JP7113451B2 - Anti-vibration structure, measuring equipment - Google Patents

Description

The present invention relates to an anti-vibration structure and the like capable of mounting, for example, a high-precision optical measuring instrument.

As a method for inspecting a concrete structure such as a tunnel, a method for evaluating the soundness of a part to be inspected by measuring the natural frequency of the part to be inspected has been proposed. At this time, as a method of applying vibration to the inspection target part, for example, there is an inspection method of inspecting internal defects of the inspection target part without contact using laser, ultrasonic wave, electromagnetic wave, photoacoustic, etc. (for example, Patent Document 1).

JP-A-2005-147813

According to the non-contact vibration measuring method disclosed in Patent Document 1, it is possible to efficiently measure the soundness of a concrete structure. However, in such a non-contact vibration measurement of an inspection object, since it is necessary to detect slight vibrations of the inspection object, the influence of noise from the surroundings is extremely large.

For this reason, a vibration isolation structure is required in order to accurately measure the vibration of the part to be inspected. Various structures have been proposed as such anti-vibration structures, but as a simple structure, there is a method of suspending an anti-vibration object via an elastic member. For example, there is an anti-vibration structure in which an optical measuring device is suspended from a vehicle body by a spring.

However, since the suspension spring alone does not have a damping mechanism, resonance occurs when the vehicle shakes, and the optical device may be destroyed when the optical device collides with the vehicle in the vehicle body. However, using a complicated damping mechanism or an expensive damping device increases the cost.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an anti-vibration structure or the like which has a simple structure and is capable of reducing the influence of surrounding vibrations.

In order to achieve the above object, a first invention is a vibration isolation structure comprising a main body, a frame provided on the main body, and a stationary structure in which a device is suspended from the frame via an elastic member. A plate and a vibration-isolating material provided on the outer surface of the surface plate, wherein the vibration-isolating material is belt-shaped and placed under tension, and on each side surface of the surface plate, The vibration isolating structure is characterized in that the vicinities of both end portions of the vibration isolating material are joined to fixed portions of the main body that face each side surface, and that substantially the center of the vibration isolating material is joined to the side surface of the surface plate. .

It is preferable that a stopper is arranged on each of the side surfaces and the lower surface of the surface plate with a gap from the opposing surface on the main body side, and a cushioning member is provided on the end surface of the stopper.

According to the first invention, since the surface plate is suspended from the frame of the main body via the elastic member, it is possible to efficiently reduce horizontal and vertical vibrations to a low frequency by the principle of the pendulum and the principle of the spring. can. In addition, since the substantially V-shaped belt-like vibration-damping material is joined between each side surface of the surface plate and the main body, it is possible to exhibit a damping force against shaking in the vertical and horizontal directions.

In addition, stoppers provided with buffer members are arranged on each side surface and bottom surface of the surface plate with a gap between them and the opposing surface on the main body side, so that they can function as shock absorbers against large displacements. can.

A second invention is a measuring device comprising the anti-vibration structure according to the first invention, wherein a measuring device is mounted above the surface plate, and a traveling device is provided below the main body. .

An upper surface of the main body may have an arcuate concave shape in a cross section of the main body in the width direction.

According to the second invention, it is possible to prevent the vibration from the traveling device in the lower part of the main body from being transmitted to the measuring device mounted on the surface plate. Therefore, it is possible to prevent the optical axis from being deviated due to the damage of the measurement equipment and the loosening of screws.

Further, by forming the upper surface of the main body into an arcuate concave shape, interference between the surface plate and the main body can be avoided even if a slope called cant is formed in the track.

ADVANTAGE OF THE INVENTION According to this invention, it is a simple structure and can provide the vibration-proof structure etc. which can reduce the influence of a surrounding vibration.

FIG. 2 is a schematic plan view showing the anti-vibration structure 1; The schematic side view which shows the vibration-proof structure 1. FIG. FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1; FIG. 4 is an enlarged view of portion B in FIG. 3 ; The C section enlarged view of FIG. 1 is a schematic cross-sectional view showing a vibration isolation structure 1; FIG. 2 is a schematic cross-sectional view showing the measuring device 30; FIG. 4A and 4B are diagrams showing the effect of the anti-vibration structure 1. FIG. 4A and 4B are diagrams showing the effect of the anti-vibration structure 1. FIG. 4A and 4B are diagrams showing the effect of the anti-vibration structure 1. FIG.

An embodiment of the present invention will be described in detail below with reference to the drawings. FIG. 1 is a schematic plan view showing a vibration isolation structure 1, and FIG. 2 is a schematic side view. The vibration isolation structure 1 mainly includes a main body 3, a surface plate 5, a frame 7, an elastic member 11, vibration isolation members 13a and 13b, and the like.

As shown in FIG. 1, the main body 3 is, for example, substantially rectangular in plan view, and frames 7 are provided near the ends of the short sides of the main body 3 facing each other. The frame 7 is substantially U-shaped and has legs on both sides and a beam extending over the legs. The main body 3 and the frame 7 are made of steel and have a predetermined rigidity. Note that the shapes of the main body 3 and the frame 7 are not limited to the illustrated examples.

As shown in FIG. 2, a plurality of elastic members 11 are suspended below the beams of the frame 7 . The elastic member 11 is, for example, a coil spring. A lower end of the elastic member 11 is connected to the surface plate 5 . That is, the platen 5 is suspended from the frame 7 by the plurality of elastic members 11 . At this time, a gap is formed between the lower surface of the platen 5 and the upper surface of the main body 3 .

In addition, a notch is provided at the corner of the surface plate 5 to avoid interference with the frame 7, and a gap is also provided between the frame 7 and the side surface 5b on the long side of the surface plate 5 (the side surface of the notch). It is formed. Therefore, the surface plate 5 does not come into direct contact with the main body 3 and the frame 7 . The surface plate 5 is a so-called optical surface plate, and an optical measuring instrument can be mounted on the upper portion thereof.

Anti-vibration materials 13 a and 13 b are arranged on the outer surface of the platen 5 . The vibration isolator 13a is provided near both ends of the short side surface 5a of the surface plate 5, and the vibration isolator 13b is provided near the end of the long side surface 5b of the surface plate 5, respectively. That is, the anti-vibration materials 13a and 13b are provided at a total of eight locations near the four corners of the surface plate 5. As shown in FIG. The vibration-damping members 13a and 13b are strip-shaped elastic bodies made of resin, for example.

As shown in FIG. 2 , a pair of fixing portions 19 are fixed to the outer surface of the frame 7 (the side surface on the short side of the main body 3 ) over the leg portions on both sides of the frame 7 . The pair of fixing portions 19 are arranged vertically apart from each other.

3 is a cross-sectional view taken along the line AA of FIG. 1, and FIG. 4 is an enlarged view of a portion B of FIG. As shown in FIG. 4, both ends of the vibration isolator 13a are joined to a pair of upper and lower fixing portions 19. As shown in FIG. Further, the vicinity of the central portion of the vibration isolator 13a is joined to the side surface 5a of the surface plate 5 on the short side. That is, the vibration isolator 13a is fixed to each part in a substantially V-shape. Predetermined tension is applied to the vibration isolator 13a between the fixed portions.

Similarly, both ends of the vibration isolator 13b are joined to the inner surface (fixed portion) of the frame 7. As shown in FIG. Further, the vicinities of the central portion of the vibration isolator 13b are joined to the long-side side surfaces 5b of the surface plate 5 (the side surfaces of the notch portion). That is, the vibration isolator 13b is also fixed to each portion in a substantially V-shape, and a predetermined tension is applied between the respective fixed portions.

As shown in FIGS. 1 and 2, a wall portion 17 stands near the end of the main body 3 on the short side. In the illustrated example, two walls 17 are provided on each side. Further, stoppers 15a are provided on the side surfaces 5a of the surface plate 5 at portions facing the wall portions 17, respectively. A predetermined gap is formed between the tip of the stopper 15 a and the wall portion 17 .

Similarly, a wall portion 17 is erected in the vicinity of the end portion on the long side of the main body 3 . In the illustrated example, two walls 17 are provided on each side. Stoppers 15b are provided on the side surfaces 5b of the platen 5 at the portions facing the wall portions 17, respectively. A predetermined gap is formed between the tip of the stopper 15b and the wall portion 17. As shown in FIG.

Further, as shown in FIG. 3, a plurality of stoppers 15c are provided on the lower surface 5c of the platen 5. As shown in FIG. A predetermined gap is formed between the tip of the stopper 15c and the main body 3. As shown in FIG. That is, stoppers 15a, 15b, 15c are arranged on the side surfaces 5a, 5b and the lower surface 5c of the surface plate 5 with gaps between them and the opposing surfaces on the main body 3 side.

FIG. 5 is an enlarged view of part C in FIG. The stopper 15c is mainly composed of an elastic member 23 and a cushioning member 21. As shown in FIG. An elastic member 23 made of a coil spring is arranged on the connection portion side with the platen 5 , and a cushioning member 21 is provided at the tip of the elastic member 23 . That is, a buffer member 21 is provided on the end face of the stopper 15c. The cushioning member 21 is made of resin, for example. The stopper 15c functions as a shock absorber by means of the elastic member 23 and the buffer member 21. As shown in FIG.

The stoppers 15a and 15b have the same configuration as the stopper 15c. That is, an elastic member 23 made of a coil spring is arranged on the connection portion side with the surface plate 5 , and a cushioning member 21 is provided at the tip of the elastic member 23 .

Next, the function of the anti-vibration structure 1 will be described. The surface plate 5 has a suspension structure in which it is suspended from the main body 3 by an elastic member 11 . Therefore, with respect to the vibration of the main body 3, the vibration of the surface plate 5 in the horizontal direction can be reduced to a low frequency by the principle of the pendulum. Similarly, with respect to the vibration of the main body 3, the vibration of the surface plate 5 in the vertical direction can be reduced to a low frequency by the effect of the spring.

Further, force is applied obliquely to the side surfaces 5a and 5b of the surface plate 5 by the vibration-isolating members 13a and 13b to which tension is applied in a V-shape. Therefore, the surface plate 5 is maintained in a balanced state by the horizontal and vertical component forces. When the surface plate 5 vibrates from this state, damping force acts by the vibration-isolating members 13a and 13b. For this reason, together with the elastic member 11, transmission of the vibration of the main body 3 to the surface plate 5 can be suppressed.

Here, if a large displacement occurs in the surface plate 5, the vibration-isolating materials 13a and 13b may be damaged, or the surface plate 5 may come into contact with the main body 3 or the frame 7 and a large impact may be applied to the surface plate 5. There is However, since stoppers 15a, 15b, and 15c are arranged on the side surfaces 5a, 5b and the lower surface 5c of the surface plate 5, when the surface plate 5 is displaced greatly, the stoppers 15a, 15b, and 15c do not move to the main body. 3 (wall portion 17) to absorb the impact. Therefore, the impact on the surface plate 5 can be mitigated.

In addition, as shown in FIG. 6, the upper surface of the main body 3 may have an arcuate concave shape in the cross section of the main body 3 in the width direction (the direction perpendicular to the traveling direction). As will be described later, the anti-vibration structure 1 may run on a track, and the track may have an inclination called cant. Even in this case, since the anti-vibration structure 1 is of a suspension type, the surface plate 5 can be kept substantially horizontal. At this time, interference between the surface plate 5 and the main body 3 can be avoided by forming the concave shape.

Next, a measuring device using the anti-vibration structure 1 will be described. FIG. 7 is a cross-sectional view (corresponding to FIG. 3) showing the measuring device 30. As shown in FIG. The measuring device 30 is provided with a traveling device 33 under the main body 3 of the vibration isolation structure 1 . The measuring device 30 can travel on the ground or on the track by the travel device 33 . Note that the traveling device 33 does not necessarily have a power source, and may travel by being towed by another vehicle.

A measuring device 35 is provided above the surface plate 5 . The measuring device 35, for example, emits (oscillates) a laser, an ultrasonic wave, an electromagnetic wave, or the like to the surface of the inspection object, and receives (receives) a reflected laser, an ultrasonic wave, an electromagnetic wave, or the like, to detect internal defects of the inspection object. It is possible to detect For example, the metrology device 30 can be driven down a central passageway in a tunnel to detect internal defects in the concrete walls of the tunnel. For such a measuring device 35, for example, the method described in Patent Literature 1 can be applied.

The anti-vibration structure 1 can suppress transmission of vibration of the main body 3 during running and vibration due to a driving source or the like to the surface plate 5 . Here, for example, when the measuring device 30 is used in a tunnel, the vibration component is a low frequency component of 4 Hz or less, and the amount of vibration is small. Therefore, there is almost no disturbance vibration during measurement. In this case, the anti-vibration structure 1 can suppress high-frequency vibrations due to impacts between the main body 3 and the wall surface of the central passage when the vehicle is running. By suppressing high-frequency vibration in this way, it is possible to suppress loosening of screws. As a result, it is possible to prevent the optical path deviation of the optical circuit of the measuring device 35 and the like.

As described above, the vibration-isolating structure 1 according to the embodiment of the present invention can efficiently suppress the transmission of vibrations by the vibration-isolating members 13a and 13b in the hanging-type vibration-damping structure. Therefore, a vibration damping device having a complicated structure is not required, and vibration can be efficiently suppressed with an extremely simple structure.

In addition, the stoppers 15a, 15b, and 15c can suppress impacts, etc., on the surface plate 5 during large displacements. Note that the stoppers 15a, 15b, and 15c are not necessarily required if a large displacement does not occur.

Moreover, by the measuring device 30 using such an anti-vibration structure 1, for example, defects in a tunnel can be measured with high accuracy.

The effect of the anti-vibration structure according to the present invention was evaluated. FIG. 8 evaluates the difference in vibration-isolating effect depending on the presence or absence of the vibration-isolating materials 13a and 13b in the suspension-type vibration-isolating structure. In the figure, L indicates horizontal vibration without vibration isolator, and M indicates vertical vibration without vibration isolator. Further, N in the figure indicates horizontal vibration with the vibration-isolating members 13a and 13b arranged, and O in the drawing indicates vertical vibration with the vibration-isolating members 13a and 13b arranged.

In the case of only the suspension spring (elastic member 11), the natural frequency is low and the vibration isolation effect is improved, but the resonance magnification is high, so the shaking on the surface plate 5 during running of the measuring device 30 is increased. . Also, without anti-vibration material, the shaking is not a simple translational motion, but many vibration modes occur.

On the other hand, by arranging the vibration-isolating materials 13a and 13b, this shaking is suppressed, and since the vibration-isolating materials 13a and 13b are provided at eight locations near the four corners of the surface plate 5, the surface plate 5 are suppressed and aggregated into a single mode. Therefore, the influence on the measuring device 35 on the surface plate 5 can be suppressed.

Next, the vibration isolation effect in the vertical direction was evaluated for the vibration isolation structure 1 when the measuring device 30 was run. The measuring device 30 was run on a straight course made of asphalt, and vertical vibrations of the main body 3 and vertical vibrations of the surface plate 5 were detected by acceleration sensors. The sensor sensitivity was set to 3 m/s ² =1V.

FIG. 9A shows measurement results of vertical vibration of each part. The upper part of FIG. 9(a) (D in the figure) shows the measurement result of vibration in the lower part of the main body 3, and the middle part of FIG. 9(a) (E in the figure) shows the measurement result of the vibration in the upper part of the frame 7. , the lower part (F in the figure) of FIG.

The reason why the vibration (E in the figure) of the spring top (frame 7) suspending the surface plate 5 is larger than the vibration of the lower part of the main body 3 (D in the figure) is that the main body 3 is tilted. be. On the other hand, in the vibration of the surface plate 5 suspended from the frame 7 (F in the drawing), the small vibrations generated especially in the lower and upper portions of the main body 3 were suppressed. In other words, a vibration suppressing effect was obtained with respect to high-frequency vibrations.

FIG. 9(b) is a diagram showing the vibration transmissibility calculated from the ratio of the vibration of the upper part of the platen 5 to the vibration of the lower part of the main body 3, where the horizontal axis is the frequency. As can be seen from the figure, the resonance frequency is found at about 5 to 6 Hz (G in the figure), and it can be seen that the higher the frequency, the better the vibration damping effect. That is, it was possible to efficiently suppress the high-frequency component of the vibration, which causes loosening of the screw and displacement of the lens in the measuring device 35 on the surface plate 5 .

Similarly, the vibration isolation effect in the horizontal direction was evaluated for the vibration isolation structure 1 when the measuring device 30 was run. Horizontal vibrations of the main body 3 and horizontal vibrations of the surface plate 5 when the measuring device 30 was run on grass were detected by an acceleration sensor. The sensor sensitivity was set to 3 m/s ² =1V.

FIG. 10(a) shows the measurement result of horizontal vibration of each part. The upper part of FIG. 10(a) (H in the figure) shows the measurement result of vibration in the lower part of the main body 3, and the middle part of FIG. 10(a) (I in the figure) shows the measurement result of the vibration in the upper part of the frame 7. , the lower part (J in the figure) of FIG.

Similar to the vibration in the vertical direction, with respect to the vibration of the lower part of the main body 3 and the vibration of the spring top (frame 7) suspending the surface plate 5, small high-frequency vibrations were suppressed. In other words, a vibration suppression effect was obtained for high-frequency vibrations in the horizontal direction as well.

FIG. 10(b) is a diagram showing the vibration transmissibility calculated from the ratio of the vibration of the upper part of the platen 5 to the vibration of the lower part of the main body 3, where the horizontal axis is the frequency. From the figure, it can be seen that the resonance frequency is seen at about 3 Hz (K in the figure), but the resonance magnification is small, and the vibration of 5 Hz or more is damped. That is, even in the horizontal direction, the high-frequency component of the vibration, which causes loosening of the screws and displacement of the lens in the measuring device 35 on the surface plate 5, can be efficiently suppressed. In this way, it was possible to confirm the effect of suppressing the influence on the measuring device 35 on the surface plate 5 by the anti-vibration structure 1 also in the running test.

Although the embodiments of the present invention have been described above with reference to the accompanying drawings, the technical scope of the present invention is not influenced by the above-described embodiments. It is obvious that a person skilled in the art can conceive various modifications or modifications within the scope of the technical idea described in the claims, and these are naturally within the technical scope of the present invention. be understood to belong to

Reference Signs List 1 Vibration isolation structure 3 Body 5 Surface plate 5a, 5b Side surface 5c Bottom surface 7 Frame 11 Elastic member 13a, 13b Vibration isolation material 15a, 15b, 15c Stopper 17 Wall portion 19 Fixed portion 21 Cushioning member 23 Elastic member 30 Measuring device
33 …… Traveling device
35……Measuring equipment

Claims (4)

It has an anti-vibration structure,
the main body;
a frame provided on the main body;
a surface plate suspended from the frame via an elastic member and on which a device is mounted;
a vibration isolator provided on the outer surface of the surface plate;
and
The vibration-isolating material is belt-shaped and placed under tension, and on each side surface of the surface plate, the vicinities of both ends of the vibration-isolating material are joined to fixed portions of the main body that face each side surface. and a substantially center portion of the vibration-isolating member is joined to the side surface of the surface plate. A stopper is arranged on each side surface and the bottom surface of the surface plate with a gap between it and the surface facing the main body,
2. The vibration isolation structure according to claim 1, wherein a buffer member is provided on an end surface of said stopper. Equipped with the vibration isolation structure according to claim 1 or claim 2,
A measuring device is mounted above the surface plate,
A measuring device, wherein a traveling device is provided on the lower part of the main body. 4. The measuring device according to claim 3, wherein the upper surface of the main body has an arcuate concave shape in a cross section of the main body in the width direction.

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