JP2013117287A - Vibration control system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control system capable of controlling resonance even for vibration based on various loads.SOLUTION: A vibration control system includes a device 11 installed in plant equipment, a caster 13 for supporting the deadweight of the device 11 and displacing the device 11 in a horizontal direction, and a support structure 14 disposed at least in a horizontal uniaxial direction while forming a given clearance 15 between itself and the device 11. The support structure 14 displaces the device 11 within a range of the clearance 15 on the occurrence of a first load for vibrating the first device 11 by a first frequency, and also is disposed by coming into contact with the device 11 and disposed by forming the given clearance 15 capable of supporting the device 11 on the occurrence of a second load for vibrating the device by a second frequency smaller than the first frequency.

Description

  The present invention relates to a vibration isolation system applied to equipment installed in, for example, plant equipment.

  Various devices installed in plant facilities are designed in consideration of the load generated from the device itself, the load generated from other devices installed in the vicinity, the load brought by nature such as snow, wind, earthquake, etc. . In particular, it is desirable that the equipment related to the safety system of a nuclear power plant maintain its function against an external force such as a hydrodynamic dynamic load in addition to an earthquake as a dynamic load.

  For example, Patent Document 1 discloses a technology that avoids or suppresses resonance that may occur in a support frame that contacts a vibrating body that generates vibration and supports the vibrating body. This support frame has a rigidity adjusting portion, and the rigidity of the support frame is changed by attaching ribs or injecting concrete to the rigidity adjusting portion. Thereby, the natural frequency of the support frame changes, and resonance with the vibrating body is avoided or suppressed.

JP 2010-190157 A

  As described above, not only a load from a vibration body that can be assumed in advance, but also various loads due to an impact or a seismic motion caused by an event occurring inside or outside the building can be generated in equipment installed in the plant facility.

  The technique of Patent Document 1 is a technique for avoiding or suppressing the resonance of the support frame due to the excitation force propagated from the vibrating body. However, in order to change the natural frequency of the support gantry, it is necessary to attach ribs or inject concrete in advance. Resonance could not be avoided or suppressed.

  The present invention has been made in consideration of such circumstances, and an object thereof is to provide a vibration isolation system capable of suppressing resonance even with respect to vibrations based on various loads.

  In order to solve the above-described problems, the vibration isolating system according to the embodiment of the present invention includes an apparatus installed in plant equipment, an apparatus support member that supports the weight of the apparatus and that displaces the apparatus in the horizontal direction. A support structure disposed at least in a horizontal uniaxial direction so as to form a predetermined gap with the device, wherein the support structure has a first load that vibrates the device at a first frequency. When the second load that causes the device to be displaced within the gap and vibrates at a second frequency smaller than the first frequency is generated, the device can contact the device and support the device. A predetermined gap is formed and arranged.

  In the vibration isolating system according to the present invention, resonance can be suppressed even with respect to vibration based on various loads.

1 is a schematic front view showing a first embodiment of a vibration isolating system of the present invention. The schematic front view which shows 2nd Embodiment of the vibration isolating system of this invention. It is a 1st modification of 2nd Embodiment of the vibration isolating system of this invention, Comprising: The schematic enlarged front view which shows especially a support structure periphery. It is a 2nd modification of 2nd Embodiment of the vibration isolating system of this invention, Comprising: The rough expanded front view which shows especially a support structure periphery. The schematic front view which shows the 3rd modification of 2nd Embodiment of the vibration isolating system of this invention. The schematic front view which shows 3rd Embodiment of the vibration isolating system of this invention. The schematic front view which shows 4th Embodiment of the vibration isolating system of this invention. The enlarged view of the area | region VIII of FIG. The schematic front view which shows the vibration proofing system as a 1st modification of the vibration proofing system of 1st-3rd embodiment. The schematic front view which shows the anti-vibration system as the 2nd modification of the anti-vibration system of 1st-3rd embodiment.

  An embodiment of a vibration isolating system according to the present invention will be described with reference to the accompanying drawings.

  In each embodiment, an example will be described in which the vibration isolation system according to the present invention is provided in a plant facility such as a nuclear power plant and applied to equipment installed in the plant facility.

[First Embodiment]
FIG. 1 is a schematic front view showing a first embodiment of a vibration isolating system according to the present invention. In FIG. 1, the configuration other than the device 11 is shown in cross section.

  The anti-vibration system 1 is arrange | positioned on the baseplate 10 installed on the building floor 2 of plant equipment.

  The base plate 10 is fixed on the building floor 2 by fixing means such as anchor bolts. A device 11 is arranged on the base plate 10. The device 11 houses a component 12 such as a relay. The component 12 is a component designed to have a predetermined acceleration resistance (for example, 3G) and subjected to a required acceleration resistance test.

  The equipment 11 is supported on the building floor 2 (foundation board 10) via casters 13 (equipment support members). The caster 13 supports the weight of the device 11. The caster 13 is a member that freely displaces (moves) the device 11 in the horizontal direction, such as a spherical bearing, and has no restoring force at least in the horizontal direction.

  The device 11 is surrounded by a support structure 14 in the horizontal direction on the outer peripheral surface from the base plate 10 to a predetermined height. It is desirable that the support structure 14 is fixed on the base plate 10 and is not displaced by contact with the displacement of the device 11 in the horizontal direction. The support structure 14 does not have to surround all four sides of the device 11 in the horizontal direction, and may be at least in the horizontal uniaxial direction or the biaxial direction, or may intermittently surround the four sides. The peripheral shape of the support structure 14 is not limited to the structure shown in FIG. 1 as long as it has a support surface 14 </ b> A facing the device 11.

  A gap 15 is formed between the support structure 14 and the device 11. The gap 15 has a size in which a displacement in which the device 11 responds to a dynamic design load (for example, a displacement when the building floor 2 vibrates at a frequency of 15 Hz or more) is added with allowance for variation. Have. That is, the support structure 14 is arranged so that the device 11 is displaced within the gap 15.

  Next, the operation of the vibration isolation system 1 in the first embodiment will be described.

  In general, the dynamic loads that should be considered for equipment related to the safety system of nuclear power plants are the loads and accidents that occur during normal operation, mostly occurring in part of the building, excluding earthquake loads. Is a first load generated by propagating the building through the building (hereinafter simply referred to as “load during normal operation”). For example, in a coolant loss accident (LOCA), which is an example of an accident event, a support point reaction force at the time of pipe breakage propagates to a building and excites equipment in the building. Also, any impact from outside the building propagates to the building and excites the equipment inside the building.

  Depending on the excitation force on the building structure due to these events, the natural frequency components of the building floor and wall (building structure) are dominant. The natural frequency of this building structure is approximately 15 Hz or higher, and therefore the dominant frequency of the excitation force (normal load) acting on the equipment in the building is also approximately 15 Hz (first frequency).

  Then, the vibration isolating system 1 in 1st Embodiment suppresses the resonance of the apparatus 11 and the acceleration added to the apparatus 11 is reduced when the caster 13 of the apparatus 11 acts. As a result, the acceleration applied to the component part 12 accommodated in the device 11 can be reduced.

  That is, it is known that the absolute acceleration frequency response magnification of sinusoidal forced vibration with constant acceleration in a one-degree-of-freedom system without attenuation is represented by the following formula (1).

  According to Equation (1), the response magnification is 1 when λ (λ> 0) is small. As λ is increased from this point, the response magnification increases as λ approaches 1, and when λ = 1, the response magnification becomes infinite. Further, when λ is larger than 1, for example, the response magnification decreases again to 1/3 when λ = 2 and 1/8 when λ = 3, and approaches 0 as λ increases.

  Here, since the apparatus 11 having the casters 13 has no restoring force, the natural frequency is 0 Hz. That is, it can be seen that λ in Equation (1) is infinite and the acceleration response magnification is close to zero.

  On the other hand, the caster 13 can freely move a dynamic load (hereinafter simply referred to as “seismic load”) as a second load such as a seismic load that excels at a frequency of several Hz (second frequency). A large response displacement occurs in the device 11 that moves to the position. For example, it is known that the response displacement of the vibration isolating system 1 having a natural frequency of 0.5 Hz or less with respect to an earthquake load reaches several hundred mm.

  For this reason, the gap 15 provided between the device 11 and the support structure 14 has a negligible value (the device 11 and the support structure 14 are in contact with each other). The device 11 supported in the horizontal direction by the support structure 14 has an increased support rigidity and can secure a high natural frequency. As a result, λ in Expression (1) is a value close to 1, and the vibration of the device 11 is hardly amplified.

  For example, references (H. Niwa, E. Manome, Y. Sakurai, N. Sasaki, “Resonant Frequents in Piping Systems, i.sup.48, p. 91, SM. 7, it is known that a response displacement of 10 times the clearance and a response displacement of 1/2 or 100 times the natural frequency of the device itself is almost the same as the original natural frequency.

  Such a vibration isolating system 1 according to the first embodiment has a vibration isolating or vibration isolating effect against a load during normal operation because the caster 13 acts. Further, the vibration isolating system 1 can support the seismic load, and the natural frequency of the device 11 is changed by being supported by the support structure 14 so that the response magnification can be reduced. As a result, the anti-vibration system 1 can suppress the acceleration applied to the device 11 to be small even when a load during normal operation or a seismic load is applied to the device 11.

  Further, the vibration isolating system 1 does not generate an acceleration higher than that of the device 11 with respect to the component 12 housed in the device 11 in which the acceleration can be kept small. For this reason, if it is confirmed by an acceleration resistance test or the like that the function can be maintained up to a reasonable acceleration (for example, 3G) in advance for the component 12, the component 12 is arranged in a plant facility having a different location environment or structural condition. However, it is effective in that it is not necessary to newly confirm the function maintenance of the component parts 12 by applying the anti-vibration system 1.

[Second Embodiment]
FIG. 2 is a schematic front view showing a second embodiment of the vibration isolating system of the present invention. In FIG. 2, the configuration other than the device 11 is shown in cross section.

  The anti-vibration system 21 in the second embodiment is different from the first embodiment in that a support protrusion 22 is provided on the support structure 14. Since the configuration other than the support protrusion 22 of the vibration isolation system 21 is substantially the same as that of the vibration isolation system 1 of the first embodiment, the same reference numerals are given to the configurations and parts corresponding to those of the first embodiment, and they are duplicated. Description is omitted.

  The support protrusion 22 is a protrusion that protrudes toward the device 11 on the surface of the support structure 14 that faces the device 11. For example, two support protrusions 22 are provided at different positions in the height direction. The support protrusions 22 may be provided continuously on the surface of the support structure 14 facing the device 11 or may be provided partially. A gap 23 is provided between the support protrusion 22 and the device 11 and has a size that takes into account the displacement in which the device 11 responds to a dynamic design load with allowance for variation.

  The anti-vibration system 21 according to the second embodiment causes the support protrusion 22 to abut on and support a predetermined portion of the device 11 when an earthquake load occurs. In the first embodiment, the device 11 brings the device 11 and the support structure 14 into surface contact, whereas in the second embodiment, the device 11 makes the point contact between the device 11 and the support protrusion 22 on the end surface 24 of the support protrusion 22. , Can be contacted reliably. As a result, the anti-vibration system 21 can reliably support the device 11 by the support protrusion 22 against an earthquake load, and can increase the natural frequency of the device 11. The anti-vibration system 21 has a natural frequency higher than the dominant frequency due to the seismic load, and can avoid resonance and keep the response magnification small.

  In addition to the effects of the first embodiment, the vibration isolation system 21 according to the second embodiment can prevent the resonance of the device 11 against the seismic load as described above. As a result, the acceleration resistance required for the device 11 can be reduced. It can be set within a reasonable range.

  In addition, you may comprise the anti-vibration system 21 in 2nd Embodiment like the 1st-3rd modification demonstrated below.

  FIG. 3 is a schematic enlarged front view showing a periphery of the support structure 14 as a first modification of the second embodiment of the vibration isolating system of the present invention.

  An anti-vibration system 31 as a first modification has a pad 32 on the facing surface of the device 11 facing the support protrusion 22. The pad 32 is disposed at a location where the support protrusion 22 and the device 11 are in contact. The pad 32 increases the rigidity of the surface of the device 11 with which the support protrusion 22 contacts, and functions as a deformation preventing material for the device 11. The pad 32 is, for example, a metal member. A gap 33 is provided between the pad 32 and the support protrusion 22 and has a size that takes into account the variation in which the device 11 responds to a dynamic design load with allowance for variation.

  When the device 11 collides with the support protrusion 22 due to the movement of the device 11 due to the seismic load, the device 11 may be deformed or damaged if the rigidity of the device 11 is small. The vibration isolating system 31 receives, with the pad 32, an impact at the time of contact with the support protrusion 22 of the device 11. Thereby, the vibration isolating system 31 can prevent the device 11 from being deformed or damaged.

  FIG. 4 is a schematic enlarged front view showing a second modified example of the second embodiment of the vibration isolating system of the present invention and particularly showing the periphery of the support structure 14.

  An anti-vibration system 41 as a second modification has an impact relaxation material 42 at the tip of the support protrusion 22. A gap 43 is provided between the shock absorbing material 42 and the pad 32. The gap 43 has a size that takes into account the displacement in which the device 11 responds to a dynamic design load with allowance for variation. The shock absorbing material 42 is formed of, for example, a material (for example, rubber) that can absorb and relieve a required shock.

  In addition to the effects of the second embodiment, the vibration isolation system 41 receives an impact when the device 11 collides with the support protrusion 22 by the shock absorbing material 42, thereby generating a large acceleration that may occur at the time of the collision. Can be prevented.

  FIG. 5 is a schematic front view showing a third modification of the second embodiment of the image stabilization system of the present invention.

  An anti-vibration system 51 as a third modification includes a plurality of springs 52 as an example of an elastic body that connects the support structure 14 and the device 11 and supports them in the horizontal direction. The total spring constant of the plurality of springs 52 is set so that the natural frequency of the device 11 in the horizontal direction is ½ or less of the dominant frequency of the dynamic load to be designed.

  Since the vibration isolating system 51 continuously supports the device 11 with the spring 52, the shock to the device 11 when colliding with the support protrusion 22 can be reduced as in the case of the vibration isolating system 41 as the second modified example. Can do.

[Third Embodiment]
FIG. 6 is a schematic front view showing a third embodiment of the vibration isolating system of the present invention. In FIG. 6, the configuration other than the device 11 is shown in cross section.

  The point where the vibration isolating system 61 in the third embodiment is different from that in the first embodiment is that the device 11 is installed on the building floor 2 on which the OA floor 62 is installed. Since the configuration of the vibration isolation system 61 other than the support structure 65 and the OA floor 62 is substantially the same as that of the vibration isolation system 1 of the first embodiment, the same reference numerals are used for the configurations and parts corresponding to those of the first embodiment. A duplicate description will be omitted.

  The base plate 10 is fixed on the building floor 2 by fixing means such as anchor bolts. A device 11 is arranged on the base plate 10. An OA floor 62 is provided on the building floor 2. The OA floor 62 is supported by the building floor 2 via the support pillar 63, and forms a space 64 having a certain height on the building floor 2 (below the OA floor 62). A power cable or the like is wired in the space 64.

  The OA floor 62 has an accommodating portion 66 as a notch portion (a portion where the OA floor 62 is not provided) having a size larger than the outer shape of the device 11 and considering the gap 67 in order to accommodate the device 11. The OA floor 62 is supported in the height direction from the building floor 2 (foundation board 10) by the support structure 65 on the periphery of the housing portion 66.

  The device 11 is accommodated in the accommodating portion 66 on the outer peripheral surface from the base plate 10 to a predetermined height, and is surrounded by the support structure 65 in the four horizontal directions. It is preferable that the support structure 65 is fixed on the base plate 10 and is not displaced by a collision caused by the horizontal movement of the device 11. The support structure 65 does not have to surround all four sides of the device 11 in the horizontal direction, and may be at least in the horizontal uniaxial direction or biaxial direction, or may intermittently surround the four sides.

  A gap 67 is formed between the support structure 65 and the device 11. The gap 67 has a size that takes into account a variation considering the variation in a displacement in which the device 11 responds to a dynamic design load (for example, a displacement when the building floor 2 vibrates at a frequency of 15 Hz or more). Have. That is, the support structure 65 is arranged so that the device 11 is displaced within the gap 67.

  In addition to the effects of the first embodiment, the anti-vibration system 61 according to the third embodiment has a support structure 65 provided with an accommodating portion 66 on the OA floor 62 even when the OA floor 62 is provided on the building floor 2. Is provided under the floor of the OA floor 62, which is effective in that the access (wiring) under the OA floor 62 associated with the provision of the support structure 65 is not hindered.

[Fourth Embodiment]
FIG. 7 is a schematic front view showing a fourth embodiment of the vibration isolating system of the present invention.
FIG. 8 is an enlarged view of region VIII in FIG.

  The vibration isolating system 71 according to the fourth embodiment is different from the first embodiment in that the caster 13 has a movable protrusion 72 and a caster lock mechanism 74 for the movable protrusion 72. Since the configuration other than the movable projection 72 and the caster lock mechanism 74 of the vibration isolation system 71 is substantially the same as that of the vibration isolation system 1 of the first embodiment, the same reference numerals are given to the configurations and parts corresponding to those of the first embodiment. A duplicate description will be omitted. In particular, the support structure 14 of the anti-vibration system 71 is substantially the same as that of the first embodiment, and thus illustration thereof is omitted.

  As shown in FIG. 8, the base plate 10 has pressure chambers 14 a and 14 b around the caster 13. The pressure chambers 14 a and 14 b are connected to each other by a communication pipe 75. The pressure chambers 14a and 14b have an opening in the upward direction. The movable protrusion 72 is disposed in the pressure chambers 14 a and 14 b so as to be movable up and down around the caster 13.

  The caster lock mechanism 74 includes a pipe 76, a pump 78, and motor operated valves 79a and 79b. The pipe 76 has one end connected to the pressure chamber 14 a and the other end connected to the pump 78. The pipe 76 has a branch pipe 77 that branches between the pressure chamber 14 a and the pump 78. The end of the branch pipe 77 is opened to the atmosphere. The electric valve 79 a is provided between the pump 78 and the branch point of the branch pipe 77. The motor operated valve 79 b is provided on the branch pipe 77.

  The pump 78 supplies a required pressure to the pressure chambers 14 a and 14 b via the pipe 76. At this time, the pump 78 supplies a pressure such that the movable protrusion 72 rises and protrudes from the base plate 10.

  Next, the operation of the vibration isolation system 71 in the fourth embodiment will be described.

  Normally, the motorized valve 79a is opened and the motorized valve 79b is closed. The pump 78 supplies a required pressure to the pressure chambers 14a and 14b. The movable protrusion 72 protrudes upward from the base plate 10 by the supplied pressure. Thereby, in the normal time, the caster 13 is restrained from moving in the horizontal direction by the movable protrusion 72. Since the device 11 becomes a boundary condition with a fixed lower end and has a high natural frequency, resonance with vibrations of surrounding structures due to an earthquake load (second load) can be prevented.

  On the other hand, when a disturbance due to a load during normal operation (first load) occurs and an alarm is issued (in an abnormal state), the motor-operated valve 79a is normally closed from the normally open state, and the motor-operated valve 79b is normally operated. Controlled from closed to open. The supply of pressure from the pump 78 to the pressure chambers 14a and 14b is stopped, and the pressure in the pressure chambers 14a and 14b decreases. The movable protrusion 72 is accommodated in the pressure chambers 14a and 14b, and the movement of the caster 13 in the horizontal direction is effective. Thereby, the natural frequency of the apparatus 11 falls and the acceleration added to the apparatus 11 can be reduced.

  That is, the anti-vibration system 71 ensures the natural frequency suitable for the seismic load in the device 11 during normal operation by controlling the movable protrusion 72 as described above, and is suitable for the load during normal operation during abnormal conditions. The natural frequency can be secured.

  Contrary to the above-described operation, the movable protrusion 72 may be accommodated in the pressure chambers 14a and 14b in a normal state and protrude from the base plate 10 in an abnormal state.

  Specifically, at the normal time, the motor-operated valve 79a is closed and the motor-operated valve 79b is opened. The movable protrusion 72 is accommodated in the pressure chambers 14a and 14b, and the movement of the caster 13 in the horizontal direction is effective.

  When an earthquake alarm is issued, or when information such as earthquake detection information in the seismic observation network is obtained (in an abnormal state), the motor-operated valve 79a is normally opened from the closed state, and the motor-operated valve 79b is It is controlled from normal opening to closing. The pump 78 supplies a required pressure to the pressure chambers 14a and 14b. The movable protrusion 72 protrudes upward from the base plate 10 by the supplied pressure.

  In this case, contrary to the operation described above, the natural frequency of the device 11 during normal operation is low, and the anti-vibration system 71 increases the acceleration applied to the device 11 even when a load during normal operation (first load) occurs. Can be reduced. Further, when the earthquake load (second load) is generated, the function of the caster 13 is suppressed. As a result, the device 11 becomes a boundary condition with a fixed lower end and the natural frequency becomes high, so that the vibration isolation system 71 can prevent resonance with vibration of surrounding structures due to seismic load.

  The vibration isolating system 71 according to the fourth embodiment includes the movable protrusion 72 and the caster lock mechanism 74, so that the natural frequency of the device 11 can be controlled according to the type of vibration applied to the device 11. Thereby, the vibration isolating system 71 can suppress the resonance between the device 11 and the surrounding structure, and can further reduce the acceleration applied to the device 11.

  It should be noted that the present invention is not limited to the above-described embodiment as it is, and can be implemented in various forms other than the above-described examples in the implementation stage, and various modifications can be made without departing from the spirit of the invention. Can be omitted, added, replaced, or changed. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  For example, although the example which applies the caster 13 which does not have the restoring force of a horizontal direction was demonstrated as an example of the apparatus support member which supports the dead weight of the apparatus 11, it replaced with this by the load by which the natural frequency is assumed. A member having a slight restoring force that is smaller than the dominant frequency due to the generated vibration may be applied.

  FIG. 9 is a schematic front view showing a vibration isolation system 81 as a first modification of the vibration isolation systems 1 to 61 of the first to third embodiments. About the anti-vibration system 81, about the structure and part corresponding to the said embodiment, the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

  The device 11 is supported on the base plate 10 via a laminated rubber 82 which is an example of a member having good vibration absorption. The laminated rubber 82 preferably has a horizontal spring constant such that the natural frequency of the device 11 supported by the laminated rubber 82 is ½ or less of the dominant frequency of the dynamic load to be designed.

  FIG. 10 is a schematic front view showing a vibration isolation system 91 as a second modification of the vibration isolation systems 1 to 61 of the first to third embodiments. About the anti-vibration system 91, about the structure and part corresponding to the said embodiment, the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

  The vibration isolation system 91 includes a caster 13 and a coil spring 92. The coil spring 92 is fixed to the device 11 and the base plate 10 via a support member, and restricts the movement of the caster 13 in the horizontal direction. The caster 13 and the coil spring 92 support the device 11 so that the natural frequency in the horizontal direction of the device 11 is ½ or less of the prevailing frequency of the dynamic load designed as in the case of the laminated rubber 82 in FIG. 9. It is preferable that it is comprised.

  In this way, by setting the horizontal spring constants of the laminated rubber 82 and the coil spring 92 so that the dominant frequency of the device 11 is less than or equal to ½, in the above formula (1), λ ≧ 2. For this reason, the vibration isolation system 81 can set the response magnification to 1/3 or less.

1, 21, 31, 41, 51, 61, 71, 81, 91 Anti-vibration system 2 Building floor 10 Base plate 11 Equipment 12 Component 13 Casters 14, 65 Support structure 15, 23, 33, 43, 67 Clearance 22 Support projection 32 Pad 42 Impact relaxation material 52 Spring 62 OA floor 66 Housing portion 72 Movable projection 74 Caster lock mechanism 82 Laminated rubber 92 Coil spring

Claims (13)

Equipment installed in the plant equipment;
A device support member for supporting the weight of the device and displacing the device in a horizontal direction;
A support structure disposed at least in a horizontal uniaxial direction to form a predetermined gap with the device,
When the first load that causes the device to vibrate at the first frequency is generated, the support structure displaces the device within the gap and vibrates at a second frequency smaller than the first frequency. When the second load is generated, the vibration isolating system is arranged so as to form the predetermined gap that can contact the device and support the device.   2. The anti-vibration device according to claim 1, wherein the support structure includes a support protrusion that protrudes toward the device and abuts against a predetermined portion of the device, and forms the predetermined gap between the support protrusion and the device. system.   The vibration isolating system according to claim 2, further comprising an impact relaxation material that relaxes an impact caused by contact with the device on a contact surface of the support protrusion with the device.   The anti-vibration system according to claim 2 or 3, further comprising a deformation preventing material that prevents deformation due to contact with the device on a contact surface of the device with the support protrusion.   The anti-vibration system according to any one of claims 1 to 4, further comprising an elastic body that couples the device and the support structure.   The vibration isolation system according to claim 1, wherein the device support member is a caster.   The vibration isolation system according to claim 6, wherein the device support member further includes an elastic body that restricts movement of the device in a horizontal direction within a predetermined range.   The vibration isolation system according to claim 6, further comprising a caster lock mechanism that permits movement of the caster when the first load occurs and restricts movement of the caster when the second load occurs.   The vibration isolating system according to any one of claims 1 to 5, wherein the device support member is a laminated rubber.   The vibration isolation system according to any one of claims 1 to 9, wherein the first load includes a load that can be generated during normal operation of the plant equipment.   The vibration isolation system according to any one of claims 1 to 9, wherein the second load includes an earthquake load.   The said predetermined clearance gap adds the allowance which considered the dispersion | variation in the said response displacement to the response displacement of the said apparatus when the said 1st load acts. Anti-vibration system. Further comprising an OA floor disposed on a building floor of the plant facility and having a cutout portion larger than an outer shape of the device;
The device is accommodated in the notch and disposed on the building floor,
The said support structure is a vibration isolating system as described in any one of Claims 1-12 which supports the said OA floor from the said building floor in the height direction in the edge periphery of the said notch part.

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