JP4429309B2 - Field scope shaft support mechanism and gimbal head using the same - Google Patents

Description

  The present invention relates to a shaft support mechanism for a field scope and a gimbal head using the same.

  In a so-called Digico device that connects a field scope to a digital camera and photographs a bird or the like from a distance, the total length of the optical system is relatively long at 40 to 60 cm and the weight is relatively heavy at 2 to 4 kg. For this reason, a field scope is attached to the tripod via a pan head.

  In this case, if the elevation angle of the field scope is changed, the position of the center of gravity changes. Therefore, if the braking of the field scope support mechanism is loosened, the position of the center of gravity may change at an accelerated rate and the equipment may fall.

Therefore, in order to prevent the center of gravity from changing even if the elevation angle of the digital apparatus is changed, a gimbal head is used.
JP 2001-263330 A

  In this type of head support mechanism for a field scope and a gimbal head using the same, braking by frictional force can be adjusted by changing the pressing force between the sliding surfaces. In order to make it possible to change the elevation angle gently without vibrating the field scope, it is necessary to make the static friction coefficient between the sliding surfaces substantially the same as the dynamic friction coefficient. For this purpose, it is necessary to obtain a frictional force by smoothing the sliding surface and increasing the pressing force.

  However, since the frictional force between a pair of sliding surfaces has been used in the past, a relatively large vertical drag is required to obtain an appropriate frictional force. In addition to being inferior in performance, there was a problem that operability deteriorated. Even when silicone grease is put between sliding surfaces to enable smooth movement due to its viscosity, it is necessary to further increase the vertical drag to obtain sufficient braking when moving the equipment. There has been a problem that the influence of alteration due to the oxidation of grease becomes relatively large.

  In view of such problems, an object of the present invention is to improve the durability and operability of a fieldscope shaft support mechanism and a gimbal head using the same.

In the first aspect of the shaft support mechanism for the field scope according to the present invention,
A support shaft is erected from the field scope mounting portion on the base end side, a screw is formed at the tip of the support shaft, and a cut surface parallel to the longitudinal direction is formed between the screw and the intermediate position in the longitudinal direction. A supported spindle,
A radial bearing and a shaft support body in which a hole into which the radial bearing is fitted are formed, an insertion hole is formed in one end surface, and an engagement piece is erected on the end surface are provided, and the support shaft is the radial An inner race of the bearing and a shaft support portion inserted and inserted into the insertion hole,
Each of the plurality and the support shaft side plate engaging hole is formed in the central portion, and a central portion the insertion hole is formed in and periphery shaft支体side plate engaging notch or engaging hole is formed on, alternately sheet farthest side from chromatic to and journal portion is axial支体side plates, are inserted support shaft into the insertion hole of the engaging hole and the shaft支体side plate support shaft side plates, said supporting shaft The engagement hole of the support shaft side plate is engaged with the position of the cut surface so that the side plate rotates integrally with the support shaft, and the engagement notch or the engagement hole of the support shaft side plate is A friction part that engages with an engagement piece and prevents rotation of the shaft support side plate;
A braking adjustment dial in which a screw to be screwed with the screw of the support shaft is formed at the center;
A thrust roller bearing that is disposed between the shaft support side plate on the farthest side and the braking adjustment dial, and a hole through which the support shaft is inserted is formed in the center portion;
The braking adjustment dial has a pressing surface that directly or indirectly contacts the roller of the thrust roller bearing.

  According to a second aspect of the field scope shaft support mechanism of the present invention, in the first aspect, a hole that is disposed between the thrust roller bearing and the pressing surface of the braking adjustment dial and through which the support shaft is inserted is a central portion. It further has a pressing spring formed.

In the first aspect of the gimbal head for field scope according to the present invention,
A rotating body in which a support shaft is erected from a base-side field scope mounting portion, and a screw is formed at the distal end of the support shaft;
A radial bearing, and a shaft support body in which a hole into which the radial bearing is fitted is formed, and an insertion hole is formed on one end surface, and the support shaft is respectively provided in the inner race and the insertion hole of the radial bearing. Inserted and inserted shaft support, and
Insertion hole is formed in the center portion, of the support shaft in the insertion hole, and a plurality of slip plates portion protruding from the end face of the shaft 支体 is inserted,
A braking adjustment dial having a recess for accommodating the plurality of slip plates, wherein a screw to be screwed with the screw of the support shaft is formed at the center of the bottom surface of the recess;
A hole is formed in the central portion between the plurality of slip plates and the bottom surface of the recess of the brake adjustment dial or between the plurality of slip plates and the end surface, and through which the support shaft is inserted. A pressure spring;
And off I over field scope for axial support mechanisms drag between the plurality number of sheets of the slip plate was made to increase by screwing the have to rotate the said braking adjusting dial to the end surface side,
An arm in which a base end portion is pivotally supported and a shaft support body of the shaft support mechanism is fixed to a distal end portion;
A base on which a support shaft of the support mechanism is erected;
And the base is directly or indirectly attached to the adapter on the field scope side.

In the second aspect of the gimbal head for field scope according to the present invention , in the first aspect, the plurality of slip plates are each coated with fluororesin on at least one surface of the metal plate.

According to the configuration of the first aspect of the field scope shaft support mechanism, when the brake adjustment dial is turned and screwed to the shaft support side, a plurality of support side plates and the shaft support side are arranged alternately. A frictional force is generated between four or more pairs of sliding surfaces between the plates and between the end face of the shaft support and the next support side plate, and the pressing force applied from the brake adjustment dial is more than four pairs of sliding surfaces. Acts as a vertical drag between each moving surface. For this reason, even if the frictional force between one face is relatively small, the total frictional force is more than four times that, and the pressing force can be reduced to 1/4 or less than the conventional to obtain the same frictional force. There is an effect.

  As a result, wear deterioration due to friction is reduced, smooth rotation can be maintained over a long period of time, and durability is improved. Further, since the torque required for the rotation of the brake adjustment dial may be ¼ or less than the conventional torque, the operability is improved. In other words, the support surface side plate and the support body side plate having a smooth surface with a relatively small friction coefficient can be used, and thus, the field scope can be made smooth and smooth without using grease between the sliding surfaces. There exists an effect that it becomes possible to rotate stably. Further, if grease is not used, there is no deterioration in friction performance due to its oxidation, so that the durability is improved from this viewpoint.

  Further, since the thrust roller bearing is disposed between the shaft support side plate farthest from the shaft support and the brake adjustment dial, the brake adjustment dial can be rotated with a relatively small torque. The operability is improved.

According to the configuration of the second aspect of the field scope shaft support mechanism , a pressing spring is further provided between the thrust roller bearing and the pressing surface of the braking adjustment dial. Thus, the change of the frictional force can be moderated. This makes it possible to finely adjust the change in the frictional force, thereby improving the operability.

According to the configuration of the first aspect of the field scope gimbal head, when the braking adjustment dial is rotated and screwed to the end face side, the plurality of slip plates are pressed to the end face side. Since slip occurs between the plurality of slip plates, the rotating body can be smoothly rotated even if the thrust roller bearing of the first aspect is not used.

  In addition, the change in the frictional force between the plurality of slip plates is gradually increased by the pressing spring, and the frictional braking force at the time of adjusting the elevation angle of the field scope can be finely adjusted.

Since a plurality of slip plates are overlapped, the entire sliding area is relatively wide, and the normal drag acting between the slip plates is the same according to the law of action / reaction, so that it is conventional to obtain the same friction force. As a result, the pressing force can be greatly reduced, smoother sliding is possible, wear deterioration due to friction is reduced, smooth rotation can be maintained over a long period of time, and durability is improved. Further, since the torque required for the rotation of the brake adjustment dial may be small, the operability is good. For these reasons, the field scope can be smoothly and stably rotated without using silicone grease, and the friction performance is not deteriorated due to oxidation of the silicone grease.
Since the digital camera device has a relatively large enlargement magnification, the field of view fluctuates greatly due to slight shaking. Therefore, if the tripod is turned back, fine adjustment must be performed again, and there is a risk of missing a photo opportunity. According to the above, it is possible to prevent such a situation from occurring due to the above-described action.

According to the configuration of the second aspect of the gimbal pan head for the field scope, slip occurs between the plurality of slip plates at the time of adjusting the elevation angle of the field scope, and the kinetic friction coefficient and static friction at the time of the slip are caused by the fluororesin layer. Since the coefficient is relatively small, the field scope can be smoothly rotated when adjusting the elevation angle, and the elastic deformation of the tripod at this time can be reduced. It is possible to reduce the tripping back of the tripod with the disappearance of the elastic deformation of the tripod when it is separated from the digital apparatus.

  Other objects, configurations and effects of the present invention will become apparent from the following description.

  FIG. 7 is a perspective view of the main part of the digital system, and FIG. 8 is a perspective view of the main part of the digital system of FIG. 7 viewed from the opposite side.

  In this system, a field scope 12 is attached to the upper end of a tripod 10 via a camera platform 11 so that its elevation angle and azimuth can be changed. A digital camera 13 is attached to the eyepiece of the field scope 12 via an adapter.

  The pan head 11 has a cantilever gimbal structure. An adapter 120 fixed to the field scope 12 (not visible by being hidden by the adapter 110 in FIG. 8) is attached to the adapter 110 at the top inner tip of the camera platform 11 so that its longitudinal position can be adjusted.

  In the gimbal head 11, a shaft support mechanism 112 is fixed to the upper end of an L-shaped arm 111 with its central axis orthogonal to the central axis of the tripod 10. On the other hand, as shown in FIG. 5, the base 31 of the rotating body 30 is screwed to the pan-head adapter 110, and the shaft 32 (see FIG. 2A) of the rotating body 30 is inserted through the shaft support portion 20. A braking adjustment dial 40 is screwed to the tip portion.

  FIG. 1 is an exploded perspective view of the shaft support mechanism 112, and FIG. 5 is a perspective view of the assembled shaft support mechanism 112. 2A and 2B are a front view and a right side view of the rotating body in FIG. 1, respectively, and FIGS. 3A and 3B are a front view and a right side of the shaft support portion 20 in FIG. FIGS. 4A and 4B are a front view and a right side view of the brake adjustment dial in FIG. 1, respectively. FIG. 6 shows the shaft support mechanism 112 in an assembled state, in which the top from the center line is a longitudinal sectional view, and the bottom from the center line is an external front view.

  In the rotating body 30, a shaft 32 is erected at the center portion of the base 31, and stop holes 310 to 313 are positioned 90 degrees apart from each other about the shaft 32 on the base 31 around the shaft 32. Is formed. Screws (not shown) are inserted into the retaining holes 310 to 313, and the base 31 is screwed to the pan / tilt head side adapter 110 of FIG. A male screw 33 is formed at the tip of the shaft 32, and a female screw 41 is formed on the axial center of the braking adjustment dial 40, and the male screw 33 is screwed to the female screw 41.

  On the other hand, in the shaft support portion 20, holes 22 and 23 are formed in the shaft support body 21 side by side in the axial direction of the shaft support body 21, and screws (not shown) are inserted into these to support the shaft support body 21 in FIG. 8. The arm 111 is screwed to the front end surface. In order to enable this screwing, holes 24 and 25 for inserting drivers are formed in the shaft support 21 at positions facing the holes 22 and 23. A hole 260 is formed in the central portion of the end surface 26 opposite to the opening end of the shaft support portion 20. On the other hand, the angular ball bearings 271 and 272 are combined in the back, and the shaft 32 of the rotating body 30 is fitted into the center holes of the inner races 281 and 282 and the washer 273 with an elastic layer, and the angular ball bearings 271 and 272 and the elastic A layered washer 273 is fitted into the shaft support 21 as shown in FIG. The washer 273 with an elastic layer is formed by attaching a layer of elastic Teflon (trade name of fluororesin such as tetrafluoroethylene resin) on one surface of a metal washer to the surface on the brake adjustment dial 40 side. . The distal end side of the shaft 32 is loosely inserted into the hole 260 in the end surface 26 of the shaft support 21. Pin holes 290 to 293 into which the engaging pins 510 to 513 of the friction portion 50 are respectively inserted are formed in the outer peripheral edge portion of the end face 26.

  Here, between the middle of the shaft 32 and the male screw 33, a pair of cut surfaces 341 and 342 parallel to each other and cut in parallel with the axis of the shaft 32 are formed.

  In the friction portion 50, an engagement hole 520 a for engaging with the cut surfaces 341 and 342 is formed in the center portion of the support shaft side plate 520, and the shaft 32 is inserted into the engagement hole 520 a, thereby supporting the support shaft side. The plate 520 rotates integrally with the shaft 32 around the axis of the shaft 32. The spindle side plate 520 is disposed inside the engagement pins 510 to 513.

  On the other hand, the shaft support side plate 530 has an outer diameter equal to the outer diameter of the shaft support 21, and notches 531 a to 531 d are formed at the peripheral edge portions corresponding to the engagement pins 510 to 513. The portions of the cut surfaces 341 and 342 of the shaft 32 are inserted into the hole 531e formed in the center portion of the shaft support plate 530, and the engagement pins 510 to 513 are engaged with the notches 531a to 531d, respectively. In the present embodiment, five sets of the support shaft side plate 520 and the support shaft side plate 530 are used (support shaft side plates 520 to 523 and support shaft side plates 530 to 534). The shaft 32 of the rotating body 30 is inserted through the five central holes.

  When the rotating body 30 is rotated in a state where the opposing surfaces of the supporting shaft side plates 530 to 534 and the supporting shaft side plates 520 to 523 are in contact with each other, the rotation of the supporting shaft side plates 530 to 534 is caused by the above engagement. It is blocked and a frictional force is generated between both sides.

  Between the friction part 50 and the braking adjustment dial 40, a thrust roller bearing 60 and a washer 61 with an elastic layer as a pressing spring are arranged. The washer 61 with an elastic layer has the same configuration as the washer 273 with an elastic layer, and its Teflon is attached to the surface on the brake adjustment dial 40 side. Holes 601 and 611 are formed in the thrust roller bearing 60 and the washer 61 with an elastic layer, respectively. The shaft 32 of the rotating body 30 is further inserted into the holes 601 and 611. In this state, the male screw 33 is screwed into the female screw 41 of the brake adjustment dial 40 as described above.

  As shown in FIG. 6, a cylindrical hole 42 is formed concentrically with the center of the brake adjustment dial 40 on the bottom surface side of the brake adjustment dial 40, and a friction portion 50, a thrust roller bearing 60, and a washer with an elastic layer are formed thereon. 61 is loosely inserted. A hole 43 that is slightly larger than the outer shape of the shaft 32 is formed between the hole 42 and the female screw 41, and the distal end portion of the cut surface 34 is loosely inserted therein. A hole 44 concentric with the hole 43 is also formed on the side opposite to the hole 43 with respect to the female screw 41.

  A screw hole is formed in the front end surface of the female screw 41, and a screw 46 is screwed into the screw hole via a washer 45. Even if the pressing force by the brake adjustment dial 40 is zero, there is a gap between the step position between the hole 44 and the female screw 41 and the washer 45. Accordingly, the washer 45 functions as a stopper when the brake adjustment dial 40 is rotated too much counterclockwise.

  In order to improve operability, circumferential grooves 471 to 473 are formed on the outer peripheral surface of the brake adjustment dial 40 as shown in FIG. 4A, and rubber rings 481 are formed in these grooves as shown in FIG. ˜483 is attached. Further, as shown in FIG. 8, the tip of the lever 114 is fixed to the adapter 110.

  Further, at the base end portion of the arm 111 of the pan head 11, a shaft support mechanism 112 </ b> A having the same configuration as the shaft support mechanism 112 can freely adjust the rotation angle around the center portion of the tripod 10, so that the base of the tripod 10 can be adjusted. It is attached to the department.

  Next, the prototype will be explained.

  In the prototype, the rotating body 30, the shaft support 21, the support side plates 520 to 524, and the support side plates 530 to 534 were made of stainless steel. The brake adjustment dial 40 was made of aluminum that can be easily processed. The outer diameters of the shafts 520 to 524 and the shafts 530 to 534 were 26 mm and 38 mm, respectively. Furthermore, the thickness of the support shaft side plates 520 to 524 and the support shaft side plates 530 to 533 was 0.5 mm. The thickness of the shaft support side plate 534 closest to the brake adjustment dial 40 was 3 mm. The pitch between the male screw 33 and the female screw 41 was 0.5 mm.

  Next, the operation of the digital system configured as described above will be described.

  In FIG. 8, with the brake adjustment dial 40 loosened, the field scope 12 is swung around the axis of the shaft support mechanism 112 so that the left and right sides of the field scope 12 are balanced. A shorter fieldscope side adapter 120 (invisible in FIG. 8 is hidden behind the adapter 110) with respect to the longer pan head side adapter 110 so that the center of gravity with the camera 13 is located substantially on the axis of the shaft support mechanism 112. Slide and tighten the screw 113 to fix the camera platform side adapter 110 to the field scope side adapter 120.

  Next, the braking force is moderately adjusted with the brake adjustment dial 40, the lever 114 is gripped, and the elevation angle of the field scope 12 is adjusted in relation to the subject.

  In this adjustment, when the braking force is increased, the braking adjustment dial 40 is rotated clockwise to be screwed to the rotating body 30 side.

  At this time, since there is almost no friction between the thrust roller bearing 60 and the washer 61 with an elastic layer, the brake adjustment dial 40 can be smoothly and easily rotated. Since the shaft support plate 534 closest to the brake adjustment dial 40 is relatively thick as described above, the shaft support plate 534 is supported by the brake adjustment dial 40 via the washer 61 with elastic layer and the thrust roller bearing 60. When pressed to the 20 side, the pressing force from the shaft support side plate 534 is uniformly applied on the surfaces of the shaft support side plates and the support side plates on the shaft support portion 20 side. Thereby, the frictional force between the sliding surfaces of the shaft support side plates 530 to 534 and the support shaft side plates 520 to 524 becomes uniform, and the field scope 12 can be smoothly rotated. Further, the support shaft side plates 520 to 524 and the support shaft side plates 530 to 534 are made of stainless steel and have smooth surfaces, and the static friction coefficient thereof is substantially equal to the dynamic friction coefficient, so that the field scope 12 is smoothly and stably rotated. be able to.

  When the braking adjustment dial 40 is further screwed to the shaft support portion 20 side and the vertical drag acting between the adjacent sliding surfaces of the shaft support side plates 520 to 524 and the shaft support body side plates 530 to 534 is increased, it is proportional to this. This increases the frictional force between the sliding surfaces. At this time, since the elastic layer is formed on the washer 61 with an elastic layer, the change of the pressing force with respect to the screwing distance of the brake adjustment dial 40 can be moderated, and thereby the fine adjustment of the change of the frictional force becomes possible.

  Further, since there are five sets of the spindle side plates 520 to 524 and the shaft support side plates 530 to 534 and the frictional force acts between the end face 26 and the spindle side plate 520 in contact therewith, these frictions are also generated. The surface pair becomes 10, and the pressing force applied from the braking adjustment dial 40 acts as a vertical drag between each of these 10 pairs of opposing surfaces. For this reason, even if the friction force between the one-to-face surfaces is relatively small, the total friction force is ten times that, and the pressing force can be reduced to 1/10 compared to the conventional case to obtain the same friction force.

  Thereby, wear deterioration due to friction is reduced, smooth rotation can be maintained over a long period of time, and durability is improved. Further, since the torque required for the rotation of the brake adjustment dial 40 may be 1/10 of the conventional one, the operability is good. In other words, the spindle side plates 520 to 524 and the shaft support side plates 530 to 534 can be made of stainless steel having a smooth surface whose static friction coefficient is almost equal to the dynamic friction coefficient, thereby using silicone grease or the like. Even without this, the field scope 12 can be smoothly and stably rotated. Further, since the friction performance is not deteriorated due to the oxidation of the silicone grease, the durability is improved from this viewpoint.

  FIG. 9 is an exploded perspective view of the shaft support mechanism 112B according to the second embodiment of the present invention. FIG. 10 shows the shaft support mechanism 112B in an assembled state, in which the upper side from the center line is a longitudinal sectional view and the lower side from the center line is an external front view.

  The rotating body 30A is different from the rotating body 30 in that the cut surfaces 341 and 342 in FIG. 1 are not formed. The shaft support 20 </ b> A is different from the shaft support 20 in that the pin holes 290 to 293 in FIG. 1 are not formed in the end surface 26 of the shaft support 21. The friction part 50A does not have the engagement pins 510 to 513 in FIG. 1, and uses slip plates 540 to 545 instead of the support side plates 520 to 524 and the support side plates 530 to 534. Different from the friction part 50. The slip plates 540 to 545 are all the same as the washer 61 in FIG. 1, and all have Teflon attached to the surface on the adjustment dial 40 side. Further, instead of the thrust roller bearing 60 and the washer 61 shown in FIG. 1, a pressing spring including washers 62 and 63 and a wave washer 64 interposed therebetween is used. Each of the slip plates 530 to 534, the washers 62 and 63, and the wave washer 64 has an insertion hole formed in the center thereof, and the shaft 32A of the rotating body 30A is inserted through these holes.

  Other configurations are the same as those of the first embodiment.

  In the second embodiment configured as described above, the braking adjustment dial 40 is rotated clockwise to increase the braking force.

  At this time, the brake adjustment dial 40 is screwed toward the rotating body 30A and the slip plates 540 to 545 are pressed by the pressing spring, but the friction coefficient between the Teflon and the metal surface is relatively small (for example, the dynamic friction coefficient is 0). .05, the coefficient of static friction is 0.1), the friction part 50A has only a frictional force that restricts rotation, and slip occurs between the opposing surfaces of the slip plates 540 to 545. Even if one thrust roller bearing 60 is not used, the rotating body 30A can be smoothly rotated.

  Further, due to the elasticity of Teflon deposited on one surface of each of the pressing spring and the slip plates 540 to 545, the change in the frictional force at the frictional portion 50A increases more slowly than in the first embodiment. Thus, the friction braking force at the time of adjusting the elevation angle of the field scope 12 can be finely adjusted as compared with the case of the first embodiment.

  Since the entire sliding area of the slip plates 540 to 545 is relatively wide and the normal drag acting between each surface is the same due to the law of action and reaction, the pressing force is greatly increased compared to the conventional to obtain the same friction force. Thus, smoother sliding is possible, wear deterioration due to friction is reduced, smooth rotation can be maintained over a long period of time, and durability is improved. Further, since the torque required for the rotation of the brake adjustment dial 40 may be small, the operability is good. Therefore, the field scope 12 can be smoothly and stably rotated without using silicone grease, and the friction performance is not deteriorated due to oxidation of the silicone grease. .

  Furthermore, when the elevation angle of the field scope 12 is adjusted, slip occurs between the opposing surfaces of the slip plates 540 to 545, and the dynamic friction coefficient and the static friction coefficient at the time of the slip are small as described above due to the Teflon layer. The field scope can be smoothly rotated during adjustment, and the elastic deformation of the tripod at this time can be reduced, which causes the elastic deformation of the tripod to disappear when the field scope stops and the hand is released from the digital device. It is possible to almost eliminate the tripod back.

  Since the digital zoom device has a relatively large enlargement magnification, the field of view fluctuates greatly due to slight shaking, and therefore, when the tripod is turned back, fine adjustment must be performed again, and there is a risk of missing a photo opportunity. According to the above, it is possible to prevent such a situation from occurring due to the above-described action.

  In Example 3 of the present invention, the direction of the slip plates 540 to 545 is changed so that the adjacent Teflon layers of the slip plates 540 to 545 face each other and contact each other in Example 2 of FIGS. 9 and 10. That is, in FIG. 9, the slip plates 540 to 545 are arranged and assembled so that the Teflon layers of the slip plates 540 to 545 are the right side, the left side, the right side, the left side, the right side, and the left side.

  Other points are the same as those of the second embodiment.

  As a result of trial manufacture and confirmation, it was found that Example 3 can adjust the elevation angle more smoothly and stably than the case of Example 2, and has good operability. This is because the friction force between the Teflon surfaces is sufficiently smaller than the friction force between the metal surface and the Teflon surface (for example, the static friction coefficient and the dynamic friction coefficient between the Teflon surfaces are 0.04 and 0.05, respectively). It is considered that sliding does not occur between the metal surface and the Teflon surface, and sliding occurs only between the Teflon surfaces, and that the static friction coefficient is smaller than the dynamic friction coefficient between the Teflon surfaces.

  Note that the present invention includes various other modifications.

  For example, on the metal surfaces of the slip plates 540 to 545 and the washers 62 and 63, an oil film may be formed so as to prevent oxidation.

  In Example 1, a single-sided Teflon-coated metal plate may be used as in Example 2 or 3. Furthermore, in Examples 1 to 3, a double-sided Teflon-coated metal plate may be used.

  Furthermore, a configuration using one ball bearing instead of the angular ball bearings 271 and 272 may be used.

  In addition, with respect to the pressing spring, the metal surface of the slip plate 545 may be used by omitting the washer 62 instead of the washer 62 which is a component in the second or third embodiment, and further, the washer 63 may be omitted and adjusted. The inner surface of the dial 40 may be used. Moreover, in Example 1, the pressure spring of Example 2 is used instead of the washer 61 with elastic layer as the pressure spring, or the washer with elastic layer of Example 1 is used instead of the pressure spring of Example 2 or 3. The structure using 61 may be sufficient. The arrangement of the pressing spring may be on the end face 26 side.

  Further, instead of the male screw 33, a concave portion is formed at the tip of the shaft 32, and a female screw is formed on the inner peripheral surface of the concave portion. On the other hand, a male screw that is screwed with this is provided at the center of the adjustment dial 40. It may be a configuration.

It is a disassembled perspective view of the shaft support mechanism which concerns on Example 1 of this invention. (A) And (B) is the front view and right view of a rotary body in FIG. 1, respectively. (A) And (B) is the front view and right view of the axial support part 20 in FIG. 1, respectively. (A) And (B) is the front view and right view of a brake adjustment dial in FIG. 1, respectively. It is a perspective view which shows the state by which the axial support mechanism of FIG. 1 was assembled. Above the center line is a longitudinal sectional view of the shaft support mechanism of FIG. 5, and below the center line is an external front view of the shaft support mechanism. It is a principal part perspective view of a Digico system. It is the principal part perspective view which looked at the digital system of FIG. 7 from the other side. It is a disassembled perspective view of the shaft support mechanism which concerns on Example 1 of this invention. Above the center line is a longitudinal sectional view of the shaft support mechanism of FIG. 9 assembled, and below the center line is an external front view of the shaft support mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Tripod 11 Gimbal head 110 Head adapter 111 Arm 112, 112A, 112B Axis support mechanism 12 Field scope 120 Field scope side adapter 13 Digital camera 20, 20A Axis support 21 Axis support 22-25 Hole 26 End face 260, 531d, 601, 611, 43, 44 Holes 271, 272 Angular contact ball bearings 273, 61 Buffer plate 281, 282 Inner race 290-293 Pin hole 30, 30A Rotating body 31 Base 310-313 Stop hole 32, 32A Shaft 33 Male thread 341 , 342 Cut surface 40 Adjustment dial 41 Female screw 42 Hole 45 Washer 50, 50A Friction part 510-513 Engagement pin 520-524 Axle side plate 520a Engagement hole 530-534 Axle side plate 531a- 531d Notch 540-545 Slip plate 60 Thrust roller bearing 62, 63 Washer 64 Wave washer

Claims (7)

A support shaft is erected from the field scope mounting portion on the base end side, a screw is formed at the tip of the support shaft, and a cut surface parallel to the longitudinal direction is formed between the screw and the intermediate position in the longitudinal direction. A supported spindle,
A radial bearing and a shaft support body in which a hole into which the radial bearing is fitted are formed, an insertion hole is formed in one end surface, and an engagement piece is erected on the end surface are provided, and the support shaft is the radial An inner race of the bearing and a shaft support portion inserted and inserted into the insertion hole,
Each of the plurality and the support shaft side plate engaging hole is formed in the central portion, and a central portion the insertion hole is formed in and periphery shaft支体side plate engaging notch or engaging hole is formed on, alternately sheet farthest side from chromatic to and journal portion is axial支体side plates, are inserted support shaft into the insertion hole of the engaging hole and the shaft支体side plate support shaft side plates, said supporting shaft The engagement hole of the support shaft side plate is engaged with the position of the cut surface so that the side plate rotates integrally with the support shaft, and the engagement notch or the engagement hole of the support shaft side plate is A friction part that engages with an engagement piece and prevents rotation of the shaft support side plate;
A braking adjustment dial in which a screw to be screwed with the screw of the support shaft is formed at the center;
A thrust roller bearing that is disposed between the shaft support side plate on the farthest side and the braking adjustment dial, and a hole through which the support shaft is inserted is formed in the center portion;
And the brake adjustment dial has a pressing surface that directly or indirectly contacts the roller of the thrust roller bearing.   2. The pressure spring according to claim 1, further comprising a pressing spring disposed between the thrust roller bearing and the pressing surface of the braking adjustment dial and having a hole through which the support shaft is inserted formed in a central portion. A shaft support mechanism for field scope.   3. The field according to claim 2, wherein both the support shaft side plate and the support shaft side plate are made of stainless steel, and the pressing spring is formed by attaching an elastic layer to one surface of a metal plate. Scope support mechanism for scope.   The support shaft-side plate or the support shaft-side plate has a fluororesin layer attached to at least one surface of a metal plate. A shaft support mechanism for field scope. A shaft support mechanism for a field scope according to any one of claims 1 to 4,
An arm in which a base end portion is pivotally supported and a shaft support body of the shaft support mechanism is fixed to a distal end portion;
A base on which a support shaft of the support mechanism is erected;
A gimbal head for field scope, wherein the base is directly or indirectly attached to an adapter on the field scope side. A rotating body in which a support shaft is erected from a base-side field scope mounting portion, and a screw is formed at the distal end of the support shaft;
A radial bearing, and a shaft support body in which a hole into which the radial bearing is fitted is formed, and an insertion hole is formed on one end surface, and the support shaft is respectively provided in the inner race and the insertion hole of the radial bearing. Inserted and inserted shaft support, and
Insertion hole is formed in the center portion, of the support shaft in the insertion hole, and a plurality of slip plates portion protruding from the end face of the shaft 支体 is inserted,
A braking adjustment dial having a recess for accommodating the plurality of slip plates, wherein a screw to be screwed with the screw of the support shaft is formed at the center of the bottom surface of the recess;
A hole is formed in the central portion between the plurality of slip plates and the bottom surface of the recess of the brake adjustment dial or between the plurality of slip plates and the end surface, and through which the support shaft is inserted. A pressure spring;
And off I over field scope for axial support mechanisms drag between the plurality number of sheets of the slip plate was made to increase by screwing the have to rotate the said braking adjusting dial to the end surface side,
An arm in which a base end portion is pivotally supported and a shaft support body of the shaft support mechanism is fixed to a distal end portion;
A base on which a support shaft of the support mechanism is erected;
A gimbal head for field scope, wherein the base is directly or indirectly attached to an adapter on the field scope side. 7. The field scope gimbal head according to claim 6 , wherein each of the plurality of slip plates has a fluororesin applied to at least one surface of the metal plate .

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