JP2962070B2 - Reflector support mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reflector supporting mechanism for supporting a large reflector such as a telescope or a parabolic antenna.

[0002]

2. Description of the Related Art In the following description, a reflection telescope will be described as an example. FIG. 13 is a perspective view of a conventional supporting mechanism of a small-sized reflecting telescope similar to that shown in Japanese Patent Laid-Open No. 4-20913, and FIG. 14 is a sectional view of the same. FIG.
In FIG. 14, reference numeral 1 denotes a reflecting mirror of a reflecting telescope, hereinafter referred to as a mirror. 1a is the mirror surface of the mirror 1. 2 is a support flange for supporting a mirror 1 and a support mechanism (described later) around the mirror, and 3 is a support flange for integrating the mirror with a lens barrel (described later), and 3 is a mirror 1 that applies a load in the radial direction of the mirror 1 (that is, a direction perpendicular to the mirror axis). 4 is an axial support mechanism that receives a load of the mirror 1 in the axial direction (that is, the mirror axis direction) below the mirror 1, and 5 is a tilt and height adjustment of the mirror 1 with respect to the support flange 2. It is a positioning mechanism for performing.

[0003] Reference numeral 30 denotes a telescopic lens barrel, 31 denotes a holding ring for holding the mirror 1 in order to prevent the mirror 1 from falling off, 32
Is a support rod for attaching the holding ring 31 to the support flange 2.

The operation of FIGS. 13 and 14 will be described. The radial support mechanism 3 is provided at three or more locations on the outer periphery of the mirror 1 and presses the mirror 1 so as not to shift in the horizontal direction in the figure. Further, the mirror 1 receives a vertical force from both the holding ring 31 and the axial support mechanism 4, but the reflecting surface 1a of the mirror 1 needs to maintain a high shape accuracy such that an error of several microns is not allowed. It is. Therefore, it is not preferable to apply a strong, one-sided force to deform the mirror 1. Further, the support flange 2, the radial support mechanism 3, the axial support mechanism 4, and the like are made of a durable metal in order to maintain high accuracy.

The conventional support mechanisms shown in FIGS. 13 and 14 have the following disadvantages because they are configured as described above. That is, since the presser ring 31 covers a part of the reflection surface 1a of the mirror 1, the utilization efficiency of the reflection surface 1a is reduced. Since many structures are provided on the side surface of the mirror 1, the maximum diameter of the telescope becomes larger than the diameter of the mirror 1.

When the diameter of the reflecting mirror is 1 m or more, the thickness of the mirror 1 is relatively thin compared to the diameter, and the rigidity of the mirror 1 is low.
That is, the axial support mechanism 4 and the radial support mechanism 3
In order to support the weight of the mirror 1 with the press ring 31, it is necessary to strongly tighten the mirror 1, and the mirror 1 is easily deformed. When the angle of the telescope is changed, the direction in which the weight of the mirror 1 is applied changes, so that the manner in which the load is applied to each of the support mechanisms changes, so that the mirror 1 is easily deformed. When the mirror 1, the support flange 2, and other parts expand and contract due to a temperature change, distortion is likely to occur in each part due to a difference in expansion and contraction rate. In view of the above, a slightly different system is used for a large telescope having a large diameter as described below.

When the diameter of the mirror 1 is large, the system shown in FIG. 15 is used. FIG.
FIG. 1 is a cross-sectional view of a conventional large-sized reflector supporting mechanism similar to that shown in Japanese Patent Application Laid-Open Publication No. H10-209,873. In the figure, 1, 2, 5, and 30 are the same as in FIG. 43 is a radial support mechanism for supporting the load of the mirror 1 in the radial direction, 44 is an axial support mechanism for supporting the load of the mirror 1 in the axial direction,
Reference numeral 60 denotes a central axis (hereinafter referred to as an axis) of the mirror 1 shown for explanation.

FIG. 15 shows two radial support mechanisms 4.
Although three and four axial support mechanisms 44 are shown, in an actual apparatus, ten or more units are used.

To explain the details of FIG. 15, FIG. 16 is an enlarged view of the axial support mechanism 44 of FIG. 15, and FIG. 17 is an enlarged view of the radial support mechanism 43 of FIG. For convenience of explanation, FIG. 15 shows a case where the mirror 1 is horizontal, that is, the axis 60 of the mirror 1 is vertical.
16 and 17 show the case where the axis 60 of the mirror 1 forms an angle θ with the horizontal plane.

In FIG. 16, 1, 2, 44, and 60 correspond to FIG.
Is the same as 6 is a link rotatably connected at one end to the bottom surface of the mirror 1 via a bottom surface pin joint 9 (described later);
Is a lever movably connected to the other end of the link 6, 8 is an axial weight provided at the other end of the lever 7, and 9 is a mirror as a first joint for rotatably connecting the link 6 and the mirror 1. 1 is a bottom joint provided on the bottom surface of the first joint, 10 is a pin joint as a second joint that rotatably connects the link 6 and the lever 7, and 11 is a support shaft that supports the lever 7 in a swingable manner. Mounted on flange 2. The axial support mechanism 44 includes a link 6, a lever 7, an axial weight 8, a bottom pin joint 9, a pin joint 10, and a support shaft 11.

In FIG. 17, 1, 2, 43, and 60 correspond to FIG.
Is the same as Numeral 12 is a side pin joint 15 at one end (described later).
, A link rotatably connected to the side surface of the mirror 1, 13 a lever movably connected to the other end of the link 12, 14 a radial weight provided at the other end of the lever 13, and 15 a link A side surface pin joint provided on a side surface of the mirror 1 as a first joint for rotatably connecting the mirror 12 to the mirror 12, and a pin 16 as a second joint for rotatably connecting the link 12 and the lever 13 to each other. Joint, 17 is lever 1
The support shaft 3 is pivotally supported and is attached to the support flange 2. Radial support mechanism 43 is link 1
2, a lever 13, a radial weight 14, a side pin joint 15, a pin joint 16 and a support shaft 17.

Next, the operation will be described. First, FIG.
In the axial support mechanism 44, when this is the weight of the mirror 1 and W ₁ in charge, component W _A1 of the axial direction of the self-weight W ₁ is represented from the figure as follows. W _A1 = W ₁ sin θ (1) where W ₁ is the weight of the mirror 1 supported by the axial support mechanism 44 .theta .: the elevation angle of the mirror 1. On the other hand, the axial force acting on the mirror 1 by the axial support mechanism 44 _FA1 is as follows, ignoring the weight of the link 6, the lever 7, and the like.

[0013] _{F A1 = W 2 sin θ ·} (l 2 / l 1) ···· (2) wherein W _2: Aki weight l ₁ sialic wait 8: distance between the pin joint 10 and the support shaft 11 l ₂ : Distance between the support shaft 11 and the center of gravity of the axial weight 8 In order to set W _A1 = F _A1 , W ₁ sin θ = W ₂ sin θ · (l ₂ / l ₁ ) W ₂ · (l ₂ / l ₁ ) = W ₁ ···· (3) and so that, to balanced regardless of the weight W ₂ and the axial weights 8, the weight and axial weight 8 of the mirror 1 be determined leverage l ₂ / l ₁ θ (W _A1 =
F _A1 ), and the axial support mechanism 44 can support the axial component of the weight of the mirror 1 irrespective of the elevation angle of the mirror 1.

The mirror 1, the support flange 2, the lever 7
Even if it expands or contracts due to a change in temperature, the link 6 is provided, so that an unreasonable force, for example, a radial force, does not directly act on the mirror 1. Θ = 0 °, that is, the axis 6 of the mirror 1
When 0 is horizontal, F _A1 = 0 as evident from equation (2).
As a result, the axial weight 8 has no role. That is, the axial weight 8 is used only to generate a force in the axial direction.

Meanwhile, the radial support mechanism 43 shown in FIG. 17, when the weight of the mirror 1 and W _1, component W _R1 in the radial direction of the self-weight is represented as follows: As can be seen from Figure 17. W _R1 = W ₁ cos θ (4) where W ₁ is the weight of the mirror 1 borne by the radial support mechanism 43 θ: the elevation angle of the mirror 1 On the other hand, the radial force acting on the mirror 1 by the radial support mechanism 43 F _R1 is as follows.

[0016] _{F R1 = W 3 cos θ ·} (l 4 / l 3) ···· (5) where W _3: the weight of the radial weights 14 l _3: the distance between the pin joint 15 and the support shaft 17 l ₄ : Distance between the support shaft 17 and the center of gravity of the radial weight 14 Therefore, the weight W ₃ and leverage of the radial weight 14
If it is set so as to satisfy l ₄ / l ₃ order, W ₃ · (l ₄ / l ₃ ) = W ₁ ... (6) The weight of the mirror 1 and the radial weight 14 are set to the elevation angle of the mirror 1. Regardless, they can be balanced (W _R1 = F _R1 ),
The radial support mechanism 43 can support the radial component of its own weight regardless of the elevation angle of the mirror 1.

When θ = 90 °, that is, when the axis 60 of the mirror 1 is directed to the zenith, W _R1 = 0 as apparent from the equation (4), and the radial weight 14 plays no role. Absent. That is, the radial weight 14 is used only to generate a radial force.

Next, the moment about the center of gravity of the mirror 1 will be described with reference to FIG. In the figure, W ₁ , F _A1 ,
F _R1 is the same as FIG. 16 and FIG. The radial support mechanism 43 and the axial support mechanism 44 in FIG.
Each of them is used and balanced. Therefore, for convenience of explanation, in FIG. 18, the radial force of the first radial support mechanism 43 is F _R1 , the radial force of the second radial support mechanism 43 is F _R2 , and the axial force of the first axial support mechanism 44 is Is F _A1 , and the axial force by the second axial support mechanism 44 is F _A2 . The center of gravity of the mirror 1 is G.

The leading the shortest distance to reach the radial force F _R1 from the center of gravity G l _R1, shortest distance l _R2 leading to radial F _R2, the shortest distance from the center of gravity G in the axial force F _A1 to l _A1, the axial force F _A2 The shortest distance is l _A2 . At this time, the center of gravity G
Adjust the mounting position of each support mechanism so that the following equation is satisfied with respect to the moment around. That is, the clockwise moment around the center of gravity = the counterclockwise moment around the center of gravity. (F _R1 × 1 _R1 ) + (F _A2 × 1 _A2 ) = (F _R2 × 1 _R2 ) + (F _R1 × 1 _A1 ) (7) The slight moment force from the positioning mechanism 5 However, a similar balance is established for this as well.

Due to manufacturing errors, all the axial loads, radial loads, and moments around the center of gravity described above cannot all be perfectly balanced, but the slight imbalance that occurs is caused by the positioning mechanism 5. Is absorbed by This is naturally performed in the process of determining the position of the mirror 1 by the positioning mechanism 5.

As described above, the weight of the mirror 1 is
Almost all radial and axial support mechanisms 43, 4
4 and the mirror 1 moves freely, so that the mirror 1 appears to be floating. Therefore, the mirror 1 is apparently light, and the position and angle with respect to the support flange 2 can be easily adjusted by the positioning mechanism 5 even if the weight of the mirror 1 is large.

In each of the conventional support mechanisms shown in FIGS. 13 to 18, the mirror 1 can be moved to the front, rear, left and right, or can be tilted in all directions. It is an essential condition for the mirror 1 to be able to move the mirror 1 as an apparatus.

[0023]

The conventional mirror support mechanism has the following problems since it is constructed as described above. 1. Since the structure is provided on the side surface of the mirror, the maximum diameter of the telescope is larger than the outer diameter of the mirror. 2. The axial weight is used only for generating the axial force, and the radial weight is used only for generating the radial force. Each weight needs an amount capable of independently supporting the weight of the mirror 1 alone. growing.

3. Since a large number of support mechanisms are distributed around and below the mirror, an assembler must walk around the mirror for assembly or maintenance. It takes time to work. 4. Since the length of the lever that can be manufactured is naturally limited, if the mirror is large, the weight of the weight becomes considerable, and it is not easy to adjust its position. There was a problem to say.

The present invention has been made to solve the above problems, and has the following objects. 1. A reflecting mirror support mechanism in which the structure on the side surface of the mirror is reduced and the outer diameter of the telescope does not need to be larger than the diameter of the mirror. 2. The same weight supports the weight of the mirror regardless of whether the angle of the mirror is horizontal or vertical, thus providing a reflector support mechanism that requires only a small amount of weight.

3. A reflector support mechanism that can be operated without having to walk around the mirror for assembly and maintenance / inspection, with the arrangement of the mechanisms concentrated in one place. 4. A reflector support mechanism that can easily adjust the position of the weight is obtained. It is intended to be.

[0027]

According to a first aspect of the present invention, there is provided a reflector supporting mechanism which changes its attitude with respect to the direction of gravity.
Reflector support for mounting the reflector on the support flange
In the mechanism, disposed on the back surface of the reflector,
A thrust bearing provided at the position of the center of gravity;
Swing bearing provided on the surface and swingable to the swing bearing
Hollow supported at one end by the thrust bearing
The arm and the inside of the hollow arm slide in the mirror axis direction of the reflecting mirror.
A movable shaft that is inserted so that it can be inserted and one end of which is in contact with the back surface of the reflecting mirror
And rotatable about a fulcrum provided on the hollow arm.
Held and rotatably coupled to the movable shaft
A link mechanism, and the support flange provided on the link mechanism.
The mirror axis direction and the mirror of the reflecting mirror are changed according to the posture change of the lunge.
The load acting in the direction perpendicular to the shaft is supported via the movable shaft.
A weight is provided.

Further, the reflecting mirror support mechanism according to the second aspect of the invention, when one end is coupled to the thrust bearing together
At the other end, in a direction perpendicular to the mirror axis of the reflector
A hollow arm with a weight to adjust the supporting force
It is a digit.

Further , the reflecting mirror support mechanism according to the third aspect of the present invention has a support frame whose posture changes in the direction of gravity.
In the reflector support mechanism for attaching the reflector to the
And the center of gravity of the reflector is disposed on the back surface of the reflector.
And the thrust bearing provided on the support flange.
Pivoted bearing, and pivotably supported by the pivot bearing.
A hollow arm having one end coupled to the thrust bearing;
Slidably inserted in the mirror axis direction of the reflector inside the hollow arm
A movable shaft having one end in contact with the back surface of the reflecting mirror;
The end of the movable shaft is housed in a housing provided in the hollow arm.
And the mirror axis direction of the reflecting mirror through the movable shaft.
And a first hydraulic pressure supporting a load acting in a direction perpendicular to the mirror axis
Cylinder and the support flange with the change in attitude
A weight that moves along the center axis of the hollow arm, and this weight
Hydraulic pressure generated by movement of the connected second piston
To the first hydraulic cylinder via a hydraulic pipe.
A second hydraulic cylinder is provided.

The first hydraulic cylinder is connected to a second hydraulic cylinder provided on the hollow arm by hydraulic piping, and a piston of the second hydraulic cylinder is movable along the axis of the hollow arm. A heavy weight is attached.

[0031] The fourth reaction Ikyo <br/> supporting mechanism according to the aspect of the invention, moving the second hydraulic cylinder on the hollow arm shaft
A guide that supports as much as possible and is provided on the axis of the hollow arm,
And an adjusting screw supporting the hydraulic cylinder ,
Move the mounting position of the second hydraulic cylinder on the axis of the hollow arm
A weight position adjusting device is provided.

Further, the reflecting mirror support mechanism according to the fifth aspect of the present invention is intended for use when applying the supporting mechanism according to manufacture the first to fourth invention of the reflecting mirror is difficult. Some mirrors used in certain applications have an asymmetric mirror structure. In such a mirror, since the position of the center of gravity G is displaced from the structural center of the mirror, providing a support mechanism installation hole in accordance with the position of the center of gravity can handle an unbalanced load in a flexible manner. It is very difficult because it requires advanced technology.

To solve this problem, the fifth aspect of the present invention is described.
The reflecting mirror support mechanism according to the invention of
For mounting the reflector on the supporting flange
In the mirror support mechanism, the mirror is provided on the back side of the reflecting mirror.
A thrust bearing provided near the center of gravity of the reflecting mirror;
A swing bearing provided on a support flange, and the swing bearing
Oscillatingly supported at one end to the thrust bearing
Through the arm having a weight at the other end and the center of gravity of the reflector.
Moves along a line parallel to the axis of the reflector, one end at one end
Link mechanism with weight and fulcrum on support flange
The other end is pivotally connected to the other end, and the other end is in contact with the reflecting mirror
And a movable shaft.

[0034]

In the reflecting mirror supporting mechanism according to the first to fifth aspects of the present invention, since the supporting mechanism is provided only on the back surface of the mirror and not on the side surface, the outer diameter of the telescope is reduced by the diameter of the mirror. It is not necessary to make it much larger.

Further, in the first, third and fourth inventions, the same weight always supports the load in both the axial direction and the radial direction of the mirror regardless of the angle of the mirror. Since there is no need to install weights, the entire weight of the weight can be reduced.

In any of the first to fifth inventions, since the support mechanism is arranged near the center of gravity of the back surface of the mirror, there is no need to walk around the mirror for maintenance and inspection. Is easy.

The reflecting mirror support mechanism according to the fourth aspect of the present invention can be obtained by simply turning the adjusting screw of the weight position adjusting device.
Since the weight can be moved in the mirror axial direction, it is easy to adjust the position of the weight.

[0038]

【Example】

Embodiment 1 FIG. An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of a reflector supporting mechanism according to an embodiment of the present invention. The position of the center of gravity of the mirror 1 is set to G as in FIG.
Indicated by In the figure, 1, 2, 5, and 60 are the same as those in the related art, and the description is omitted. Reference numeral 29 denotes a support mechanism installation hole provided at the center of gravity of the back surface of the mirror 1, and the upper part thereof is a hemispherical surface centered on the center of gravity G. Reference numeral 18 denotes a sleeve fitted and fixed in a support mechanism installation hole 29;
Is a thrust bearing provided on the sleeve 18 and at the center of gravity G of the mirror 1.

Reference numeral 20 denotes a support arm provided on the support flange 2, and reference numeral 21 denotes a swing bearing provided on the support arm 20, and a so-called spherical bearing is used. Reference numeral 22 denotes a hollow arm in the form of a hollow pipe fixed to the swing bearing 21, and reference numeral 23 denotes a spherical bush provided at one end of the hollow arm 22. By inserting the spherical bush 23 into the thrust bearing 19,
It constitutes a swingable thrust bearing.

Numeral 24 denotes a movable shaft inserted into the hollow arm 22, one end of which extends outside from the end of the spherical bush 23 provided at the end of the hollow arm 22, and supports the mirror 1. It is in contact with the inner surface of the installation hole 29.

Reference numeral 25 denotes a link fulcrum provided at one end of the hollow arm 22, and is provided at two places in the figure. Reference numeral 26 denotes a link mechanism rotatably held at the link fulcrum 25.
Are indicated. The end of the link mechanism 26 is rotatably connected to the movable shaft 24. The link mechanism 26 is a movable shaft 24
Is almost at a right angle. Reference numeral 27 denotes a weight attached to the end of the link mechanism 26, the position of which can be adjusted by a nut 28. Link mechanism 26, weight 27, and nut 2
8 constitute an X-axis weight moving mechanism 50. 2
The position of the center of gravity of one weight 27 is indicated by g. The distance between the center of gravity g of the two weights 27 and the oscillating bearing 21 is l ₈ ,
And it represents the distance between the spherical bushing 23 l _7.

FIG. 2 shows a detailed view of the swing bearing portion in order to show details of the structure of FIG. In the figure, reference numeral 33 denotes the central axis of the hollow arm 22. The spherical bush 23 can be inclined with respect to the opposing thrust bearing 19 (not shown) within a range of β °, and the hollow arm 22 is provided with an operating angle α ° of the swing bearing 21.
Can swing around the swing bearing 21 within the range of (1). Further, the swing bearing 21 and the spherical bush 2
3 the distance between l ₇ has a structure that can be varied slightly by a mounting screw or nut.

FIG. 3 is a schematic diagram of the operation of the swing bearing unit for explaining the operation of each unit. FIG. 3 shows the movement of the bearing constituted by the thrust bearing 19 and the spherical bush 23 and the swing bearing 21.
Is somewhat exaggerated. As described above, the portion where the movable shaft 24 contacts above the support mechanism installation hole 29 is formed in a hemispherical surface with the center of gravity G as the center.

The movement shown in FIG. 3 is equally possible in any direction, in which the mirror 1 tilts in the left-right direction and in the front-back direction. Further, only the angle of the swing bearing 21 can be changed without changing the angle of the spherical bush 23, or the reverse movement can be performed. Mirror 1
And the angle between the support flange 2 and the support flange 2 are not parallel. Again
In FIG. 3, the mirror 1 can be moved vertically by its thrust bearing 19.

In FIG. 3, the movable shaft 24 is slidable in the hollow shaft 22. For example, when the movable shaft 24 protrudes long from the end of the spherical bush 23, the mirror 1 is pushed up.
Conversely, when the length protruding from the end of the spherical bush 23 is reduced, the mirror 1 is lowered. This movement is possible only within a range where the spherical bush 23 does not protrude from the thrust bearing 19.

The mirror 1 can be freely tilted with respect to the support flange 2 in any direction (front and rear, up and down, left and right) due to the rotational movement and the parallel movement of each bearing and the expansion and contraction of the movable shaft 24 (in a certain range). Within).

To show the structure of the other parts of FIG. 1 in detail,
FIG. 4 shows a detailed view of the link mechanism section. In FIG. 4, the weight 27
Will be described. The distance from the central axis 33 of the hollow arm 22 to the two link fulcrums 25 is the same,
This is referred to as l _5. Further, distance from the link fulcrum 25 to the center of gravity of each side weight 27 are identical, which l ₆
And

The two link mechanisms 26 are provided at opposite ends of the hollow arm 22 in opposite directions.
From the above, the center of gravity of the two weights 27 is located on the central axis 33 of the hollow arm 22. The angle formed by the link mechanism 26 with the hollow arm 22 can be changed by changing the length of the movable shaft 24 or the position of the oscillating bearing 21 on the hollow arm 22, and is adjusted to be substantially 90 °. ing.

Next, the balance of forces will be described. FIG.
FIG. 5A shows an action diagram of an axial force of the support mechanism shown in FIG. 1, and FIG. 5B shows an action diagram of a radial force. In the figure, the force and its component force are indicated by a thick line, and the distance between the structure and the force acting is indicated by a thin line.

In FIG. 5a), the gravity acting on the weight 27 is W ₂₇ , the gravity acting on the center of gravity G of the mirror 1 is W ₁ , and the force of the weight 27 acting on the movable shaft 24 is F ₂₄ as in the conventional description. I have. Axial component W of self-weight W ₁ of mirror 1
As described above, _A1 is represented as follows. W _A1 = W ₁ sin θ (1) where W ₁ : weight of mirror 1 θ: elevation angle of mirror 1

On the other hand, the axial force F _{24 applied} to the mirror 1 by the movable shaft 24 is the same as that of the prior art.
Neglecting the weight of such or a link mechanism _{26, F 24 = W 27 sinθ} · (l 6 / l 5) · 2 ···· (8) wherein W _27: Gravity of the weight 27 l _5: link fulcrum 25 L ₆ : the distance between the link fulcrum 25 and the center of gravity of the weight 27

Therefore, the weight W ₂₇ of the weight ₂₇ and the lever ratio
If l ₆ / l ₅ is determined so as to satisfy the following expression, 2 · W ₂₇ · (l ₆ / l ₅ ) = W ₁ ··· (9) The weight of the mirror 1 in the axial direction and the weight 27 It can be balanced (W _A1 = F ₂₄ ), and can support the axial component of its own weight irrespective of the elevation angle of the mirror 1. Further, even if each part relatively expands and contracts relatively due to a difference in the coefficient of thermal expansion between the mirror 1 and the support flange 2, an excessive force is directly applied to the mirror 1 because the tip of the movable shaft 24 is spherical. Does not work.

On the other hand, as shown in FIG.
The distance between the 1 and the spherical bush 23 and l _7, the rocking bearing 21
When the distance to the center of gravity g of the two weights 27 and l _8. When the weight of the mirror 1 and W _1, component W _R1 in the radial direction of the self-weight is to be expressed in the following manner as described above. W _R1 = W ₁ cos θ (4) where W ₁ : weight of mirror 1 θ: elevation angle of mirror 1

On the other hand, the radial force F ₂₃ of the spherical bush 23 acts on the mirror 1 is as follows. F ₂₃ = W ₂₇ cos θ · (l ₈ / l ₇ ) × 2 (10) where W ₂₇ : weight of weight 27 l ₇ : distance between swing bearing 21 and spherical bush 23 l ₈ : swing Distance between the dynamic bearing 21 and the center of gravity g of the two weights 27

Accordingly, the weight W ₂₇ of the weight ₂₇ and the lever ratio
If l ₈ / l ₇ is set so as to satisfy the following equation, 2 x W ₂₇ · (l ₈ / l ₇ ) = W ₁ ··· (11) The weight of the mirror 1 and the weight of the weight 27 are balanced. (W _R1 =
F ₂₃ ), which can be connected to the spherical bush 2 via the hollow shaft 22.
3, the radial component of the weight of the mirror 1 can be supported regardless of the elevation angle of the mirror 1. Further, even if the relative expansion and contraction due to the difference in the coefficient of thermal expansion between the mirror 1 and the support flange 2 and the bending of the hollow arm 22 occur, the spherical bush 2 is located at the load transmitting point.
Since the mirror 3 is provided, no excessive force acts directly on the mirror 1.

Also, in FIGS. 5A and 5B, since the force of the movable shaft 24 and the force of the spherical bush 23 both act on a line passing through the center of gravity G of the mirror 1, the center of gravity G of the mirror 1 is No rotational moment is generated around it. Further, the rotational moment of the hollow arm 22 around the swing bearing 21 is also balanced as shown in the equation (11).

Further, as is apparent from the equations (9) and (11), between the distances l ₅ , l ₆ , l ₇ , l ₈ , l ₆ / l ₅ = l ₈ / l _7. Adjust each distance so that the relationship of 12) is established. Also nut 2
8 adjusts the position of the weight 27, the radial force F
It is possible to change only the axial force F ₂₄ without affecting the _23.

The center of gravity G of the mirror 1 due to a manufacturing error or the like.
In addition, the center of gravity g of the two weights 27 may slightly deviate from the expected position, so that a slight error may occur in the above-described balance. Absorbed by mechanism 5.

In the first embodiment, the support mechanism of the reflecting mirror is the mirror 1
, The optical path blocking (shielding) ratio is 0% since there is no support mechanism on the outer peripheral side surface of the mirror 1 at all.
Becomes Further, it is not necessary to make the outer diameter of the lens barrel larger than the diameter of the mirror 1.

The weight 27 has an angle θ = 0 to the mirror 1.
Since the same weight always supports both the axial load and the radial load at 180 °, it is not necessary to prepare the weight 27 separately from the axial radial, so that the entire weight of the weight can be reduced.

The support mechanism of the reflecting mirror is the center of gravity G of the mirror 1.
, The structure is concentrated at one place on the back surface of the mirror 1 and maintenance and inspection are easy.

Also, in terms of assemblability, the hollow arm 22 is held only by the swing bearing 21, and the fitting portion between the spherical bush 23 attached to the tip of the hollow arm 22 and the thrust bearing 19 is parallel to the spherical surface. Since the hole is formed, the spherical bush 23 may be inserted into the support mechanism installation hole 29 of the mirror 1 after assembling the entire mirror support mechanism, so that the workability of assembly is improved and the maintainability at the time of disassembly and inspection is improved. Also improve.

FIG. 1 shows a case where there are a pair of link mechanisms 26 on the left and right. However, more link mechanisms 26 may be used. Further, it does not mean that the spherical bush 23 must completely coincide with the center of gravity G of the mirror 1.

Embodiment 2 FIG. FIG. 6 shows an embodiment according to the second invention of the present invention. 1,2,5,18～29 At a figure, and the distance since l ₅ to l ₈ is similar to FIG 1-4 omitted. 34 is a small weight attached to the hollow arm 22;
The position on the hollow arm 22 can be adjusted by the nut 28. The hollow arm 22, the nut 28, and the small weight 34 constitute a Z-axis weight moving mechanism 51. Centroid g of the two weights 27 and the distance between the center of gravity of small weight 34 to l _9.

[0065] FIG. 6 (8) and for axial force F ₂₄ is At a (9) is established in the same manner. Radial force F
Since the weight W ₃₄ of a small weight 34 is applied for _{23 F 23 = W 27 cosθ ·} (l 8 / l 7) × 2 + W 34 · cos θ · (l 8 + l 9) / l 7 ···· (13 ).

Here, it is assumed that the weight of the small weight is W ₃₄ = A · W ₂₇ . Here, A is, for example, about 0.1 to 0.3.
The expression (13) is as follows: F ₂₃ = W ₂₇ cosθ ｛2l ₈ / l ₇ + A · (l ₈ + l ₉ ) / l ₇ } (14) W ₁ = W ₂₇て by using the expression (4) (2 + A) l ₈ + A · l ₉ ｝ / l ₇ (15)

[0067] Since equation (9) and (15), changing the l ₆ by moving the weight 27 on the link mechanism 26, it can be adjusted only axial force without affecting the radial force, also the weight 3
4 When the Changing l ₉ moves on the hollow arm 22, it can be seen that may alter only radial forces without affecting the axial force. This has the advantage that the work becomes easier in the actual adjustment work.

Embodiment 3 FIG. FIG. 7 is a sectional view of a reflecting mirror support mechanism according to the third invention of the present invention. In the figure, 35 is a housing provided at the end of the hollow shaft 22, 36 is a first hydraulic cylinder fixed inside the housing 35, 37 is a first piston that moves in the first hydraulic cylinder 36 And is connected to the movable shaft 24.

Reference numeral 38 denotes a second hydraulic cylinder fixed inside the housing 35, and reference numeral 39 denotes a second piston that moves in the second hydraulic cylinder 38. Reference numeral 40 denotes a weight having a weight W ₄₀ , which is connected to the second piston 39. Reference numeral 41 denotes a weight 40 having the second piston 39 in the housing 35,
A roller for supporting the hollow arm 22 so as to freely move along the center axis 33 is a hydraulic pipe connecting the first hydraulic cylinder 36 and the second hydraulic cylinder 38. The distance l ₇ is similar to FIG. 1, the distance l ₈ is the distance between the center of gravity of the oscillating bearing 21 and the weight 40.

FIG. 8 shows a perspective view of the internal structure of the housing 35 of FIG. 7 in order to show the structure of FIG. 7 in more detail. The pressure receiving area S ₁ of the _first hydraulic cylinder 36 is larger than the pressure receiving area S ₂ of the second hydraulic cylinder 38.

[0071] Figure 7, Te is at the support mechanism of the reflecting mirror shown in FIG. 8, working Raku radial force F ₂₃ on the spherical bushing 23 in the same form as equation (10) in the case of Figure 1, namely F ₂₃ = W ₄₀ cos θ · l ₈ / l ₇ (16) Here, W ₄₀ is the weight of the weight 40. Thus, from Expression (4), W ₄₀ · (l ₈ / l ₇ ) = W ₁ ··· (17) holds, and the radial load can be balanced regardless of the angle θ of the mirror 1.

On the other hand, in the axial direction, the weight 40
The force F ₂ exerted on the second piston by the weight W ₄₀ is F ₂ = W
₄₀ · sin θ, and the hydraulic pressure P generated in the second cylinder 38 by this is: P = K · (F ₂ / S ₂ ) = K · (W ₄₀ / S ₂ ) · sin θ (18) ). Here, S ₂ is the pressure receiving area of the second piston, and K is a proportional coefficient.

This pressure P is transmitted into the first hydraulic cylinder 36, and generates a force F ₁ on the first piston 37 as shown in the following equation. _{P = K · F 1 / S} 1 Therefore _{F 1 = W 40 · (S} 1 / S 2) from equation (18) · sin theta becomes ... (19). This force F ₁ acts on the mirror 1 via the movable shaft 24. In order for this to be balanced with the axial load of the mirror 1, W ₁ = W ₄₀ · S ₁ / S ₂ ··· (20) from equation (1), and W ₄₀ and the pressure receiving area ratio S ₁ / S ₂ are expressed by equation (1). If it is selected so as to satisfy 20), the load in the axial direction can be balanced with the weight 40 regardless of the angle θ of the mirror 1.

In the support mechanism of the reflector shown in FIG. 7, the weight 40 can be arranged on the axis of the hollow arm 22 as compared with the case of FIG. 1, so that the whole mechanism is made smaller. It has the feature of being able to do things. The housing 35 does not need to be cylindrical as shown in FIG. 8, and if there are first and second cylinders and pillars supporting the weight, the wall surface of the housing 35 may be omitted, so that maintenance from outside is difficult. Absent.

Embodiment 4 FIG. FIG. 9 shows a reflecting mirror support mechanism according to the fourth invention of the present invention. In the figure, reference numeral 45 denotes a guide that slidably supports the side surface of the second cylinder 38 and is attached to the housing 35. The second cylinder 38 is the housing 3
It is not fixed to 5 and can move on the central axis 33 of the hollow arm 22 in the guide 45. Reference numeral 46 denotes an adjusting screw attached to the housing 35, and its tip supports the bottom surface of the second cylinder 38. The adjusting screw 46 is the hollow arm 22
Is provided on the axis 33. The guide 45, the second cylinder 38, the adjusting screw 46, the weight 40, and the second piston 39 constitute a weight position adjusting device 52.

Next, the operation will be described. Although the second cylinder 38 can move along the central axis 33, the weight of the weight 40 is always applied to the second cylinder 38 through the second piston 39, so that the second cylinder 38
Is pressed against the adjusting screw 46. When the adjusting screw 46 is rotated and moved into and out of the housing 35, the second cylinder 38 is also kept in contact with the adjusting screw 46 while the center axis 3
3 move on. When the second cylinder 38 moves, the second
The piston 39 moves in the same manner, and the weight 40 connected to the second piston 39 moves similarly. At this time the first
Piston 36 does not move. This is because the position of the mirror 1 is apparently fixed by the positioning mechanism 5 finally.

As a result of the adjustment of the adjusting screw 46, the position of the weight 40 changes, resulting in a distance L ₈ between the fulcrum bearing 21 and the weight 40.
(8) is changed, the radial force F ₂₃ acting on the spherical bush 23 is changed. There is no change as seen in the axial force F ₂₄ acting this time on the movable shaft 24 formula (20).

In FIG. 9, the axial force F ₂₄ and the radial force F ₂₃ can be changed at the same ratio at the same time by adding or removing a small weight to the weight 40. By adjusting the radial force F
Only ₂₃ can be changed alone. By utilizing this property, the axial force and the radial force can be adjusted to arbitrary values.

In FIG. 9, the radial force can be adjusted by adjusting the adjusting screw 46 from outside the supporting device.
Adjustment is easy.

Embodiment 5 FIG. An embodiment of a support mechanism for a reflecting mirror according to the fifth invention of the present invention will be described with reference to FIG. The support mechanism installation hole 29 is located at a position including the center of gravity G of the above-described reflector.
The reflecting mirror having a structure in which it is difficult to provide is usually an asymmetric structure. In such a reflector,
The operating angle range of the mirror 1 is not 0
Many are used only within ９０90 °, that is, from the horizontal direction to the zenith. That is, rather than continuously changing the angle to the side opposite the zenith, the mirror is rotated horizontally about a vertical axis when pointing beyond the zenith to the opposite sky. FIG. 10 shows an embodiment according to the fifth invention of the present invention as an example which can be used when there is such a restricted condition.

In FIG. 10, the center of gravity G is the support mechanism installation hole 29.
Outside. 47 is a swing bearing 21 and a spherical bush 23
And a weight 27 is provided at the end of the arm. Arm 47 need not be hollow. The movement of the arm 47 is similar to that of the hollow arm 22 in FIG. The thrust bearing 19 is provided near the center of gravity G in a plane including the center of gravity G of the mirror 1 and orthogonal to the mirror axis 60. Thrust bearing 19 and center of gravity G
Is preferably 1/10 or less of the diameter of the mirror 1. Reference numeral 48 denotes an axial support mechanism, and the movable shaft 24 is provided so as to move along a line passing through the center of gravity G and parallel to the axis 60 of the mirror 1. The lever 7, the axial weight 8, the support shaft 11, and the nut 28 are the same as those in the related art, but since the bottom surface pin joint 9 is not used at the joint with the mirror 1, the mirror 1 can be easily assembled.

The single axial support mechanism 48 has the ability to receive the entire weight of the mirror 1, and no other mechanism than the positioning mechanism 5 supports the axial load of the mirror 1. Since the radial force acting via the spherical bush 23 acts in the direction passing through the center of gravity G, no moment is generated as in the case of FIG. In the axial support mechanism 48, no moment is generated because the line of action of the force passes through the center of gravity G of the mirror 1.

Embodiment 6 FIG. If the position of the support mechanism installation hole 29 is sufficiently distant from the center of gravity G, as shown in FIG.
4 can be installed in accordance with the center of gravity G, but if the position of the support mechanism installation hole 29 can be slightly separated from the center of gravity G, it becomes difficult. FIG. 11 shows another embodiment of the fifth aspect of the present invention in such a case.

In the figure, the movable shaft 24 is provided at two places.
The weights of the two weights 8 provided on the respective levers 7 having the same structure as the conventional one are set so that their weights are different from each other. By adjusting the position of the weight 8, the point of application of the axial force obtained by combining the two axial forces can be moved, so that the axial force can be adjusted to the center of gravity G, and the installation position of the support mechanism installation hole 29 can be changed. The degree of freedom for selection increases.

Embodiment 7 FIG. In Examples 1 to 6,
Although the one in which the spherical bush 23 is provided at the tip of the hollow arm 22 or the arm 47 is shown, the contact portion of the thrust bearing 19 may be a spherical spherical bearing 53 and the spherical bush 23 side may be a cylinder. FIG. 12 shows such an example.

In FIG. 12, a cylindrical slide bearing 51 is inserted into the end of the hollow arm 22, and a plurality of parallel springs 52 are arranged before and after the slide bearing 51 to facilitate movement.
7, the length of the hollow arm 22 caused by the deflection of the hollow arm 22 due to the mass of the mirror 7 and the difference in the thermal expansion between the mirror 1 and the support flange 2 are generated.
By making the movement of the contact point between the slide bearing 51 and the spherical bearing 53 a rolling movement, it is possible to reduce a supporting load error. FIG. 12 shows the case where the hollow arm 22 is used, but the same applies to the case where the arm 47 is used.

In the above description, the reflector of the reflection telescope has been described as an example. However, a so-called parabolic antenna or a telescope can be used without being limited to the primary mirror.

[0088]

As described above, according to the fourth aspect of the present invention, the following effects can be obtained. 1. Since there is no supporting structure on the side surface of the mirror, the outer diameter of the telescope does not become larger than the diameter of the mirror. 2. The entire weight is light. 3. The arrangement of the support mechanism is concentrated in one place, and the maintenance inspection is facilitated. 4. Adjustment of the position of the weight is easy.

According to the first and third aspects of the present invention, the effects described in the first, second, and third of the above effects can be obtained. Further, according to the second and fifth aspects, the effects of the first and third aspects can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view of a reflecting mirror support mechanism according to a first embodiment of the present invention.

FIG. 2 is a detailed view of the swing bearing section of FIG.

FIG. 3 is an operation schematic diagram of the swing bearing unit in FIG. 1;

FIG. 4 is a detailed view of a link mechanism of FIG. 1;

FIG. 5 is an explanatory diagram of the action of the force shown in FIG. 1;

FIG. 6 is a sectional view of a reflecting mirror support mechanism according to a second embodiment of the present invention.

FIG. 7 is a sectional view of a reflecting mirror support mechanism according to a third embodiment of the present invention.

FIG. 8 is a perspective view of the internal structure of the housing of FIG. 7;

FIG. 9 is a sectional view of a reflecting mirror support mechanism according to a fourth embodiment of the present invention.

FIG. 10 is a sectional view of a reflecting mirror support mechanism according to a fifth embodiment of the present invention.

FIG. 11 is a sectional view of a reflecting mirror support mechanism according to a sixth embodiment of the present invention.

FIG. 12 is a sectional view of a reflecting mirror support mechanism according to a seventh embodiment of the present invention.

FIG. 13 is a perspective view of a conventional support mechanism for a reflecting mirror.

FIG. 14 is a sectional view of a conventional support mechanism.

FIG. 15 is a sectional view of a conventional supporting mechanism for a large reflecting mirror.

FIG. 16 is an enlarged view of the axial support mechanism of FIG.

FIG. 17 is an enlarged view of the radial support mechanism of FIG.

18 is an explanatory diagram of the moment in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Reflecting mirror 2 Support flange 5 Positioning mechanism 19 Thrust bearing 21 Swing bearing 22 Hollow arm 24 Movable shaft 25 Link fulcrum 26 Link mechanism 27 Weight 29 Support mechanism installation hole 33 Center axis 34 Small weight 36 First hydraulic cylinder 37 First Of the piston 38 Second hydraulic cylinder 39 Second piston 40 Weight 42 Hydraulic piping 45 Guide 46 Adjusting screw 47 Arm 50 X-axis weight moving mechanism 51 Z-axis weight moving mechanism 52 Weight position adjusting device

Claims (5)

(57) [Claims] 1. A reflecting mirror supporting mechanism for mounting a reflecting mirror on a supporting flange whose attitude changes with respect to the direction of gravity, disposed on the back surface of the reflecting mirror and provided at the center of gravity of the reflecting mirror. A thrust bearing, a swing bearing provided on the support flange, a hollow arm swingably supported by the swing bearing and having one end coupled to the thrust bearing, and inside the hollow arm. A movable shaft that is slidably inserted in the mirror axis direction of the reflecting mirror and one end of which is in contact with the back surface of the reflecting mirror ;
Pivotally held at a fulcrum provided on the hollow arm
Link machine rotatably coupled to the movable shaft
And the link mechanism is provided with the support flange.
The mirror axis direction and the perpendicular angle of the mirror axis with the change of the attitude
Weight supporting the load acting in the direction via the movable shaft
Reflecting mirror support mechanism, characterized in that the provided. 2. The hollow arm has one end connected to a thrust bearing.
At the other end, perpendicular to the mirror axis of the reflector
Weight to adjust the supporting force to support the load acting on
The reflector support mechanism according to claim 1, wherein: 3. A reflecting mirror supporting mechanism for mounting a reflecting mirror on a supporting flange whose attitude changes with respect to the direction of gravity. The reflecting mirror is disposed on the back surface of the reflecting mirror and provided at the center of gravity of the reflecting mirror. and a thrust bearing that is, the a swing bearing provided on a supporting flange, a hollow arm having one end swingably supported on the swing bearing is coupled to the thrust bearing, the inside of the hollow arm A movable shaft that is slidably inserted in the mirror axis direction of the reflecting mirror, one end of which is in contact with the back surface of the reflecting mirror ;
The end of the movable shaft is housed in a housing provided in the hollow arm.
And the mirror axis direction of the reflecting mirror through the movable shaft.
And a first hydraulic pressure supporting a load acting in a direction perpendicular to the mirror axis
Cylinder and the support flange with the change in attitude
A weight that moves along the center axis of the hollow arm, and this weight
Hydraulic pressure generated by movement of the connected second piston
To the first hydraulic cylinder via a hydraulic pipe.
A reflecting mirror support mechanism provided with a second hydraulic cylinder . 4. A second hydraulic cylinder comprises a guide movably supporting the second hydraulic cylinder on the axis of the hollow arm, and an adjusting screw provided on the axis of the hollow arm and supporting the second hydraulic cylinder. claims, characterized in that it has a weight position adjusting device for moving the mounting position of the hydraulic cylinder on the hollow arm shaft
Reflector supporting mechanism according to 3. 5. A supporting member whose posture changes in the direction of gravity.
In the reflector support mechanism for attaching the reflector to the lunge,
Disposed on the back surface of the reflector, near the center of gravity of the reflector.
A thrust bearing provided beside and on the support flange
A swing bearing provided, parallel to the arm and the axis of the center of gravity of the street reflector of said reflecting mirror having a weight on the pivotably supported by the swing bearing one end coupled to the thrust bearing and the other end Has one end rotatably connected to the other end of the link mechanism having a weight at one end and a fulcrum on the support flange, and the other end having a movable shaft in contact with the reflector. A reflecting mirror support mechanism , characterized in that: