JP2010010808A - Image input device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an image input device for maintaining excellent mesh between a gear and a pinion gear of a driving means even when eccentricity in the diameter direction against a rotation center of a cam ring occurs to a gear of an outer circumference of the cam ring. <P>SOLUTION: The image input device of high resolution is provided with: a ring member which includes a cam surface abutted to a protection member of a parallel plate glass so as to incline the parallel plate glass for shifting an image formed to an image pickup element and rotatably provides an axis with a rotation center almost matching an optical axis; a gear provided on the outer circumference of the ring member; and a driving means for driving the ring member by the pinion gear meshing with the gear. The pinion gear is placed at a position where it meshes with the gear within a prescribed range from a position where a straight line passing the rotation center of the ring member and a center of the gear eccentrically spaced in the diameter direction with respect to the rotation center of the ring member by manufacturing errors crosses the gear. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an image input apparatus, and more particularly, to an image input apparatus using image shifting by a two-dimensional solid-state imaging device and a transparent parallel flat glass capable of angular displacement.

  2. Description of the Related Art Conventionally, in an image input device using a two-dimensional solid-state image sensor such as a CCD, the relative position between the image and the image sensor is changed minutely, and the image is stored each time it is changed, and the stored images are synthesized and seen. There is known one that improves the resolution by increasing the number of pixels above.

In order to improve the resolution by such a method, a glass unit incorporating a parallel plate glass is disposed between the image sensor and the photographing optical system, and the glass unit is in contact with the cam surface of the cam ring at three points, The cam ring rotatably attached to the cylinder is driven to rotate by the meshing of the gear disposed on the outer periphery thereof and the pinion gear of the motor, and the glass unit is tilted with the rotation of the motor, and the image reaches the image sensor through the glass. Has been proposed (for example, Patent Document 1).
Japanese Patent Laid-Open No. 7-255015

  However, in the conventional image input device, in the gear arranged on the outer periphery of the cam ring, the eccentricity in the diametrical direction that occurs as a manufacturing error with respect to the center of the fitting hole with the lens barrel of the cam ring, that is, the rotation center of the cam ring. Because of this, the meshing state of the gear changes as the motor rotates due to the inability to maintain good meshing with the pinion gear arranged on the motor shaft, and noise is generated or a stepping motor is used. However, there is a problem that a step-out due to insufficient torque occurs, and a correct glass tilt angle cannot be obtained.

  In order to solve the above-described problems, an image input device according to the present invention includes an imaging element on which an image of a subject is formed by an imaging optical system, and an image formed by the imaging optical system within the imaging element plane. In order to shift, a parallel flat glass provided in the optical path of the imaging optical system, a holding member that holds the parallel flat glass, and that can be tilted together with the parallel flat glass, and the holding member. A ring-shaped member that is in contact with the optical axis of the image-forming optical system and that is pivotable about the rotational center; and the holding member with respect to the optical axis. In order to incline, cam means comprising a cam surface disposed on the ring-shaped member, a contact portion disposed on the holding member and contacting the cam surface, and formed on the outer periphery of the ring-shaped member And a pinion gear, the pinion gear Drive means for driving the ring-shaped member by meshing with a gear, and the pinion gear is arranged in a radial direction with respect to the rotation center of the ring-shaped member and the rotation center of the ring-shaped member due to manufacturing errors. A straight line that passes through the center of the eccentric gear is arranged at a position that meshes with the gear within a predetermined range from a position that intersects the gear.

  According to the present invention, even if the gear on the outer periphery of the cam ring is decentered in the diametrical direction with respect to the rotation center of the cam ring, good meshing between the gear and the pinion gear is maintained, and an appropriate glass inclination angle is maintained. Can be provided.

  Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view showing a configuration of a high-resolution image input apparatus according to the first embodiment of the present invention, and FIG. 2 is a front view of main parts of the high-resolution image input apparatus according to the first embodiment of the present invention. It is.

  The glass unit 1 includes an annular holding member 3 and a circular parallel flat glass 5 that is fitted and fixed to the holding member 3 so as to cover a central hole of the holding member 3. The glass unit 1 is configured such that light that has passed through the imaging lens 7 that is an imaging optical system passes through the parallel flat glass 5. On the outer periphery of the holding member 3, there are provided arms 3 a directed outward at three locations. A miniature bearing (hereinafter referred to as a bearing) 9 is attached to each arm 3a so that the inner ring is fixed and the outer ring can rotate. As shown in FIG. 2, two of the three arms 3a are arranged symmetrically with respect to the optical axis L, and the other one is relative to a straight line connecting the two arms 3a arranged symmetrically. Are arranged on a vertical straight line crossing the optical axis L.

  A lens barrel 10 is attached to a housing (not shown) of the high resolution image input apparatus 100. Three grooves 10a are formed at the end of the lens barrel 10 on the imaging lens 7 side, and the arms 3a are inserted into the grooves 10a on a one-to-one basis. These grooves 10a restrict the rotation of the glass unit 1 around the optical axis L, but allow a predetermined amount of swinging of the arm 3a in the optical axis L direction. An image sensor 12 is fixed to the other end of the lens barrel 10 via a circuit board 13.

  A large-diameter portion 15 is provided on the outer periphery of the lens barrel 10. A cam ring 17 and a presser ring 18 are fitted on the outer peripheral surface of the lens barrel 10. The cam ring 17 is fitted to the outer peripheral surface of the lens barrel 10 on the imaging element 12 side of the large diameter portion 15 and is rotatable around the outer peripheral surface of the lens barrel 10. The cam ring 17 is positioned in the optical axis L direction (hereinafter referred to as the optical axis direction) by the surface of the large diameter portion 15 on the imaging element 12 side. The presser ring 18 is fitted to the outer peripheral surface of the lens barrel 10 on the image sensor 12 side of the cam ring 17 and restricts the movement of the cam ring 17 in the optical axis direction. With this configuration, the cam ring 17 is restricted from moving in the optical axis direction by the large-diameter portion 15 and the presser ring 18 and can be rotated around the outer peripheral surface of the lens barrel 10. The rotation center of the cam ring 17 substantially coincides with the optical axis L.

  A gear 20 is formed on the outer periphery of the cam ring 17. A stepping motor 21 is fixed to a housing (not shown) of the high resolution image input apparatus 100. A pinion gear 21 a is provided on the motor shaft of the stepping motor 21, and the pinion gear 21 a meshes with the gear 20. Accordingly, the cam ring 17 rotates in conjunction with the driving of the stepping motor 21. A cam surface 17a extending in the circumferential direction is formed on the surface of the cam ring 17 on the imaging lens 7 side. The cam surface 17a is formed in a predetermined shape having irregularities in the optical axis direction, and the outer rings of the bearings 9 attached to the respective arms 3a are in contact with each other.

  Next, the tilting operation of the glass unit 1 will be described. The glass unit 1 is urged toward the image sensor 12 by an urging means (not shown). By urging in this way, the contact between the bearing 9 attached to the arm 3a and the cam surface 17a is always maintained.

  When the stepping motor 21 is driven, the cam ring 17 rotates around the lens barrel 10 in conjunction with this. When the cam ring 17 rotates, the bearings 9 attached to the respective arms 3a roll on the cam surface 17a. Thus, the glass unit 1 swings in the optical axis direction following the uneven shape of the cam surface 17a. By making the shape of the cam surface 17a a predetermined shape and controlling the amount of rotation of the cam ring 17, the inclination direction and the inclination angle of the glass unit 1 can be controlled. At this time, the groove 10a provided on the imaging lens 7 side of the lens barrel 10 and in which the arm 3a is inserted is used as a rotation stop around the optical axis L of the glass unit 1 and as a movable guide in the optical axis direction. Function.

  Thus, the image of the subject that has passed through the imaging lens 7 passes through the parallel flat glass 5 and reaches the image sensor 12, but the subject image changes its course according to the inclination of the glass unit 1. As a result, the image of the subject projected on the image sensor 12 is shifted.

  Next, a method for manufacturing the cam ring 17 will be described.

  FIG. 4 is a plan view of the cam ring 17 according to the present embodiment (however, the cam surface 17a is not shown).

  The cam ring 17 is manufactured by cutting a metal material such as aluminum in consideration of its durability. In the processing step, first, the center portion of the material is punched out, the shape that becomes the inner circumferential circle R1 of the cam ring 17 is formed, then the outer peripheral gear 20 is formed, and finally the cam surface 17a is formed on the basis of the inner circumferential circle R1. It becomes the order of processing. In the assembled state, the inner periphery of the cam ring 17 is fitted to the outer periphery of the lens barrel 10, and the center O1 of the inner periphery circle R1 substantially coincides with the optical axis L.

  The cam ring 17 is fitted to the outer peripheral surface of the lens barrel 10 and rotates around the outer peripheral surface of the lens barrel 10 about the center O1 of the inner peripheral circle R1. Therefore, it is desirable that the inner circumferential circle R1 and the circumscribed circle R2 of the gear 20 are concentric circles. However, in actual machining, an eccentricity δ as a machining tolerance is generated between the center O1 of the inner circumferential circle R1 and the center O2 of the circumscribed circle R2.

FIG. 4 shows that a straight line passing through the center O2 of the circumscribed circle R2 of the gear 20 and the center O1 of the inner circumferential circle R1 is H, and the gear radius r at an angle θ ′ around the center O1 of the inner circumferential circle R1 from this straight line H. And the gear radius r at the declination angle θ when the same position is viewed from the center O2 of the circumscribed circle R2. In FIG. 4, the eccentricity amount δ is exaggerated, but it is actually a minute amount due to processing tolerances. At this time, from the geometric relationship,
r ′ = (r ² + δ ² −2 · r · δ · cos θ) ^1/2 (1)
θ = θ′−arcsin (δ / r × sin θ ′) (2)
The following formula is derived.

  FIG. 5 shows the calculation of r ′ when the eccentricity of δ = 0.2 mm occurs in the cam ring 17 having a size of r = 40 mm by the above formulas (1) and (2). The eccentricity (r'-r) is taken on the axis and plotted on a graph. Θ ′ is the phase at which the distance from the center O1 of the inner circumference circle R1 to the circumscribed circle R2 of the gear 20 is minimum, that is, the position on the center O1 side of the two points where the straight line H intersects the gear 20 is the reference. Yes.

  In the first embodiment shown in FIG. 2, two of the three arms 3a of the glass unit 1 are arranged symmetrically around the optical axis L, that is, the center O1 of the inner circumferential circle R1, and the other one is symmetrical. Is arranged on a vertical straight line that crosses the center O1 of the inner circumference circle R1 with respect to the straight line connecting the two arms 3a arranged in FIG. That is, the other one arm 3a is disposed at an angle of 90 ° with each of the two arms 3a disposed symmetrically. Since the three arms 3a share the cam surface 17a at three locations, the operating range of the cam ring 17 needs to be 90 ° or less. That is, it is necessary to form the shape of the cam surface 17a so that a series of image shift operations are performed within a range in which the cam ring 17 rotates 90 °.

  Here, in the graph shown in FIG. 5, it can be seen that the fluctuation range of the eccentricity varies depending on the 90 ° rotation range of the cam ring 17, that is, how to take θ ′. Eccentricity when the pinion gear 21a meshes with the gear 20 when θ ′ is in the range of 135 ° ≦ θ ′ ≦ 225 °, or in the range of 0 ° ≦ θ ′ ≦ 45 ° and 315 ° ≦ θ ′ ≦ 360 °. The fluctuation range is a minimum value of 0.059 mm. These ranges of θ ′ are the two points where the straight line passing through the center O1 of the inner circumference R1 and the center O2 of the circumscribed circle R2 contacts the gear 20, that is, the point where the distance from the center O1 to the circumscribed circle R2 is the smallest. From the large point (θ ′ = 0 ° or 180 °), each is in the range of ± 45 ° in the circumferential direction. On the other hand, when θ ′ is in the range of 45 ° ≦ θ ′ ≦ 135 °, or in the range of 225 ° ≦ θ ′ ≦ 315 °, the variation range of the eccentric amount when the gear 20 is engaged is 0.283 mm, which is the maximum value. Become.

  Therefore, in the machining process of the cam ring 17, the eccentric amount δ and the eccentric direction of the circumscribed circle R2 of the gear 20 with respect to the inner circumferential circle R1 are measured in advance, and the fluctuation range of the eccentric amount within the rotation range of the cam ring 17 is measured. The cam surface 17a is processed at a phase where the value becomes the minimum value.

  6 shows the cam ring 17 according to the first embodiment, in which the cam surface 17a is machined with a phase in a range where the fluctuation range of the eccentricity is a minimum value within the rotation range of the cam ring 17, and the high resolution image input device 100 is processed. It is sectional drawing which shows the assembled | attached state.

In the cam ring 17 of FIG. 6, a straight line connecting the center O1 of the inner circle R1 and the center O2 of the circumscribed circle R2 is H, and two arms 3a ₁ and 3a ₂ centering on the center O1 are formed on the straight line H. 1 are arranged symmetrically. That is, on the straight line H, the arm 3a ₁ is arranged in the direction in which the distance from the center O1 of the inner circumferential circle R1 to the circumscribed circle R2 is the smallest, and the arm 3a ₂ is arranged in the direction in which the distance is the largest. The arm 3a ₃ is arranged on a straight line passing through the center O1 of the inner circumferential circle R1 with respect to the straight line connecting the arms 3a ₁ and 3a ₂ .

  The cam ring 17 is engaged with the pinion gear 21a and the gear 20 by the driving of the stepping motor 21, and rotates about the center O1 of the inner circumferential circle R1. Since the range in which the pinion gear 21a and the gear 20 mesh with each other is a range in which the fluctuation range of the eccentricity becomes the minimum value, in this embodiment, as described above, θ ′ is 135 ° ≦ θ ′ ≦ 225 °. Or ranges of 0 ° ≦ θ ′ ≦ 45 ° and 315 ° ≦ θ ′ ≦ 360 °. In other words, the range is ± 45 ° from the position where the straight line H intersects the gear 20. In FIG. 6, the stepping motor 21 is arranged so that θ ′ meshes in the ranges of 0 ° ≦ θ ′ ≦ 45 ° and 315 ° ≦ θ ′ ≦ 360 °. Of course, as shown in 21 b of FIG. 6, θ ′ may be arranged so as to mesh within a range of 135 ° ≦ θ ′ ≦ 225 °.

  Since the pinion gear 21a and the gear 20 mesh with each other in the range of 90 ° where θ ′ is 0 ° ≦ θ ′ ≦ 45 ° and 315 ° ≦ θ ′ ≦ 360 °, the cam ring 17 rotates 90 °. The shape is formed so that a series of image shift operations are performed within the range.

Accordingly, the cam surface 17a ₁ corresponding to the arm 3a ₁ is formed in an arc shape in a range of 90 ° around the center O1 of the inner circumferential circle R1. In this range, the arm 3a ₁ is in contact with the cam surface 17a ₁ . Contact the outer ring of the bearing 9 attached to the arm 3a ₁ is the cam surface 17a ₁ in particular, roll over the cam surface 17a ₁ above with the driving of the stepping motor 21. Similarly, the cam surfaces 17a ₂ and 17a ₃ are formed in the range of 90 ° around the center O1 of the inner circumferential circle R1 for the other arms 3a ₂ and 3a ₃ .

  In this way, if the cam surface 17a is machined in such a phase that the fluctuation range of the eccentric amount is within the rotation range of the cam ring 17, the eccentricity of the gear 20 with respect to the inner circumferential circle R1 of the cam ring 17 is reduced. Even if it occurs, the influence of eccentricity can be effectively suppressed, and the meshing between the pinion gear 21a and the gear 20 can be maintained in a good state. As a result, it is possible to prevent the occurrence of abnormal noise during operation or the step-out due to insufficient torque when the stepping motor 21 is used. Furthermore, the rotational speed of the cam ring 17 can be stably increased, and a faster image input process can be performed.

Note that in the engagement between the actual pinion 21a and the gear 20 in the assembled state, for example, the arms 3a ₁ is in contact with the cam surfaces 17a _1, the position of the arms 3a ₁ is, the cam surface 17a ₁ and the adjacent cam The meshing range of the gear 20 is controlled so as not to coincide with the boundary portion with the surface 17a ₃ . The other arms 3a ₂ and 3a ₃ are similarly controlled. Such control of the meshing range may be, for example, detecting the amount of rotation of the cam ring 17 by counting the number of drive pulses of the stepping motor 21 or starting the rotation of the cam ring 17 using two sensors. Control may be performed by detecting the position and the rotation end position. There is no limitation as long as the rotation range of the cam ring 17 can be controlled so that the intended range of the cam surface can be used.

  Next, a second embodiment of the present invention will be described. About 2nd Embodiment, the different structure from 1st Embodiment is demonstrated, and the same code | symbol is used about the same structure and member.

  FIG. 3 is a view showing the arrangement of the arms 3a of the glass unit 1 according to the second embodiment. In the present embodiment, the three arms 3a of the glass unit 1 are arranged so as to divide the entire circumference of the glass unit 1 into three equal parts, that is, arranged at an angle of 120 °. In this case, the operating range of the cam ring 17 needs to be 120 ° or less. That is, it is necessary to form the shape of the cam surface 17a so that a series of image shift operations are performed within a range in which the cam ring 17 rotates by 120 °.

  Here, in the graph shown in FIG. 5, it can be seen that the fluctuation range of the eccentricity changes depending on how the cam ring 17 is rotated by 120 °. When θ ′ is in the range of 120 ° ≦ θ ′ ≦ 240 °, or in the range of 0 ° ≦ θ ′ ≦ 60 ° and 300 ° ≦ θ ′ ≦ 360 °, the deviation is caused when the pinion gear 21a meshes with the outer gear 20. The fluctuation range of the core amount is a minimum value of 0.100 mm. These ranges of θ ′ are two points where a straight line passing through the center O1 of the inner circumference circle R1 and the center O2 of the circumscribed circle R2 of the gear 20 contacts the gear 20, that is, from the center O1 of the inner circumference circle R1 to the circumscribed circle R2. From the point with the smallest distance and the largest point (θ ′ = 0 ° or 180 °), each is in the range of ± 60 ° in the circumferential direction. On the other hand, the variation range of the eccentric amount when the gear 20 is engaged in the range of θ ′ of 30 ° ≦ θ ′ ≦ 150 ° or 210 ° ≦ θ ′ ≦ 330 ° is 0.346 mm, which is the maximum value. Become.

  Therefore, in the machining process of the cam ring 17 in the present embodiment, the eccentric amount and eccentric direction of the circumscribed circle R2 of the gear 20 with respect to the inner circumferential circle R1 are measured in advance, and the eccentric amount is within the rotation range of the cam ring 17. The cam surface 17a is machined at a phase such that the fluctuation range of the first is the minimum value.

  FIG. 7 shows the cam ring 17 according to the second embodiment, in which the cam surface 17a is processed with a phase in a range where the fluctuation range of the eccentricity is the minimum value within the rotation range of the cam ring 17, and the high resolution image input device 100 is processed. It is sectional drawing which shows the assembled | attached state.

In the cam ring 17 of FIG. 7, the glass unit 1 is provided with arms 3a ₁ , 3a ₂ , 3a _{3 at} positions that divide the entire circumference of the glass unit 1 into three equal parts, that is, at an angle of 120 ° to each other.

  The cam ring 17 is engaged with the pinion gear 21a and the gear 20 by the driving of the stepping motor 21, and rotates about the center O1 of the inner circumferential circle R1. The range in which the pinion gear 21a meshes with the gear 20 is a range in which the fluctuation range of the eccentricity becomes the minimum value. Therefore, in the present embodiment, as described above, θ ′ is 120 ° ≦ θ ′ ≦ 240 °. Or ranges of 0 ° ≦ θ ′ ≦ 60 ° and 300 ° ≦ θ ′ ≦ 360 °. In other words, the straight line H passing through the center O1 of the inner circle R1 and the center O2 of the outer circle R2 is within a range of ± 60 ° from the position where the gear 20 intersects. In FIG. 7, the stepping motor is arranged so that θ ′ meshes in the range of 0 ° ≦ θ ′ ≦ 60 ° and 300 ° ≦ θ ′ ≦ 360 °. Of course, as shown in 21 b of FIG. 7, θ ′ may be arranged so as to mesh within a range of 120 ° ≦ θ ′ ≦ 240 °.

  The pinion gear 21a and the gear 20 mesh with each other in the range of 120 ° in which θ ′ is 0 ° ≦ θ ′ ≦ 60 ° and 300 ° ≦ θ ′ ≦ 360 °, so that the cam surface 17a is within the range in which the cam ring 17 rotates by 120 °. The shape is formed so that a series of image shift operations are performed.

Accordingly, the cam surface 17a ₁ corresponding to the arm 3a ₁ is formed in an arc shape in a range of 120 ° around the center O1 of the inner circumferential circle R1. In this range, the arm 3a ₁ is in contact with the cam surface 17a ₁ . Contact the outer ring of the bearing 9 attached to the arm 3a ₁ is the cam surface 17a ₁ in particular, roll over the cam surface 17a ₁ above with the driving of the stepping motor 21. As for the other arms 3a ₂ and 3a ₃ , cam surfaces 17a ₂ and 17a ₃ are formed in a range of 120 ° around the center O1 of the inner circumferential circle R1. In the actual meshing of the gears in the assembled state, the positions of the arms 3a ₁ , 3a ₂ , 3a ₃ coincide with the boundary portions with the cam surfaces corresponding to the adjacent arms, as in the first embodiment. The meshing range of the gear is controlled so as not to occur.

  As described above, the processing of the cam surface 17a is performed in such a phase that the fluctuation range of the eccentricity amount becomes the minimum value within the rotation range of the cam ring 17, and this embodiment is also the same as the first embodiment. Demonstrate the effect.

  Next, the image data processing process of the high-resolution image input apparatus 100 according to the present invention will be described with reference to FIG.

  Image data photoelectrically converted by the image sensor 12 is converted into digital data by the A / D converter 25 and stored in the frame memory 26. The image reaching the image sensor 12 is moved by the inclination of the parallel flat glass 5 in the first or second embodiment described above, and the above operation is repeated every time the moved image is moved, and a predetermined number of image data is framed. Accumulated in the memory 26.

  The plurality of image data are combined by the image combining means 27 and stored in the combined image frame memory 28 as high-resolution image data. The data in the composite image frame memory 28 is displayed as a high resolution image by the display means 30 connected to the high resolution image input device 100. The A / D converter 25, the frame memory 26, the image synthesizing unit 27, and the synthesized image frame memory 28 may be arranged on the circuit board 13 of the high resolution image input device 100, or the high resolution image input device. You may arrange | position in the control apparatus not shown connected to 100. FIG.

  As described above, according to the high-resolution image input device 100 according to the present invention, even if the gear 20 of the cam ring 17 is decentered with respect to the rotation center of the cam ring 17, the pinion gear and the outer peripheral gear are excellent. Engagement is maintained, and noise during driving by the stepping motor 21 can be effectively reduced. In addition, since the stepping motor 21 can be prevented from being stepped out due to poor meshing of the gear 17, stable operation can be performed. Moreover, even if the eccentricity tolerance of the gear machining is relaxed, good engagement can be ensured, so that the cost of the cam ring part can be reduced. Furthermore, the rotational speed of the cam ring 17 can be stably increased, and a faster image input process can be performed.

  Note that the above-described embodiment is merely an example, and is not limited to the above-described configuration and shape, and can be appropriately modified and changed.

It is sectional drawing which shows the structure of the high resolution image input device which concerns on 1st Embodiment of this invention. It is a front view of the principal part of the high resolution image input device concerning a 1st embodiment of the present invention. It is a front view of the principal part of the high resolution image input device which concerns on 2nd Embodiment of this invention. It is a front view of the cam ring of the high resolution image input device according to the present invention. It is a graph which shows the relationship between the amount of eccentricity of a cam ring, and a phase. In the cam ring of 1st Embodiment, it is a front view which shows the state which processed and assembled | attached the cam surface in the phase of the range from which the fluctuation range of eccentricity becomes the minimum value within the rotation range of a cam ring. In the cam ring of 2nd Embodiment, it is a front view which shows the state which processed and assembled | attached the cam surface in the phase of the range from which the fluctuation range of eccentricity becomes the minimum value within the rotation range of a cam ring. It is a block diagram which shows the process of the image data of the high resolution image input device which concerns on this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Glass unit 3 Holding member 3a Arm 5 Parallel plate glass 7 Imaging lens 9 Bearing 10 Lens barrel 10a Groove 12 Image pick-up element 13 Circuit board 15 Large diameter part 17 Cam ring 17a Cam surface 18 Presser ring 20 Gear 21 Stepping motor 21a Pinion gear 25 A / D converter 26 Frame memory 27 Image composition means 28 Composite image frame memory 30 Display means

Claims (4)

An image sensor on which an image of a subject is formed by an imaging optical system;
In order to shift an image formed by the imaging optical system in the imaging element plane, a parallel plate glass provided in an optical path of the imaging optical system;
Holding the parallel flat glass, a holding member provided to be inclined together with the parallel flat glass; and
A ring-shaped member that comes into contact with the holding member and has a rotation center that substantially coincides with the optical axis of the imaging optical system, and is provided so as to be rotatable about the rotation center;
Cam means comprising a cam surface disposed on the ring-shaped member and an abutting portion disposed on the holding member and contacting the cam surface in order to incline the holding member with respect to the optical axis. When,
A gear formed on the outer periphery of the ring-shaped member;
A drive means for driving the ring-shaped member by having a pinion gear and the pinion gear meshes with the gear;
The pinion gear is located from a position where a straight line passing through the rotation center of the ring-shaped member and the center of the gear that is eccentric in the radial direction with respect to the rotation center of the ring-shaped member due to a manufacturing error intersects the gear. An image input device arranged at a position that meshes with the gear within a predetermined range.   Storage means for storing a plurality of images that are shifted by the inclination of the parallel plate glass and imaged by the imaging device; and image composition means for synthesizing a high-resolution image from the plurality of images stored in the storage means; The image input apparatus according to claim 1, further comprising:   The ring-shaped member is driven by the driving means within the range of X ° (0 <X ≦ 120) about the rotation center, and the meshing between the pinion gear and the gear is based on the straight line. The image input device according to claim 1, wherein the image input device is within a range of ± (X / 2) °.   The cam surface is a series of steps for inclining the holding member with respect to the optical axis in a range of X ° around the rotation center so that the pinion gear and the gear are engaged in the range. The image input device according to claim 3, wherein the image input device has a shape capable of performing the following.

Images