JP2007212504A - Shutter device and camera - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shutter device capable of maintaining stable braking performance even when the number of shutter operation times is increased. <P>SOLUTION: Regarding a front curtain braking mechanism 30 for a focal plane shutter, a front blade braking lever 16 is sandwiched between two washers 16e and 16f, and a slight amount of lubricant is added to the contact surfaces of the lever 16. A drive pin 6b of a front blade driving lever 6 that drives the light shielding blade of the front curtain comes in contact with the front blade braking lever 16, and the contact surfaces of the front blade braking lever 16 rub the washers 16e and 16f when the front blade braking lever 16 rotates; then, a frictional force is generated, and consequently, the rotating motion of the front blade driving lever 6 is braked. Since the front blade braking lever 16 is porous, the lever 16 is excellent in lubricant holdability, and the lubricant held by the lever 16 exudes onto the contact surfaces with the increase of the number of shutter operation times, then, the frictional force is kept constant, and the stabilization of the braking performance is attained. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a shutter device and a camera including the shutter device.

  In the focal plane shutter of a single-lens reflex camera, the opening and closing operation of the shutter substrate opening is performed by causing the front blade group and the rear blade group to travel through the arm members using a driving mechanism. A brake mechanism is used to stop the traveling blade group just before the end of the opening / closing operation. As this type of brake mechanism, one configured to absorb the kinetic energy of the drive lever by bringing the drive lever of the drive mechanism into contact with the brake lever is known (see, for example, Patent Document 1). . The brake lever is sandwiched between a pair of washers, and a frictional force generated between the brake lever and the washer acts as a brake force, and gradually absorbs the kinetic energy of the drive lever. Lubricant is added to the surface where friction occurs between the brake lever and the washer. Normally, the brake lever is made of steel.

JP-A-8-54663

  In the conventional focal plane shutter, the frictional force changes as the number of shutter operations increases, and the intended brake performance may not be maintained.

(1) The shutter device of the invention according to claim 1 is characterized in that a porous member holding a lubricant is used as a member that slides when the shutter blades travel.
(2) The invention according to claim 2 is the shutter device according to claim 1, wherein the porous member is obtained by firing a material containing metal as a main component.
(3) The invention according to claim 3 is the shutter device according to claim 2, wherein the metal is stainless steel.
(4) The invention of claim 4 is the shutter device according to any one of claims 1 to 3, wherein the pore diameter of the porous member is 10 to 100 μm.
(5) The invention of claim 5 is the shutter device according to any one of claims 1 to 4, wherein the volume ratio of the pores of the porous member is 10 to 30%.
(6) The invention of claim 6 is the shutter device according to any one of claims 1 to 5, wherein the porous member vaporizes the vaporizable particles after the vaporizable particles are dispersed in the base material. It is manufactured by this.
(7) The invention of claim 7 is the shutter device according to any one of claims 1 to 6, wherein the lubricant is grease.
(8) The invention according to claim 8 is the shutter device according to claim 7, wherein the grease has a consistency defined by Japanese Industrial Standard K2220 in the range of 150 to 400.
(9) The invention of claim 9 is the shutter device according to any one of claims 1 to 8, wherein the porous member is a rotating shaft for driving the shutter blade, and a brake member for braking the shutter blade. And at least one of the friction members.
(10) A camera according to a tenth aspect of the present invention includes the shutter device according to any one of the first to ninth aspects.

  According to the present invention, stable braking performance can always be obtained even if the number of shutter operations increases.

Hereinafter, a shutter device according to the present invention will be described with reference to FIGS. In the figure, the same components are denoted by the same reference numerals.
FIG. 1 is a schematic configuration diagram of a front curtain and a rear curtain of a focal plane shutter according to an embodiment of the present invention. FIG. 1 shows a state before the exposure operation in which the shutter is charged. This focal plane shutter is a high-speed shutter whose shutter speed exceeds 1/8000 seconds, for example.

  As shown in FIG. 1, the front curtain includes a front blade group 12 including four light shielding blades 12a to 12d, a front curtain main arm 14a, and a front curtain sub arm 14b. The front curtain main arm 14a has bearing holes 141 and 142 and four connection holes 143, and the front curtain slave arm 14b has a bearing hole 144 and four connection holes 145. The front curtain main arm 14a and the front curtain follower arm 14b pivotally support the four light shielding blades 12a to 12d by passing caulking pins (not shown) through the four connecting holes 143 and 145, respectively. On the other hand, the rear curtain includes a rear blade group 13 including four light-shielding blades 13a to 13d, a rear curtain main arm 15a, and a rear curtain slave arm 15b. Regarding the rear curtain, similarly to the front curtain, the rear curtain main arm 15a has bearing holes 151, 152 and four connection holes 153, and the rear curtain secondary arm 15b has bearing holes 154 and four connection holes 153. The rear curtain main arm 15a and the rear curtain follower arm 15b pivotally support the four light shielding blades 13a to 13d by passing caulking pins (not shown) through the four connecting holes 153 and 155, respectively. .

  In FIG. 1, the light-shielding blades 12a to 12d of the front curtain are in a shielded state so as to cover the opening window 1a formed in the substrate 1, and the light-shielding blades 13a to 13d of the rear curtain overlap above the opening window 1a. Thus, the open window 1a is opened. That is, the front curtain is shielded and the rear curtain is open to prevent exposure.

  The rotating shafts 6a and 61a of the front curtain are implanted in the substrate 1 and pass through the bearing hole 141 of the front curtain main arm 14a and the bearing hole 144 of the front curtain secondary arm 14b, respectively. The front curtain main arm 14a and the front curtain slave arm 14b are rotatably attached to the rotation shafts 6a and 61a, respectively, and constitute a parallel link mechanism. As will be described with reference to FIG. 2, the leading curtain main arm 14a is driven by the drive pin 6b.

  Similarly, the rotation shafts 7a and 71a of the rear curtain are implanted in the substrate 1 and penetrate the bearing hole 151 of the rear curtain main arm 15a and the bearing hole 154 of the rear curtain secondary arm 15b, respectively. The rear curtain main arm 15a and the rear curtain slave arm 15b are rotatably attached to the rotation shafts 7a and 71a, respectively, and constitute a parallel link mechanism. The rear curtain main arm 15a is driven by the drive pin 7b.

  FIG. 2 is a schematic configuration diagram of a driving mechanism and a braking mechanism of a focal plane shutter according to the embodiment of the present invention. FIG. 2 is a diagram corresponding to the shutter charge state shown in FIG. 1, and the focal plane shutter 100 includes a front curtain drive mechanism 20 and a rear curtain drive mechanism 21 for causing the shutter blades to travel. A front curtain brake mechanism 30 and a rear curtain brake mechanism 31 for stopping the travel of the blades are provided.

  The front curtain drive mechanism 20 includes a front blade locking lever 2, a spring 4, a front blade drive lever 6, and a drive spring 8. The leading blade drive lever 6 has a drive pin 6b implanted at the tip thereof, and can rotate around the rotation shaft 6a. The drive pin 6 b passes through the bearing hole 142 of the leading curtain main arm 14 a and is engaged with the circular arc groove 10 formed in the substrate 1. As shown in FIG. 2, the leading blade driving lever 6 is urged clockwise by the driving spring 8 about the rotation shaft 6 a, and the leading blade locking lever 2 is prevented from rotating. In this state, the leading blade locking lever 2 is urged counterclockwise by the rotating shaft 2a by the spring 4 and is stationary.

  The leading curtain braking mechanism 30 will be described with reference to FIG. FIG. 3 is a perspective view schematically showing the configuration of the front curtain braking mechanism 30 shown in FIG. The front curtain braking mechanism 30 includes a front blade brake lever 16 and a buffer member 18. The leading blade brake lever 16 is rotatable around a rotation axis 30a perpendicular to the substrate 1, and a friction torque acts against the rotation. The leading blade brake lever 16 is disposed so as to abut on the driving pin 6b immediately before the rotation of the leading blade driving lever 6 around the rotation shaft 6a is completed. The buffer member 18 is provided at a position where the leading blade brake lever 16 rotates and contacts around the rotation axis 30a, and limits the rotation range of the leading blade brake lever 16.

  As shown in FIG. 3, a disc spring 16c, a fixing ring 16d, a washer 16e, a leading blade brake lever 16, a washer 16f, and a pressing plate 16g are arranged in order from the bottom on the support shaft 16b erected on the substrate 1. These components are pressed in the axial direction by the pressing force of the disc spring 16c by fastening the screw 16a to the support shaft 16b. The contact surface between the leading blade brake lever 16 and the two washers 16e and 16f is a surface on which the above-described friction torque acts, and a small amount of lubricant is added to these contact surfaces. The fixing ring 16d is a component that suppresses the rotation of the disc spring 16c. Further, the buffer member 18 is inserted into the support shaft 18b erected on the substrate 1, and is fixed by the pressing plate 16g.

  This will be described with reference to FIG. 2 again. The trailing blade drive mechanism 21 includes a trailing blade locking lever 3, a spring 5, a trailing blade driving lever 7, and a driving spring 9. The rear blade drive lever 7 has a drive pin 7b implanted at the tip thereof, and can rotate around the rotation shaft 7a. The drive pin 7 b passes through the bearing hole 152 of the rear curtain main arm 15 a and is engaged with the arc groove 11 formed in the substrate 1. As shown in the figure, the rear blade drive lever 7 is urged clockwise by the drive spring 9 with respect to the rotation shaft 7 a, and the rear blade locking lever 3 is prevented from rotating. In this state, the rear blade locking lever 3 is urged counterclockwise by the spring 5 by the spring 5 and is stationary.

  The rear-curtain brake mechanism 31 is configured in the same manner as the front-curtain brake mechanism 30 and includes the rear blade brake lever 17 and the buffer member 19. The rear blade brake lever 17 is rotatable around a rotation axis 31a perpendicular to the substrate 1, and a friction torque acts against the rotation. The rear blade brake lever 17 is disposed so as to contact the drive pin 7b immediately before the clockwise rotation of the rear blade drive lever 7 is completed. The buffer member 19 is provided at a position where the rear blade brake lever 17 rotates and contacts, and restricts the rotation range of the rear blade brake lever 17.

  FIG. 4 is a schematic configuration diagram showing a state of the driving mechanism and the braking mechanism when the leading curtain has completed traveling in the focal plane shutter shown in FIG. In FIG. 4, the rear curtain does not travel and the rear curtain drive mechanism 21 and the rear curtain brake mechanism 31 are shown not to operate. The front-curtain drive mechanism 20 and the front-curtain brake mechanism 30 operate as follows according to the travel of the front curtain.

  First, when the leading blade locking lever 2 rotates clockwise with respect to the rotating shaft 2a and the engagement with the leading blade driving lever 6 is released, the biasing force by the driving spring 8 is released, and the leading blade driving lever is released. 6 rotates clockwise, and the drive pin 6b moves along the arc groove 10 in the lower left direction. At this time, the light-shielding blades 12a to 12d of the front curtain shown in FIG. 1 shift from a shielded state that covers the opening window 1a to an open state that overlaps the opening window 1a and opens the opening window 1a. When the driving pin 6b comes into contact with the leading blade brake lever 16 immediately before the traveling of the leading blade is completed, the leading blade brake lever 16 rotates clockwise. The rotational movement of the leading blade drive lever 6 is braked by the friction torque generated by the rotation of the leading blade brake lever 16, and the leading blade drive lever 6 decelerates. When the leading blade brake lever 16 comes into contact with the buffer member 18, the rotational motion of the leading blade drive lever 6 stops, and the traveling of the leading blade is completed.

  The operations of the rear-curtain drive mechanism 21 and the rear-curtain braking mechanism 31 that accompany the rear-curtain traveling are the same as those in the case of the front-curtain traveling, and will be described briefly. A predetermined time after the leading shutter blades 12a to 12d start traveling, the trailing shutter drive mechanism 21 starts traveling the trailing shutter blades 13a to 13d. The braking mechanism 31 brakes the rear blade drive lever 7, and the rear blade drive lever 7 decelerates. When the trailing blade brake lever 17 abuts against the buffer member 19, the rotational movement of the trailing blade drive lever 7 stops and the running of the trailing curtain is completed. In this way, the amount of light passing through the aperture window 1a is adjusted with time, and a desired shutter speed is obtained.

  The operation of the front curtain braking mechanism 30 will be described with reference to the perspective view of FIG. In the figure, when the driving pin 6b of the leading blade driving lever 6 indicated by a two-dot chain line contacts the leading blade brake lever 16, the leading blade brake lever 16 rotates clockwise. Since the leading blade brake lever 16 is sandwiched between the two washers 16e and 16f, when the leading blade brake lever 16 rotates, it slides on the contact surface with the washer 16e and 16f to generate a frictional force. This frictional force absorbs the rotational energy of the leading blade brake lever 16 and consequently absorbs the kinetic energy of the leading blade drive lever 6. In this deceleration process, if the braking force due to friction is too strong, there is a risk that the impact on the light-shielding blade and arm will increase, causing damage to these parts and the shutter accuracy worsening. The stopping performance will be degraded.

  A very small amount of lubricant is added to this frictional force generation region, and the lubricant enables fine adjustment of the frictional force generated between the leading blade brake lever 16 and the two washers 16e and 16f. . The present invention provides a shutter device that can stably maintain an optimally adjusted frictional force, that is, braking performance. Since the brake performance varies depending on the thickness of the washers 16e and 16f, when assembling the shutter, select an appropriate set of several types of washers prepared in advance to keep the braking force within a certain range. It is adjusted to enter.

  In the present embodiment, the leading blade brake lever 16 is a porous member, made of a porous metal material (including an alloy), and a lubricant is added to the leading blade brake lever 16. A large number of small holes are three-dimensionally distributed in the leading blade brake lever 16. The shape of these small holes is basically spherical, and some of the small holes exposed on the surface have a bag shape with a narrow opening. If the lubricant enters such a small hole, it will not easily come off. That is, the surface of the porous member is excellent in the retention of the lubricant, unlike the unevenness like a satin-like shape. Since the lubricant held in the porous member oozes out to the contact surface between the leading blade brake lever 16 and the washers 16e and 16f as the number of shutter operations increases, the frictional force can be kept constant. Contributes to stabilization of brake performance. As a result, the light-shielding blade and the arm are not easily damaged, and a highly durable shutter device can be realized. The lubricant is used not only for adjusting the friction torque, but also for preventing sliding surface wear and galling.

  Examples of the porous metal material used for the leading blade brake lever 16 include stainless steel, titanium and titanium alloy, nickel, iron-nickel alloy, nickel-cobalt alloy, copper and copper alloy, tungsten alloy, and molybdenum alloy. The pore diameter of these porous metals is 10 to 100 μm, and the pore volume ratio is 10 to 30%. With respect to the size of the hole diameter, when the hole volume ratio is the same, the smaller the hole diameter, the higher the mechanical strength of the brake lever 16, but it becomes difficult for the lubricant to be taken in and the holding performance also decreases. The above-mentioned 10 to 100 μm is appropriate as the hole diameter capable of achieving both strength and lubricant retention performance. If the hole diameter is the same, a larger amount of lubricant can be retained as the volume ratio of the small holes increases, but the strength decreases because the ratio of the metal component decreases. Considering the strength and the amount of the lubricant, the above-mentioned 10 to 30% of the volume ratio of the small holes is appropriate.

  As the lubricant added to the leading blade brake lever 16, grease, paste, solid lubricant, dry film lubricant, or the like is used. For example, as grease, lithium soap is added to squarel raw material oil, lithium soap is added to poly alpha olefin base oil, PTFE (polytetrafluoroethylene) is added to poly alpha olefin base oil, etc. Examples include those mainly containing a fluororesin, and those obtained by adding a fluororesin or the like to a base oil of perfluoropolyether. The grease preferably has a consistency of 150 to 400 defined by Japanese Industrial Standard K2220 at -40 to 40 ° C. When the consistency is below the lower limit of 150, it becomes difficult for the grease to be filled into the pores of the porous metal. When the consistency exceeds the upper limit of 400, the grease is scattered during the operation of the shutter, or the grease is removed from the sliding surface. It becomes easy to leave. In particular, a grease obtained by adding a fluororesin to a base oil of perfluoropolyether has a consistency of about 260 to 300, is chemically stable and can be used in a wide temperature range, and can keep a change in braking force small.

  Pastes include those obtained by adding a fluororesin or the like to a poly α-olefin base oil, and those obtained by adding lithium soap, molybdenum disulfide or the like to mineral oil. Examples of the solid lubricant include molybdenum disulfide, tungsten disulfide, and graphite. As dry film lubricants, there are those obtained by fixing molybdenum disulfide, tungsten disulfide, graphite or the like with an organic or inorganic binder.

<Example>
Hereinafter, the present invention will be described specifically by way of examples.
(1) The leading blade brake lever 16 is made of stainless steel SUS630 by MIM (Metal Injection Molding). FIG. 5 is a chart showing an outline of the MIM process. The MIM process has procedures of kneading, granulation, injection molding, drying, degreasing, and sintering. First, SUS630 metal powder, a binder (a binder such as resin or wax), and acrylic beads (particle size: 20 μm, mixing rate 20%) are kneaded with a kneading machine so that the metal powder, binder, and acrylic beads are uniform. A mixed raw material dispersed in the mixture was obtained. Granulation was performed from the mixed raw material.

  (2) Next, a separately manufactured die for the leading blade brake lever is set in an injection molding machine, and the mixed raw material produced in the granulation process is extruded into the die to produce an injection molded product of the leading blade brake lever 16. Produced. The brake lever injection-molded product was placed in a furnace and dried, degreased and sintered in order. Each process of drying, degreasing, and sintering is mainly a series of heat treatment processes, except that temperature conditions are different. After drying the injection-molded product, the binder was removed by a degreasing process, and acrylic beads were vaporized by a sintering process, and a finished product of the leading blade brake lever 16 was obtained. Since the portion where the acrylic beads are vaporized becomes the pores of the porous metal, the pore diameter of the porous metal and the volume ratio of the pores can be controlled by changing the particle size and mixing ratio of the acrylic beads. Further, the rear blade brake lever 17 was produced in the same MIM process. Since the volumetric shrinkage of the injection-molded product occurs due to the sintering treatment, it is necessary to design the mold in consideration of the shrinkage and select the particle size of the acrylic beads.

  Subsequently, a shutter durability test in which the shutter blades are repeatedly driven will be described. The leading blade brake lever 16 and the trailing blade brake lever 17 produced in the above MIM process are incorporated in the leading blade braking mechanism 30 and the trailing blade braking mechanism 31 of the focal plane shutter shown in FIG. Grease was applied to the contact surface with the washer (made of PET), that is, the frictional force generation region with a brush. The grease was also filled in the small holes of the brake levers 16 and 17.

  As a comparative example of the shutter durability test, brake levers having the same dimensions and shapes as the leading blade brake lever 16 and the trailing blade brake lever 17 were produced. Each brake lever of these comparative examples is obtained by pressing a steel material and applying NiP plating as in the conventional product. Each brake lever of the comparative example was incorporated into a focal plane shutter as in the example, and the same type of grease was applied to the contact surface of each brake lever with a washer (made of PET) with a brush. That is, the difference between the example and the comparative example is that the brake lever of the example is made of porous metal, whereas the brake lever of the comparative example is made of NiP-plated steel and is not porous.

  Durability tests were performed on the focal plane shutters of the above-described examples and comparative examples at two types of curtain speeds of 2.9 msec and 2.2 msec to evaluate the durability of the shutter blades and arms. The curtain speed is the time from the start of opening the opening window 1a (see FIG. 1) to completion, or the time from the start of the second curtain starting to close the opening window 1a to completion, 2.9 msec. The curtain speed is a speed enabling a shutter speed of 1/8000 sec.

  The evaluation results are as shown in FIG. FIG. 6 is a table showing the results of the shutter durability test of the example and the comparative example. As shown in FIG. 6, in the embodiment, no abnormality was observed at any curtain speed. However, in the comparative example, when the curtain speed was 2.9 msec, the number of runnings was 230,000, and the curtain speed was 2.2 msec. When the number of runnings was 160,000, abnormalities such as damage to the shutter blades occurred.

  Further, durability tests were performed on the focal plane shutters of these examples and comparative examples at a curtain speed of 2.2 msec, and the relationship between the number of runnings and the braking force was examined. FIG. 7 is a graph showing the relationship between the number of travels of the shutter blades and the braking force of the braking mechanism. In FIG. 7, the horizontal axis represents the number of runnings, the vertical axis represents the braking force, the focal plane shutters of the example and the comparative example are operated at a curtain speed of 2.2 msec, and the braking force is applied using a torque meter every predetermined number of times. The measured values are plotted. The brake lever made of porous metal according to the example has little change in brake force from the beginning to the maximum number of times of 300,000, and the brake performance is kept constant. This is because the grease impregnated in the small pores of the porous metal oozes out to the surface with the increase in the number of times of travel and suppresses an increase in frictional force. On the other hand, in the brake lever of the conventional product of the comparative example, the braking force started to increase after traveling 160,000 times, and abnormalities such as breakage of the shutter blades occurred. It was. In the endurance test of the comparative example, when there was an abnormality such as a shutter blade, it was replaced with a new one and the endurance test was continued up to 300,000 times.

  As can be seen from the durability test results described above, the focal plane shutter 100 according to the present embodiment uses a porous metal brake lever coated with grease, so that even if the number of shutter operations increases, a stable brake can be achieved. The performance can be maintained. As described above, since the braking performance is stable, the light-shielding blade and the arm are not easily damaged, and the durability of the shutter device is improved. In addition, the curtain speed can be increased, and the speed and accuracy of the shutter can be increased. As a result, according to the camera provided with the focal plane shutter 100, it is possible to improve image quality and to display various images.

  In the above-described embodiment, the porous member in which grease is applied to the brake levers 16 and 17 of the braking mechanism is used. However, the same effect can be obtained even when applied to the friction member of the braking mechanism, that is, the washer. In addition, when the porous member is applied to the rotation shaft of the drive mechanism, even if the number of shutter operations increases, the friction torque is maintained constant, so that the curtain speed hardly varies. The porous member coated with grease may be used in combination with these brake lever, washer, and rotating shaft.

  The present invention is not limited to the embodiments described above as long as the characteristics are not impaired. For example, if the brake levers 16 and 17 of the braking mechanism are porous members, the material is not limited to stainless steel. In the above embodiment, the porous brake levers 16 and 17 are manufactured by the MIM process using metal powder as a raw material, but may be manufactured by a manufacturing method other than MIM. Furthermore, the raw material is not limited to a metal or an alloy, and for example, ceramic may be used. The lubricant added to the frictional force generation region of the brake levers 16 and 17 is not limited to grease, and paste, solid lubricant, dry film lubricant, and the like can be used.

  The present invention is not limited to the focal plane shutter, but can also be applied to a lens shutter or a CCD light shielding shutter for a digital camera. The shutter device of the present invention can be mounted on a single-lens reflex camera, a compact camera, or the like.

It is a schematic block diagram of the front curtain and the rear curtain of the focal plane shutter according to the embodiment of the present invention. It is a schematic block diagram of the drive mechanism and braking mechanism of a focal plane shutter shown in FIG. FIG. 3 is a perspective view schematically showing a configuration of a front curtain braking mechanism 30 shown in FIG. 2. FIG. 3 is a schematic configuration diagram illustrating a state of a driving mechanism and a braking mechanism when a front curtain has completed traveling in the focal plane shutter illustrated in FIG. 2. It is a chart which shows the schematic procedure of a MIM process. It is a table | surface which shows the shutter durability test result of an Example and a comparative example. It is a graph which shows the relationship between the frequency | count of driving | running | working of a shutter blade | blade, and the braking force of a braking mechanism.

Explanation of symbols

1: Substrate 1a: Opening window 6: Lead blade driving lever 6a: Rotating shaft 6b: Driving pin 7: Rear blade driving lever 7a: Rotating shaft 7b: Driving pins 12a-12d, 13a-13d: Shading blade (shutter blade )
16: Front blade brake lever 16e, 16f: Washer 17: Rear blade brake lever 18, 19: Buffer member 20: Front curtain drive mechanism 21: Rear curtain drive mechanism 30: Front curtain brake mechanism 31: Rear curtain brake Mechanism 100: Focal plane shutter

Claims (10)

  A shutter device characterized in that a porous member holding a lubricant is used as a member that slides when a shutter blade travels. The shutter device according to claim 1,
The said porous member is obtained by baking the material which has a metal as a main component, The shutter apparatus characterized by the above-mentioned. The shutter device according to claim 2,
The shutter device, wherein the metal is stainless steel. In the shutter device according to any one of claims 1 to 3,
The shutter device according to claim 1, wherein the porous member has a pore diameter of 10 to 100 μm. In the shutter device according to any one of claims 1 to 4,
The shutter device according to claim 1, wherein a volume ratio of pores of the porous member is 10 to 30%. In the shutter device according to any one of claims 1 to 5,
The porous member is manufactured by vaporizing the vaporizable particles after dispersing the vaporizable particles in a base material. In the shutter device according to any one of claims 1 to 6,
The shutter device, wherein the lubricant is grease. The shutter device according to claim 7.
The shutter device according to claim 1, wherein the grease has a consistency defined by Japanese Industrial Standard K2220 in a range of 150 to 400. In the shutter device according to any one of claims 1 to 8,
The shutter device, wherein the porous member is used for at least one of a rotation shaft for driving the shutter blade, a brake member for braking the shutter blade, and a friction member.   A camera comprising the shutter device according to claim 1.

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