JP4697741B2 - Vibration control cabinet - Google Patents

Description

  The present invention relates to a vibration control cabinet that mitigates shaking such as an earthquake and protects items contained therein, and particularly for electric / electronic devices and electric / electronic devices having a vibration control function for storing precision devices. Suitable for cabinets.

For example, a cabinet that houses electrical / electronic equipment and precision equipment (hereinafter referred to as “electronic equipment, etc.”) can be used to reduce vibrations such as earthquakes and protect these equipment. What is supported by means is known. As the vibration absorbing means, there are a plate spring interposed (Japanese Patent Laid-Open No. 2005-217380) and a combination of a spring and a roller member (Japanese Patent Laid-Open No. 2002-2135130, Japanese Patent Laid-Open No. 2000-320610). Are known.
JP 2005-217380 A JP 2002-213530 A JP 2000-320610 A

  As shown in FIG. 1, the cabinet 100 described above has a double structure of an outer cabinet 101 and an inner cabinet 102, and a vibration absorbing element is disposed between the inner cabinet 102 and the outer cabinet 101. And although illustration is abbreviate | omitted, the impact by the vibration of the earthquake transmitted to an electronic device etc. is relieve | moderated by accommodating an electronic device etc. in the inner cabinet 102. FIG. In such a structure, the front surface 103 of the outer cabinet 101 is used for taking out and operating electronic devices housed in the inner cabinet 102, and the back surface 104 of the outer cabinet 101 is used for wiring the devices housed in the inner cabinet 102. Open each one. For these reasons, a reinforcing structure can be provided on the side surfaces 105 and 106 of the outer cabinet 101, but a sufficient reinforcing structure cannot be provided on the front surface 103 and the rear surface 104 of the outer cabinet 101 (see FIG. 1 is abbreviate | omitting illustration about a reinforcement structure.). For this reason, the outer cabinet 101 can secure strength against shaking in the front-rear direction a, but cannot secure sufficient rigidity against shaking in the left-right direction b. When subjected to earthquake motion, the outer cabinet 101 tends to swing in the left-right direction b. The cabinet 100 wants to mitigate the shock caused by the vibration of the earthquake transmitted to the electronic equipment and the like housed in the inner cabinet 102 and to suppress the shaking of the outer cabinet 101 in the left-right direction b to some extent.

  What is described in said patent document uses the spring element as a vibrational absorption element. The spring element has almost no damping action and little action to consume vibration energy. In addition, the spring element alone hardly obtains an action of absorbing vibration energy, and may resonate with earthquake motion. For this reason, the effect which suppresses a vibration is not fully acquired.

  The inventors consider that the inner cabinet is supported by the sliding bearing device or the rolling bearing device, and that the vibration energy is absorbed by using a viscoelastic body such as rubber instead of the spring element. The viscoelastic body can absorb vibration energy as the amount of shear deformation increases, and has a function of quickly damping the vibration. However, in order to effectively exhibit such a function, it is necessary to select an appropriate viscoelastic body.

The vibration damping cabinet according to the present invention includes an outer cabinet, an inner cabinet disposed inside the outer cabinet, and a vibration damping unit disposed between the inner cabinet and the outer cabinet . It is composed of a vibration damping device and a sliding bearing device or a rolling bearing device. The vibration damping device has a laminated body in which viscoelastic bodies and intermediate plates are alternately stacked, and is attached between a pair of plates. One plate is fixed to the inner cabinet and the other plate is fixed to the floor or ceiling material of the outer cabinet, and the sliding bearing device or rolling bearing device is an extension that extends beyond the viscoelastic body of the intermediate plate. Each of which is mounted on the existing part, supports the inner cabinet, and includes a sliding bearing member or a rolling bearing member capable of sliding or rolling with respect to a pair of plates, When the viscoelastic body of the vibration device, the total mass of the inner cabinet containing mass which is loaded in the inner cabinet was M (kg), at 20 ° C. of the temperature environment, the shear strain rate γ = 1.0, f = 2 When a vibration of 0.0 Hz is applied, a spring value of 0.28 M (N / mm) or more and 0.70 M (N / mm) or less is exhibited, and the loss coefficient tan δ is 0.4 or more. It is a feature.

  According to this vibration control cabinet, since an optimal viscoelastic body is adopted according to the total mass M of the inner cabinet, a viscoelastic body that can exhibit appropriate vibration control performance in response to various earthquake motions is adopted. be able to.

  Hereinafter, a vibration control cabinet according to an embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected and demonstrated to the member and site | part which show the same effect | action.

  As shown in FIG. 2, the vibration suppression cabinet 10 according to the embodiment of the present invention includes an outer cabinet 11, an inner cabinet 12 disposed inside the outer cabinet 11, and the inner cabinet 12 and the outer cabinet 11. The sliding bearing devices 13 and 14 for supporting the inner cabinet 12 disposed therebetween and the vibration damping device 15 disposed between the inner cabinet 12 and the outer cabinet 11 are configured. Further, the vibration damping device 15 attaches the viscoelastic bodies 31 and 32 between the pair of plates 33 and 34, fixes one plate 33 of the pair of plates 33 and 34 to the inner cabinet 12, and the other plate 34. Are fixed to the floor material 21 or the ceiling material 23 of the outer cabinet 11. The viscoelastic bodies 31 and 32 have a shear strain rate γ = 1... In a temperature environment of 20 ° C. when the total mass of the inner cabinet 12 including the mass body loaded on the inner cabinet 12 is M (kg). When a vibration of 0, f = 2.0 Hz is applied, a spring value of 0.28 M (N / mm) or more and 0.70 M (N / mm) or less is exhibited, and the loss coefficient tan δ is 0.4. The above was used. Here, γ is the shear strain rate, and is obtained by dividing the shear deformation amount d of the viscoelastic body by the height t of the viscoelastic body, as shown in FIG.

  In this embodiment, the outer cabinet 11 includes a rectangular flooring 21, column members 22 erected at the four corners of the flooring 21, and a reinforcing material (not shown) that reinforces the standing state of the column members 22, The ceiling member 23 is arranged on the upper portion of the column member 22. Although not shown, the reinforcing material is provided on the side surfaces 24 and 25 of the outer cabinet 11 and is installed between the column material 22 and the beam material 22 and the floor material 21 or the column material 22 and the ceiling material. 23 and a brace material installed obliquely between the two. The reinforcing material is not provided on the front surface and the back surface of the outer cabinet 11.

  The inner cabinet 12 is disposed inside the outer cabinet 11. In this embodiment, the inner cabinet 12 includes a rectangular lower plate member 26, a column member 27 attached to the corner of the lower plate member 26 in the height direction, and a rectangular upper plate member 28 attached to the upper portion of the column member 27. It is composed. In this embodiment, a mounting portion (mounting hole) is provided in the column member 27 so that a unit (not shown) that accommodates the device can be mounted in a plurality of stages in the height direction. The inner cabinet 12 is installed inside the outer cabinet 11 with a vibration damping device 15 interposed, as will be described later.

  The vibration control cabinet 10 used in the test described later has an outer cabinet 11 having a width of 800 mm, a depth of 1000 mm, and a height of 2000 mm, and an inner cabinet 12 having a width of 700 mm, a depth of 900 mm, and a height of 1900 mm. Using.

  The mass of the inner cabinet 12 itself is 51 kg. In FIG. 2, although not shown, a plurality of cases are installed in the height direction in the inner cabinet 12, and the mass is adjusted by installing a weight in the case. In the vibration suppression cabinet 10 having the above dimensions, the maximum load capacity for guaranteeing the vibration suppression function is set to 300 kg. In this test, a total weight of 300 kg is installed in the inner cabinet 12. Also, there is usually a tendency to install heavy items down and light items up. For this reason, in this test, among the tests of A to I, in the test of J, the weight is arranged so that the center of gravity of the inner cabinet 12 is located at a half height of the inner cabinet 12. In other tests, the weight was arranged so that the center of gravity of the inner cabinet 12 was located at 2/5 height of the inner cabinet 12. Further, the columnar material 27 of the inner cabinet 12 is provided with acceleration sensors at three positions in the height direction, and the acceleration at each position is measured.

  As shown in FIG. 2, the sliding bearing devices 13 and 14 and the vibration damping device 15 are disposed between the inner cabinet 12 and the outer cabinet 11. In this embodiment, as shown in FIGS. 3A and 3B, the sliding bearing devices 13 and 14 and the vibration damping device 15 are unitized into one device (hereinafter, such units are referred to as “vibration damping unit”). "). Of such a vibration damping unit 30, the part functioning as the vibration damping device 15 is obtained by attaching viscoelastic bodies 31 and 32 between a pair of plates 33 and 34. One plate 33 is fixed to the inner cabinet 12, and the other plate 34 is fixed to the floor material 21 or the ceiling material 23 of the outer cabinet 11. In this embodiment, as shown in FIGS. 3 (a) and 3 (b), the portion functioning as the vibration damping device 15 includes a laminated body 40 in which viscoelastic bodies 31 and 32 and intermediate plates 35 are alternately laminated. It is attached between a pair of plates 33 and 34.

  Hereinafter, a specific configuration of the vibration control unit 30 will be described.

  As shown in FIG. 4, the damping unit 30 includes viscoelastic bodies 31 and 32, a pair of upper and lower fixing plates 33 and 34, an intermediate plate 35, a first mounting plate 36, and a second mounting plate 37. The sliding bearing members 38 and 39 are used.

  The part of the damping unit 30 that functions as the damping device 15 is a laminate 40 in which viscoelastic bodies 31 and 32 and intermediate plates 35 are alternately stacked and attached between a pair of fixing plates 33 and 34. is there. In this embodiment, the part functioning as the vibration damping device 15 includes a laminated body 40 in which the first attachment plate 36, the viscoelastic body 31, the intermediate plate 35, the viscoelastic body 32, and the second attachment plate 37 are laminated and fixed in this order. The fixing plates 33 and 34 are attached to the first attachment plate 36 and the second attachment plate 37 on both sides of the laminate 40 in the lamination direction.

  A portion of the vibration control unit 30 that functions as the sliding support devices 13 and 14 includes the intermediate plate 35 of the laminated body 40, a pair of fixing plates 33 and 34, and sliding support members 38 and 39. The intermediate plate 35 of the laminated body 40 extends to the left and right sides of the viscoelastic bodies 31 and 32, and mounting holes 41 and 42 for attaching the sliding bearing members 38 and 39 are formed in such extended portions. ing. For example, when the laminated body 40 is attached to the pair of fixing plates 33 and 34, the sliding support members 38 and 39 are attached to the attachment holes 41 and 42 of the intermediate plate 35 together with the laminated body 40. It is good to interpose between the fixing plates 33 and 34. When the sliding support members 38 and 39 are attached to the pair of upper and lower fixing plates 33 and 34 together with the laminated body 40, the sliding bearing members 38 and 39 are accommodated between the pair of fixing plates 33 and 34, and between the pair of fixing plates 33 and 34. It has a height that can slide.

  For example, the vibration damping unit 30 is configured such that the laminated body 40 and the sliding bearing members 38 and 39 are fixed to a pair of upper and lower sides in a state where the sliding bearing members 38 and 39 are mounted in the mounting holes 41 and 42 of the intermediate plate 35 of the laminated body 40. The first mounting plate 36 is mounted on one fixing plate 33 and the second mounting plate 37 is mounted on the other of the mounting plates 36 and 37 on both sides of the stack 40 in the stacking direction. It may be attached to the fixing plate 34. The vibration damping unit 30 assembled in this manner is disposed between the inner cabinet 12 and the outer cabinet 11, and one of the upper and lower fixing plates 33, 34 is attached to the inner cabinet 12. The other fixing plate 34 is fixed to the outer cabinet 11.

  The vibration damping unit 30 absorbs vibration energy acting on the inner cabinet 12 from the outer cabinet 11 by the shear deformation of the viscoelastic bodies 31 and 32 in the portion functioning as the vibration damping device 15, and is absorbed by the inner cabinet 12. The generated vibration can be reduced. As shown in FIG. 5, the parts functioning as the sliding bearing devices 13 and 14 are configured such that the inner cabinet 12 and the outer cabinet 11 are separated by the sliding bearing members 38 and 39 that slide between the pair of fixing plates 33 and 34. Are supported, and the pair of fixing plates 33 and 34 are relatively displaced in the horizontal direction while maintaining a parallel state. In this embodiment, when there is no portion that functions as the sliding support devices 13 and 14, when the pair of upper and lower fixing plates 33 and 34 are relatively displaced in the horizontal direction, the displacement increases, as shown in FIG. Thus, it is conceivable that a force acts so that one fixing plate 33 rotates with respect to the other fixing plate 34. According to the vibration control unit 30, the fixing plate 33 is supported by the portion that functions as the sliding support devices 13 and 14, and thus such an event does not occur.

  As shown in FIGS. 3A and 3B, the vibration control unit 30 is attached to the floor material 21 and the ceiling material 23 of the outer cabinet 11, respectively. For example, as shown in FIGS. 3A and 3B, the vibration damping device 15 is attached to the floor material 21 and the ceiling material 23 at positions directly below and above the axial direction of the pillar material 27 of the inner cabinet 12. Good. In the vibration damping unit 30, the portion functioning as the sliding bearing device 13, 14 supports the vertical load, and prevents the compressive load from acting on the viscoelastic bodies 31, 32. Note that the vibration control unit 30 attached to the ceiling material 23 side uses a part that functions as the sliding bearing devices 13 and 14, but the ceiling material 23 is supported by the sliding bearing devices 13 and 14. Since the vertical load is small, the vibration damping unit 30 without the sliding bearing devices 13 and 14 may be used.

  Such a vibration damping cabinet 10 can be schematically represented as shown in FIG. 8, and the viscoelastic bodies 31 and 32 of the vibration damping device 15 are expressed as a combination of the spring element K and the damper element C. The As can be seen from this schematic diagram, the vibration damping device 15 exhibits the vibration damping function with the inner cabinet 12 as one mass body.

  From this, the present inventors give the vibration control cabinet 10 a vibration based on a preset vibration waveform in order to find a condition of the viscoelastic body that can effectively reduce the response acceleration of the inner cabinet 12. The vibration tests A to I which give vibration based on a predetermined vibration waveform simulating actual seismic motion while changing the viscoelastic bodies 31 and 32 were performed.

  In this test, the viscoelastic body shown in FIG. 9 was used. As shown in FIG. 9, among the tests A to J, the F test and the I test were different in composition and changed in shape.

The shapes of the viscoelastic bodies used in the tests A to J are as follows.
A: 35mm x 35mm x 20mm (width, depth, height)
B: 41mm x 41mm x 20mm (width, depth, height)
C: 46mm × 46mm × 20mm (width, depth, height)
D: 49mm × 49mm × 20mm (width, depth, height)
E: 52.5mm × 52.5mm × 20mm (width, depth, height)
Same as F: C
G: 30mm × 30mm × 20mm (width, depth, height)
H: 59mm × 59mm × 20mm (width, depth, height)
Same as I: C
Same as J: C

  In addition, as shown in FIG. 4, the value of the height t of the viscoelastic body used in the tests A to J is the sum of the heights of the viscoelastic bodies 31 and 32 used in the vibration control unit. Used.

  In the F test, a viscoelastic body having a loss coefficient tan δ of 0.5 is used, in the I test, a viscoelastic body having a loss coefficient tan δ of 0.35 is used, and in the other tests, the loss coefficient tan δ is 0.6. A viscoelastic body was used. Further, in this vibration damping device, when vibration is applied, the viscoelastic body absorbs vibration energy by shearing deformation. As described above, in this test, the vibration absorption performance of the viscoelastic body was changed in each of the tests A to I by changing the shape of the viscoelastic body and the loss coefficient tanδ.

Further, the shapes of the viscoelastic bodies used in the tests of A to J are as described above, and the following maximum spring values are obtained at a temperature environment of 20 ° C., shear strain rate γ = 1.0, and f = 2.0 Hz, respectively. (N / mm)
A: 104 (N / mm)
B: 148 (N / mm)
C: 184 (N / mm)
D: 210 (N / mm)
E: 240 (N / mm)
F: 184 (N / mm)
G: 80 (N / mm)
H: 300 (N / mm)
I: 184 (N / mm)
J: 184 (N / mm)

As the vibration waveform, vibration waveforms simulating various earthquakes such as a so-called NTT standard wave, NEBS standard wave, Hyogo Nanbu seismic wave, Niigata Chuetsu earthquake wave and the like were used. The NTT standard wave is one of the vibration waveforms adopted by Nitto Kogyo Co., Ltd. in this test, and has a waveform as shown in FIG. 10 in the horizontal direction. In FIG. 10, the vertical axis indicates the acceleration (m / s ² ) of the vibration in the horizontal direction, and the horizontal axis indicates time (sec). Further, in such a vibration test, it is preferable to install a vibration control cabinet on a vibration table (not shown) and apply vibration with the direction indicated by W in FIG. 2 as the horizontal direction. In this test, a vibration test was performed using a table of 2700 mm × 2700 mm, maximum load mass: 2000 kg, maximum acceleration; horizontal 2 G, vertical 1 G, maximum displacement; horizontal ± 200 mm, vertical ± 100 mm.

In such a vibration test, in the case where the outer cabinet 11 and the inner cabinet 12 are directly screwed and attached without using the vibration damping device 15, the vibration based on these vibration waveforms is applied, and as a result, the observation is performed in the inner cabinet 12. The maximum response acceleration performed was 53.9 mm / s ² .

On the other hand, the following maximum response accelerations were obtained in the tests A to J with respect to the vibration control cabinet to which the vibration control device was attached.
A: 26.1 (mm / s ² )
B: 21.0 (mm / s ² )
C: 24.7 (mm / s ² )
D: 26.8 (mm / s ² )
E: 28.6 (mm / s ² )
F: 28.7 (mm / s ² )
G: 30.4 (mm / s ² )
H: 32.5 (mm / s ² )
I: 31.2 (mm / s ² )
J: 27.2 (mm / s ² )

As described above, by attaching such a vibration damping device, the maximum response acceleration is reduced, and the vibration damping function of the vibration damping device is exhibited. Among these, it was confirmed that those that can suppress the maximum response acceleration to 30 mm / s ² have little influence on electric and electronic equipment. That is, from the above test, it was found that by adopting the viscoelastic body used in the tests of A to F and J, it is possible to provide a vibration control cabinet that has little influence on electrical and electronic equipment.

  As shown in FIG. 8, when the total mass of the inner cabinet including the mass body loaded on the inner cabinet is 351 (kg) as shown in FIG. When the body is subjected to vibration with a shear strain rate γ = 1.0 and f = 2.0 Hz in a temperature environment of 20 ° C., the body is about 100 (N / mm) or more and about 240 (N / mm) or less. It has been found that a spring having a spring value and a loss coefficient tanδ of 0.4 or more should be adopted. If the loss coefficient tan δ is 0.4 or more, vibration absorption performance higher than that can be exhibited. Therefore, it can be adopted without considering the upper limit, and only the lower limit is considered.

Next, in the above test, the total mass of the inner cabinet was 351 kg, but in the actual vibration control cabinet, the load capacity that guarantees the vibration control performance during an earthquake varies depending on the dimensions and needs of the vibration control cabinet. Therefore, as a viscoelastic body of a damping cabinet capable of exhibiting appropriate damping performance in response to various earthquake motions, it is necessary to change the spring value substantially in proportion to the total mass M of the inner cabinet. It is considered . According to the above test, when the total mass of the inner cabinet is 351 kg , the viscoelastic body has a shear strain rate of γ = 1.0 and f = 2.0 Hz in a temperature environment of 20 ° C. (N / mm) or more and about 240 (N / mm) or less as long as it exhibits a spring value. When converted per unit mass (1 kg) of the inner cabinet, about 100/351 = about 0.28. Any material can be used as long as it exhibits a spring value of (N / mm) or more and about 240/351 = about 0.68 (N / mm) or less. For this reason, when the total mass of the inner cabinet 12 including the mass body loaded on the inner cabinet 12 is M (kg), the shear strain rate γ = 1.0 and f = 2.0 Hz in a temperature environment of 20 ° C. When vibration is applied, a spring value of 0.28 M (N / mm) or more and 0.70 M (N / mm) or less and a loss coefficient tan δ of 0.4 or more may be used.

  When the spring value is smaller than 0.28 M (N / mm), the inner cabinet 11 moves excessively in the outer cabinet 12. If the outer cabinet 12 is too small with respect to the inner cabinet 11, the inner cabinet 11. And the malfunction which the outer cabinet 12 collides easily arises. Further, if the outer cabinet 12 is too large with respect to the inner cabinet 11, it takes place when installing the vibration control cabinet, which is not desirable. Further, when the spring value is larger than 0.70 M (N / mm), the viscoelastic bodies 31 and 32 are hardly deformed, and the vibration absorbing function by the viscoelastic bodies 31 and 32 is hardly exhibited.

  As described above, the outer cabinet 11, the inner cabinet 12 disposed inside the outer cabinet 11, and the sliding bearing devices 13 and 14 that support the inner cabinet 12 disposed between the inner cabinet 12 and the outer cabinet 11. Alternatively, it includes a rolling support device and a vibration damping device 15 disposed between the inner cabinet 12 and the outer cabinet 11, and the vibration damping device 15 includes viscoelastic bodies 31 and 32 between a pair of plates 33 and 34. A vibration-damping cabinet that is attached and has one plate 33 fixed to the inner cabinet 12 and the other plate 34 fixed to the floor material 21 or the ceiling material 23 of the outer cabinet 11. 10, the total mass of the inner cabinet 12 including the mass bodies loaded on the inner cabinet 12 on the viscoelastic bodies 31 and 32 is M (kg). When the vibration of shear strain rate γ = 1.0 and f = 2.0 Hz is applied in a temperature environment of 20 ° C., 0.28 M (N / mm) or more and 0.70 M (N / mm) A material that exhibits the following spring value and has a loss coefficient tanδ of 0.4 or more may be used. Thereby, according to the total mass M of the inner cabinet 12, the viscoelastic body which can exhibit suitable damping performance corresponding to various seismic motion can be employ | adopted.

  As mentioned above, although the damping cabinet which concerns on one Embodiment of this invention was demonstrated, the damping cabinet which concerns on this invention is not limited to the said embodiment.

  For example, the vibration control cabinet is not limited to the above-described embodiment, and can be broadly applied to a form that can be conceptually applied to a model illustrated in FIG.

  Various changes can be made to the composition and shape of the viscoelastic body. For example, 100 to 150 parts by mass of silica is added to 100 parts by mass of a base rubber having a C—C bond in the main chain, and a high damping rubber in which 10 to 30% by mass of a silane compound is blended with respect to the silica is used. Thus, the strain dependency, frequency dependency, and temperature dependency described above can be satisfied.

〔式中、Ｒ¹ 、Ｒ² 、Ｒ³ およびＲ⁴ のうちの少なくとも１つはアルコキシ基、またはハロゲン原子を示し、他は同一または異なって水素原子、アルキル基またはアリール基を示す。〕で表されるシラン化合物とを含有するゴム組成物の加硫成形により形成される。また、基材ゴムとしては、主鎖にＣ−Ｃ結合を有する種々のゴムがいずれも使用可能である。具体的には天然ゴム（ＮＲ）の他、イソプレンゴム（ＩＲ）、ブタジエンゴム（ＢＲ）、スチレン−ブタジエン共重合ゴム（ＳＢＲ）、エチレン−プロピレン共重合ゴム（ＥＰＭ）、アクリロニトリル−ブタジエン共重合ゴム（ＮＢＲ）、ブチルゴム（ＩＩＲ）などがあげられる。これらはそれぞれ単独で使用される他、２種以上を併用することもできる。 The silane compound is represented by the following general formula:

[Wherein, at least one of R ¹ , R ² , R ³ and R ⁴ represents an alkoxy group or a halogen atom, and the other represents the same or different and represents a hydrogen atom, an alkyl group or an aryl group. It is formed by vulcanization molding of a rubber composition containing a silane compound represented by the formula: Further, as the base rubber, any of various rubbers having a C—C bond in the main chain can be used. Specifically, in addition to natural rubber (NR), isoprene rubber (IR), butadiene rubber (BR), styrene-butadiene copolymer rubber (SBR), ethylene-propylene copolymer rubber (EPM), acrylonitrile-butadiene copolymer rubber. (NBR), butyl rubber (IIR) and the like. These may be used alone or in combination of two or more.

In the silane compound represented by the general formula (1), examples of the alkoxy group corresponding to R ^{1 to} R ⁴ include those having various carbon numbers represented by C _n H _{2n + 1} O. Preferable examples include methoxy and ethoxy having 1 to 2 carbon atoms. Examples of the halogen atom include fluorine, chlorine, bromine and the like.

Examples of the alkyl group include those having various carbon numbers represented by C _n H _{2n + 1} , and the carbon number is particularly preferably about 1 to 20. Examples of such alkyl groups include methyl, ethyl, n-propyl, isopropyl, n-butyl, isobutyl, secondary butyl, tertiary butyl, pentyl, hexyl, heptyl, octyl, nonyl, decyl, undecyl, dodecyl and the like. can give.

  Examples of the aryl group include phenyl, tolyl, xylyl, biphenylyl, o-terphenyl, naphthyl, anthryl, phenanthryl and the like. Specific examples of such silane compounds include, but are not limited to, n-hexyltrimethoxysilane, triethoxyphenylsilane, diethoxydimethylsilane, dimethyldichlorosilane, methyldichlorosilane, and the like.

  In addition to the above, the rubber composition includes, for example, a vulcanizing agent, a vulcanization accelerator, a vulcanization acceleration aid, a vulcanization retarder, a reinforcing agent other than silica, a filler, a softening agent, a plasticizer, and a tackifier. In addition, various additives may be added. Among the above, examples of the vulcanizing agent include sulfur, organic sulfur-containing compounds, and organic peroxides. Among these, examples of the organic sulfur-containing compounds include N, N'-dithiobismorpholine and the like. Examples of the peroxide include benzoyl peroxide and dicumyl peroxide.

  Examples of the vulcanization accelerator include thiuram vulcanization accelerators such as tetramethylthiuram disulfide and tetramethylthiuram monosulfide; zinc dibutyldithiocarbamate, zinc diethyldithiocarbamate, sodium dimethyldithiocarbamate, diethyl Dithiocarbamates such as tellurium dithiocarbamate; thiazoles such as 2-mercaptobenzothiazole and N-cyclohexyl-2-benzothiazolesulfenamide; organics such as thioureas such as trimethylthiourea and N, N′-diethylthiourea Examples of the promoter include inorganic promoters such as slaked lime, magnesium oxide, titanium oxide, and risurge (PbO).

  Examples of the vulcanization acceleration aid include fatty acids such as stearic acid, oleic acid and cottonseed fatty acid, and metal oxides such as zinc white. Examples of the vulcanization retarder include aromatic organic acids such as salicylic acid, phthalic anhydride, and benzoic acid; N-nitrosodiphenylamine, N-nitroso-2,2,4-trimethyl-1,2-dihydroquinone, N-nitroso And nitroso compounds such as phenyl-β-naphthylamine.

  The total amount of the vulcanizing agent, vulcanization accelerator, vulcanization acceleration aid, and vulcanization retarder is preferably about 4 to 15 parts by mass with respect to 100 parts by mass of the base rubber. . Examples of the antioxidant include imidazoles such as 2-mercaptobenzimidazole; phenyl-α-naphthylamine, N, N′-di-β-naphthyl-p-phenylenediamine, N-phenyl-N′-isopropyl-p- Examples include amines such as phenylenediamine; phenols such as di-t-butyl-p-cresol and styrenated phenol.

  The blending amount of the antioxidant is preferably about 1.5 to 5 parts by mass with respect to 100 parts by mass of the base rubber. Carbon black is mainly used as a reinforcing agent other than silica, inorganic reinforcing agents such as silicate-based white carbon, zinc white, surface-treated precipitated calcium carbonate, magnesium carbonate, talc, clay, or coumarone. -Organic reinforcing agents such as indene resin, phenol resin, and high styrene resin (styrene-butadiene copolymer having a high styrene content) can also be used.

  Examples of the filler include calcium carbonate, clay, barium sulfate, and diatomaceous earth. The blending amount of the reinforcing agent and / or filler other than the silica is preferably about 5 to 50 parts by mass with respect to 100 parts by mass of the base rubber. Examples of the softener include vegetable oil-based, mineral oil-based, and synthetic softeners such as fatty acids (stearic acid, lauric acid, etc.), cottonseed oil, tall oil, asphalt substances, and paraffin wax.

  The blending amount of the softening agent is preferably about 10 to 100 parts by mass with respect to 100 parts by mass of the base rubber. Examples of the plasticizer include various plasticizers such as dibutyl phthalate, dioctyl phthalate, and tricresyl phosphate. As for the compounding quantity of a plasticizer, about 5-20 mass parts is preferable with respect to 100 mass parts of base rubber.

  Further, examples of the tackifier include coumarone / indene resin, aromatic resin, aromatic / aliphatic mixed resin, rosin resin, and cyclopentadiene resin. The compounding amount of the tackifier is preferably about 5 to 50 parts by mass with respect to 100 parts by mass of the base rubber.

  In addition to the above, for example, a dispersant, a solvent and the like may be appropriately blended in the rubber composition. The rubber composition is produced by kneading the above components using, for example, a closed kneader. The viscoelastic body is formed, for example, by molding the rubber composition into a sheet using a roller head extruder, punching out the sheet so as to have a predetermined shape, and then cutting the punched sheet into a predetermined thickness. In a state where a plurality of sheets are laminated so as to have, they are manufactured by heating in a predetermined mold and performing vulcanization molding.

  Moreover, in the vibration suppression cabinet mentioned above, a vibration suppression apparatus is not limited to said form, It is good to change suitably the shape of each member.

  For example, in the above-described embodiment, as shown in FIGS. 3 (a) and 3 (b), the vibration damping unit 30 has the sliding support members 38 and 39 disposed on both sides of the intermediate plate 35, and the viscoelastic bodies 31 and 32. The structure which comprised integrally the site | part which functions as the damping device 15 provided with and the sliding bearing devices 36 and 37 was illustrated. The vibration control cabinet according to the present invention is not limited to this embodiment. For example, the part functioning as the vibration damping device 15 is an example in which one intermediate plate 35 and two viscoelastic bodies 31 and 32 are stacked. However, the number of stacked viscoelastic bodies 31 and 32 and the intermediate plates 35 is as follows. It is not limited to this. The number of layers may be three or five or more. Moreover, although the attachment plates 36 and 37 are fixed to both sides in the stacking direction of the laminate 40 and are attached to the fixing plates 33 and 34 with the attachment plates interposed, as shown in FIG. The bodies 31 and 32 may be directly fixed to the fixing plates 33 and 34.

In addition, as shown in FIG. 12, instead of the sliding bearing devices 36 and 37, rolling bearing devices 46 and 47 may be used. In the reference example shown in FIG. 13, a damping device 53 constructed in the viscoelastic body 51 and the plate 52 constitute a sliding bearing device 54 separately. In the reference example shown in FIG. 13, a sliding support device 54 that supports the inner cabinet 12 is provided and a vibration damping device 53 is provided in the vicinity thereof. However, as shown in FIG. Alternatively, the rolling bearing device 55 may be used.

The perspective view which shows the cabinet which accommodates an electronic device etc. FIG. The front view of the vibration suppression cabinet which concerns on one Embodiment of this invention. (A) is the figure which expanded A in FIG. 2, (b) is the figure which expanded B in FIG. The figure which shows the damping device of the damping cabinet which concerns on one Embodiment of this invention. The top view which shows the state which the vibration acted on the damping device of the damping cabinet which concerns on one Embodiment of this invention. The top view which shows the state which the vibration acted about the damping device of the damping cabinet which concerns on one Embodiment of this invention, when there is no sliding support apparatus. The figure explaining the shear strain rate (gamma). The conceptual diagram of the vibration suppression cabinet which concerns on one Embodiment of this invention. The figure which shows the compounding example of the viscoelastic body used for the vibration suppression cabinet which concerns on one Embodiment of this invention. The figure which shows an example of the vibration waveform used for the vibration test of the damping cabinet. The figure which shows the sliding support apparatus and damping device of the damping cabinet which concern on other embodiment of this invention. The figure which shows the rolling support apparatus and damping device of the damping cabinet which concern on other embodiment of this invention. The figure which shows the sliding support device and damping device of the damping cabinet which concern on a reference example . The figure which shows the rolling support apparatus and damping device of the damping cabinet which concerns on another reference example .

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Damping cabinet 11 Outer cabinet 12 Inner cabinet 13, 14 Sliding support device 15 Damping device 21 Floor material 22 Column material 23 Ceiling material 24, 25 Side surface 26 Lower plate material 27 Column material 28 Upper plate material 30 Damping unit 31, 32 Elastic body 33, 34 Fixing plate 35 Intermediate plate 36 First mounting plate 37 Second mounting plate 38, 39 Sliding bearing member 40 Laminated body 41, 42 Mounting hole 51 Viscoelastic body 52 Plate 53 Damping device 54 Sliding bearing device 55 Rolling bearing device

Claims (2)

Comprising an outer cabinet, an inner cabinet disposed in the inside of the outer cabinet, and a damping unit disposed between the inner cabinet and the outer cabinet,
The vibration control unit is composed of a vibration control device and a sliding support device or a rolling support device,
The vibration damping device, a laminate obtained by laminating a viscoelastic member and the intermediate plate are alternately mounted between a pair of plates, one of said pair of plates, the one plate is fixed to the cabinet, the other plate be those fixed to the flooring or ceiling material of the outer cabinet,
The sliding bearing device or the rolling bearing device is mounted on each of the extended portions of the intermediate plate extending from the viscoelastic body, supports the inner cabinet, and slides or rolls with respect to the pair of plates. It is equipped with movable sliding bearing material or rolling bearing material,
The viscoelastic body of the vibration damping device, when the total weight of the cabinet, including a mass which is loaded into said cabinet was M (kg), at 20 ° C. of the temperature environment, the shear strain rate gamma = 1. When a vibration of 0, f = 2.0 Hz is applied, a spring value of 0.28 M (N / mm) or more and 0.70 M (N / mm) or less is exhibited, and the loss coefficient tan δ is 0.4. A vibration control cabinet characterized by the above. A damping unit disposed between an outer cabinet of the cabinet and an inner cabinet disposed inside the outer cabinet,
Consists of vibration control device and sliding support device or rolling support device,
The vibration damping device is a laminate in which a viscoelastic body and an intermediate plate are alternately laminated, and is attached between a pair of plates.
The sliding bearing device or the rolling bearing device is mounted on each of the extended portions of the intermediate plate extending from the viscoelastic body, supports the inner cabinet, and slides or rolls with respect to the pair of plates. It is equipped with movable sliding bearing material or rolling bearing material,
When the total mass of the inner cabinet including the mass body loaded on the inner cabinet is M (kg), the shear strain rate γ = 1. When a vibration of 0, f = 2.0 Hz is applied, a spring value of 0.28 M (N / mm) or more and 0.70 M (N / mm) or less is exhibited, and the loss coefficient tan δ is 0.4. A vibration control unit characterized by the above.

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