JP6989940B2 - Pseudo-rigid body unit and pseudo-rigid body system - Google Patents

Description

The present invention protects precision equipment such as audio equipment, measuring / measuring equipment, and medical equipment, or equipment having a vibration source such as a generator and a transformer, and in normal times, between the floor surface and the equipment to be protected. It relates to a vibration isolation / vibration isolation device that not only shuts off vibrations but also has a vibration damping effect that prevents the equipment from tipping over or being damaged due to shocking disturbances in an emergency such as an earthquake.

Hereinafter, a background technique for applying the present invention to an audio speaker will be described. In the audio field, the pursuit of sound that is as close as possible to the original sound has been made in each component such as amplifiers, speakers, CD players, and cables. Despite the transition from analog to digital era and the introduction of various innovative technologies, the technology of the process from recording to playback is still limited, and the original sound is perceived by human hearing. The current situation is that it cannot be faithfully reproduced. One of the factors that an audio device cannot follow the original sound (for example, the sound of a live orchestra) is the influence of vibration on the audio device. As is well known, audio equipment generates vibrations by itself and is affected by various vibrations from the outside. In the case of an amplifier, a "beat" is generated by the AC basic signal of the power transformer and its harmonic component. In the case of a CD player, the motor that rotates the disc is the vibration source. In the case of a speaker, the reaction force of the voice coil that drives the cone vibrates the speaker enclosure (box) body. This vibration is transmitted to the floor on which the speaker is installed, and excites the complex natural vibration mode of the entire room including the floor. The disturbance vibration that is complicatedly superimposed on the original sound vibrates the speaker body again. The hypothesis that the cross-modulation distortion generated at this time deteriorates the sound quality of the audio equipment has been proposed, but the vibration due to mutual interference between the audio equipment and the installation surface is an important factor that deteriorates the quality of the reproduced sound. The fact that there is is believed to be an unmistakable fact.

Insulators are one of the means to improve the sound quality of audio equipment. In the analog era, in order to suppress howling, insulators were mainly installed between the analog player and the floor surface, and were indispensable as a means to block the transmission of vibration. With the transition from analog to CD players, insulators have come to be used as a tuning tool to improve the sound quality of audio equipment and adjust it to the listener's favorite sound, rather than as a howling prevention measure. It is well known that the sound quality changes due to the application of insulators, but the mechanism that brings about the effect has not been fully elucidated theoretically, and it has been developed empirically and by trial and error. many. There are two types of insulators that have been used in the past.

(1) Insulator made of hard material One type of insulator uses a hard material. In recent years, instead of the above-mentioned shock absorber, a hard material such as wood, resin, metal, ceramic, etc. has been devised for the purpose of effectively absorbing the vibration generated by the audio device and releasing it to the outside. It has been commercialized. In the case of a rigid insulator, it is used as a means for tuning the reproduced sound using a character of a high-quality acoustic material.

(2) Floating type insulator This type of insulator is intended to shut out vibration, and a cushioning body with low rigidity is used. As the shock absorber, there are those using a rubber material, those using a spring coil, those using an air floating board containing air, and those using the repulsive force of magnetic force. In this floating method, the purpose of blocking vibration between the audio device and the floor surface is as follows. The floor of a private house where speakers are installed usually has a distributed vibration mode with an eigenvalue of 20 to 100 Hz. The vibration of the speaker transmitted to the floor excites the complicated natural vibration mode of the entire room including the floor. The disturbance vibration that is complicatedly superimposed on the original sound vibrates the housing of the speaker again. The mutual interference of the vibration between the audio device and the floor surface causes inter-modulation distortion, which is a serious factor for deteriorating the quality (sound quality) of the reproduced sound. The occurrence of this cross-modulation strain cannot be basically avoided by the above-mentioned rigid material equation. However, at the cost of improving the sound quality by blocking vibration, there is a problem that the elastically supported speaker tends to swing with respect to an external force and the installation becomes unstable.

Therefore, the present inventors have proposed the following insulator structure in Patent Document 1 in which the audio device and the insulator are made into a completely integrated structure that cannot be detached to improve the installation stability of the elastically supported audio device.

In FIG. 35, 550 is an insulator main body, 551 is an upper sleeve which is a wind chime member, 552 is a lower sleeve, and 552 is a surging prevention member (vibration prevention means) installed in the center of the lower sleeve. The upper sleeve 551 is arranged on the upper part of the lower sleeve 552, and a spring coil 554 which is an elastic member is provided inside both sleeves 551 and 552. Reference numeral 555 is a convex portion formed on the upper end surface of the upper sleeve 551, and is fitted with a concave portion formed on the spacer portion 556 mounted on the bottom surface of the speaker. As shown in FIG. 36, the spacer portion 556 and the speaker 557 are fastened by bolts 559 using the spike screw portion 558 on the bottom surface of the speaker. The spacer portion 556 and the bolt 559 are illustrated by imaginary lines. Reference numeral 560 is a fastening bolt for preventing the upper sleeve 551 and the lower sleeve 552 from coming off, and 561 is a tubular portion formed in the lower sleeve 552 for accommodating the head of the fastening bolt.

36 (a) is a cross-sectional view in the vicinity of the spacer portion 556, and FIG. 36 (b) is an enlarged view of FIG. 36 (a). The insulator main body portion 550 shows a structure in which the spacer portion 556 is fitted to the spacer portion 556 in a non-removable state. Specifically, the insulator main body 550 is inserted into the spacer portion 556 in the axial direction and rotated 90 degrees after the insertion, so that the insulator main body 550 cannot be detached from the spacer portion 556. ..

Japanese Unexamined Patent Publication No. 2014-128000 Japanese Unexamined Patent Publication No. 2014-163505

Koichi Kobayashi et al., “Rocking Vibration of Structures during Earthquakes”, JSME Proceedings (C), Vol.77, No778, (2001-6) Chung Mann, et al., “Rocking Vibration Characteristics of Rigid Block Structures Excited by Sine and Cosine”, Proceedings of the Japan Society of Mechanical Engineers (C), Vol.66, No645, (2000-5) Aiko Furukawa et al., "Proposal of Criteria for Overturning Tombstones in the Event of an Earthquake", Proceedings of the 30th JSCE Seismic Engineering Research Presentation

Now, how to prevent the audio equipment from moving and falling in the horizontal direction when a shocking disturbance load is applied to the audio equipment installed on the floor is an extremely important issue in practical use. Not only does it damage expensive audio equipment and furniture placed around it, but large speakers with a load of 50 to 100 kg or more carry the risk of personal injury. When planning earthquake countermeasures for audio speakers, there are unique unsolved problems that are not found in earthquake countermeasures for equipment used in industry. It is a device to be protected, "how to take measures against earthquakes in an emergency without deteriorating the sound quality (quality) of the speaker in normal times".

As described above, the floating insulator is disadvantageous in terms of installation stability as compared with the rigid body support at the cost of improving the sound quality by vibration isolation. As described above, in the disclosed technology of Patent Document 1, when a shocking external force is applied to the speaker (protected device) supported by the floating insulator, the insulator main body is in the horizontal and vertical directions with respect to the speaker. The insulator does not easily separate from the speaker because the movement is restricted and installed. However, the above-mentioned disclosed technique is limited to the range of reducing the drawbacks of the floating type as compared with the rigid type insulator (rigid body support type), and does not consider the prevention of the speaker body from tipping over due to the locking vibration caused by the seismic wave.

Due to the recent trend, the form of many speakers has changed from the conventional floor type to the tall boy type with a small installation area. The shift to the tall boy type is due to the residential environment in which the speakers are installed, and the measures for speaker installation stability are becoming more and more strict. Details will be described later, but in the case of a speaker, it is difficult to anchor it to the floor (completely fastened to the floor) due to acoustic characteristics.

By the way, the fall and damage of furniture caused by the Great Hanshin-Awaji Earthquake in 1995 caused enormous damage to expensive audio equipment such as speakers. Sixteen years later, in 2011, the Great East Japan Earthquake also caused enormous damage. Since the Great Hanshin-Awaji Earthquake, the lessons learned from the many earthquakes have never been put to good use. The reason why it is difficult to take measures against earthquakes in speakers, which seems easy at first glance, is that no "technical means to satisfy the following two conditions (1) and (2) at the same time" has been found to date.
(1) Stablely install the speaker on the floor so that the speaker does not come off the floor and fall.
(2) Do not deteriorate the acoustic characteristics of the speaker.

Conventionally, the following speaker fall countermeasures have been commercially available as earthquake countermeasure products, and have been implemented with some ingenuity on the user side.

(i) Method of fixing the tuning belt to the floor FIG. 37 is a diagram showing a method of fixing the tuning belt to the floor of the speaker. 500 is a speaker, 501 is a spike that supports the speaker, 502 is a floor surface, 503 is a fall prevention tuning belt, and 504 is a bolt that fixes this tuning belt to the floor surface. By this method, it is possible to prevent the speaker of the above (1) from tipping over, but the quality of the reproduced sound of the above (2) is surely deteriorated. In the case of a speaker, the reaction force of the voice coil that drives the cone vibrates the speaker enclosure (housing) body. That is, in the speaker, the cone driven by the voice coil is not the only sound source, but the entire housing is the source of sound. The speaker housing is a resonance body similar to that of musical instruments such as violins and cellos, which has resonance frequencies of many harmonics. These instruments are supported at one point on the floor by spike-shaped endpins during performance. The reason is that the acoustic characteristics of the musical instrument, which is a resonator, are not impaired. If the housing of the speaker is restrained with a tuning belt, the characteristics as a resonator similar to that of a musical instrument are lost, and the condition (2) above cannot be satisfied.

(ii) Method of connecting the device and the wall surface with an elastic member FIG. 38 shows a method of connecting the upper side surface of the speaker and the wall surface with an elastic member by using an earthquake countermeasure product commercially available as a seismic guss. 38a is a top view and FIG. 38b is a front view. 510 is a speaker, 511 is a spike that supports the speaker, 512 is a floor surface, 513 is a wall surface, and 514 is a fall-prevention earthquake-resistant guss. Similarly, in this case as well, in order to prevent the speaker from tipping over, the seismic gush must maintain sufficient strength (rigidity), and the delicate acoustic characteristics as a resonator of the speaker cannot be maintained.

(iii) Method of fixing between the device and the floor surface by interposing a rigid body member FIG. 39 is a method of completely fixing the speaker main body to the floor surface by interposing a rigid body member between the bottom surface portion of the speaker and the floor surface. 520 is a speaker, 521 is a speaker cone, 522 is a speaker enclosure (housing), 523 is a floor surface, 524 is a rigid body member installed between the speaker and the floor surface, and 525 connects the speaker housing 522 and the rigid body member. The bolt 526 is a bolt that connects the rigid body member and the floor surface 523. By this method, it is possible to prevent the speaker from tipping over in the above (1), but the quality of the reproduced sound is surely deteriorated as in the above-mentioned method. When the reaction force of the voice coil driving the cone 521 vibrates the housing 522 of the speaker, the vibrations 527a and 527b are transmitted to the floor surface 523 via the rigid body member. The vibration of the speaker transmitted to the floor surface 523 excites the complicated natural vibration mode of the entire room including the floor surface, and vibrates the speaker housing 522 again. That is, the deterioration of sound quality caused by the mutual interference between the low frequency floor vibration and the vibration of the speaker body cannot be basically avoided as long as the speaker is rigidly supported.

(iv) Method of applying anti-vibration gantry In the field of industrial equipment, anti-vibration gantry has been widely used in order to prevent the vibration of compressors, transformers, air conditioners, generators, etc., which are vibration sources, from being transmitted to the outside. rice field. Vibration isolation is to prevent the vibration of the target device from being transmitted to the floor surface, and vibration isolation is to prevent the vibration of the floor surface from being transmitted to the target device. Anti-vibration and anti-vibration consisting of spring, mass and damper can be expressed by the same analysis model. Therefore, it is a very natural idea to use an anti-vibration stand that has both anti-vibration and anti-vibration functions to support the speaker.

40a is a front view of the speaker, FIG. 40b is a front view of the anti-vibration stand, and FIG. 41 is an enlarged view of a portion A (displacement regulation mechanism) of FIG. 40. 530 is the speaker body, 513 is the speaker cone, 532 is the speaker enclosure (housing), and 533a and 533b are the feet of the speaker housing. 534 is a vibration-proof mount, 535 is an upper mount, 536 is a lower mount, 537a and 537b are vibration absorbers composed of spring coils, and part A (arranged on the left and right) in the figure is a displacement control mechanism, and 538 is a floor surface. .. By this displacement regulation mechanism (A), the upper limit gap T _m and the lower limit gap T _n that regulate the vertical movement of the upper gantry 535 are adjusted by using a tool while the device to be protected is mounted.

Here, it is assumed that the speaker main body 530 is installed and fixed on the upper pedestal 535 by using the foot portions 533a and 533b. Since the displacement control mechanism is non-contact in the normal state, the anti-vibration pedestal 534 can have two functions of anti-vibration and anti-vibration. However, the upper gantry 535, which is usually made of a metal plate, has a complex resonance mode with a higher frequency than the floor of a private house. Therefore, in this case as well, deterioration of sound quality caused by mutual interference between the vibrations of the upper gantry 535 and the speaker body cannot be avoided.

In the case of a vibration-proof pedestal, the pedestal is fastened (not shown) to the foundation concrete (floor surface 538) by anchor bolt construction. FIG. 42 is a model diagram showing a case where speakers are arranged in a room in stereo. 670a is the left speaker system, 670b is the right speaker system, 671 is the listener, and 672 is the wall of the room. Speakers are usually located in the corners of a room, close to the wall 672. In addition, it is assumed that it will be installed in a limited space. The position G where the speaker is installed in the room and the inclination angle θ are often changed and fine-tuned on a daily basis according to the genre of music, the taste of the listener, etc., depending on the unique acoustic characteristics of the entire room. This point is fundamentally different from industrial anti-vibration pedestals, such as air conditioners, generators, and transformers, which, once installed by anchor construction, have almost no rearrangement changes. Therefore, in the case of an audio speaker, it is not realistic to completely fix it to the floor surface like an industrial device because it is necessary to adjust the position G and the inclination angle θ (see FIG. 42) at any time.

In the anti-vibration pedestal (Patent Document 2) used in the industrial field, as described above in FIG. 40b, as shown in FIG. 41, the upper and lower pedestals 535 are moved up and down in case of a large vibration such as an earthquake. A displacement regulating mechanism (A) that regulates the relative movement amounts T _m and T _n in the directional and horizontal directions is provided between the upper pedestal 535 and the lower pedestal 536. It has been found that the impact load applied to the protected equipment can be sufficiently reduced by setting the allowable clearance in the displacement control mechanism to T _m = T _n = 1.5 to 2.5 mm. The smaller the gap on each side of the upper limit gap T _m and the lower limit gap T _n , is preferable in terms of reducing the impact load. However, even in the case of conventional industrial use where clearance adjustment is essential, the above T _m and T _n values are practical limits due to variations in the accuracy of the members that make up the anti-vibration stand. In the case of industrial equipment, as a standard specification that can be applied to a wide range of objects, the manufacturer selects the specification (rigidity) of the spring coil so that the natural frequency of the equipment supported by the spring coil is f ₀ = 4Hz, and the above Set the gap. In the case of industrial equipment, it is essential to adjust the above-mentioned gaps T _m and T _n using a tool with the equipment to be protected installed. However, in the case of audio equipment, which is a consumer product, when considering the speaker installation environment (see Fig. 41), end users, who are ordinary citizens, use tools to adjust the gaps T _m and T _n , which require skill. It's not realistic to do. In addition, since the mass of the speaker used by the user varies, the natural frequency cannot be specified, and a speaker support means that can be applied in a wide mass range is required. Therefore, in the case of speakers, the important point is not to completely prevent falls, but to increase the "margin to fall" against ground motion disturbances. In summary, no "dramatic solution for earthquake countermeasures without deteriorating the delicate acoustic characteristics of the speaker as a resonator" has been found to date.

Specifically, the first invention is
The upper member provided on the side where the equipment to be protected is mounted, and
The lower member provided on the installation floor side and
An elastic support member provided between the upper member and the lower member to support the mass of the protected device, and
An upper limit value regulating unit provided so as to form a gap between the upper member and the lower member and restricting the upward movement of the upper member by a first predetermined amount or more.
The device to be protected is provided with a lower limit value restricting portion provided so as to form a gap between the upper member and the lower member and restricting downward movement of the upper member by a second predetermined amount or more. The possible range of mass m is m ₀ ≤ m ≤ m _max ,
The rigidity of the elastic support member is K,
When the rigidity K of the elastic support member and the mass m of the device to be protected are m ₀ , the resonance frequency is f ₀ .
When the elastic support member supports the protected device having a mass of m _max , the displacement from the balanced position when the elastic support member supports the protected device having a mass of m ₀ is x _n .
The average gap between the upper limit value regulation part and the lower limit value regulation part determined by this displacement x _n is δ _mean ,
The limit gap determined by the fall limit or the allowable limit of the generated impact load is set to δ _max .
While maintaining the mean gap δ _mean <the limit gap δ _max ,
The pseudo-rigid body unit is characterized in that the resonance frequency f ₀ is set so that the gap between the upper limit value regulating unit and the lower limit value regulating unit can be maintained in a non-contact state.

That is, in the present invention, the gap determined by the overturning limit of the protected device or the allowable limit of the generated impact load is δ _max , and the one-sided average gap determined by the upper limit gap δV ₂ and the lower limit gap δV ₁ is δ. It was found that there is a constituent condition of the pseudo-rigidized unit that can maintain the state of δ _mean <δ _max without adjustment even when the mass of the protected device differs in a wide range when set to _mean . Since there is no adjustment, there is no need for a screw part to adjust the gap, the number of parts is small, and a pseudo-rigid body unit can be realized with an extremely simple configuration.

Specifically, in the second invention , the gap of the upper limit value regulating portion when the mass is m = m ₀ is set to δV _2mini .
When the mass is m = m _max , the gap of the lower limit value regulation part is δV _1min ,
It is set so that δV _2min > 0 and δV _1min > 0.

That is, in the present invention, in addition to the mass increase rate n and the resonance frequency f ₀ , the variation determined by the position of the center of gravity of the mass and the variation in the height accuracy of the elastic support member are taken into consideration, and δV _{2 min} . > 0 and δV _1min > 0 may be set. As a result, it is possible to realize a system that can maintain a high margin, maintain vibration isolation or vibration isolation in normal times, and achieve both fall prevention and impact force mitigation in an emergency without adjustment.

Specifically, the third invention
The mass increase rate n = m _max / m ₀ , and the mass increase rate n and the resonance frequency f ₀ are set so as to satisfy the following conditions.

That is, in the present invention
One-sided mean gap δ _mean = δV ₁ = δV ₂ under the condition that the gap δV ₂ in the upper limit value regulating section and the gap δV ₁ in the lower limit value regulating section are substantially equal. Here, δ _max is an allowable gap determined by the overturning limit or the limit of the generated impact load under the condition of the external force (magnitude of the acceleration of the seismic wave) assumed by the pseudo-rigid body system. The fluctuation range of the spring displacement from the equilibrium state x _n = the left side of the above equation ≒ δ _mean . Therefore, if the mass increase rate n and the resonance frequency f ₀ are set so as to satisfy the above conditions, a pseudo-rigid body system capable of maintaining installation stability without adjustment can be realized.

Specifically, the fourth invention is
The average gap is set to 1.0 × 10 ^-3 m ≤ δ _mean ≤ 2.5 × 10 ^-3 m.

That is, in the present invention, based on the results of the industrial seismic reduction mechanism, if the allowable clearance δ _max = 1.0 to 2.5 mm in the displacement regulation mechanism is set, the impact load applied to the protected device can be sufficiently reduced. That is, even when a seismic wave having a seismic intensity of 5 or more is input, a seismic reduction effect that can reduce the damage of the device to be protected to a seismic intensity of 5 or less can be obtained.

Specifically, the fifth invention is
A central member extending downward from the upper member is provided, and the upper limit value regulating unit regulates the amount of upward movement of the upper member by a gap δV ₂ between the central member and the lower member. It is composed and
The lower limit value regulating unit is configured to regulate the amount of downward movement of the upper member by the gap δV ₁ between the central member and the lower member.
Moreover, the upper limit value regulating unit and the lower limit value regulating portion are arranged side by side along the axial direction of the central member.

That is, in the present invention, the device to be protected is mounted on the upper portion of the upper surface convex portion of the upper sleeve via the fastening member. At this time, the bottom surface of the device to be protected is not always bold and often has a locally inclined or uneven surface. Due to the configuration in which the upper limit value regulation unit and the lower limit value regulation unit are arranged coaxially, even if the bottom surface of the device to be protected has an inclined or uneven surface, the upper limit value / lower limit value gap set in consideration of the variation factor. The effect on can be minimized.

Specifically, the sixth invention
With the plurality of pseudo-rigid body units of the first invention ,
A unit-side fastening portion provided on the protected device side of the upper member,
With the fastening portion on the protected device side provided on the bottom surface of the protected device,
By a connecting member that connects the unit-side fastening portion and the protection target device-side fastening portion.
It constitutes a system in which the equipment to be protected and the pseudo-rigid body unit are integrated.

That is, in the present invention
By configuring the pseudo-rigid body unit so that it cannot be detached from the protected device, it is possible to realize a pseudo-rigid body system having better installation stability as compared with the case where the conventional floating unit is mounted.

Specifically, the seventh invention
With the plurality of pseudo-rigid body units of the first invention ,
A board having a larger area than the bottom surface of the device to be protected and to which the plurality of pseudo-rigid body units are fastened is provided.
It provides a system in which the protected device is mounted in a state of being fastened to the plurality of pseudo-rigid body units.

That is, in the present invention
By attaching the board to the protected device and increasing the support width with respect to the floor surface, the installation stability of the protected device can be significantly improved as compared with the case where the board is not attached.

Specifically, the eighth invention is
The plurality of pseudo-rigid body units according to claim 1,
The area is larger than the bottom area of the pseudo-rigid body unit, and a split board, which is fastened to each of the plurality of pseudo-rigid body units, is provided, and the protected device is fastened to the plurality of pseudo-rigid body units. It provides the system to be installed.

That is, in the present invention
For example, if the device to be protected is supported by a 4-split board, each split board can be freely opened and closed in the horizontal direction according to the installation environment of the device to be protected. When the present invention is applied to a tall boy type speaker having a small installation area, it is possible to realize a pseudo-rigid body system having the characteristics of installation stability without losing the advantage of the tall boy type space saving.

Specifically, the ninth invention is
It is a pseudo-rigid body unit that supports the speaker as a device to be protected, and has a mass increase rate of n = m _max / m ₀ , which is set in the range of n ≧ 1.5 and 8Hz ≦ f ₀ ≦ 15Hz.

That is, in the present invention
(1) In the case of audio speakers, which are consumer products, the practical limit of the product lineup (number of varieties) according to the weight of the speaker is n ≧ 1.5. (2) When the natural frequency f ₀ > 15Hz, the acoustic characteristics are easily affected by the floor vibration, and when f ₀ <8Hz, the spring displacement increases significantly, so it is difficult to make adjustment-less. By setting the range of n ≧ 1.5 and 8Hz ≦ f ₀ ≦ 15Hz in consideration of the above (1) and (2), a pseudo-rigid body system that can utilize the features of the present invention can be realized.

Specifically, the tenth invention is
It is a pseudo-rigid body unit that supports the speaker as a device to be protected, and is configured to handle the minimum mass of the speaker in the range of m ₀ = 15 to 25 kg and the maximum mass in the range of m _max = 30 to 50 kg.

That is, in the present invention
Due to the demand for speakers that are widely used in the audio field with a mass increase rate of n = 2, the mass range of the low-load unit is as follows: minimum mass m ₀ = 15 to 25 kg, maximum mass m _max = 30 to 50 kg. do. In this case, the pseudo-rigid body unit (commodity A) for low load is 15 to 30 kg, and the pseudo-rigid body unit (commodity B) for low load is 25 to 50 kg. Further, the pseudo-rigid body unit (commodity A) may be 30 to 60 kg for a medium load and 60 to 120 kg for a large load, assuming three types of products.

Specifically, the eleventh invention
It is a pseudo-rigid body unit of the first invention that supports an audio device as a device to be protected.
A cylindrical space having a volume capable of accommodating the spike main body portion on the audio device side or a part of the spike main body portion is formed in the central portion of the upper member.
The unit-side threaded portion formed on the side surface of the cylindrical space,
The audio side screw part for attaching spikes provided on the bottom of the audio device,
The audio device and the pseudo-rigid body unit are integrated by a connecting member connecting the unit-side screw portion and the audio-side screw portion.

That is, in the present invention
By forming a wide space in which the spikes can be stored in the upper member, it can also be used as the "floating spike receiver" described later in the twelfth invention . In the pseudo-rigid body unit in the present embodiment, the conditions of δV ₁ > 0 and δV ₂ > 0 can be maintained without adjustment even if the speaker mass changes within an allowable range, as in the above-described embodiment.

Specifically, the twelfth invention
In the pre-stage of the work of integrating the audio device and the pseudo-rigid body unit,
The spike tray is arranged on the floor surface side bottom surface of the cylindrical space so that it can be applied as a spike receiver for sound quality evaluation.

That is, in the present invention
Floating spike support, which was difficult in the past, is possible for the following reasons. (1) The axial movement of the upper member on which the spike tray is installed is restricted by a narrow gap. (2) The tip of the spike is deeply stored in the gap, the height of the tip of the spike is sufficiently low with respect to the floor surface, and the spike body does not easily separate from the pseudo-rigid body unit. In addition, since it is not necessary to attach / detach spikes and install the unit on the board, it is possible to easily evaluate the sound quality of this insulator before integrating the speaker, the pseudo-rigid body unit, and the board.

Specifically, the thirteenth invention
The upper member provided on the side where the equipment to be protected is mounted, and
The spindle extending downward from this upper member,
The lower member provided on the installation floor side and
The spindle is housed in the lower member so as to be movable in the axial direction.
Alternatively, the spindle houses the lower member so as to be movable in the axial direction.
An elastic support member provided between the upper member and the lower member to support the load of the protected device, and
The spindle and its facing surface maintain a gap δ _S in a static equilibrium state.
It is configured to have a gap δ _D when it deviates from the static equilibrium state.
In normal times, the equipment to be protected obtains vibration isolation or anti-vibration action by maintaining a gap δ _S wider than the gap δ _S , and at the same time.
In an emergency when the device to be protected swings, the tilt angle of the spindle is regulated by the narrow gap δ _D by the axial movement of the spindle, thereby suppressing the swing motion of the device to be protected. It is configured to be obtained.

That is, in the present invention
By setting the gap between the spindle and the sleeve to an appropriate stepped structure,
(I) In normal times, the unit spindle remains in a non-contact state, and vibration isolation and vibration isolation performance can be obtained.
(Ii) Even if the load of the device to be protected changes over a wide range, the non-contact state can be maintained without adjustment.
(Iii) In an emergency when locking vibration occurs, the tilt angle suppressing action of suppressing the swinging motion of the entire protected device works by restraining the tilt angle direction of the left and right spindles.
The reason why the above (i) to (iii) can be realized without adjustment is that the important point is that the left and right spindles alternately repeat the relative movement in the axial direction due to the locking vibration. That is, by arranging this unit on the left and right and mounting the device to be protected, the locking vibration itself suppresses the locking vibration independently. Due to the effect of this self-reliance suppressing action, stable vibration isolation / vibration isolation performance can be obtained against fluctuations in the mounted load, and in an emergency, the fall prevention / impact load reduction effect installed in the optimum state can be obtained without adjustment.

Specifically, the fourteenth invention
With the pseudo-rigid body unit of the first invention ,
The mass of the protected device is m, the height of the center of gravity of the protected device is H, the distance between the left and right support portions of the protected device is B ₀ , and the distance between the support portion and the center of gravity of the protected device is R. Angle φ = tan ^-1 (B ₀ / 2H), gravity acceleration _g , board mass m _b , distance between the center of gravity of the board and the corners of the board BG, support and board When the distance between the corners is B ₁ , the maximum tilt angle when a static load in the horizontal direction is applied to the device to be protected is θ _r , and η is defined by the following equation.

η≧1となるように構成したものである。

It is configured so that η ≧ 1.

That is, in the present invention, the displacement suppression value θ _r , the board width B ₁ , and the board mass m _b are set so that η ≧ 1 for the device whose geometric shape is composed of R and Φ. Then, (i) a static overturning margin equal to or higher than that of the rigid body support can be obtained, and the installation instability, which is a drawback of the rigid body support type, can be improved. (Ii) The effect due to the rigid body support, that is, the slow vibration / vibration isolation effect, and the effect of avoiding the occurrence of cross-modulation distortion due to mutual interference with the floor surface in the case of audio equipment can be obtained. That is, the above (i) and (ii) can be realized at the same time.

By applying the present invention, even if the mounted weight of the protected device varies over a wide range, the vibration isolation / vibration isolation effect is maintained in normal times, and in the event of an earthquake, the protection target device is prevented from tipping over and the impact load is reduced. Is obtained without adjustment.
In addition, even in office spaces and general houses where it is difficult to install anchor bolts on the floor, earthquake countermeasures can be taken with a simple and easy-to-install structure. For example, if the "pseudo-rigid body unit" according to the present invention is applied to an audio speaker, a long-standing unsolved problem, that is, (i) stable installation on the floor surface so that the speaker does not separate from the floor surface and falls over. (Ii) Do not deteriorate the acoustic characteristics of the speaker. It is possible to provide a drastic solution that satisfies the above (i) and (ii) at the same time. The effect is remarkable.

The figure which shows the case where the pseudo-rigid body unit which concerns on Embodiment 1 of this invention is applied to a speaker. The front sectional view of Embodiment 1. In the model diagram of the pseudo-rigid body unit of the present invention, FIG. 3 (a) is a diagram showing the case of m = m ₀ , and FIG. 3 (b) is a diagram showing the case of m = n × m ₀ . A graph showing the vibration isolation performance for frequency for the natural frequency f ₀ = 8Hz and f ₀ = 15Hz. A graph showing the relationship between the displacement x ₀ from the free length of the spring coil and the natural frequency f ₀ . The figure which shows the state which the central axis of a pseudo-rigid body unit is inclined by the angle θ. The model diagram of FIG. A front sectional view showing an application example of the present invention assuming versatility including industrial use. A graph obtained by obtaining the displacement x from the free length of the spring coil with respect to the natural frequency f ₀ , with the mass increase rate n as a parameter. A model diagram that considers a conventional speaker as a rigid block and finds its fall limit. The model figure which obtains the fall limit of a speaker in the case of applying this invention. A more detailed analysis model diagram of FIG. 11 above. Graph of ascent start acceleration α _s for rigid block tilt angle θ _r . Graph of ascent start acceleration α _s with respect to mass ratio m _b / m of rigid block. _Graph of the ratio α _s / α s 0 of the ascent start acceleration to the board width ratio B _W / B ₀ . A front sectional view showing a third embodiment of the present invention. A front sectional view showing a fourth embodiment of the present invention. The fifth embodiment of the invention is shown, FIG. 18 (a) is an AA arrow view of FIG. 18 (b), and FIG. 18 (b) is a BB arrow view of FIG. 18 (a). The front sectional view of the pseudo-rigid body unit which is the 6th Embodiment of this invention. The figure which shows the relationship between the spindle and the sleeve of each seismic reduction unit at the time of rocking vibration by a seismic wave. FIG. 20 is a front sectional view of the main body of the left seismic isolation unit. A seventh embodiment of the present invention is shown, FIG. 22 (a) is a diagram showing a state of B _W = B W _max , and FIG. 22 (b) is a diagram showing a state of B _W = B W _min . FIG. 22 (a) is a front sectional view focusing on the pseudo-rigid body unit and the board. The figure which shows the case where the speaker mounted on the 4-divided board is arranged close to the wall surface in the corner part of a room. A model diagram showing a state in which a rigid body block is mounted on a pseudo-rigid body unit fastened on a board. An analysis model diagram showing a state in which locking vibration is generated in a rigid body block. Analysis model diagram in which the nonlinear gap function F _Φ is introduced. Graph of spring reaction force K _Φ (y) · y characteristics with respect to spring displacement y. It is a figure which shows the horizontal acceleration which gives rocking vibration to a rigid body block, FIG. 29a is a figure which shows the vibration waveform with respect to time, and FIG. 29b is a figure which shows the frequency with respect to time. A graph of the analysis results showing the response characteristics of the rotation angle of the locking vibration. Graph of analysis result showing the generated force response characteristic of the support part by locking vibration. Graph of analysis results showing the generated force response characteristics when the displacement regulation gap is ± 1.5 mm. Graph of analysis results showing the generated force response characteristics when the displacement regulation gap is ± 0.5 mm. Graph of analysis result of maximum compressive load for one side gap of displacement regulation. The audio insulator of Patent Document 1 is shown, FIG. 35a is a top view, and FIG. 35b is a front sectional view. A cross-sectional view of the vicinity of the spacer portion, FIG. 36 (b) is a partially enlarged view of FIG. 36 (a). A diagram showing conventional speaker earthquake countermeasures and fixing the tuning belt to the floor. A conventional speaker earthquake countermeasure is shown, FIG. 38a is a top view, and FIG. 38b is a front view. A diagram showing conventional speaker earthquake countermeasures and fixing the speaker to the floor with a rigid body. A diagram of installing a speaker on an anti-vibration stand as an earthquake countermeasure, FIG. 40a is a model diagram of the speaker, and FIG. 40b is a front sectional view of the anti-vibration stand. FIG. 40 is an enlarged view of part A. A model diagram showing the case where the speakers are arranged in stereo in the room.

Hereinafter, each embodiment of the present invention will be described in the next step.
[1] Application example to audio speakers
[2] Application examples assuming versatility including industrial use

The present invention maintains the anti-vibration / anti-vibration effect in normal times and protects in an emergency when an earthquake occurs, even if the mounted weight of the protected device (for example, speaker) supported by the floating insulator varies over a wide range. It was found that there is a configuration condition of the unit that can obtain the effect of preventing the target device from tipping over and reducing the impact load without adjustment.

Here, (1) an elastic support member (spring coil) that supports the load of the device to be protected, (2) means for regulating the movement amount of the elastic support member in a narrow gap, and the above (1) and (2) are combined into one unit. The unit structure built into the unit is called a floating "pseudo-rigidized unit" in order to clearly express the characteristics of the technology. Further, a unit that does not require adjustment of a narrow gap set for pseudo-rigid body formation even if the mass of the device to be protected varies over a wide range is called an "adjustment-less pseudo-rigid body formation unit". Since there is no adjustment, there is no need for threaded parts required for clearance setting, the number of parts is small, and a pseudo-rigid body unit can be realized with an extremely simple configuration. First, the above [1] will be described.

[1] Application example to audio speakers
[First Embodiment]
FIG. 1 shows a case where the “adjustment-less pseudo-rigid body unit” according to the first embodiment of the present invention is applied to an audio speaker. FIG. 2 is a front sectional view of the adjustment-less pseudo-rigid body unit. Reference numeral 150 is a speaker which is a device to be protected, 151 is a board on which the speaker is mounted, and 152a to 152d are adjustmentless pseudo-rigid body units (152c is not shown). The pseudo-rigid body unit is fastened to the board 151 with bolts. The board 151 is not anchored to the floor surface, can move horizontally with respect to the floor surface, and can float in the vertical direction.

In FIG. 2, 153 is an upper sleeve (upper member which is a wind chime member), 154 is a lower housing (lower member), 155 is a central shaft, 156 is a spring coil, 157 is a positioning portion of the spring coil, and 159 is surging. The preventive members 160a and 160c are bolts to be fastened to the board 151 (160b and 160d are not shown). Reference numeral 161 is a fastener fastened to the lower end surface of the central shaft 155 with bolts 162, and reference numeral 163 is a connecting member for connecting the speaker 150 and the upper sleeve 153 of the pseudo-rigid body unit. 163a is a speaker-side threaded portion of the connecting member, 163b is a unit-side threaded portion of the connecting member, 164a is an upper surface convex portion on the upper surface portion of the upper sleeve 153, and 164b is an outer peripheral portion. The speaker 150 is mounted on the upper surface convex portion 164a via the connecting member 163. Reference numeral 165 is a displacement regulating portion formed in the central portion of the lower housing 154. In FIG. 2, the weight of the device to be protected (speaker) and the displacement of each spring of the pseudo-rigid body installed at the four corners are in a static equilibrium state. At this time, the gap between the lower end surface 166 of the displacement regulating portion 165 and the fastener 161 is a gap (defined as an upper limit gap) δV ₂ that can move upward from the static equilibrium state of the upper sleeve 153. Further, the gap between the upper end surface 167 of the displacement regulating portion 165 and the upper sleeve side facing surface 168 is a gap (defined as a lower limit value gap) δV ₁ that can move downward from the static equilibrium state of the upper sleeve 153.

By the way, in the present embodiment, as described above, by interposing and integrating the pseudo-rigid body unit between the speaker and the board, the long-standing problem of the speaker, that is,
[i] Install the speaker stably on the floor so that the speaker does not come off the floor and fall.
[ii] Does not deteriorate the acoustic characteristics of the speaker.

We were able to realize an audio system that satisfies the above [i] and [ii] at the same time. To summarize the reason, the upper limit gap δV ₂ and the lower limit gap δV ₁ that can be moved from the static equilibrium state of the upper sleeve prevent the speaker from tipping over even if the mounted mass of the speaker varies over a wide range. It can be set small enough for planning. Moreover, in the steady state, the states of δV ₁ > 0 and δV ₂ > 0, which are necessary for maintaining the vibration isolation performance, can be maintained without adjustment.

That is, in the present invention, when the one-sided average limit gap determined by the tipping limit of the speaker is δ _max , and the one-sided average gap determined by the upper and lower limit gaps δV ₂ and δV ₁ is δ _mean , the protected device (speaker). It was found that there is a condition that the state of δ _mean <δ _max can be maintained without adjustment even if the mass of) differs over a wide range. By the way, in a non-steady state such as an earthquake, the smaller the δ _mean , the smaller the maximum inclination angle θ _r when a load is applied to the protected device in the horizontal direction, which is advantageous for preventing the protected device from tipping over. .. The details of this point will be described later in Chapter [2].

Hereinafter, the conditions for specifically realizing the "adjustment-less quasi-rigid body system" proposed by the present invention will be described. Assuming that the minimum mass of the device to be protected is m ₀ and the mass increase rate from the mass m ₀ is n, the mounted mass of the device to be protected changes in the range of m ₀ ≤ m ≤ n × m ₀ . FIG. 3 (a) shows a model of the case where the mounted mass of the pseudo-rigid body unit is m = m ₀ , and FIG. 3 (b) shows the case of m = n × m ₀ . When the loading mass is m = m ₀ , the lower limit gap δV ₁ is the maximum value, and δV ₁ = _δV 1 max. The upper limit gap δV ₂ is the minimum value, and δV ₂ = δV _{2 min} . When the mounted mass is m = n × m ₀ , the upper limit gap δV ₂ is the maximum value, and δV ₂ = _δV 2 max. The lower limit gap δV ₁ is the minimum value, and δV ₁ = δV _{1 min} . Each of the above gaps is set under the following conditions.
(1) Natural frequency f ₀
(2) Allowable fluctuation range of speaker mass (mass increase rate n)
(3) When the following variation factors are taken into consideration (a) Variation in the mass mounted on each unit (b) Processing accuracy of the spring coil

(4) When considering the flatness of the bottom surface of the device to be protected Consider the effect of the natural frequency f ₀ in (1) above on the clearance setting. Here, it should be noted that in the case of audio speakers, the optimum natural frequency range is in a high region as compared with industrial equipment. In the case of industrial equipment, it is usually set near the natural frequency f ₀ = 4Hz. The reason for this is that, in the case of industrial equipment, there are many places where the main body of the device to be protected has low rigidity and a low natural frequency, and the problem caused by the resonance phenomenon at these places is taken into consideration. In this study, we focused on the fact that the speaker structure is closer to a rigid body and the natural frequency is higher than that of industrial equipment. As a result of audition experiments and vibration measurements for speakers supported by floating insulators, the following points were clarified.
(I) When the natural frequency f ₀ <5 to 6Hz ... The bass range tends to be boomy (ii) When the natural frequency f ₀ > 15Hz ... The acoustic characteristics are easily affected by the floor vibration.

In (i) above, the audio playback sound is boomy, which means that there is no lingering sound after repelling the instrument-based sound, and the sound is covered by the next sound, that is, the sound in which the low-pitched sound is not braked. Is. This boomy phenomenon is likely to occur when the support rigidity of the speaker body is low. In the case of a tallboy speaker, it has been pointed out that the reproduced sound tends to be boomy because the position of the center of gravity is high and the support width of the bottom of the speaker with respect to the floor is small. Furthermore, when the speaker is supported by a floating insulator, if the rigidity of the insulator is low, boomy tends to occur.

The reason for (ii) above is as follows. The floor of a private house where speakers are installed usually has a distributed vibration mode with an eigenvalue of 20 to 100 Hz. When the vibration of the speaker is transmitted to the floor surface, it excites the complicated natural vibration mode of the entire room including the floor surface. In order to avoid the deterioration of sound quality caused by the mutual interference between the low frequency floor vibration and the speaker body vibration, the upper limit of the natural frequency of the floating insulator is set to a value that is not affected by the floor vibration. There is a need to. FIG. 4 shows the vibration isolation performance with respect to the frequency in the case of natural frequencies f ₀ = 8Hz and f ₀ = 15Hz. The vibration isolation characteristic has a characteristic (base) that is inclined with respect to the frequency around the resonance point f ₀ . In order to avoid the influence of floor vibration, vibration isolation performance <0 is a necessary condition in the region where the floor has a distributed vibration mode. The allowable upper limit of the natural frequency including point B in the figure is f ₀ = f _B = 15 Hz.

In addition to the above-mentioned constraint condition of the natural frequency from the aspect of acoustic characteristics, the condition of the natural frequency for realizing the adjustment-less adjustment of the pseudo-rigid body unit is as follows. Set the mass m and the spring stiffness K so that the natural frequency f ₀ determined by the mass m of the speaker and the spring stiffness K of the spring coil. The graph of FIG. 5B shows the relationship between the displacement x ₀ of the spring coil from the free length and the natural frequency f ₀ .

In the figure, the case where the mass m ₀ is multiplied by n (n = 2 in the figure) while keeping the same spring rigidity K is shown in the graph of FIG. 5 (c). If the mass m ₀ is n times the same spring rigidity K, then f ₀ ² ∝ K / m ₀ , so the spring coil displacement x from the free length is n times, that is, x = x ₀ → It becomes nx ₀ . Therefore, the fluctuation range x _n of the spring displacement from the equilibrium state [Fig. 5 (b)] is

式（２）から固有振動数f ₀が高い程、質量増大率nが小さい程、平衡状態[図５（b）]からのスプリング変位の変動幅x_nを小さくできる。

From equation (2), the higher the natural frequency f ₀ and the smaller the mass increase rate n, the smaller the fluctuation range x _n of the spring displacement from the equilibrium state [FIG. 5 (b)].

The permissible fluctuation range of the speaker mass in (2) above is as follows. The mass of speakers that are generally popular in the audio field is m = 25-100Kg. Many small speakers with m <25 kg are also used, but they are excluded from the application of this example because they do not cause great damage even if they fall. Large speakers with m> 100Kg are excluded because there is little demand. Here, it is assumed that two types of pseudo-rigid body units are prepared, one for low load and the other for high load. In this case, the low load unit is responsible for 25 to 50 kg, and the high load unit is responsible for 50 to 100 kg. In both cases, the permissible fluctuation range of mass is doubled (mass increase rate n = 2). For example, when using a low load unit (25 to 50 kg) and setting f ₀ = 14 Hz at m ₀ = 25 kg, the displacement of the spring coil from the free length is x ₀ = 1.26 mm from equation (1). Is. When the maximum allowable load is m _max = n × m ₀ = 50 kg, the spring displacement from m ₀ = 25 kg x _n = (n-1) x ₀ = 1.26 mm.

The smaller the mass increase rate n, the smaller the spring displacement x _n , so the allowable natural frequency f ₀ can be set to a low value. However, in consumer products such as audio speakers, which are the targets of this embodiment, there is a limit to the product lineup (number of varieties) that matches the weight of the speaker (pseudo-rigid body unit), and the range of n ≧ 1.5 is set. Was the practical limit.
The larger the mass increase rate n, the smaller the number of varieties. However, as shown in the graph of FIG. 9 described later, the fluctuation range x _n of the spring displacement from the equilibrium state increases. If the natural frequency increases f ₀ , the fluctuation range x _n can be reduced, but due to the limitation of f ₀ ≤ 15 Hz, n ≤ 3 is the limit.

Table 1 shows the one-sided average gap δV _mean under ideal conditions obtained only from the natural frequency f ₀ of (1) above and the mass increase rate n of (2) above. In this case, δV _mean = x _n / 2. From the graph of FIG. 5, when the natural frequency becomes smaller at the boundary of f ₀ = f _A = 8 Hz, the displacement x _n increases significantly, so the one-sided mean clearance δV _mean must be increased. As a result, the installation stability of the equipment to be protected is greatly reduced. To summarize the results under ideal conditions
(Iii) When the natural frequency f ₀ <8Hz ... Spring displacement increases significantly The constraint conditions from the acoustic characteristics of (i) to (ii) above and the spring displacement x _n of (iii) above From the condition of making it smaller, the natural frequency range is preferably 8 Hz ≤ f ₀ ≤ 15 Hz. Here, as described above, δ _max is set as the one-sided average limit gap determined from the overturning limit of the pseudo-rigid body system under the condition of the assumed external force (magnitude of the acceleration of the seismic wave). Here, the one-sided average is defined as (upper limit gap + lower limit gap) / 2. Therefore, if the resonance frequency f ₀ is set so as to satisfy the condition of δV _mean = x _n / 2 = <δ _max under ideal conditions, a pseudo-rigid body system that can maintain installation stability without adjustment can be realized. ..

By the way, in order to assume a wide range of applications and to realize mass production of units, it is necessary to consider the factors of variation such as the mass of the mounted equipment and the unit parts. Hereinafter, the one-sided average gap δV _mean is obtained in consideration of the variation factor of (3) above. Each gap in FIG. 3 has the following equation.

The settings of _{δV 1min} and δV 2min considering the variation factor are as follows. In this embodiment, for δV _1min and δV _2min , which are determined by the variation factor, the variation in the mass (center of gravity position) mounted on each unit (3) and (a) above and the machining accuracy of the spring coil (3) and (b) above are taken into consideration. Then, I asked for it as follows. It is assumed that the variation in the mounted mass is ± 30% and the height accuracy of the spring is ± 0.5 mm. The variation in the mounted mass is mainly determined by the position of the center of gravity, and is as follows. In the case of a speaker, since the unit having a voice coil is on the front side, the position of the center of gravity is often different from the center of the figure. Therefore, when the speaker is supported in four places, it is necessary to expect a difference of about ± 30% in the load applied to each spring coil.
The above-mentioned variation in height accuracy of the spring coil is taken into consideration because the spring coil is a difficult-to-process member that requires polishing. Since the spring coil is easily elastically deformed by the machining pressure, it is necessary to expect the height accuracy in the axial direction to be ± 0.5 mm even when it is polished.

Considering the above variation factors, the setting example of each gap when f ₀ = 14Hz is set at m ₀ = 25kg is shown below.

(I) Example of setting _δV 2min: For δV _2min , assuming that the mass is 30% lighter than m ₀ , x ₀ = 1.26 → 1.26 × 0.7 = 0.88 mm. The height of the spring is 0.5 mm higher than the standard. As a result, δV 2min = ( _1.26-0.88 ) +0.5 = 0.88mm. Therefore, if the gap of δV _2min on the left is allowed, the variation in mass and spring height can be absorbed and δV _2min > 0 can be maintained.

(Ii) Example of setting δV _1min : For δV _1min , assuming that the mass is 30% heavier than n × m ₀ , x ₀ = 1.26 × 2 × 1.3 = 3.28 mm. The height of the spring is 0.5 mm lower than the standard. As a result, δV _1min = (3.28-2.52) +0.5 = 1.26mm. Therefore, if the gap of δV _1min on the left is allowed, the variation in mass and spring height can be absorbed and δV _1min > 0 can be maintained.

From the results of (i) and (ii) above, when f ₀ = 14Hz is set at m ₀ = 25kg, δV _1max = x _n + δV _1min = 1.26 + 1.26 = _2.52mm , δV _2max = x _n + δV 2min = 1.26 + 0.88 = 2.14mm.
Based on the same consideration as above, Table 2 shows the set values of each gap when the natural frequency is set to f ₀ = 8 to 14 Hz.

The one-sided mean gap in Table 2 is δV _mean = (δV _1max + δV _2min ) / 2 = (δV _1min + δV _2max ) / 2.

From Table 2, it can be seen that when the variation factor is taken into consideration, the one-sided mean gap δ _mean needs to be expected to be approximately twice as much as the ideal condition (Table 1). Therefore, as the spring displacement x _n from the minimum mass, x _n ≈ δV _mean . Here, as described above, δ _max is set as the limit gap determined from the overturning limit of the pseudo-rigid body system under the condition of the assumed external force (magnitude of acceleration of seismic wave). Therefore, if the resonance frequency f ₀ is set so as to satisfy the condition of δV _mean ≈ x _n <δ _max , it is possible to realize a pseudo-rigid body system that can maintain the installation stability without adjustment even when the variation factor is taken into consideration. ..

The flatness of the bottom surface of the device to be protected in (4) above has the greatest effect on the setting of the upper and lower limit gaps. However, in the present embodiment, the influence on the gap setting can be minimized by devising the structure of the unit. This point will be described below. As shown in FIG. 2, the spring and the displacement regulation mechanism are built in the same unit, and the upper limit value δV ₂ and the lower limit value δV ₁ are set on the same axis as the central axis. The reason why this structure greatly contributes to the realization of "adjustment-less pseudo-rigid body system" will be described with reference to FIGS. 6 and 7. FIG. 6 is a diagram showing a state in which the central axis of the pseudo-rigid body unit is tilted by an angle θ, and FIG. 7 is a model diagram of FIG. As shown in FIG. 2, the protected device (speaker) is mounted on the upper portion of the upper surface convex portion 164a of the upper sleeve 153 via the fastening member 163. At this time, the bottom surface of the device to be protected is not always bold and often has a locally inclined or uneven surface. Let R ₁ be the radius of the upper convex portion 164a, R ₂ be the radius of the disk-shaped fastener, and L be the length of the central axis. When the outer peripheral portion of the upper convex portion 164a has a step of ± ΔY ₁ , the step ΔY ₃ of the outer peripheral portion of the fastener 161 is obtained.

Assuming that R ₁ = 40 mm, R ₂ = 7 mm, L = 23.9 mm and ΔY ₁ = 1 mm, from Eq. (4),
ΔY ₃ = 0.182 mm, and ΔY ₃ is sufficiently smaller than ΔY ₁ . Since the upper limit gap δV ₂ ≫ΔY ₃ , even if the bottom surface of the device to be protected has an inclined or uneven surface, the influence on δV _{2 min} , which is set in consideration of the variation factor of the upper limit gap, can be minimized. The effect of setting δV _1min of the lower limit gap can also be minimized. From the above results, in the present embodiment, the influence of the flatness of the bottom surface of the device to be protected (3) and (a) on the setting of the gap can be ignored.

In the present embodiment, the upper limit gap δV ₂ and the lower limit value gap δV ₁ are sufficiently small even when the mounted mass of the speaker varies over a wide range, and in a steady state, δV ₁ > 0 and δV ₂ > 0. Was able to be maintained without adjustment, and the speaker's long-standing challenges [i] [ii] could be satisfied. Since there is no adjustment, there is no need for a screw part to adjust the gap, the number of parts is small, and a pseudo-rigid body unit can be realized with an extremely simple configuration.

Further, in addition to the above [i] and [ii], the [iii] board, unit, and speaker can be easily installed and assembled. [iv] After installing the speaker, the board on which the speaker is mounted can be moved on the floor surface, so that the speaker position G and the inclination angle θ (see FIG. 42) can be easily readjusted. [v] Since the thickness of the board can be reduced, the interior (aesthetics) is not lost, and the advantages of the tallboy speaker with a small installation area are not impaired. Moreover, the material and shape of the board do not affect the acoustic characteristics. Etc. can be obtained.

As mentioned above, at the cost of quality improvement by vibration isolation (avoidance of cross-modulation distortion due to interference with floor vibration), the elastically supported protected equipment (speaker) tends to swing against external force and cannot be installed. There was a problem of becoming stable. However, if the movement of the elastic support member is restricted by a narrow gap to make it a "pseudo-rigid body", it not only compensates for the drawback of the floating type, which is easy to fall because it is easy to swing, but also the advantages of the floating type (automatic centering action, automatic gap equalization). On the contrary, the speaker can keep the non-contact state with respect to the floor surface at all times. Incidentally, the automatic alignment action is an action of keeping the axis of the upper sleeve 153 coaxial with the lower housing 154 due to the horizontal rigidity of the spring coil 156 in the static equilibrium state. The automatic gap equalization action is an action in which the upper limit gap δV ₂ and the lower limit value gap δV ₁ maintain constant values due to the vertical rigidity of the spring coil 156. Therefore, the delicate characteristics of the speaker as a resonator, which is the case when the housing is fixed with the conventional seismic resistance, are not lost. However, in an emergency, the speaker is integrated with the board, so it is installed stably so that it will not tip over. That is, "pseudo-rigid body formation" makes it possible to easily maintain narrow gaps in the vertical and horizontal directions, which was not possible with the rigid body support type. The present invention utilizes the disadvantages of the floating type as the advantages.

In the embodiment, the upper limit value regulating portion and the lower limit value regulating portion are configured by the gap between the central shaft 155 extending downward from the upper sleeve 153 and the lower member. The structure of this embodiment may be turned upside down to form a central fixed shaft in the lower housing, and an upper limit value regulating portion and a lower limit value regulating portion may be formed between the central fixed shaft and the upper sleeve. (Not shown)

In this embodiment, assuming that two types of pseudo-rigid body units are prepared, one for low load and the other for high load, the case where the low load unit supports 25 to 50 kg and the high load unit supports 50 to 100 kg was evaluated. .. The setting of the mass range of the speakers supported by the unit may be slightly different. For example, the mass increase rate n = 2, and the mass range of the low load unit may be a minimum mass m ₀ = 15 to 25 kg and a maximum mass m _max = 30 to 50 kg. In this case, the pseudo-rigid body unit (commodity A) for low load is 15 to 30 kg, and the pseudo-rigid body unit (commodity B) for low load is 25 to 50 kg. Further, the pseudo-rigid body unit (commodity A) may be 30 to 60 kg for a medium load and 60 to 120 kg for a large load, assuming three types of products.

[2] Application examples assuming versatility including industrial use
[Second Embodiment]
FIG. 8 is a front sectional view showing an application example of the "adjustment-less pseudo-rigid body unit" of the present invention assuming versatility including industrial use, and regulates an upper limit value and a lower limit value in the same manner as in the above-described embodiment. The location is provided by utilizing the internal space of the spring, and a dustproof film is provided so as to cover the outer peripheral portion of the spring. In this embodiment, in addition to the functions of the above-described embodiment, the unit is covered with a stretchable dustproof film (for example, a bellows-shaped outer peripheral portion) to form a closed structure. With this sealed structure, it is possible to prevent the compression coil spring, surging prevention member, and the like housed inside the unit from being deteriorated by wind, rain, and ultraviolet rays. In addition, since the narrow gap of the vertical position regulating portion is not affected by dust, the function of "adjustment-less pseudo-rigid body" can be permanently maintained.

470 is the upper base, 471 is the lower housing, 472 is the spring coil, 473 and 474 are the positioning portions of the spring coil, 475a is the upper surface convex portion of the upper base portion, and 475b is the outer peripheral portion. The device to be protected 476 (indicated by an imaginary line) is mounted on the convex portion on the upper surface. Reference numeral 477 is an upper central shaft that protrudes upward from the upper base and has a threaded portion to be fastened to the protected device side, and 478 is a lower central shaft formed on the lower housing side. 479 is a fastener fastened to the lower end surface of the lower central shaft 478 with bolts 480, 481 is a displacement regulating portion formed in the lower housing, and 482 is an upper base side facing surface of the displacement regulating portion. The definitions of the upward movable gap (upper limit gap) δV ₂ from the static equilibrium state and the downward movable gap (lower limit value gap) δV ₁ from the static equilibrium state are the same as in the above-described embodiment. Is. Reference numeral 483 is a dustproof film (bellows portion) mounted between the upper base 470 and the lower housing 471.

In FIG. 9, the displacement x from the free length of the spring coil with respect to the natural frequency f ₀ is obtained by using the mass increase rate n as a parameter. In the graph of FIG. 5 described above, the range of the mass increase rate n and the optimum natural frequency f ₀ was obtained for the Tallboy speaker as an application target. Hereinafter, the conditions for applying the present invention to a wide range of objects including not only speakers but also industrial equipment will be described.

Under the condition of the assumed external force (magnitude of acceleration of seismic wave), δ _max is the limit gap determined by the overturning limit of the pseudo-rigid body system or the allowable limit of the generated impact load.
It is assumed that the load applied to each unit is uniform and the accuracy of parts such as spring coils does not vary at "the center of the figure of the device to be protected ≒ the position of the center of gravity". In this case, as described above, the mass increase rate n and the resonance frequency f ₀ may be set so as to satisfy the condition of δV _mean = x _n / 2 = <δ _max .

As described above, when the variation factor is taken into consideration, it is necessary to expect the one-sided mean gap δ _mean to be approximately twice as much as the ideal condition (Table 1). As shown in Table 2, the fluctuation range of the spring displacement from the equilibrium state x _n ≈ δV _mean . therefore,

If the mass increase rate n and the resonance frequency f ₀ are set so as to satisfy the above conditions, it is possible to realize a pseudo-rigid body system that can maintain installation stability without any adjustment, regardless of the application target. By the way, according to the results of the industrial seismic reduction mechanism, it is known that the impact load applied to the protected equipment can be sufficiently reduced by setting the allowable clearance δ _max = 1.5 to 2.5 mm in the displacement regulation mechanism. That is, even when a seismic wave having a seismic intensity of 5 or more is input, a seismic reduction effect that can reduce the damage of the device to be protected to a seismic intensity of 5 or less can be obtained. The smaller the clearance δ _max is, the more preferable it is, but in the case of conventional industrial use where clearance adjustment is essential, the lower limit of the above numerical value δ _max = 1.5 mm is the practical limit due to the accuracy error of the members constituting the vibration isolation frame. rice field. (Refer to the method of setting the gaps T _m and T _n in FIGS. 40b to 41).
Compared to the industrial anti-vibration stand that constitutes the framework of the main body by welding, the pseudo-rigid body unit of the present invention can sufficiently increase the accuracy of individual parts and the accuracy of assembly in response to the request of the object to be applied. Therefore, the lower limit of the allowable clearance δ _max in the displacement regulation mechanism = 1.0 mm was possible. Therefore, the average clearance in the case of the pseudo-rigid body unit may be set to δ _max = 1.0 to 2.5 mm.

[3] Theoretical analysis for static fall criteria

When the device to be protected (speaker) is mounted on the pseudo-rigid body unit fixed to the board and the board and the floor surface are not fixed by an anchor or the like, an analysis is performed to obtain the static overturning standard of the device to be protected. .. The contents shown below are the same for industrial equipment in which an anchor is not installed between the board and the floor.

[3-1] Static fall reference FIGS. 10 and 11 are model diagrams for determining the fall limit of the speaker by regarding it as a rigid block. FIG. 10 shows a case where a conventional speaker is used, and FIG. 11 shows a case where the pseudo-rigid body unit of the present invention is applied. In FIG. 10, 169 is the floor surface, 170 is the right end portion of the bottom surface of the speaker 150, and 171 is the left end portion of the bottom surface. When a horizontal force F _α acts on the center of gravity of a rigid block with a support width of B ₀ , a height of the center of gravity of H, and a weight of W, the overturning moment generated by this horizontal force is F _α × H. On the other hand, gravity produces a resistance moment W × B _0/2 in the direction of canceling the overturning moment. If the overturning of an object occurs when the overturning moment exceeds the resistance moment, the static overturning condition is

However, in equation (6), it is assumed that the center of gravity is located at the center of the speaker figure. If F _α = mα and W = mg, as is well known in the past, the minimum horizontal acceleration at which an object falls is

As mentioned above, the form of the speaker these days is shifting from the conventional floor type to the tall boy type. From equation (7-2), it can be seen that the tall boy type speaker with a small width B ₀ and a high height H has a small acceleration α _s that starts rocking vibration. Hereinafter, a basic equation for obtaining a static overturning reference of a rigid body block mounted on the pseudo-rigid body unit of the present invention will be derived. FIG. 12 is a more detailed analysis model diagram of FIG. m is the mass of the rigid block, R is the distance between the support on the bottom of the block and the center of gravity G, B ₀ is the distance between the left and right supports of the block, B ₁ is the distance between the right support and the right corner of the board, and B ₂ is. The distance between the left support and the left corner of the board, B _G is the distance between the center of gravity of the board and the right corner of the board, and m _b is the mass of the board. Further, tan (φ) = B ₀ / 2H, where H is the height of the center of gravity of the rigid block. The part indicated by the chain line circle AA is composed of a displacement control mechanism and a spring that suppress the upper limit value and the lower limit value. In the left corner of the block in the figure, the displacement is regulated by the upward movement limit amount δV ₂ by setting the upper limit value, and in the right corner, the displacement is regulated by the downward movement limit amount δV ₁ by setting the lower limit value. There is. Therefore, when a horizontal static load is applied to the rigid block, the maximum tilt angle is

From the static equilibrium condition of the rotational moment at the right corner of the bottom of the rigid block

From equations (9) and (10), the forces F ₁ and F ₂ that the rigid block receives from the board side are

The rotational moment M with the right corner of the board as the fulcrum is

The input acceleration α = α _s at which the rigid block starts to ascend is set to M> 0.

In Eq. (14), if θ _r → 0 of the first term on the right side is set, g × tan (φ) = B ₀ × g / 2H, and the above-mentioned static overturning condition of the normal rigid block [Equation (7-). 2)] matches. The second term on the right side corresponds to the effect of improving the static fall margin by mounting the board, and the third term on the right side corresponds to the effect of improving the fall margin by considering the mass m _b of the board.

[3-2] Ascent start acceleration for the tilt angle of the rigid body block Fig. 13 shows the ascent start acceleration α _s for the tilt angle θ _r [(δV ₁ + δV ₂ ) / B ₀ ] of the rigid body block with the board width B _W as a parameter. Is obtained by Eq. (14). B ₁ is calculated as board width B _W (= B ₁ + B ₀ + B ₂ ) and B ₁ = B ₂ . The mass of the rigid block is m = 30Kg, the height of the center of gravity is H = 710mm, φ = 5.43deg, R = 713mm, and the support width of the rigid block is B ₀ = 135mm. However, the mass m _b of the board is not taken into consideration. The graph of B _W = 135 mm is a characteristic without board mounting (B _W = B ₀ ), and the block starts to ascend near α _s ≈ 1 m / s ² (100 Gal) (chain line circle BB).

The above static fall criterion (floating start acceleration) does not match the dynamic fall condition. However, in the case of a target device (for example, a tall boy type speaker) having a narrow support width B _W and a high center of gravity position H, the static fall standard ≒ dynamic fall condition.
Here, it is assumed that a pseudo-rigid body unit is attached, the board width is B _W = 500 mm, and the gap between the upper limit value and the lower limit value is set to δ V ₁ = δ V ₂ = 2.35 mm. At this time, the inclination angle θ _r = 2deg of the rigid block. It can be seen that the ascent start acceleration is improved by 3.2 times (CC point) compared to the case where the board is not attached (BB point).

[3-3] Acceleration at the start of ascent to the mass ratio of the board and the rigid block Fig. 14 shows the mass ratio of the board and the rigid block m _b / m with the board width B _W as a parameter.
The ascent start acceleration α _s for is obtained by Eq. (14). The gradient of the ascent start acceleration α _s with respect to the mass ratio m _b / m increases as the board width B _W increases. The reason for this is that the moment of inertia of the board is proportional to the position of the center of gravity of the board and the square of the distance B _G between the board corners. When the board width B _W = 500 mm, if a board with mass m _b = 12 kg (0.4 × 30) is attached (EE point), the static tipping condition is for a lightweight board (DD point) with m _b ≒ 0 kg. Improve 1.6 times.

[3-4] Conditions for eliminating spring-type installation instability When the normal rigid body block ascent start condition α _s0 = g × tan (φ), the equation (14) is divided by α _s0 .

Equation (15) summarizes the effects of the present invention. That is, the maximum inclination angle θ _r , the board width B ₁ , and the board mass m _b are set so that the device whose geometric shape is composed of R and Φ is protected (see FIG. 12) and η ≧ 1. Then, (i) a static inversion margin equal to or higher than that of the rigid body support can be obtained. That is, it is possible to improve the installation instability, which is a drawback of the spring type (or the floating type composed of an elastic body such as a spring).
(ii) The effect of supporting the spring, that is, the slow vibration / vibration isolation effect in the case of industrial equipment, or the effect of avoiding the occurrence of cross-modulation distortion due to mutual interference with the floor surface in the case of audio equipment. Is obtained.

By applying the present invention, the above (i) and (ii) can be realized at the same time. In FIG. 15, the ratio α _s / α s 0 of the ascent start acceleration to the board width ratio B _W / B ₀ is obtained by _Eq . (15) with the rigid body block inclination angle θ _r as a parameter. However, the mass m _b of the board is not taken into consideration. Rigid body block tilt angle θ _r = 3deg and board width ratio B _W / B ₀ is 1.55 times (GG point) compared to the case without pseudo-rigid body unit (rigid body support: θ _r = 0) (FF point). For example, the static tipping standard can be the same as the case of the above rigid body support.
For example, when evaluating the static overturning criterion of a rigid body block having a quadrangular cross section using Eq. (15), it is sufficient to select conditions that facilitate overturning in the front-back direction and the left-right direction of the rigid body block. That is, it is sufficient to calculate the four rotational moments M with the front, rear, left and right corners of the board as fulcrums, and select the condition in which M is the smallest. Even if the cross-sectional shape of the rigid block is not a quadrangle but a triangle or a polygon, the condition that minimizes the rotational moment M may be selected. The same applies to the case of the "four-divided board method" described later in the seventh embodiment.

In this analysis that obtained the static overturning standard, for example, the "condition for eliminating the spring-type installation instability" is related to the number of pseudo-rigidized units on the board, the position to be arranged, the shape of the board, the structure, and the like. Applicable without. It can also be applied to a system in which the elastic support member and the displacement suppressing mechanism are separated.

The pseudo-rigid body unit can be applied in any form. For example, it can be applied to the method of suppressing the locking vibration by the axial displacement regulation shown in the first embodiment, or the method of suppressing the locking vibration by the inclination angle of the unit spindle as described later in the sixth embodiment.

[4] Other application cases
[Third Embodiment]
FIG. 16 is a front sectional view showing a third embodiment of the “adjustment-less pseudo-rigid body unit” of the present invention. By forming a wide space in which the spikes can be stored in the upper sleeve, as will be described later in FIG. 23, a structure that can also be used as a "floating spike receiver" is shown. 250 is a speaker, 251 is a board, and 252 is an adjustmentless pseudo-rigid body unit. 253 is the upper sleeve (wind chime member), 254 is the lower housing (lower member), 255 is the central shaft (center member), 256 is the spring coil, 257, 258 is the positioning part of the spring coil 256, and 259 is the surging prevention member. 260a and 260c are bolts to be fastened to the board 151. 261 is a fastener, 263 is a connecting member, 263a is a speaker-side threaded portion of the connecting member, 263b is a unit-side threaded portion of the connecting member, 264a is an upper surface convex portion of the upper sleeve 253, and 264b is an outer peripheral portion. Reference numeral 265 is a displacement regulating portion, and the gap between the lower end surface 266 of the displacement regulating portion 265 and the fastener 261 is a gap (upper limit gap) δV ₂ that can be moved upward of the upper sleeve 253. Further, the gap between the upper end surface 267 of the displacement regulating portion 265 and the upper sleeve side facing surface 268 becomes a gap (lower limit value gap) δV ₁ that can move downward of the upper sleeve 253. Reference numeral 269 is a gap portion in which the spike described later in FIG. 17 can be stored. Similar to the first embodiment, the pseudo-rigid body unit in the present embodiment is configured so that the conditions of δV ₁ > 0 and δV ₂ > 0 can be maintained without adjustment even if the speaker mass changes within an allowable range. There is.

[Fourth Embodiment]
FIG. 17 shows a case where the fastening member 263 of the “adjustment-less pseudo-rigid body unit” shown in FIG. 16 is removed and this unit is applied as a floating spike support structure.
This embodiment is a pre-stage of the third embodiment in which the speaker, the pseudo-rigid body unit, and the board are integrated, and is configured for sound quality evaluation. Reference numeral 270 is a spike tray installed on the bottom surface 271 of the gap portion 269, reference numeral 272 is a spike main body portion fixed to the speaker 250, and reference numeral 272a is a spike tip portion. When supporting an audio device such as a speaker with spikes, the spike saucer that receives the spike tip 272a is often placed directly on the rigid floor surface. Placing spike pans on tall floating insulators such as springs, airs, and magnets is usually avoided due to installation instability. This is because when the tip of the spike separates from the spike tray due to an external force applied to the speaker, the speaker easily tilts and falls due to the size of the drop of each support point. The pseudo-rigid body unit of the present embodiment enables floating spike support, which was difficult in the past, for the following reasons.
(1) The axial movement of the upper sleeve 253 on which the spike tray 270 is installed is restricted by a narrow gap.
(2) The spike tip portion 272a is deeply stored in the gap portion 269, the height (Hs) of the spike tip portion 272a is sufficiently low with respect to the floor surface, and the spike body 272 is easily a pseudo-rigid body. Do not leave the conversion unit.

Further, when the pseudo-rigid body unit is installed in the lower part of the spike main body 272, the spike saucer 270 installed on the bottom surface 271 moves horizontally (arrows) with respect to the axis of the spike main body and automatically adjusts. Since it is a core, the installation work of the speaker is easy. Since there is no need to attach / detach spikes and install the unit board, it is easy to evaluate the sound quality of this insulator before integrating the speaker, pseudo-rigid body unit, and board (third embodiment). can.

[Fifth Embodiment]
FIG. 18 shows a fifth embodiment of the present invention, in which FIG. 18 (a) is an AA arrow view of FIG. 18 (b) and FIG. 18 (b) is a BB arrow view of FIG. 18 (a). .. The pseudo-rigid body unit in the present embodiment has both high-rigidity support by a spring coil in the vertical direction and low-rigidity support of the wire suspension method in the horizontal direction. Further, in order to make the body pseudo-rigid, a displacement regulating unit for regulating axial displacement in a narrow gap is provided. Regarding the wire suspension method, there is a prior art according to Japanese Patent Application Laid-Open No. 2011-27249, but the method of regulating axial displacement in a narrow gap is not disclosed in the same document.

301 is a pseudo-rigid body unit, 302 is an upper base, 303 is an intermediate base, 304a, 304b, 304c are columns, 305 is a spring side upper base, 306 is a spring side lower base, 307 is a spring coil, and 308 is a surging prevention member. , 309 are support shafts, and 310 is a lower base. A device to be protected is mounted on the upper portion of the upper base 302 (a method of fastening the pseudo-rigid body unit and the device to be protected is not shown). 311a, 311b, and 311c are wires connecting the upper base 305 on the spring side and the intermediate base 303, 312 are bolts for fastening the lower base 306 on the spring side and the support shaft 309, 313 are upper fixing screws, and 314 are lower fixing screws. .. The gap between the lower fixing screw 314 and the intermediate portion base 303 becomes a gap (upper limit gap) δV ₂ that can move upward in the intermediate portion base 303. Further, the gap between the upper fixing screw 313 and the intermediate portion base 303 becomes a gap (lower limit value gap) δV ₁ that can move downward in the intermediate portion base 303.

In the embodiment, the upper limit gap δV ₂ and the lower limit value gap δV ₁ were set at the time of unit assembly. That is, the above-mentioned clearance and spring rigidity are set so that the vibration blocking and the fall prevention effect can be compatible without adjustment even if the mounted mass changes during operation.

[Sixth Embodiment] Tilt angle regulation method FIGS. 19 to 21 show a floating type "tilt angle / independence suppression type" adjustment-less pseudo-rigid body unit according to the sixth embodiment of the present invention. By setting the gap between the spindle and the sleeve to an appropriate stepped structure,
(I) In normal times, the unit spindle remains in a non-contact state, and vibration isolation and vibration isolation performance can be obtained.
(Ii) Even if the load of the device to be protected changes over a wide range, the non-contact state can be maintained without adjustment.
(Iii) In an emergency when locking vibration occurs, the tilt angle suppressing action of suppressing the swinging motion of the entire protected device works by restraining the tilt angle direction of the left and right spindles.

The reason why the above (i) to (iii) can be realized without adjustment is that the point that the left and right spindles alternately repeat the relative movement in the axial direction due to the locking vibration is used, which is an important point of view. Even if a heavy object is mounted on the seismic isolation unit and shaken in the horizontal direction, the spindle does not move in the axial direction, so that the tilt angle suppressing effect cannot be obtained. That is, by arranging the pseudo-rigid body unit on the left and right and mounting the device to be protected, the locking vibration itself suppresses the locking vibration independently. Due to the effect of this self-reliance suppressing action, stable vibration isolation / vibration isolation performance can be obtained against fluctuations in the mounted load, and in an emergency, the fall prevention / impact load reduction effect installed in the optimum state can be obtained without adjustment. In addition, the conventional vibration-reducing structure for industrial equipment eliminates the need for readjustment of the gaps T _n and T _m with narrow upper and lower limits, which were required in response to changes in the load of the equipment to be protected. (See FIGS. 40b and 41)

FIG. 19 is a front sectional view of the pseudo-rigid body unit in a steady state. 10a is the unit main body, 11 is the upper base (upper member), 12 is the lower housing (lower member), 13 is the main shaft formed on the central axis of the upper base 11, and 14 is the spring coil which is an elastic support member. , 16 are positioning portions formed on both members for keeping the axes of the lower housing 12 and the upper base 11 in the same state with the spring coil 14 mounted. Reference numeral 17 denotes a surging prevention member (surging resonance preventing means), and the surging preventing member is deformed and always in contact with the inner peripheral surface of the spring coil 14. 18a, 18b, 18c, and 18d are bolts for fastening this unit to a board (described later) installed on the floor (18b and 18d are not shown). 19 is the upper surface portion of the upper base 11, 20 is a screw portion formed in the central portion of the upper surface portion, 21 is a device to be protected (indicated by an imaginary line), and 22 is to fasten the device to be protected and the unit main body 10a. It is a fastening member for. Reference numeral 23a is a threaded portion formed on the protected device side of the fastening member, 23b is an intermediate member, and 23c is a threaded portion formed on the unit main body portion 10a side. Reference numeral 24 is a fixing sleeve formed in the central portion of the lower housing 12. The main shaft 13 is housed in the fixed sleeve 24 so as to be movable in the axial direction. Reference numeral 25 is a fastener fastened to the lower end surface of the spindle 13 with bolts 26.

The outer surface of the main shaft 13 has a stepped shape, 27a is a main shaft convex portion A, 27b is a main shaft convex portion B, and 27c is a main shaft convex portion C. Further, 28a is a spindle recess A, and 28b is a spindle recess B.

The inner surface of the fixed sleeve 24 also has a stepped shape, 29a is a sleeve convex portion A, 29b is a sleeve convex portion B, 30a is a sleeve concave portion A, 30b is a sleeve concave portion B, and 31 is an installation board (described later). In a steady state (FIG. 19) in which no external force is applied to the protected device 21, the static load of the protected device 21 is in equilibrium with the reaction force due to the displacement of the spring 14. At this time, the heights of the spindle recess A28a and the spindle recess B28b in the axial direction are at the positions of the sleeve convex portion A29a and the fixed sleeve convex portion B29b. The gap between the main shaft concave portion A28a and the sleeve convex portion A29a is δ ₁ , the gap between the main shaft convex portion B27b and the sleeve concave portion A30a is δ ₂ , and the gap between the main shaft concave portion B28b and the sleeve convex portion B29b is δ ₃ . When the spindle 13 is not tilted, each gap is configured to be sufficiently large and have the same dimensions, δ ₁ = δ ₂ = δ ₃ = δ _max . (The above figures are not shown)

FIG. 20 shows the relationship between the spindle and the sleeve of each seismic reduction unit when rocking vibration is generated by a seismic wave. Due to the locking vibration, the main shafts 13 and 113 of the left and right vibration reduction unit main bodies 10a and 10b alternately move up and down greatly. In the figure, the spindle 13 rises in the direction of the arrow C1 in the figure, and the spindle 113 descends in the direction of the arrow C2 in the figure. FIG. 21 shows an enlarged view of the left side vibration damping unit main body 10a. In the figure, the main shaft 13 is in contact with the main shaft convex portion B27b and the sleeve convex portion A29a at the upper portion (chain line circle A1). Further, in the lower portion (chain line circle B1), the main shaft convex portion C27c and the sleeve convex portion B29b come into contact with each other. The distance between the upper end portion of the sleeve convex portion A29a and the lower end portion of the sleeve convex portion B29b is defined as the spindle support width B. Assuming that the gap between the main shaft convex portion B27b and the sleeve convex portion A29a and the gap between the main shaft convex portion C27c and the sleeve convex portion B29b are both δ _min , the maximum inclination angle θ _max of the main shaft 13a is as follows.

Similarly, the inclination angle of the main shaft 113 of the right seismic isolation unit main body 10b also contacts at two points, the upper part (chain line circle A2) and the lower part (chain line circle B2). The maximum inclination angle θ _max of the spindle 113 is the same as in Eq. (16). When the locking vibration occurs, the upper limit of the tilt angle (θ _max ) of the entire protected device 21 is determined by the maximum tilt angle θ _max of the spindle, as shown in FIG.

In this embodiment, the spindle is housed in the fixed sleeve so as to be movable in the axial direction. The spindle may be shaped like a sleeve and housed so as to be movable in the axial direction with respect to the fixed shaft. (Not shown)

[7th Embodiment]
22 (a) and 22 (b) show a case where the "adjustment-less pseudo-rigid body unit" according to the seventh embodiment of the present invention is applied to an audio speaker. FIG. 23 is a partially enlarged view of FIG. 21 (a). 350 is a speaker, 351a to 351d are adjustmentless pseudo-rigid body units, 352a to 352d are 4-split boards on which the pseudo-rigid body unit is mounted, and 353 is a floor surface (see FIG. 23). Each pseudo-rigid body unit is fastened to each of the split boards with bolts. Each of the boards is not anchored to the floor surface, can move horizontally with respect to the floor surface, and can float in the vertical direction. Each of the split boards 352a to 352d is independently provided for each of the pseudo-rigid body units 351a to 351d, and each split board has the central axis of the pseudo-rigid body unit as an axis as shown by arrow A. It can be opened and closed freely in the horizontal direction. Assuming that the effective board width determined by the open / closed state of the left and right split boards is B _W , Fig. 22 (a) shows the state of B _W = B W _max with the widest effective board width, and Fig. 22 (b) shows B _W = B W _min . Indicates the state.

FIG. 23 is a front sectional view focusing on the pseudo-rigid body unit and the board in FIG. 22 (a). Focusing on the pseudo-rigid body unit 351a, 354a and 354b are bolts that fasten the board 352a and the lower housing of the pseudo-rigid body unit from the bottom surface of the board 352a. When there are no obstacles such as walls around the speaker 350 mounted on the 4-split board, the state of B _W = B _Wmax , which has the widest effective board width, is the safety margin against falling against a disturbance load. Is the largest.

FIG. 24 shows a case where the speaker 350 mounted on the quadrant board is arranged in the corner portion of the room in the vicinity of the wall surface 355. The boards 352a and 352d installed in the direction without a wall show a state in which the opening is fully extended, and the boards 352b and 352c installed in the direction with a wall show a state in which the opening is set small.

As mentioned above, due to the recent trend, the form of many speakers has changed from the conventional floor type to a tall tall boy type with a small installation area. The transition to the tall boy type is due to the residential environment in which the speakers are installed. With the 4-split board proposed in the present embodiment, a pseudo-rigid body system can be realized without losing the advantage of the tall boy type space saving. The single body shape of each divided board is not a rectangle, but may be, for example, an L-shaped shape or a + -shaped shape. In the case of the + type shape, the lengths in the vertical direction and the horizontal direction do not have to be the same, and may be arbitrarily selected according to the structure to be applied. If the device to be protected is supported at three points, a three-piece board may be applied.

[Supplement 1] ・ ・ ・ Theoretical analysis of locking vibration
[1-1] Conventional research examples on locking vibration There are many research examples on rocking vibration of structures generated during an earthquake. For example, in Non-Patent Document 1, Kobayashi et al. Obtained the overturning condition of a structure in a two-degree-of-freedom locking system in which two rigid bodies are stacked by numerical simulation. In Non-Patent Document 3, Chung et al. Propose a non-linear locking model considering sliding motion between a structure and a base (installation surface), and evaluate the validity of the mechanical model experimentally. In Non-Patent Document 4, Furukawa et al. Obtained the minimum value of the height-width ratio of a tombstone that overturns with respect to the maximum acceleration for each frequency, and created an overturning standard. In all of the above studies, the dynamic characteristics of an unconstrained rigid block when an external force is applied were obtained.

However, in order to simultaneously realize vibration isolation / vibration isolation performance in normal times and earthquake countermeasures in an emergency by using the rigid body block as a device to be protected, (i) the rigid body block is supported by a spring.
(Ii) The displacement of the rigid block is regulated within a narrow gap.
At this stage, there is no research example other than the research of the present invention that theoretically elucidates the dynamic behavior (dynamics) of the rigid block under the conditions of (i) and (ii) above.

[1-2] Theoretical analysis for impact load
[1-2-1] When the equipment to be protected is mounted on the pseudo-rigid body unit (seismic reduction unit) fastened to the basic board and the board and the floor surface are completely fixed by an anchor or the like, the above-mentioned An analysis is performed to determine the impact load applied to the support of the device to be protected. Hereinafter, by incorporating the displacement regulation mechanism of the upper limit value and the lower limit value, the basic equation regarding the vertical displacement of the center of gravity of the rigid body supported by the spring and the inclination angle θ with the corner of the block as the fulcrum is derived.

FIG. 25 shows a state in which pseudo-rigid body units 10a to 10d are fastened on a board 31 anchored to a floor surface 32, and a protected device 21 (hereinafter referred to as a rigid body block) is mounted on the pseudo-rigid body units 21a to 10d. FIG. 26 is an analysis model diagram showing a state in which locking vibration is generated in the rigid body block (the rigid body block is tilted at an angle θ).
Here, m is the mass of the rigid body block, R is the distance between the bottom corner of the block and the position of the center of gravity G, B ₀ is the distance between the left and right support parts of the block, I ₀ is the rotational moment of the rigid body block with the bottom corner as the fulcrum, and the rigid body. Let H be the height of the center of gravity of the block, and tan (φ) = B ₀ / 2H. The part indicated by the chain line circle BB is composed of a displacement regulating mechanism that adjusts the upper limit value and the lower limit value and a spring.
In FIG. 26, let Y be the displacement of the center of gravity of the rigid body block, and y ₁ and y ₂ be the displacements of the left and right corners from the static equilibrium point.

From equations (17) and (18)

Here, the following nonlinear clearance function is introduced to obtain the reaction force of the left and right support parts by giving the displacements y ₁ and y ₂ and the velocities dy ₁ / dt and dy ₂ / dt.

The reaction force F _s from the left and right supports acting on the center of gravity G of the block is

Therefore, the equation of motion in the direction of rotation with the right corner as the fulcrum and the equation of motion in the vertical direction at the center of gravity G is

Therefore, by solving the above differential equations (24) and (25) simultaneously, the angle θ and the displacement Y in the locking vibration can be obtained. Here, the nonlinear gap function F _Φ (Narrow Gap Function) was introduced to solve the vibration phenomenon accompanied by collision in a minute gap. FIG. 27 shows the analysis model. By introducing the above-mentioned clearance function in order to obtain the reaction force from the support portion, the solution can be continuously obtained by the transient response analysis without switching the equation of motion before and after the collision discontinuously.

Collision-free y_{b b}<y₁< y y_aAnd y_{b b}<y₂< y y_aIn the range of, the spring rigidity of the left and right support parts is K.₁, K₂ As the spring reaction force and displacement of each support₁, Y₂The relationship is linear.

In the range of y ≤ y _a and y ≥ y _b , the reaction force due to the non-linear spring rigidity whose absolute value increases sharply with respect to the displacement, and the non-linear decay with respect to the displacement and velocity are expressed in equations (24) and ( 25) Give to the equation of motion. However, at y = y _a and y = y _b , the characteristics of the reaction force with respect to the displacement are continuously connected. FIG. 28 shows an example of the spring reaction force K _Φ (y) · y characteristics with respect to the displacement y.

[1-2-2] Analysis results of rotation angle and impact load Below, when horizontal acceleration is applied to the rigid body block, the rotation angle of the locking vibration and the generated force of the support part are analyzed. The analysis conditions are block support width B ₀ = 282 mm, center of gravity height H = 710 mm, R = 0.274 m, block mass m = 30 Kg, block moment of inertia I ₀ = 21.0 Nms ² , support spring rigidity K ₁ = K ₂ = 5.92 × 10 ⁴ N / m, the vertical resonance frequency f _0H = 10Hz determined by the above m, K ₁ , and K ₂ , and the rotational resonance frequency f _0R = 1.3Hz. The horizontal accelerations that give locking vibrations to the rigid block are shown in FIGS. 29a and 29b. That is, it is assumed that a Sweep waveform that changes in a range of constant amplitude a = 3 m / s ² and frequency f = 6 Hz → 0.4 Hz is given to the floor surface over a time of 30 seconds.

FIG. 30 shows the response characteristics of the rotation angle of the locking vibration when the displacement regulation δV ₁ = δV ₂ = 1.5 mm is applied with the lower limit value gap δV ₁ and the upper limit value gap δV ₂ . The response characteristics when there is no displacement regulation are shown by a chain line in the same graph. When there is no displacement regulation, the rotation angle θ of the locking vibration indicates the resonance peak value (θ _max = 17deg) near the time t = 25s. The time t indicating this resonance peak value corresponds to the time when the frequency of the Sweep acceleration type (FIG. 29b) coincides with the rotational resonance frequency f _0R = 1.3Hz of the rigid body block. When the displacement is regulated, the rotation angle θ keeps a constant value in the vicinity of the resonance point.

FIG. 31 shows the response characteristics of the generated force F ₁ (left corner of the bottom surface of the block) of the pseudo-rigid body support unit under the same conditions as in FIG. When four pseudo-rigid body units are arranged on the bottom surface of the rigid body block, the generated load in this graph corresponds to two units. The waveform of F ₁ > 0 is the compressive load, and the waveform of F ₁ <0 is the extraction load. If the board is not anchored, this pull-out load will cause the rigid block to float.

When the displacement is regulated, both the compressive load and the pull-out load applied to the support portion of the device to be protected peak in the vicinity of the resonance point. That is, if both the upper limit gap δV ₂ and the lower limit value gap δV ₁ are set to 1.5 mm, the maximum compressive load is reduced to 1/5 (F ₁ = 2800N → 600N).

In FIGS. 32 and 33, the response characteristics of the generated force F ₁ of the unit support portion are obtained in comparison with the case of rigid body support. In FIG. 32, the gap δ is ± 1.5 mm (δV ₁ = δV ₂ = 1.5 mm), and in FIG. 33, the gap δ is ± 0.5 mm (δV ₁ = δV ₂ = 0.5 mm). From the analysis result of FIG. 33, a surprising finding that "a resonance phenomenon exists even if an object moves in a narrow gap of 1 mm while being accompanied by a collision" can be obtained. When the gap ± 1.5 mm is reduced to the gap ± 0.5 mm, the maximum compression load F _max = 600N → 390N is reduced. The maximum pull-out load is reduced from F _max = 250N to 90N. In FIG. 32, in the section where the time is 0 <t <16.5s, that is, in the section where the frequency of the input acceleration is 3 to 6Hz, the generated force is reduced as compared with the case of rigid body support due to the vibration isolation characteristics determined by the spring and the mass. ..

FIG. 34 shows the maximum compressive load F _max of the support portion with respect to the one-sided gap δ (= δV ₁ = δV ₂ ) of the displacement regulating portion. From the graph in the figure, it can be seen that if the gap δ → 0 is set, the maximum compressive load F _max asymptotically approaches the generated force of the rigid body support, and the impact load can be reduced to a level close to the rigid body support.

From the above analysis results, the smaller the one-sided clearance δ (= δV ₁ = δV ₂ ) of the displacement regulating portion, the smaller the force F _max generated by the support portion accompanied by the impact during rocking vibration.
For example, when a precision component is mounted on a device to be protected, the magnitude of the generated force F _max is an important evaluation index indicating the magnitude of damage applied to the precision component.

As described above, in the pseudo-rigid body unit of the present invention, the displacement regulating mechanism (the place where the gaps δV ₁ and δV ₂ are adjusted) and the springs that support the load are arranged coaxially and in close positions. There is. All the parts that require high accuracy are axisymmetric parts, and by combining these axisymmetric parts, the gaps (δV ₁ and δV ₂ ) of the displacement regulating part can be set accurately and narrowly. As a result, the impact load applied to the mounted equipment can be significantly reduced. Further, when the board is not anchored to the floor surface as in each of the above-described embodiments, the effect of reducing the impact load and the pull-out load is an evaluation index indicating the magnitude of the allowance for falling (fall prevention effect). ..

[Supplement 2]
The "adjustment-less pseudo-rigid body unit" according to the present invention can be applied by arranging it according to the needs of the application target regardless of whether it is for industrial use or consumer use. For example, in medical equipment installed in hospitals, storage shelves for dangerous chemicals, railway operation control panels, emergency computer systems for fire departments and police, and semiconductor improvement for the purpose of protecting expensive, important, and valuables. It can be applied as an earthquake countermeasure for wafer-related equipment. Alternatively, it can be applied to transformer equipment, private power generation equipment, etc. that require a large load support of 5 to 10 tons. In addition, since a seismic isolation system consisting of an adjustment-less pseudo-rigid body unit and a board (or a split board) can be realized with an extremely simple configuration, a rack of computer servers installed in an office environment is fully exempted. It can be applied as a simple seismic isolation device that omits anchor fixing, targeting works of art that do not require earthquakes, precision equipment with casters, etc.

The present inventors have already proposed a vibration reduction unit (pseudo-rigid body unit) having a built-in clearance adjustment mechanism using screws or the like in Japanese Patent Application No. 2016-005992. The various seismic reduction unit structures and seismic reduction systems proposed in the above-mentioned special application can be applied as targets for the adjustment-less system proposed by the present invention. The screw structure disclosed in the above-mentioned special application, the method of arranging the damping material for reducing the impact force, and the like may be applied as they are. Further, in the above-mentioned special application, two cases are shown in which the board on which the vibration reduction unit is mounted is anchored to the floor surface and the board is not anchored. Even in the case of the present application, a board on which an adjustment-less / vibration-reducing unit is mounted may be used by anchoring it to the floor surface. Even in this case, even if the condition of the mass of the device to be protected changes within the expected range after installation, the original performance can be maintained without adjustment.

In the above-described embodiment of the present invention, the structure in which the threaded portion including the fastening nut and the like is not provided is shown, but the threaded portion for setting the gap may be provided in the adjustment-less / pseudo-rigid body unit. For example, the clearance adjustment using a screw may be performed by the manufacturer before the product (pseudo-rigid body unit and system) is shipped, and the end user may not have to adjust the clearance of the screw portion. The clearance adjustment of the screw portion performed by the manufacturer may be performed according to the weight of the device to be protected, that is, the type of the product, which has a different target weight. Even if the end user adjusts the gap, the configuration may be significantly simplified. In this case, instead of assembling the screw and the nut, the gap may be roughly adjusted, for example, a detachable ring-shaped spacer may be attached.
The pseudo-rigid body unit of the present invention and the displacement regulating mechanism (A in FIG. 40b) conventionally used in the anti-vibration stand or the like may be independently arranged in parallel to support the device to be protected. In this case, for example, the gap of the displacement regulating mechanism A is set to be slightly larger than that of the pseudo-rigid body unit. Further, the displacement regulating mechanism A may be provided with a damping material such as rubber, and may have a “double defense configuration” capable of significantly reducing the impact load against an acceleration input exceeding an assumption.

In the above-described embodiment (for example, FIG. 1) in which the unit of the present invention is applied to a speaker, a structure is shown in which the speaker and the pseudo-rigid body unit are integrated by a connecting member by using the spike screw portion of the speaker. In this case, the speaker and the pseudo-rigid body unit were separate products. If the speaker main body is pre-designed on the premise that the pseudo-rigid body unit is mounted, the configuration shown below may be used. For example, the bottom of the speaker is shaped like a skirt, and the pseudo-rigid body unit is arranged so that the skirt covers the outer peripheral portion of the pseudo-rigid body unit. With this configuration, decoration such as plating on the outer peripheral portion of the unit becomes unnecessary, and cost reduction can be achieved. If the wind chime effect is omitted, the tubular upper sleeve (for example, the upper member 153 in FIG. 2) may be omitted. In the case of a speaker in which the spike screw portion is not a structure installed on the bottom surface of the speaker but is composed of legs overhanging from the bottom of the speaker, the configuration shown below may be used. That is, with a configuration that also serves as a case for accommodating the spike screw portion and a case for accommodating the pseudo-rigid body unit, (1) when mounting the spikes and (2) when mounting the pseudo-rigid body unit, the above (1). ) (2) can be selected by the end user. In this case, the decoration of the outer peripheral portion of the pseudo-rigid body unit becomes unnecessary, and the cost can be reduced.

In the embodiment, the case where the present invention is applied to a speaker is shown, but the weight for accommodating a CD player, an analog player, a preamplifier, a power amplifier, a personal computer for PC audio, or these audio components, which are audio devices, is shown. It can also be applied to large audio racks (shelf), various musical instruments (for example, acoustic instruments), and musical instruments such as pianos. Various structural proposals such as units and boards proposed for audio can also be applied to industrial use.

The number of spring coils (elastic support members) mounted on the adjustment-less / pseudo-rigid body unit is not one, but may be arranged, for example, on the circumference. In this case, the upper limit value regulating unit and the lower limit value regulating unit may be provided on the center line of the circumference, that is, on the axis of the "spring center of gravity" of the plurality of spring coils.

In the embodiment, a spring coil having a uniform outer diameter in the axial direction is used as the elastic support member, but the elastic support member is not limited to the above shape. For example, conical coil springs, disc springs, or structures in which these disc springs are stacked in multiple stages, bamboo child springs, ring springs, spiral springs, thin leaf springs, stacked leaf springs, U-shaped springs, etc. It should be selected in consideration. In addition to the spring coil, a wire suspension method as shown in the fifth embodiment (FIG. 18) or a method in which a wire and a U-shaped spring are combined can also be applied.

Most of the above-described embodiments show the case where the device to be protected and the adjustment-less / pseudo-rigid body unit are fastened with a connecting member or the like. If the width of the device to be protected is long enough and the margin for tipping is large enough, it is possible to simply place the device to be protected on top of multiple adjustment-less pseudo-rigid body units fixed to the board without fixing it. good. Alternatively, the board may be omitted, and the adjustment-less / pseudo-rigid body unit may be simply fastened to the device to be protected. Alternatively, the connecting member and the board may be omitted, and the adjustment-less / pseudo-rigid body unit may be simply arranged at the bottom of the device to be protected.

152 ... Pseudo-rigid body unit 153 ... Upper member 154 ... Lower member 156 ... Elastic support member 165 ... Upper limit value regulation part 165 ... Lower limit value regulation part

Claims (11)

The upper member provided on the side where the equipment to be protected is mounted, and
The lower member provided on the installation floor side and
An elastic support member provided between the upper member and the lower member to support the mass of the protected device, and
An upper limit value regulating unit provided so as to form a gap between the upper member and the lower member and restricting the upward movement of the upper member by a first predetermined amount or more.
The device to be protected is provided with a lower limit value restricting portion provided so as to form a gap between the upper member and the lower member and restricting downward movement of the upper member by a second predetermined amount or more. The possible range of mass m is m ₀ ≤ m ≤ m _max ,
The rigidity of the elastic support member is K,
When the rigidity K of the elastic support member and the mass m of the device to be protected are m ₀ , the resonance frequency is f ₀ .
When the elastic support member supports the protected device having a mass of m _max , the displacement from the balanced position when the elastic support member supports the protected device having a mass of m ₀ is x _n .
The average gap between the upper limit value regulation part and the lower limit value regulation part determined by this displacement x _n is δ _mean ,
The limit gap determined by the fall limit or the allowable limit of the generated impact load is set to δ _max .
While maintaining the mean gap δ _mean <the limit gap δ _max ,
The resonance frequency f ₀ is set so that the gap between the upper limit value regulation unit and the lower limit value regulation unit can be maintained in a non-contact state.
When the mass is m = m ₀ , the gap of the upper limit value regulation part is δV _2mini ,
When the mass is m = m _max , the gap of the lower limit value regulation part is δV _1min ,
Set so that δV 2min> 0 and δV _1min > ₀ ,
A pseudo-rigid body unit characterized in that the mass increase rate n and the resonance frequency f ₀ are set so as to satisfy the following conditions with the mass increase rate n = m _max / m ₀ .

The pseudo-rigid body unit according to claim 1, wherein the average clearance is 1.0 × 10 ^-3 m ≦ δ _mean ≦ 2.5 × 10 ^-3 m. The upper member includes a central member extending downward, and the upper limit value regulating portion is configured to regulate the amount of upward movement of the upper member by a gap δV ₂ between the central member and the lower member. And
The lower limit value regulating unit is configured to regulate the amount of downward movement of the upper member by the gap δV ₁ between the central member and the lower member.
The pseudo-rigid body unit according to claim 1, wherein the upper limit value regulating unit and the lower limit value regulating unit are arranged side by side along the axial direction of the central member. The plurality of pseudo-rigid body units according to claim 1,
A unit-side fastening portion provided on the protected device side of the upper member,
With the fastening portion on the protected device side provided on the bottom surface of the protected device,
By a connecting member that connects the unit-side fastening portion and the protection target device-side fastening portion.
A pseudo-rigid body system characterized in that the device to be protected and the pseudo-rigid body unit are integrated. The plurality of pseudo-rigid body units according to claim 1,
A board having a larger area than the bottom surface of the device to be protected and to which the plurality of pseudo-rigid body units are fastened is provided.
A pseudo-rigid body system characterized in that the device to be protected is mounted in a state of being fastened to the plurality of pseudo-rigid body units. The plurality of pseudo-rigid body units according to claim 1,
The area is larger than the bottom area of the pseudo-rigid body unit, and a split board, which is fastened to each of the plurality of pseudo-rigid body units, is provided, and the protected device is fastened to the plurality of pseudo-rigid body units. A pseudo-rigid body system characterized by being mounted. A claim that is a pseudo-rigid body unit that supports a speaker as a device to be protected, and is characterized in that the mass increase rate is n = m _max / m ₀ , and the range is n ≧ 1.5 and 8 Hz ≦ f ₀ ≦ 15 Hz. Item 1. The pseudo-rigid body unit according to item 1. The protected device is a speaker.
The pseudo-rigid body unit according to claim 1, wherein the minimum mass of the speaker is supported in the range of m ₀ = 15 to 25 kg, and the maximum mass is supported in the range of m _max = 30 to 50 kg. The pseudo-rigid body unit according to claim 1, which supports an audio device as a device to be protected.
A cylindrical space having a volume capable of accommodating the spike main body portion on the audio device side or a part of the spike main body portion is formed in the central portion of the upper member.
The unit-side threaded portion formed on the side surface of the cylindrical space,
The audio side screw part for attaching spikes provided on the bottom of the audio device,
A pseudo-rigid body system characterized in that the audio device and the pseudo-rigid body unit are integrated by a connecting member connecting the unit-side screw portion and the audio-side screw portion. In the pre-stage of the work of integrating the audio device and the pseudo-rigid body unit,
The pseudo-rigid body system according to claim 9 , wherein the spike tray is arranged on the floor surface side bottom surface of the cylindrical space so that it can be applied as a spike receiver for sound quality evaluation. The plurality of pseudo-rigid body units according to claim 1 ,
A board having a larger area than the bottom surface of the device to be protected and to which the plurality of pseudo-rigid body units are fastened is provided.
The mass of the protected device is m, the height of the center of gravity of the protected device is H, the distance between the left and right support portions of the protected device is B ₀ , and the distance between the support portion and the center of gravity of the protected device is R. Angle φ = tan ^-1 (B ₀ / 2H), gravity acceleration _g , board mass m _b , distance between the center of gravity of the board and the corners of the board BG, support and board When the distance between the corners is B ₁ , the maximum tilt angle when a static load in the horizontal direction is applied to the device to be protected is θ _r , and η is defined by the following equation.

A pseudo-rigid body system characterized in that η ≧ 1.

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