. This is the same state as state ST31 in FIG. As described above, one shutter operation is completed.

The charge operation in continuous shooting charges the front curtain and the rear curtain at the same time. In this case, by driving the locking mechanism 70 immediately before the charging operation and rotating the rotor 730 to the release position, the locking lever 74 is retracted from the arm portion 610B, and the force of the spring 44 causes the blade group 41 to move. follows the drive member to close the opening 31a in the main plate. This will be described in detail with reference to FIGS. 42 and 43. FIG.

A state ST61 in FIG. 42 is a state of the shutter when the exposure of the imaging element 3 is completed, and shows a state in which the driving member 61 has finished rotating clockwise.

State ST62 shows a state in which locking mechanism 70 is driven and rotor 730 is rotated to the release position. At this time, the cam portion 610i on the outer peripheral surface of the arm portion 610B contacts the rib 744 of the locking lever. The lock lever 74 presses the arm portion 610B by the rotational force of the rotor 730, but the force of the drive spring 63A attached to the drive member 61 is large, so the arm portion 610B is stopped while being pressed by the lock lever 74. .

After that, the charge operation is performed by the charge mechanism 80 . Driving the motor 81 rotates the front cam gear 854 and the rear cam gear 855 . The force from the front cam gear 854 moves the charge slider 82 to generate a pressing force on the engaging portion 610b, thereby rotating the body portion 610A of the drive member 61 counterclockwise and charging the drive spring 63A. be. At this point, the rear cam gear 855 is not yet in contact with the driving member 62 . The arm portion 610B is rotated so as to follow the body portion 610A by the biasing force of the spring 44 attached to the blade mechanism 40 . Since the locking mechanism 70 is in the released state, the arm portion 610B rotates while following the body portion 610A. In addition, the reversing lever 920 is rotated by the charge slider 82 while the charge slider 82 is moving. As a result, the restraint of the driving member 62 by the lock lever 910 is released, and the driving member 62 is made chargeable.

ST63 in FIG. 43 is a state in which charging has progressed further. The charge slider 82 has completely moved, and the drive member 61 is held at the overcharge position by the charge slider 82 . The rear cam gear 855 contacts the driving member 62 and rotates it counterclockwise. The drive spring 63B begins to be charged, and then returns to state ST64 (standby phase).

Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various modifications and changes are possible within the scope of the gist of the invention.

2 shutter, 10 imaging device, 30 base plate, 31a aperture, 41 blade group, 51 blade group, 60 drive mechanism, 80 charge mechanism, 81 motor, 82 charge slider

Claims (9)

a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
The thick portion has a first side surface on the locking portion side and a second side surface on the opposite side in the circumferential direction,
The second side surface is formed in a direction intersecting the tooth space,
A blade driving device characterized by: a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
The thick portion includes a first thick portion on one side in the circumferential direction of the locking portion and a second thick portion on the other side,
The first thick portion has a first side surface on the locking portion side and a second side surface on the opposite side in the circumferential direction, and the second side surface extends in a direction intersecting the tooth space. is formed in
The second thick portion has a third side surface on the locking portion side and a fourth side surface on the opposite side in the circumferential direction, and the fourth side surface is formed along the tooth space. has been
A blade driving device characterized by: a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The peripheral wall has a reinforcing portion at a portion circumferentially adjacent to the locking portion,
The reinforcing portion is a thick portion thicker than the tooth groove portion,
In the thick portion, one axial end of the worm wheel is wider in the circumferential direction than the other axial end.
A blade driving device characterized by: a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The worm wheel has tooth grooves formed obliquely with respect to the axial direction of the worm wheel,
A blade driving device characterized by: The blade driving device according to claim 3 ,
In the thick portion, the one end of the worm wheel is thicker than the other end.
A blade driving device characterized by: a base member forming an aperture through which light passes;
a blade for opening and closing the opening;
a driving member to which the blades are connected;
a drive spring having one end connected to the drive member and biasing the drive member to move the blades;
a worm wheel to which the other end of the drive spring is connected;
a worm that meshes with the worm wheel and can adjust the biasing force of the drive spring by changing its rotational position;
a charging mechanism for charging the drive spring;
a cover member arranged to face the base member;
A blade drive device comprising:
the worm is arranged at an angle with respect to a virtual plane containing the opening;
a locking portion for locking the other end of the drive spring is formed on the peripheral wall of the worm wheel;
The charging mechanism includes a charging slider that moves in a predetermined direction between the base member and the cover member as the charging operation,
The worm is supported by the cover member,
the cover member has a bulging portion that avoids interference with the charge slider,
The bulging portion is formed so that the width gradually narrows in the predetermined direction,
A blade driving device characterized by: The blade driving device according to claim 6 ,
The charging mechanism includes a motor as a drive source,
The axial direction of the motor and the predetermined direction are parallel to the traveling direction of the blades,
A blade driving device characterized by: The blade driving device according to claim 6 ,
When viewed in the optical axis direction of the aperture, the worm extends parallel to the predetermined direction.
A blade driving device characterized by: The blade driving device according to claim 1,
The worm and the driving member are arranged so as to overlap each other in the optical axis direction of the aperture.
A blade driving device characterized by:

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