JPH10281222A - Kinematic mount - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure sufficient strength and prevent the occurrence of breakage due to deformation by a method wherein a fine strain is absorbed by low rigidity and deformation against a high load is suppressed by high rigidity. SOLUTION: A displayed kinematic mount is a mount, for example, for mounting a loading apparatus on the body structure of an artificial satellite, and comprises an external housing 1 fixed at a body 5 to be constrained and formed of a metal, such as an aluminum alloy or a stainless alloy; an internal spherical body 2 arranged at the internal part of the external housing 1 and fixed at a base 4 and formed of a metal, such as an aluminum alloy or a stainless alloy; and an O-ring 3 mounted in the groove 8 of the internal spherical body 2 and formed of fluorine or silicone rubber having spring properties.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a kinematic mount and, more particularly, to a device and a fixing object for avoiding a problem that structural distortion when fixing the device and thermal distortion during operation adversely affect the device. The present invention relates to a kinematic mount suitable for being interposed between the mount.

[0002]

2. Description of the Related Art Conventionally, a kinematic mount has been widely used as a mechanism for avoiding structural distortion or the like when fixing a device. The kinematic mount is a mount having a function of absorbing structural distortion, thermal distortion, and the like generated above and below the mount. Conventional kinematic mounts have the characteristic of avoiding in-plane distortion by using a spherical bearing.

FIGS. 8A and 8B show a conventional kinematic mount structure, wherein FIG. 8A is an external view, FIG. 8B is a side view, and FIG. 8C is a sectional view of FIG. The pedestal 110
Shafts 113 of two upper and lower spatial bearings 114 penetrate and extend vertically. A spring holding plate 116 is fixed to the upper end of the shaft 113 in the axial direction via a spring holding screw 117. I have. Further, a satellite mounting device mounting plate 118 is fixed to the shaft 113 on the axially lower side of the spring holding plate 116 fixing portion. Further, a spring holding plate 116 is fixed to a lower end of the shaft 113 in the axial direction via a spring holding screw 117.

[0004] At an outer peripheral portion of the shaft 113 on the lower side in the axial direction, a spatial bearing 114 is disposed. The spatial bearing 114 is fixed inside the pedestal 110 via a bearing fixing plate 111 and a screw 112. I have. The lower part of this bearing 114,
A spring 115 is stretched between the spring holding plate 116 and the spring 115. Similarly, a peripheral bearing 114 is provided on the outer peripheral portion on the axially upper side of the shaft, and a spring 115 is provided between the peripheral bearing 114 and the spring holding plate 116.
Is stretched. That is, in the kinetic mount shown in FIG. 8, the shafts 113 of the two upper and lower spatial bearings 114 are connected to each other,
The two in-plane deformations of these two bearings 1
By the movement of 14, a structure in which the distortion of five degrees of freedom is absorbed.

FIGS. 9A and 9B are views showing another conventional kinematic mount structure, wherein FIG. 9A is a plan view, FIG. 9B is a sectional view taken along the line BB of FIG. c)
FIG. 4 is a cross-sectional view taken along the line AA of FIG. In this drawing, a bearing fixing plate 204 is fixed to a top of a housing 201 fixed on a structure 208 via a screw 205, and inside the housing 201,
The spherical bearing 202 is fixed. The artificial bearing-mounted device fixing insert 203 is supported by the spherical bearing 202, and the satellite-mounted device 209 is fixed to the artificial satellite-mounted device fixing insert 203. In the drawings, reference numerals 206 and 207 indicate leaf spring structures.

[0009] That is, in the kinetic mount shown in FIG. 9, distortion is absorbed by the leaf spring structures 206, 207, and distortion of the upper and lower rotational components is removed by one spherical bearing 202.

FIG. 10 is a cross-sectional view showing the operation of absorbing distortion by the above-described conventional kinematic mount. As shown in this figure, the structure 208 and the housing 20
When a load (external force) is applied from the direction indicated by the arrow in FIG.
No. 06 absorbs the above-mentioned load and causes distortion. The housing 201 rotates with this. However, since the rotational movement of the housing 201 is absorbed by the spatial bearing 202, no distortion is transmitted to the satellite-mounted device 209. As a result, the structure 208 and the satellite-mounted device 209 are
Can move left and right without distortion.

[0008]

However, the above-mentioned prior art has the following problems (1) and (2). (1) In a conventional kinematic mount, rigidity when absorbing strain is constant regardless of the magnitude of strain (see FIG. 6). The reason for this is that in the example in which the two spatial bearings shown in FIG. 8 are used, the rigidity at the time of absorbing the strain is reduced in advance by the pressurization of the two spatial bearings (for the purpose of increasing the rigidity of the bearings). The load applied to the moving body is determined by the frictional resistance, and in the example using one of the spatial bearings shown in FIG. 9, the rigidity at the time of absorbing the strain is determined by the spring rigidity of the leaf spring structure. That's because.

For the above reasons, when a large external load is applied to the kinematic mount, the kinematic mount suffers from insufficient strength due to large deformation, and in the worst case breaks. Would. Especially,
This kind of kinematic mount is used for the precision equipment mounted on the satellite.If the satellite is in orbit, the spring stiffness of the kinematic mount should be reduced to avoid thermal distortion. Is advantageous in terms of performance, but on the other hand, it is disadvantageous with respect to the load when launching a rocket.

Therefore, if the rigidity of the kinematic mount is increased in order to make it durable against the load applied to the kinematic mount, the kinematic
There is a problem that the strain relief, which is the original purpose of the mount, does not function sufficiently.

(2) The conventional kinematic mount can absorb all in-plane distortions, but cannot absorb out-of-plane distortions. For this reason, when kinematic mounts are used for, for example, four or more of the artificial satellite-mounted devices, the deformation of the fixed point between the artificial satellite-mounted device and the kinematic mount in the out-of-plane direction may be reduced. To be transmitted directly to the device, causing distortion.

The present invention has been made in view of the above circumstances, and absorbs minute strain with low rigidity and suppresses deformation with high rigidity against a large load, thereby securing sufficient strength and ensuring large strength. It is an object of the present invention to provide a kinematic mount that can avoid damage due to deformation.

[0013]

In order to solve the above-mentioned problems, an invention according to claim 1 is a kinematic mount used for fixing a device, comprising a hollow device fixing member having high rigidity. An internal member having high rigidity, which is disposed inside the device fixing member and fixed to the base portion, and a cushioning member interposed between the device fixing member and the internal member and having a spring property. It is characterized by:

According to a second aspect of the present invention, there is provided the kinetic mount according to the first aspect, wherein the cushioning member comprises:
It is characterized by being made of fluorine-based or silicon-based rubber.

According to a third aspect of the present invention, there is provided the kinetic mount according to the first or second aspect, wherein the cushioning member is formed of an O-ring member.

According to a fourth aspect of the present invention, there is provided the kinetic mount according to the first or second aspect, wherein the shock-absorbing member is formed of a spherical member.

[0017]

According to the structure of the present invention, when a large load is applied to the kinematic mount, the springy cushioning member interposed between the highly rigid device fixing member and the internal member has an elasticity. It is completely crushed within the deformation and absorbs the strain. Thereafter, a load is transmitted between the highly rigid device fixing member and the internal member. That is, when a load is input, the load is absorbed by the rigidity of the springy cushioning member, and when a certain amount of distortion occurs, the rigidity of the device fixing member and the internal structure is increased in place of the springy cushioning member. The member is responsible for transmitting the load. In this case, since the device fixing member and the internal member of the kinematic mount are formed of a metal such as an aluminum alloy or a stainless alloy, the rigidity can be set high with respect to a large load applied from the outside.

[0018]

Embodiments of the present invention will be described below with reference to the drawings. The description will be specifically made using an embodiment. FIG. 6 is an explanatory diagram showing a relative relationship between an input load and a strain (fracture strain). In the figure, a straight line indicated by a dashed line indicates a case where rigidity is low, and a straight line indicated by a chain line indicates a case where rigidity is high. In order to absorb structural strain and thermal strain when fixing the equipment, it is better that the slope of the straight line indicating the relative relationship between the input load and the strain is steep, in order to have durability against large loads It is better that the above-mentioned gradient is gentle.
Therefore, an embodiment of a kinematic mount that realizes a nonlinear gradient having a feature of absorbing both structural strain and thermal strain and durability against a large load will be described in detail below.

First Embodiment FIG. 1 shows a kinematic system according to a first embodiment of the present invention.
FIG. 2 is a cross-sectional view showing the structure of the mount, FIG. 2 is an external view of an inner sphere and an O-ring constituting the kinematic mount, and FIG. 3 is a diagram obtained by dividing the outer housing constituting the kinematic mount into two parts. It is sectional drawing which shows a state. The kinematic mount of the first embodiment includes an outer housing 1, an inner sphere 2, a pair of O-rings 3,
3 is provided. The kinematic mount is used by being fixed between the base 4 and the restrained body 5.

The structure of the kinematic mount of this embodiment will be described in detail. The outer housing 1 is formed of a metal such as an aluminum alloy or a stainless steel alloy, and the inside thereof has a sphere portion 6 of the inner sphere 2 (described later). And has a structure that can be divided into two housing members having the same shape, as well as a spherical space having a diameter larger than the diameter of the housing member. This will be described in detail with reference to FIG. The internal sphere 2 is formed of a metal such as an aluminum alloy or a stainless steel alloy, for example, and includes a sphere portion 6 and a base fixing portion 7 integrally connected to the sphere portion 6. External housing 1
Are arranged so as to wrap the sphere portion 6 of the inner sphere 2 via the pair of O-rings 3.

The outer peripheral surface of the sphere 6 of the inner sphere 2 is
As shown in FIG. 3, a pair of annular grooves 8 having a diameter smaller than the diameter of the spherical body 6 are formed. Internal sphere 2
Are arranged symmetrically with respect to the center of the spherical portion 6, and a pair of O-rings 3, 3 are mounted in these grooves 8, 8, respectively. The O-ring 3 is formed of, for example, a fluorine-based or silicon-based rubber having a spring property. The base fixing portion 7 of the internal sphere 2 is fixed to the upper surface of the base 4 via a plurality of bolts 9. Further, on the upper surface of the outer housing 1, a constrained body 5 is fixed via bolts (not shown).

The structure of the outer housing 1 will be described in more detail. As shown in FIG. 3, the outer housing 1 can be divided into a pair of housing members 10 and 11 having the same shape. The housing member 10 is configured as a hemispherical space having a diameter larger than the diameter of the sphere portion 6 of the inner sphere 2. Similarly, the housing member 11 is configured as a hemispherical space whose inside has a diameter larger than the diameter of the sphere portion 6 of the internal sphere 2.

The housing members 10 and 11 constituting the outer housing 1 are provided with positioning pins and pin holes (not shown). These pins ensure reproducibility of the position when the housing members 10 and 11 are connected. The outer housing 1 includes a pair of housing members 1.
After the sphere 6 of the inner sphere 2 is wrapped inside from both sides by 0 and 11, it is joined by bolts (not shown).

Next, the operation of the kinematic mount of this embodiment will be described. For example, as shown in FIG. 4, when a large load is input from the direction of the arrow to the kinematic mount fixed between the base 4 and the restrained body 5, the outer housing 1 and the inner sphere 2 The springy O-ring 3 interposed between the spherical body 6 is completely crushed in the elastic deformation and absorbs the strain. Thereafter, a load is transmitted between the outer housing 1 and the inner sphere 2. In this case, since the outer housing 1 and the inner sphere 2 are made of a metal such as an aluminum alloy or a stainless steel alloy as described above, the rigidity can be set high with respect to a large load applied from the outside.

As described above, according to the structure of this embodiment, the outer housing 1 and the inner sphere 2 of the kinematic mount are formed from a metal such as an aluminum alloy or a stainless alloy, and the sphere of the outer housing 1 and the inner sphere 2 is formed. Since the O-ring 3 made of a fluorine-based or silicon-based rubber having a spring property is interposed between the O-ring 3 and the portion 6, when a load is input, the load is applied due to the rigidity of the O-ring 3 having the spring property. At the point when a certain amount of strain is absorbed, O
Instead of the ring 3, the rigid outer housing 1 and the inner sphere 2 can bear the load transmission.

Therefore, it is possible to make the stiffness of the kinematic mount non-linear with respect to the input load. As a result, the strain is easily absorbed with a low stiffness with respect to a minute deformation, and the kinematic mount is easily affected with a large load. The deformation increases and the rigidity increases. As a result, the strength of the kinematic mount can be sufficiently ensured, and breakage due to large deformation can be avoided. The same applies to out-of-plane strain. Therefore, it is possible to accurately absorb both in-plane distortion and out-of-plane distortion.

As a modification of the first embodiment, instead of forming the grooves 8 and 9 on the outer peripheral surface of the sphere 6 of the inner sphere 2, for example, as shown in FIG. A plurality of holes 13 are formed on the outer peripheral surface of the
A rubber ball 14 made of, for example, a fluorine-based or silicon-based material having spring properties may be attached to the rubber ball 14. Also in this modified example, the same effect as in the first embodiment described above can be obtained.

Second Embodiment FIG. 7 shows a kinematic circuit according to a second embodiment of the present invention.
FIG. 2 is a cross-sectional view illustrating a configuration of a mount. The kinematic mount of the second embodiment includes an outer housing 21, an inner sphere 22, a spring 23, and an outer sphere 24 having the same structure as the first embodiment. The kinematic mount of the second embodiment has a non-linear stiffness with respect to an input load, as in the first embodiment described above. It has features that combine functions. In FIG. 7, illustration of the restrained body and the base is omitted.

The structure of the kinematic mount will be described in detail. The outer housing 21 is formed of a metal such as an aluminum alloy or a stainless steel alloy.
The inside thereof is configured as a spherical space having a diameter larger than the diameter of the spherical body portion 26 of the internal spherical body 22,
It has a structure that can be divided into two housing members 30 and 31 having the same shape. The internal sphere 22 is formed of a metal such as an aluminum alloy or a stainless steel alloy, for example, and includes a sphere portion 26 and a base fixing portion 27 integrally connected to the sphere portion 26. The base fixing portion 27 is fixed to a base (not shown).

The outer shell sphere 24 is made of, for example, a metal such as an aluminum alloy or a stainless steel alloy, and has an outer diameter equal to the inner diameter of the outer housing 21 and is divided into a plurality of members. Have been.
The outer shell sphere 24 is fixed in close contact with the inner wall of the outer housing 21. Further, a plurality of springs 23 are fixed between the outer shell sphere 24 and the sphere portion 26 of the inner sphere 22. The outer housing 21 is arranged so as to wrap the sphere portion 26 of the inner sphere 22 through the spring 23 and the outer sphere 24 and is fixed to a constrained body (not shown).

Next, the operation of the kinematic mount of this embodiment will be described. When a large load is applied to the kinematic mount, the spring 2 interposed between the outer housing 21 and the sphere portion 26 of the inner sphere 22
3 is completely crushed within the elastic deformation and absorbs the strain. Thereafter, a load is transmitted between the outer housing 21 and the inner sphere 22. In this case, since the outer housing 21 and the inner sphere 22 are formed of a metal such as an aluminum alloy or a stainless steel alloy as described above, the rigidity can be set high with respect to a large load applied from the outside.

According to the structure of the second embodiment, the outer housing 21 and the inner sphere 2 of the kinematic mount are mounted.
2 is formed from a metal such as an aluminum alloy or a stainless steel alloy, and the outer housing 21 and the inner sphere 2 are formed.
Since the spring 23 is interposed between the spring 23 and the second spherical portion 26, when a load is input, the load is absorbed by the rigidity of the spring 23, and when a certain amount of distortion occurs, the spring 23 Instead, the rigid outer housing 21 and inner sphere 2
2 can handle load transmission.

Therefore, the stiffness of the kinematic mount can be made non-linear with respect to the input load. As a result, the strain can be easily absorbed with a low stiffness with respect to a minute deformation, and the kinematic mount can be easily absorbed with a large load. The deformation increases and the rigidity increases. As a result, the strength of the kinematic mount can be sufficiently ensured, and breakage due to large deformation can be avoided. The same applies to out-of-plane strain. Therefore, it is possible to accurately absorb both in-plane distortion and out-of-plane distortion.

Although the embodiment of the present invention has been described in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and there are design changes and the like that do not depart from the gist of the present invention. Is also included in the present invention. For example, the materials of the outer housing and the inner sphere of the kinematic mount of the first and second embodiments are not limited to aluminum alloy or stainless alloy. Further, the O of the first embodiment
The material of the ring is not limited to fluorine-based or silicon-based rubber. Further, the rubber ball according to the modification of the first embodiment is spherical, but may be another shape such as an ellipse.

[0035]

As described above, according to the kinematic mount of the present invention, a hollow equipment fixing member having high rigidity and a high rigidity member arranged inside the equipment fixing member and fixed to the base. Since it has a rigid internal member and a cushioning member having a spring property interposed between the device fixing member and the internal member, a kinetic
When a load is input to the mount, the load is absorbed by the rigidity of the springy cushioning member, and when a certain amount of distortion occurs, the rigidity of the device fixing member and the internal The member can take on the load transfer, in other words, the stiffness of the kinematic mount can be made non-linear with respect to the input load, resulting in low rigidity and small distortion for small deformations. It becomes easy to absorb, and the deformation becomes large and the rigidity becomes large under a large load. As a result, the strength of the kinematic mount can be sufficiently ensured, and breakage due to large deformation can be avoided. The same applies to out-of-plane strain. Therefore, it is possible to accurately absorb both in-plane distortion and out-of-plane distortion.

[Brief description of the drawings]

FIG. 1 is a diagram showing a first embodiment of the present invention;
FIG. 2 is a cross-sectional view illustrating a configuration of a mount.

FIG. 2 is a view showing the appearance of an internal sphere and an O-ring constituting the kinematic mount.

FIG. 3 is a sectional view showing a state in which an outer housing constituting the kinematic mount is divided into two parts.

FIG. 4 is a sectional view of a main part showing a state where a large load is input to the kinematic mount.

FIG. 5 is a view showing the appearance of an internal sphere and a rubber ball according to a modification of the first embodiment.

FIG. 6 is an explanatory diagram showing a relative relationship between an input load and a strain.

FIG. 7 shows a kinematic device according to a second embodiment of the present invention.
FIG. 2 is a cross-sectional view illustrating a configuration of a mount.

8A and 8B are diagrams showing a configuration of a conventional kinematic mount, where FIG. 8A is an external view, FIG. 8B is a side view,
(C) is a sectional view of (b).

9A and 9B are diagrams showing a configuration of another conventional kinematic mount, wherein FIG. 9A is a plan view and FIG.
(C) is a cross-sectional view taken along line BB of FIG.
It is sectional drawing which follows A.

FIG. 10 is a cross-sectional view for explaining a movement of absorbing the distortion by the kinematic mount.

[Explanation of symbols]

 1, 21 Outer housing 2, 12, 22 Inner sphere 3 O-ring 4 Base 5 Constrained body 6, 16, 26 Spherical part 7, 27 Base fixing part 8 Groove 10, 11, 30, 31 Housing member 13 Hole 14 Rubber ball 23 spring 24 outer sphere

Claims (4)

[Claims] 1. A kinematic mount used for fixing a device, comprising: a hollow device fixing member having high rigidity; and a high rigidity disposed inside the device fixing member and fixed to a base. A kinematic mount, comprising: an internal member having the elastic member; and a cushioning member having a spring property interposed between the device fixing member and the internal member. 2. The cushioning member according to claim 1, wherein the cushioning member is made of fluorine-based or silicon-based rubber.
Kinematic mount described. 3. The kinematic mount according to claim 1, wherein said buffer member is formed of an O-ring member. 4. The kinematic mount according to claim 1, wherein said buffer member is formed of a spherical member.