JP2000227379A - Device and method for adjusting bucket swing-up angle of centrifugal loading device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a device for performing more accurate load test by optimizing a swing-up angle without adding any heavy objects. SOLUTION: Outer force devices 14 and 9 are equipped to regulate a swing-up angle by applying outer force to a bucket 7 for a test piece that is supported by a rotary stand 6 for generating 100 G so that it can be rocked freely and the test piece is placed. The outer force device 14 is a stopper that is fixed onto the rotary stand 6, controls the swing-up movement of the bucket 7 for test piece during the swing-up movement, and stops it at a theoretical position. Also, the outer force device is an eccentricity mechanism for suspending the bucket 7 with an eccentric rocking shaft.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an apparatus and a method for adjusting a swing angle of a bucket of a centrifugal loading device.

[0002]

2. Description of the Related Art Buildings such as buildings are built on the ground. A physical test of the ground can only be performed after the construction has been completed. 2. Description of the Related Art A centrifugal loading device that virtually generates a large gravitational field is used to perform a preliminary test on a test object such as a ground on which a large gravity acts. In the centrifugal loading device, a bucket for loading a test body and a bucket for placing a balance weight are arranged symmetrically with respect to the rotation axis of the turntable and suspended swingably.

In such a centrifugal loading device, a dynamic loading experiment is performed in parallel with a static loading experiment. Dynamic loading experiments
This is a dynamic loading experiment in which a dynamic force such as vibration is applied to a test object loaded on a bucket to know the physical properties of the test object. In this dynamic loading test, it is necessary to fix the swung bucket on a turntable, and a seating means for fixing the bucket is provided on the turntable.

[0004] The centrifugal force acting on the eccentric bearing used in the eccentric mechanism of the seating device acts on the bucket in the direction of swinging the bucket more. Due to this effect, the bucket is swung further higher than the swing angle position larger than the theoretical value. The seating means raises the bucket to an over-angle position beyond the desired accuracy range.

[0005] An apparatus has been known which is an improvement of a low-precision experimental apparatus based on a volume angle without correction. In order to achieve a swing angle that matches the theoretical value, a power mechanism that forcibly applies a force to the bucket from its turntable is used. Such a power mechanism results in very high equipment costs.

[0006] Abnormality of the swing angle of the bucket of the centrifugal loading device is also caused by a bearing for swingably suspending the bucket. Since there is frictional resistance between the bucket and the bearing that are lifted by centrifugal force, the lift angle of the bucket is different from the lift angle calculated as having no friction. It is preferred that the swing angle be within the desired accuracy range in the gravitational field of the planned strength.

[0007] Rolling bearings having a small frictional resistance have to be large bearings in order to support a bucket subjected to a huge centrifugal force, and the arrangement space on a turntable designed on a scale as small as possible is limited. Invite. When an experiment is performed at a swing angle (volume angle) different from the theoretical value using a sliding bearing having a large friction coefficient but a small scale, the accuracy is naturally poor.

[0008] It is desired to reduce the equipment cost of a bucket swing angle adjusting device of a centrifugal loading device for giving a bucket a swing angle that matches a theoretical value within a required accuracy range. In particular, it is desired to reduce the cost of the device including the seating device.

[0009]

SUMMARY OF THE INVENTION It is an object of the present invention to provide an apparatus and a method for adjusting a swing angle of a bucket of a centrifugal loading apparatus capable of performing a more accurate loading test by optimizing the swing angle. Is to do. Another problem of the present invention is that even if a bearing that can reduce the scale but has a large frictional resistance is used, by optimizing the swing angle,
An object of the present invention is to provide a bucket raising angle adjusting device for a centrifugal loading device and a method for adjusting the same, which can perform a more accurate experiment. Still another object of the present invention is to provide a bucket of a centrifugal loading device that can perform a more accurate test with high reliability by making the theoretical value and the actual value of the tilt angle coincide by optimizing the tilt angle. An object of the present invention is to provide a swing angle adjusting device and an adjusting method thereof. Still another object of the present invention is to provide an apparatus for performing a more accurate test with high reliability by giving a bucket a swing angle that matches a theoretical value within a required accuracy range by optimizing a swing angle. An object of the present invention is to provide a bucket raising angle adjusting device for a centrifugal loading device and a method for adjusting the same, which can reduce the device cost. Still another object of the present invention is to provide a bucket with a swing angle that matches a theoretical value within a required accuracy range by optimizing a swing angle, and to provide a highly accurate test with a seating device with high reliability. An object of the present invention is to provide a bucket raising angle adjusting device for a centrifugal loading device and a method of adjusting the same, which can reduce the device cost of the device performed in degrees.

[0010]

Means for solving the problem Means for solving the problem are expressed in correspondence with the claims. In the following description, numerals with () appear in the following description. It shows that it corresponds to the member, the process, and the operation of at least one of a plurality of forms of the present invention. It is not a thing, but to clarify the correspondence.

A bucket raising angle adjusting device for a centrifugal loading device according to the present invention comprises: a rotary drive mechanism (5); and a rotary table (6) that rotates together with a rotary shaft (2) driven by the rotary drive mechanism (5). ), And a bucket (7) for a test object, which is swingably supported by the turntable (6) and on which the test object (16) is placed.
And the balance weight (1
7) A balance weight bucket (8) for mounting the same, and an external force device (14) supported on the turntable (6) to apply an external force to the test object bucket (7) to regulate the swing angle thereof. , 9).

The external force devices (14, 9) are fixed on the turntable (6), and stop the swinging motion of the test specimen bucket (7) during the swinging motion to stop at the theoretical position. It comprises a device (14) and a seating device (11) for fixing the bucket for test specimen (7) swung up by centrifugal force at the restrained position.

It is particularly preferred that the stopping device (14) includes a variable device for changing the theoretical position. The seating device (11) includes a test piece bucket side geometric structure and a turntable side seating structure, and the turntable side seating structure includes:
It has an eccentric body (E in FIG. 4) and an oscillating shaft (9) that is a moving body that presses against the eccentric body (E) and moves linearly. The bucket (7) has a curved surface (12) on the bucket side for the test body equidistant from the oscillation axis of the oscillation of the bucket (7), and the moving body (9) has The test piece has a curved surface (13), and the test piece bucket-side curved surface (12) is relatively a moving body-side curved surface (13).
Exercise in parallel.

Here, the moving body is a bucket for a test body (7).
It is the same as the swing axis that moves linearly in the centrifugal direction in the same way,
In addition, it coincides with the specimen bucket (7) which moves in the same direction as the swing axis in the centrifugal direction. Such a coincidence has a lightweight and secure seating mechanism and its geometry.

According to the method for adjusting the bucket raising angle of the centrifugal loading device according to the present invention, the rotary table (6) which rotates together with the rotary drive mechanism (5) and the rotary shaft (2) driven by the rotary drive mechanism (5). ), And a bucket (7) for a test object, which is swingably supported by the turntable (6) and on which the test object (16) is placed.
And a centrifugal loading device comprising a balance weight bucket (8) swingably supported on the turntable (6) for mounting the balance weight (17) thereon. This is a method of adjusting the bucket raising angle of the loading device, and is an over-rotation for applying a centrifugal force to swing the bucket for specimen (7) at an angle larger than the theoretical raising angle to the bucket for specimen (7). A step for giving a speed to the turntable (6), and forcibly stopping the test piece bucket (7) by a stopper (14) provided on the turntable (6) at a position of a raising angle corresponding to a theoretical value. The difference between the theoretical value and the swing angle of the theoretical value corresponding to the overspeed is within an allowable range.

The direction of the pseudo-gravity field obtained by the combination of gravity and centrifugal force cannot always be strictly perpendicular to the mounting surface.
It can be forcibly stopped. High-accuracy experiments are possible within the allowable range. It is possible to provide an experimental device with high accuracy within an allowable range without adding a heavy object.

The external force device has a geometric structure, which passes through the center of gravity of the bucket for test specimen (7) when the turntable (6) is stationary and the center of gravity. A virtual swing axis for virtually supporting the bucket (7) so as to swing freely in a direction perpendicular to the vertical, passing through the vertical line, and a vertical plane including the vertical line and the swing axis. A separated vertical plane that is separated from and parallel to the vertical plane, and a realistic plane that is included in the separated vertical plane and that is parallel to the swing axis and that swingably supports the test bucket (7). And the pivot axis.

The bucket (7) is eccentric given such a geometric structure, and the swing angle can approach the theoretical value within an allowable range while receiving frictional resistance. It is possible to provide a highly accurate experimental device without adding a heavy object. The eccentric body constituting the eccentric mechanism can be also used as an eccentric swing shaft for suspending the bucket.

When the turntable (6) is stationary, the virtual pivot axis and the realistic pivot axis are preferably included in one horizontal plane. If the separation distance between the virtual oscillation axis and the actual oscillation axis is represented by an eccentric distance e, α · sin (θ) −cos (θ) = μ “0” √ (1 + α)
Α) R / √ (L·L + e · e), tan (θ ″ 1 ″) = e / L, tan (θ ″ 0 ″) = 1 / α, Δθ = θ−θ ″ 1 ″ (Δθ−Δθ) Absolute value of “0”) <= design value on angular accuracy α: centrifugal acceleration / gravity acceleration L: distance between the virtual swing axis and the center of gravity θ: realistic swing axis The eccentric distance e is given so as to satisfy the above-mentioned equation (5) of the angle between the plane including the line and the center of gravity and the horizontal plane. By satisfying such a condition, a highly accurate swing angle can be realized within an allowable range.

A bucket raising angle adjusting device for a centrifugal loading device according to the present invention includes an eccentric mechanism (9) for eccentrically suspending a bucket (7) for loading a test specimen and a swinging motion of the bucket (7). Stopping means (14) for forcibly stopping the vehicle. In this case, the external force device is a combination of the eccentric mechanism (9) and the restraining means (14). This synthesis can further increase the experimental accuracy.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Corresponding to the drawings, an embodiment of a bucket raising angle adjusting device for a centrifugal loading device according to the present invention is provided with a rotary drive mechanism. The rotation drive mechanism includes a base 1. A rotating shaft 2 is rotatably supported on the base 1. The rotation axis 2 of the rotation axis 2 is
It is orthogonal to the horizontal plane corresponding to FL. The rotating shaft 2 is connected to a main motor 5 via a reduction gearbox 4 and a shaft coupling. The turntable 6 is connected to the rotation shaft 2 via a key. The turntable 6 is formed by both left and right arms, and has a structure which is generally symmetrical with respect to the rotation axis 3 in design.

A holder 7 for the test specimen and a holder 8 for the balance weight are arranged symmetrically with respect to the axis of rotation 3, supported by the turntable 6, and suspended swingably. The cage 7 for the test body and the cage 8 for the balance weight have a structure which is substantially symmetrical with respect to the rotation axis 3 in design. The retainer for test specimen 7 and the retainer for balance weight 8 are supported by the suspension shafts 9 and 9 'so as to be rotatable and swingable. The suspension shafts 9, 9 ′ are parallel to each other horizontally and fixed to the turntable 6.

FIG. 2 shows a right end portion of the rear view of FIG.
The right end portion of the test sample holder 7 and the turntable 6 in the swung up state is shown. At the right end of the turntable 6, a seat 11 which is a part of a seating device is shown. The seat 11 is a conventional means for seating and fixing the test object bucket 7 swung up by the centrifugal force at the swinging position. The seat 11 linearly moves relative to the test specimen holder 7. In the embodiment, the seat 11 is fixed to a turntable, and the test object bucket 7 is driven by an eccentric rotation mechanism described later.
Reciprocates linearly with respect to the seat 11.

The conventional seating device includes a bucket-side geometric structure for the test specimen and a turntable-side seating structure. The test piece bucket side geometric structure includes the test piece bucket 7 itself and an eccentric rotator mechanism described later. The test piece bucket 7 itself has a test piece bucket side curved surface 12 equidistant from the swing axis L of the swing. The test piece bucket-side curved surface 12 is preferably a cylindrical surface having a center line about the oscillation axis L, but is formed into a spherical surface around one point on the oscillation axis L. be able to.

The turntable-side seating structure is the seating described above.
The seat 11 has a seat-side curved surface 13 equidistant from the swing axis L. As the seat-side curved surface 13, the swing axis L
Is preferable, but it can be formed as a spherical surface centered on one point on the oscillation axis L. Bucket side curved surface 12 and seating side curved surface 1 for test specimen
The curvatures of 3 are the same or approximately equal. When the seat 11 relatively linearly moves, the bucket 12 and the curved surface 13 are always parallel to each other. Design dimensions are shown in units of mm for reference.

A stopping device is fixedly provided on the turntable 6. The stopping device is a stopper 14 for stopping the swinging motion of the test object bucket 7 during the swinging motion and stopping at the theoretical position. The stopper 14 is firmly fixed and attached to the structure side of the turntable 6. The holder for the specimen 7 has its side surface (the upper surface when swung up) 1
5 collides with the stopper 14 and its swing is stopped.

The mounting position of the stopper 14 can be changed. The specimen 16 is loaded on a platform formed in the specimen holder 7. The balance weight 17 is placed on a platform formed on the balance weight holder 8.

FIG. 3 shows the eccentric rotator mechanism 18 having the above-described geometric structure on the bucket side for the test object. The eccentric rotating body that is the swing shaft 9 is a cylindrical body. The cylinder rotates with a line separated by a distance a from the center line of the cylinder as a rotation axis.
FIG. 4 shows calculation of a displacement amount when the eccentric rotator 9 rotates. The eccentric circle is represented by C, its center point is represented by O, and its radius is represented by R. The eccentric point is relatively E
Indicated by

The intersection of the horizontal line 31 passing through the eccentric point E and the circle C is indicated by U. The point where the horizontal line 31 intersects with the rotational displacement circle C ′ in which the eccentric circle C rotates counterclockwise around the eccentric point E by the angle θ is indicated by K. The intersection of the eccentric circle C and the rotational displacement line 32 in which the horizontal line 31 rotates clockwise about the eccentric point E by the angle θ is indicated by Q. The point at which a vertical line 33 perpendicular to the line 31 and passing through the center O intersects the eccentric circle C is indicated by T. Point Q to line O
Points orthogonally projected on T are indicated by S.

EQ = X, QS = Y, ES = Z,
When the amount of eccentricity EO is represented by a or e, XX = ZZ + YY, (X-e). (X-e) + YY = QO.QO = R.
R, Z = cos (θ) X. From these three equations, X = e · sin (θ) + √ ｛R · R− (e · cos
(Θ)) (e · cos (θ))｝. Here, √ is a square root symbol acting on ｛｝.

When e is sufficiently smaller than R, the following approximate expression is obtained. X = e · sin (θ) + R (1- (1/2)) (ec
os (θ)) (e · cos (θ)) / R · R. Further, X = e · sin (θ) + R KU, which is the length of the target to be obtained, is expressed by the following equation with good approximation. KU = KO-R = X-R = e · sin (θ).

It is a sufficiently good approximation that the point K is regarded as the point farthest from the vertical line 33 among the points of the rotational displacement circle C ′. A tangent 34 parallel to the vertical line 33 and approximately tangent to the rotational displacement eccentric circle C ′ at the point K is a vertical line 33
From the tangent line which is parallel to and approximately tangent to the rotational eccentric circle C at the point U, has moved horizontally by e · sin (θ). If the amount of eccentricity is 30 mm and θ is 60 °, the amount of movement is approximately 25 mm.

According to the design constants, the test specimen holder 7
When swinging up from the vertical direction to the horizontal direction, the specimen holder 7 is displaced in the centrifugal direction by 25 mm in the horizontal direction due to the rotational displacement of 60 ° of Q at the above-described point of the eccentric rotating circle. . Such a linear motion mechanism can be configured. This linear movement is possible during the swing-up movement of the holder 7 for the test specimen.

FIG. 5 shows another embodiment of the bucket raising angle adjusting device of the centrifugal loading device according to the present invention.
The bucket 7 has a bucket body 21. A cylindrical slide bearing 22 is interposed between the bucket body 21 and the suspension shaft 9. A ball bearing (rolling bearing) is not used as the bearing. It is assumed that the sliding bearing 22 has a larger coefficient of friction than a rolling bearing.

FIG. 5 is a design drawing, and does not show a state of being actually suspended in a gravitational field. The center of gravity of the bucket 7 is virtually represented by G. If the center of gravity with the test object loaded is G, the G is the actual center of gravity. The center of gravity differs depending on the mass of the specimen. Hereinafter, assuming that the actual center of gravity under test is G, the following mathematical expression does not lose its generality.

The bucket 7 is formed in mirror symmetry with respect to a plane passing through the center of gravity G. The straight line that intersects the orthogonal plane 24 orthogonal to the mirror reference plane 23 is defined as a virtual swing axis L (P). One point on the straight line is represented by P. Point P is called a virtual rotation center. A point projected from the point P at right angles on a line (referred to as a realistic swing axis line EL) at which an eccentric surface (not shown) parallel to the mirror surface 23 and the orthogonal surface 24 intersect is expressed by EP (not shown). Represent.

This point EP is, as described later, an eccentric point EP.
It is said. The length of the bucket 7 in the major axis direction is slightly more than 3 m, and the distance between the eccentric point EP and the virtual center point P is approximately 2 cm. Therefore, the points P and E are simultaneously drawn in FIG. It is impossible. FIG. 6 is a conceptual diagram of the bucket 7 or the bucket body 21 whose eccentric distance is exaggerated and increased. Hereinafter, the point P is represented by L (P), and the point EP is represented by E
Expressed by (P).

Distance between point L (P) and point E (P) =
e, distance between point L (P) and point G = L, radius of sliding bearing 22 or suspension shaft 9 = R. (1) When the sliding bearing 22 rotates, R is the radius of the sliding bearing 22.

When the bucket 7 is suspended at an eccentric point in a gravitational field, the following equation approximately holds. T = eW. (2) T: Eccentric moment about the eccentric point E (P) of the bucket 7 Further, the following equation is established. By substituting actual values, T = (0.02m) (15t) = 0.3t.m. t is ton.

Q = μ “s” · R · W. ... (3) Q: axial friction resistance moment (counterclockwise) W: gravity acting on the center of gravity G (unit: 1G) μ "s": maximum static friction coefficient (= 3μ "0") μ "0": Dynamic friction coefficient Here, "" indicates that an intermediate character / symbol is a subscript. By substituting actual values, Q = (3 / 0.08) (15t) (0.245m) = 0.882t / m.

If Q> = T (Eq. (2) is not an approximation in this case), the straight line connecting the point L (P) and the point G is vertically oriented. The surface can be held horizontally as designed. When the loading surface is not horizontal, the force F for pushing the bucket 7 in the horizontal direction is expressed by the following equation. F = (μ “s” · R + e) W / L. By substituting actual values, F = ｛(3.0.08) (0.145m) +0.020
m｝ · 15t / 2.575m = 0.459ton. By pushing or pulling with such a force, the loading surface can be made horizontal.

FIG. 7 shows the balance when the turntable 6 is rotating. Clockwise moment M around the axis M "
R ″ is M ”R” = Q + μ ”0” + W√ (L·L + e · e) cos (θ) (Q = μ “0” (√ (1 + α · α)) · W · R, μ “0” ({(1 + α · α)) · WR + W} (L·L + e · e) cos (θ) (4) To indicate that
Here, α: centrifugal acceleration / gravity acceleration L: distance between the virtual swing axis and the center of gravity θ: plane including the realistic swing axis and the center of gravity and a horizontal plane Angle between

The counterclockwise moment M "L" of the shaft is
It is expressed by the following equation. M “L” = αW√ (L·L + e · e) · sin (θ). ... (5) When balanced, M ”1” = M ”2”, so μ ”0” (√ (1 + α · α)) · W · R + W√ (L·L + e · e) cos (θ) = αW√ (L·L + e · e) · sin (θ). (6) From equation (6), α · sin (θ) −cos (θ) = μ “0” √ (1 + α · α) R / √ (L·L + e · e). ... (7)

Tan (θ ″ 1 ″) = e / L, tan (θ ″ 0 ″) = 1 / α. (8) If θ ″ 1 ″ and θ ″ 0 ″ expressed by Expression (8) are used,
The eccentricity e is designed so that the following equation (9) is satisfied. Absolute value of Δθ = θ−θ ″ 1 ″, (Δθ−Δθ ″ 0 ″) <= design value on angle accuracy. ... (9)

[0045]

【Example】

α = 100G, e = 0.02m, L = 2.575m, μ ”0” = 0.08, R = 0.745m. According to such a realistic design, θ = 1.09 °, Δθ = 0.564 °. Equation (9) is expressed as: Δθ ″ 0 ″ −Δθ = 0.573−0.564 = 0.00
9 <0.1 ° This value is smaller than 0.1 ° which can be satisfied as an accuracy.

FIGS. 8A, 8B and 8C-12.
(A), (b), and (c) show the steps for raising and seating the holder 7 for the specimen, and canceling the seating and lowering the holder 7 for the specimen. The seating device is the eccentric rotation mechanism 18 described with reference to FIGS.
This is schematically shown in FIG. Eccentric drive means 41
The two hydraulic cylinder devices are provided on the turntable 6. By the movements of the respective piston rods, which are the output portions of the two hydraulic cylinder devices, in the opposite directions, the specimen holder 7 is centrifuged through the eccentric rotator 42 forming an eccentric circle.
It can be moved linearly in the centripetal direction.

FIG. 8 shows a stationary state in which the holder 7 for a specimen is suspended from the suspension shaft 9 only by gravity. The eccentric rotator 42 is at the initial rotation position, and the center of the eccentric rotator 42 is almost directly below the eccentric point. Although the test specimen cage 7 is eccentrically suspended on the suspension shaft 9, the symmetrical reference plane 23 may be slightly inclined from the vertical plane depending on the magnitude of the friction coefficient of the bearing. As described above, it is almost vertical.

When the turntable 6 is driven to rotate and reaches a prescribed number of revolutions, as shown in FIGS. 9 (a), 9 (b) and 9 (c), the symmetric reference plane 23 of the holder 7 for specimens is It is oriented almost horizontally. In this state, the eccentric drive means 41 is not operating, the eccentric circle C is at the initial angular position, and the test specimen holder 7 and the seat 11 are separated. There are two methods M1 and M2 described above for controlling the horizontal direction to be the direction of the theoretical value with an accuracy within an allowable range.

M1: The turntable 6 at a rotation speed equal to or higher than the specified rotation speed.
Is rotated to forcibly stop the specimen holder 7 at the theoretical angular position by the stopper 14 shown in FIG. M2: The eccentricity a shown in FIG. 4 is adjusted appropriately to adjust the swing-up position of the holder 7 for the specimen with an allowable range of accuracy with respect to the ideal angular position.

Further, there is a method M3 for synthesizing the method M1 and the method M2. M3: While giving an appropriate amount of eccentricity a (or e), and setting the rotational speed to a value dependent on the amount of eccentricity a, the method M1
The specimen holder 7 at the swinging-up angle position closer to the theoretical value with higher accuracy than the method M2 alone.
To stop. This makes it possible to make the direction of the combined vector of the gravity vector and the centrifugal force vector and its absolute value closer to the theoretical value.

FIGS. 10A, 10B and 10C show that the vicinity of the loading surface of the test specimen holder 7 rises from 0 G to 100 G, the eccentric driving means 41 operates, and the eccentric circle C is reduced. While holding the specimen holder 7 rotated by 60 degrees and swung up to the angular position shown by the equation (9) at that position, the specimen holder 7 moves in the centrifugal direction with respect to the seat 11, FIG. 4 shows a state in which the test object bucket side curved surface 12 of the test object holder 7 is pressed against the seating side curved surface 13 of the seat 11. By the seating by this pressure contact, the swing-up angular position of the holder 7 for the test object within an allowable range with respect to the theoretical value is fixed.
In this state, a physical property experiment of a test piece such as the ground is performed.

FIGS. 11 (a), (b) and (c) show that the rotation speed of the turntable 6 is slowly reduced while maintaining the seated state.
The experiment termination process of reducing the centrifugal acceleration from 100 G to 50 G is shown. FIG. 12 (a), (b), (c)
When the centrifugal acceleration reaches 50 G, the eccentric driving means 41 is reversely activated, the eccentric circle C is returned to the original non-rotational angle position, the test specimen holder 7 is separated from the seat 11, and
G shows a state in which the holder 7 for the specimen returns to the original rest position.

[0053]

According to the present invention, the bucket raising angle adjusting device and the adjusting method of the centrifugal loading device can execute a centrifugal loading experiment with high accuracy within an allowable range with respect to a theoretical value. In particular, the angle adjustment by the eccentric mechanism and the angle adjustment by the stopping means do not cause an increase in mass of a heavy object that receives a huge centrifugal force. Adjustment of the swing angle by the combination of the eccentric mechanism and the stopping means can further increase the experimental accuracy.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of a bucket raising angle adjusting device of a centrifugal loading device according to the present invention.

FIG. 2 is a front view showing the seating device.

FIG. 3 is a front view for theoretical analysis of the seating device.

FIG. 4 is a geometrical diagram for the theoretical analysis.

FIG. 5 is a front plan view showing an eccentric mechanism.

FIG. 6 is a front view for theoretical analysis of the eccentric mechanism.

FIG. 7 is a geometrical diagram for the theoretical analysis.

8 (a), 8 (b), and 8 (c) are front views showing steps of a method of adjusting a bucket swing angle of a centrifugal loading device according to the present invention.

9 (a), 9 (b) and 9 (c) are front views showing another step of the method of adjusting the bucket raising angle of the centrifugal loading device according to the present invention.

FIGS. 10 (a), (b) and (c) are front views showing still another step of the method of adjusting the bucket raising angle of the centrifugal loading device according to the present invention.

FIGS. 11A, 11B, and 11C are front views showing still another step of the method of adjusting the bucket raising angle of the centrifugal loading device according to the present invention.

12 (a), 12 (b) and 12 (c) are front views showing still another step of the method of adjusting the bucket raising angle of the centrifugal loading device according to the present invention.

[Description of Signs] 2 ... Rotating shaft 5 ... Rotating drive mechanism 6 ... Rotating table 7 ... Bucket for test specimen 8 ... Backet for balance weight 9 ... Suspension shaft (oscillating shaft, eccentric rotating body, external force device) 11 ... Seating device 12: Curved surface on the side of the test object bucket 13: Curved surface on the side of the moving body 14: Stopper (external force device) 16: Specimen 17: Balance weight E: Eccentric body or eccentric point (E (C) or E in FIG. 4)

Claims (9)

[Claims] 1. A rotary drive mechanism, a rotary table that rotates in the same manner as a rotary shaft driven by the rotary drive mechanism, and a test body for swingably supported by the rotary table for mounting a test body. A bucket, a balance weight bucket that is swingably supported on the turntable and on which a balance weight is placed, and an external force is applied to the test piece bucket that is supported on the turntable to regulate the swing angle of the bucket. For adjusting the bucket swing angle of a centrifugal loading device, comprising an external force device for the purpose. 2. The stopping device according to claim 1, wherein the external force device is fixed on the turntable, and stops a swinging motion of the test specimen bucket during the swinging motion to stop at a theoretical position. A bucket swing angle adjusting device for a centrifugal loading device, comprising: a seating device for fixing a bucket for a test object swung up by a centrifugal force at a stop position thereof. 3. The bucket raising angle adjusting device for a centrifugal loading device according to claim 2, wherein the stopping device includes a variable device for changing the theoretical position. 4. The seating device according to claim 3, wherein the seating device comprises a test-bucket-side geometric structure and a rotary table-side seating structure, wherein the rotary table-side seating structure includes an eccentric body and the eccentric body. A rocking axis that is a moving body that linearly moves by pressing, the bucket-side geometrical structure for the test piece is a bucket for the test piece that is equidistant from the swing axis of the swing of the bucket for the test piece. The moving body has a side curved surface, the moving body has a moving body side curved surface equidistant from the oscillation axis, and the test piece bucket side curved surface relatively moves parallel to the moving body side curved surface. Bucket swing angle adjusting device for centrifugal loading device. 5. The external force device according to claim 1, wherein the external force device has a geometric structure, the geometric structure comprising: a center of gravity of the bucket for the specimen when the turntable is stationary; A virtual swing axis for virtually supporting the bucket so as to swing freely perpendicularly to the vertical line passing through the vertical line passing through the center of gravity, and the vertical line and the swing axis. An isolated vertical plane separated from the vertical plane and parallel to the vertical plane, and included in the isolated vertical plane and parallel to the oscillation axis and for swingably supporting the test specimen bucket in reality. A bucket swing angle adjusting device for a centrifugal loading device, comprising a realistic swing axis. 6. The centrifugal loading device according to claim 5, wherein the virtual swing axis and the realistic swing axis are included in one horizontal plane when the turntable is stationary. Bucket swing angle adjustment device. 7. The system according to claim 6, wherein a separation distance between the virtual oscillation axis and the realistic oscillation axis is represented by an eccentric distance e. Α · sin (θ) −cos ( θ) = μ “0” √ (1 + α
Α) R / √ (L·L + e · e), tan (θ ″ 1 ″) = e / L, tan (θ ″ 0 ″) = 1 / α, Δθ = θ−θ ″ 1 ″ (Δθ−Δθ) Absolute value of “0”) <= design value on angular accuracy α: centrifugal acceleration / gravity acceleration L: distance between the virtual swing axis and the center of gravity θ: realistic swing axis The eccentric distance e is given so as to satisfy the above-mentioned equation (5) of an angle between a plane including a line and the center of gravity and a horizontal plane. 8. A centrifugal loading device comprising: an eccentric mechanism for eccentrically suspending a bucket on which a test object is loaded by receiving a centrifugal force and suspending the bucket; and a restraining means for forcibly restraining a swinging motion of the bucket. Bucket raising angle adjustment device. 9. A rotary drive mechanism, a rotary table that rotates in the same manner as a rotary shaft driven by the rotary drive mechanism, and a test piece for mounting a test piece that is swingably supported by the rotary table. Bucket lifting of a centrifugal loading device for adjusting a swing angle of the bucket of a centrifugal loading device comprising a bucket and a bucket for balance weight for swingably supported on the turntable for placing a balance weight thereon An angle adjusting method, wherein an over-rotation speed for applying a centrifugal force to swing the test specimen bucket at an angle larger than a theoretical swing angle to the test specimen bucket is given to the turntable. And forcibly stopping the test piece bucket at a position of a swing angle corresponding to the theoretical value with a stopper provided on the turntable, the overspeed Corresponding difference between the swing-angle and the theoretical value of the corresponding theoretical value bucket swing-angle adjustment method of centrifugal loading device, characterized in that in the acceptable range.