TW466812B - Synchronous vibration control apparatus - Google Patents
Synchronous vibration control apparatus Download PDFInfo
- Publication number
- TW466812B TW466812B TW89106481A TW89106481A TW466812B TW 466812 B TW466812 B TW 466812B TW 89106481 A TW89106481 A TW 89106481A TW 89106481 A TW89106481 A TW 89106481A TW 466812 B TW466812 B TW 466812B
- Authority
- TW
- Taiwan
- Prior art keywords
- vibration
- vibration damping
- damping
- mass
- damping device
- Prior art date
Links
Landscapes
- Vibration Prevention Devices (AREA)
Abstract
Description
466812 五、發明說明（1) [發明之技術領域] :發明係關：：種用來抑制構造物 所產生雜音之同步型制振裝置。 切A由構造物 [習知技術] 振動在ΐ::振：之兩倍頻率產生 之噪音。例如，電源頻率：60ΗΖ:Κ:而產生所謂雜音 運轉除了會產生120ΗΖ的雜音，還會#產&生%其=於比變壓器的 240Hz、3 6 0Hz等之雜音。 曰 〃、问-人豳波之 一妒變Ϊ器等構造物的振動以及因此所產生的雜音很難以 之*振裝置有效地抑制，需合併使用除振裝置以及栘 «m^MDCTuned Mass Damper) . ^ ^ ^ 物的振nr量體的振動頻率調整至與產生雜音之構造 使與其逆相位共振之質量體ΐ 生之雜音。振動因此，可減低構造物之振動以及所產 用ΤΜΠ習/使用f量平衡型（MaSS BalanCe TyPe)作為使 /振裝置。質量平衡型之制振裝置在水平支摔軸 :端插入兩個相同之質量體’藉由調整兩個 位置來調節其振動頻率。 Λ里體之 [發明欲解決之問題] 度方ϋ整量平衡型之制振裝置中’必須以極高精 此種調整方制振質量體距離支樓軸中心之位置。 a非常難以手動方式進行高精度調整，且相當466812 V. Description of the invention (1) [Technical field of invention]: The invention relates to: a synchronous vibration damping device for suppressing noise generated by structures. Cut A is a structure [known technique] The noise generated by vibration at twice the frequency of ΐ :: 振:. For example, the power frequency: 60ΗZ: K: In addition to generating so-called noise, operation will produce 120ΗZ murmur, and will produce noise of 240Hz, 360Hz, etc. than the transformer. The vibrations of structures such as 〃, Q-human 豳, 妒, 妒, Ϊ, and other noises and the noise generated by them are difficult to suppress effectively. It is necessary to use a vibration-reduction device and 栘 «MCTuned Mass Damper) ^ ^ ^ The vibration frequency of the object is adjusted to the noise of the structure that produces noise, which causes the noise of the mass body that resonates with its inverse phase. Vibration Therefore, it is possible to reduce the vibration of the structure and the produced TMII / F-balanced type (MaSS BalanCe TyPe) as the vibration / vibration device. The mass balance type vibration damping device inserts two identical mass bodies at the end of the horizontal support shaft and adjusts its vibration frequency by adjusting two positions. [Problem to be Solved by the Invention] In the λ-dimension integer-balanced vibration damping device, it is necessary to adjust the position of the square damping mass body from the center of the support shaft with extremely high precision. a Very difficult to make high-precision adjustments manually, and quite
00P0080.ptd 第4頁 46681200P0080.ptd Page 4 466812
五、發明說明（2) 耗時。 動頻提供可簡單調整制振質量體之振 [解決問題之手段] 體；i二彈性：件的俜：C裝置包含：制振質量 動’並具有非線性特質量體朝-方向振 ☆較前述第一彈性構件+，：朝著丄其彈性係數實質 二方向彈性變形方式配：第1第-彈性構件 當前述制振質量體朝一方向振動以：：性J件同時支 量:彈性構件於前述制振質量體之振“向又之;Πί述 於可同之由方於第二彈性構輪^ 整手段使第二彈性構件產生長度改：產生，性變形：以調 件之長度。因&，藉由變而凋整第-彈性構 係數，㈣制振質量以：；第二性2 性構件之長度改變來徐緩改體二彈 化率。亦π，可利用實 量體之振動頻率的變 度來微調制振質量體之振動頻長度改變幅 整制振質量體之振動頻率。 而在短時間内精確地調V. Description of the invention (2) Time-consuming. The dynamic frequency provides a vibration that can easily adjust the mass of the damping body [means to solve the problem] body; i two elasticity: the 俜 of the piece: the C device contains: the damping mass movement 'and has a non-linear special mass body vibrating in the-direction ☆ The aforementioned first elastic member +, is elastically deformed in two directions: its elastic coefficient is substantially two. The first and first elastic members are vibrated in one direction when the aforementioned damping mass body is: The vibration of the aforementioned damping mass body is "reversible"; Πί is described in the same way by the second elastic construction wheel ^ The adjustment method causes the length of the second elastic member to be changed: generated, sexually deformed: the length of the adjustment. Because & By modifying the first-constitutive coefficient of elasticity, the damping mass is controlled to: slowly change the second elasticity of the body by changing the length of the second and second members. Also, π, the vibration of the real body can be used The degree of frequency variation is used to fine-tune the length of the vibration frequency of the vibration mass body to change the vibration frequency of the amplitude control vibration mass body.
00P0080.ptd 第5頁 46 6 8 1 2 五、發明說明（3) 尚且，在此所謂之「實質上小於」是指 構件具有非線性特性，第二彈性構件之彈性奴一彈性 彈性構件在實用之改變範圍内之彈性係數值’。、丨、於第一 彈性構件可具有線性特性，亦可具有非線性特性且，第二 申請專利範圍第2項之制振裝置還包含相 °_、 振質量體並與前述第一彈性構件並列連接，以用；則述制 述制振質量體之振動的衰減手段。 用來农減前 根據申晴專利範圍第2項，由於包含相 a :i f與前述第-彈性構件並列連接，以用來振、 且传x用=體之振動的衰減手段，故可獲得作為最‘同=述 置。用於制振對象處於共振狀態時之適宜同步型制振^型 整手第3項之制振裝置還具價可驅動前述調 段之專項二具：可驅動前述調整手 的場合，，亦j::在制振對象的振動頻率會產生變： 亦可自動地減低其振動。 无化 申請專利範圍第4及5項之制 互相f立並以可振動方式複數制振質-體係 立並31:及5項’因制振質量體係互相獨 T率分別同步於；振對：之置的同* 小設置面積下τ1^侬動的基頻與间相波，而在較 互可減低制振對象之基頻，亦可減低高諧 00P0080.ptd 第6頁 46681200P0080.ptd Page 5 46 6 8 1 2 V. Description of the invention (3) Moreover, the so-called "substantially smaller" means that the member has non-linear characteristics, and the elastic slave of the second elastic member is an elastic elastic member. The value of the coefficient of elasticity within the range of change '. The first elastic member may have linear characteristics or non-linear characteristics. Moreover, the vibration damping device in the second patent application scope item 2 further includes a phase mass, a vibration mass body, and is juxtaposed with the first elastic member. Connected for use; then the vibration damping means of the damping mass is described. Before being used for agricultural subtraction, according to item 2 of Shenqing's patent scope, since the phase a: if is connected in parallel with the aforementioned -elastic member to be used as a damping means for vibrating and transmitting x = body vibration, it can be obtained as Most 'same as described. A suitable synchronous vibration damping device for the vibration damping object in the resonance state. The vibration damping device of the third item is also a special two item that can drive the aforementioned adjusting section: in the case where the aforementioned adjusting hand can be driven, also j :: The vibration frequency of the object to be damped will change: It can also reduce its vibration automatically. The systems of items 4 and 5 in the scope of Wuhua's application for patents are mutually independent and multiple vibration masses are controlled in a vibratory manner-the system is integrated and 31: and the 5 items due to the vibration damping quality system are synchronized with each other separately; In the same setting *, the fundamental frequency and interphase wave of τ1 ^ non-moving under a small setting area, and the fundamental frequency of the damping object can be reduced at a relatively high level, and the high harmonic 00P0080.ptd page 6 466812
波。 [實施例] 參f圖式說明本發明較佳實施例如下。 面圖圖：為本發明同步型制振裝置之第-實施Μ的概略平 Κ施：：為沿著圖一之Π'Π線之斷面圖。峨示， f詈^同步型制振裝置10具有略環型（donut)之制振 刀別嵌裝於制振質量體1 2之凹部，且一端連接 於制振質量體12之四組碟形彈簧14a〜14d。碟形彈簧 14a 14 d為、朝著垂直方向、即圖二之上下方向彈性變形之 非線性彈簧。制振質量體12之内側下端部12a朝内側突 出=該内側下端部1 2 a支撐具有線形特性之線圈彈簧2 8 的一端。且在圖一中，制振質量體12存在於虛線u與。所 界定之區域。 碟形彈簧14a~14d之另一端支撐於在相對於碟形彈簧 14a〜14d之處分別具有開口部之圓盤狀基盤16。基盤16的 中央垂直設置了形成雄螺釘之支柱丨8。支柱丨8從下方分別 螺合彈簧推壓構件2 0與螺母22。彈簧推壓構件2〇在其外側 緣部之數個處所利用螺釘27與蓋部24及上板26螺合連接。 ^部24與制振質量體12的表面間隔預定距離，形成具有沿 著上面與側面覆蓋之形狀。 彈簧推壓構件20與制振質量體12的内側下端部i2a之 間存在著插入於支柱1 8且朝垂直方向彈性變形之線圈彈菁 28 ’該線圈彈簧28朝上方作用彈簧推壓構件2〇。因此，利 用轉動螺母22可上下移動彈簀推壓構件2〇，藉此，不但可wave. [Embodiment] A preferred embodiment of the present invention will be described with reference to the drawings. Plan view: This is a schematic plan view of the first-implementation M of the synchronous vibration damping device of the present invention. K: is a cross-sectional view taken along line II′Π of FIG.埃 示, f 詈 ^ synchronous vibration damping device 10 has a donut-shaped vibration damping blade which is embedded in the concave portion of the damping mass 12 and has one end connected to the four sets of dish-shaped masses 12 Springs 14a to 14d. The disc springs 14a to 14d are non-linear springs that elastically deform in the vertical direction, that is, in the upper and lower directions in FIG. The inner lower end portion 12a of the damping mass body 12 protrudes toward the inner side = the inner lower end portion 1 2 a supports one end of the coil spring 2 8 having a linear characteristic. And in FIG. 1, the damping mass body 12 exists on the dotted lines u and. The defined area. The other ends of the disc springs 14a to 14d are supported by disc-shaped base plates 16 each having an opening portion with respect to the disc springs 14a to 14d. The center of the base plate 16 is provided with a pillar 8 forming a male screw vertically. The pillars 丨 8 are screwed from the bottom to press the member 20 and the nut 22 from below. The spring pressing member 20 is screw-connected to the cover portion 24 and the upper plate 26 at a plurality of places on the outer edge portion thereof with screws 27. The portion 24 is spaced a predetermined distance from the surface of the damping mass body 12 to have a shape covering the upper surface and the side surface. Between the spring pressing member 20 and the inner lower end portion i2a of the damping mass body 12, there is a coil spring 28 inserted into the pillar 18 and elastically deformed in the vertical direction. The coil spring 28 acts as the spring pressing member 2 upward. . Therefore, by using the rotating nut 22, the elastic pushing member 20 can be moved up and down.
00P0Q80.ptd 第7頁 4 6 6 8 12 五 '發明說明（5) 控制線圈彈簧2 8的長度或改變量（從自然長度的改變長 度）’且可控制經由線圈彈簧28及制振質量體12，從彈簧 推壓構件20的力量作用之碟形彈簧丨4a〜i4d的長度或改變 量〇: 藉此’制振質量體1 2在挾持於四組碟形彈簣1 4 a〜1 4 d 與線圈彈簧28的狀態下’可朝著垂直方向（即圖二之上下 方向）振動。因此，其振動頻率係由碟形彈簧14a~14d的改 變量決定。亦即，改變非線性之碟形彈簧丨4a〜丨4d的改變 量，可改變其彈性係數。 圖三為碟形彈簧14a〜14d(將四組彈簧合成 … ，，一叫六 w叫 組〈場 合）以及線圈彈簧28之改變量與彈性力之關係的曲線圖。 圖三中，曲線A表示碟形彈簧14a〜14d的彈性特性，而 B表示線圈彈簧2 8的彈性特性。相對於改變量變化之沾· 力變化比例（曲線斜率）的彈性係數雖然在曲線人增加 量時搜慢變小，但在圖示之範圍内仍然比曲線β變 變 亦即’在圖示之範圍内，曲線Α之斜率較曲線8之大。 (，圈彈*28的彈性係數比碟料簧14卜14(1的彈^二 本貝施例中，因為線圈彈簧28的彈性係數比埋 14a〜14d的彈性係數小，即使大角度 螺母碟形彈簧 簧28大幅改變長度，碟形彈、 使線圈彈 因此，因為螺母2_動角 緩，亦於將制振質量體12之振動頻率碉整至預=影響徐 可於短時間内進行高精度 \ 疋的頻率， 门整。因此，根據本實施例之制00P0Q80.ptd Page 7 4 6 6 8 12 Five 'Explanation of the invention (5) Control the length or amount of change of coil spring 2 8 (change length from natural length)' and can control via coil spring 28 and damping mass 12 The length or change of the disk spring 丨 4a ~ i4d acting from the force of the spring pressing member 20: This is used to hold the vibration mass 1 2 in four groups of disk springs 1 4 a ~ 1 4 d In the state of the coil spring 28, it can vibrate in a vertical direction (that is, the up-down direction in FIG. 2). Therefore, its vibration frequency is determined by the variables of the disc springs 14a to 14d. That is, changing the amount of change of the non-linear disc springs 4a to 4d can change its elastic coefficient. Fig. 3 is a graph showing the relationship between the springs 14a to 14d (combining four sets of springs, one called six w called the set <field) and the change amount of the coil spring 28 and the elastic force. In FIG. 3, curve A indicates the elastic characteristics of the disc springs 14a to 14d, and B indicates the elastic characteristics of the coil spring 28. Relative to the change in the amount of change, the change in the coefficient of force (the slope of the curve) of the coefficient of elasticity is slower and smaller when the curve person increases the amount, but in the range shown in the figure is still changed than the curve β, that is, 'in the figure Within the range, the slope of curve A is greater than that of curve 8. (The elastic coefficient of the ring spring * 28 is higher than the spring of the disc spring 14 and 14 (1) In the example of this embodiment, because the elastic coefficient of the coil spring 28 is smaller than the elastic coefficient of the buried spring 14a ~ 14d, The shape spring spring 28 greatly changes the length, the disk springs, and the coil springs. Therefore, because the nut 2_ has a slow moving angle, it also adjusts the vibration frequency of the damping mass body 12 to a predetermined value, which can affect Xu in a short time. Accuracy \ 疋 frequency, the whole gate. Therefore, according to the system of this embodiment
4 6 6 8 1 五、發明說明（6) 振裝置1 0可更確實 ' 音。 降低構造物之振動以及由+ π由此5丨起的雜 (加速而度 1的以\量體12之振動中，在固定之制㈣ 古士 e 4 件下，制振質量體1 2之妲制振力 ，若制振質量體2 2之菥叙4S :田與振動頻率之平 2之振幅即會變小、;率變* ’制振質量體 質=合使用於高振U = 中，制 有非線性彈性特性亦可有線性彈性特性，但具 2 f率係由線圈彈簧28的彈性“：雄制振質量體1 2之振 彈性係數雙方同時控制。係數與碟形彈簧1 4a〜Ud的 線性件雖: = 作為具有非 之其他非線性特 f錐形螺旋板彈簧等 構件。 黃或具有非線性特性之公知彈性 /、久’說明本發明之笫二本加 同步型制振裝置的斷面圖。二:匕圖四為本實施例之 ;置於蓋部體 構件本石夕膠42不僅作為具有非線性特性之彈性 此，制Π 衰減制振質量體12之振動的衰減手段。因 、裝置40形成不但具有衰減且為降低振動之最佳同 _080.ptd4 6 6 8 1 V. Description of the invention (6) The vibration device 10 can be more accurate. Reduce the vibration of the structure and the impurities starting from + π from 5 (according to the acceleration of 1 and the vibration of the volume of 12), under the fixed system ㈣ 士 e 4 pieces, the vibration mass 1 2 If the damping force is 2 and 4S in the damping mass body 2: the amplitude of the flat 2 of the field and the vibration frequency will become smaller, and the rate will change * 'The damping mass and body quality = used in high vibration U = medium, Non-linear elastic characteristics and linear elastic characteristics can also be produced, but the 2 f ratio is determined by the elasticity of the coil spring 28 ": The vibration elasticity coefficient of the male vibration mass body 12 is controlled simultaneously. The coefficient is the same as that of the disc spring 1 4a ~ Although Ud's linear parts: = as other non-linear special f-shaped conical helical leaf springs and other components. Yellow or well-known elasticity / non-linear characteristics with non-linear characteristics illustrate the invention's second plus synchronous vibration damping device The second section: the dagger view is the fourth embodiment of the present embodiment; the slab rubber 42 placed on the cover body member not only serves as an elasticity with non-linear characteristics, but also a damping means for damping the vibration of the damping mass body 12. .Because, the device 40 is not only attenuated, but also the best to reduce vibration.
第9頁 486812Page 9 486812
發明說明（7) 步型’最適合使用於與制 ~ 實施例之制振裂置1〇實、盔象，、振之狀態。並且，第一 型。 “上為不具有衰減手段之反共振 的機構作為：；：以二:42 J制振質量體12之推麼力 控制具有之彈性係數與衰減〜藉此方式，矽膠42可同時 量體12之振動的彈性係^'°例如，實現關於制振質 合時，首先控制石夕膠42的(推"壓振力動來^i =及衰減定數的場 定石夕膠42部份的彈性係 =1來决疋农減定數’同時決 114a~ 1 4d ^ ^ ^ ^ 2 ^ ^ ^ ^ 來決定碟形彈簧14a〜14d的彈=的：式，轉動螺母22 預定之振動頻率振動。弹Η糸數’使制振質量體12以 本實施例中雖使用具有 42，亦可使用完全叙 =^件或哀減手段之石夕膝 減手段之♦ :，，、作為彈性構件之性質僅實質上作為衰 其次f：^Sl士llCQn 0⑴等較小彈性之材料。 同步型制振裳置的^明之第三實施例。圖五為本實施例之 重2斷面圖。圖五所示之制振裝置12係上下 置1 〇a、1 Ob。® μ圖一所说明之第一實施例相同的制振裝 51互相連接。g 兩組制振裝置1〇3、1(^藉由連接構件 l〇b之支柱18 P，連接構件51之中央凹部螺合於制振裝置 而連接於制振裝置105，且設置於凹部外‘#丨 之突出部與制振襄置10a之基盤16連接。 π外側 根據此構成，兩組制振裝置1 〇a、1 〇b之制振質量體i 2 可互相獨立振動。，因為經由下側制振裝置m之基體^Description of the Invention (7) The step type is most suitable for use in a state where the vibrations of the system and the embodiment are set to 10, the helmet, and the vibration. And, the first type. "The above is the anti-resonance mechanism without the attenuation means as :; The control of the elastic coefficient and attenuation with the thrust force of 2:42 J damping mass 12 is controlled by this way. In this way, the silicone rubber 42 can measure the body 12 at the same time. The elastic system of vibration ^ '° For example, when realizing the damping and mass coupling, first control the elastic system of Shi Xijiao 42 (push " compressive vibration force to move ^ i = and attenuate a fixed number of Shi Xijiao 42) = 1 to determine the farmer minus the fixed number 'simultaneously 114a ~ 1 4d ^ ^ ^ ^ 2 2 ^ ^ ^ ^ to determine the spring of the disc spring 14a ~ 14d =: type, rotate the nut 22 to a predetermined frequency of vibration. The number "makes the damping mass body 12 in this embodiment, although it has 42, it is also possible to use a complete set of ^ pieces or reduction methods of the stone Xi knee reduction means: ，,, the properties of the elastic member only In essence, it is a material with less elasticity such as f: ^ Sl, llCQn, 0⑴, and the like. The third embodiment of the synchronous vibration system is shown in Fig. 5. Fig. 5 is a cross-sectional view of Fig. 5. The vibration damping device 12 is arranged above and below 10a and 1 Ob. ® μ The same vibration damping device 51 of the first embodiment illustrated in FIG. 1 is connected to each other g Two sets of vibration damping devices 103 and 1 (^ are connected to the vibration damping device 105 by screwing the central recess of the connecting member 51 to the vibration damping device 105 through the pillar 18 P of the connecting member 10b, and are provided outside the recess The protruding portion of '# 丨 is connected to the base plate 16 of the vibration damping device 10a. Based on this structure, the vibration damping mass bodies i 2 of the two sets of vibration damping devices 10a and 10b can vibrate independently of each other. Base of the lower vibration damping device m ^
00P0080.ptd 第10頁 五 發明說明（8) 16、支柱18以及連接構件51將外部制振 上側制振裝置l〇a，不但下側制振裝置⑽：二振動傳達至 可配合外部制振對象之振動頻率而產生振制振質量體12 =之制振質量體12亦可配合外部制振對象，上側制振裝 而產生振動。 之振動頻率 因此，先分別調整制振裝置10b之同步 象之振動基頻（或二次諧波頻率），以及 '至制振對 之同步頻率至制振對象之振動二次譜波 制振裝置1〇a 用單一之制振裝置Ua、1()b的設置面積不但可或基頻），利 象之基頻，亦可減低其高次諧波頻率。 /低制振對 _所引起的雜音，可以配置一個 率：了 :制因 制振裝置，以及-個振動頻率為_2之制振^為之 疊三組以上之制振裝置，並分別同步調整至二、 二人3自波。而且，作為最適當之同步型場合時，與2 = 例相同，在各制振裝置1〇3、1〇b之蓋部24與制振 之間亦可配置矽膠42等衰減手段。 負ΐ體1 2 其次，說明本發明之第四實施例。圖六為本實施例包 含同步型制振裝置之制振系統的概略模式圖。圖六所示之 制振裝置50，除了具備第一實施例之制振裝置丨〇，還具備 致動機構（actuator)52。雖省略致動機構52之詳細說明， 但其女裝於制振裝置1〇之螺母22，並可轉動該螺母22。‘ 致動機構52連接於控制裝置54，且該控制裝置54連接 於振動感測器5 6、5 7。振動感測器5 6可檢知圖未示之制振 對象或配置於其附近制振對象的振動，而振動感測器5 7可00P0080.ptd Page 10 5 Description of the invention (8) 16. The pillar 18 and the connecting member 51 will externally damp the upper vibration damping device 10a, not only the lower vibration damping device ⑽: The two vibrations will be transmitted to the external vibration damping object. The vibration damping mass body 12 is generated by the vibration frequency = The vibration damping mass body 12 can also cooperate with external vibration damping objects to generate vibration on the upper side. Therefore, first adjust the vibration fundamental frequency (or second harmonic frequency) of the synchronous image of the vibration damping device 10b, and the vibration second-spectrum wave vibration damping device from the synchronous frequency of the vibration damping pair to the vibration damping object. 10a Using a single vibration damping device Ua, 1 () b not only can set the area or the fundamental frequency), the fundamental frequency of the image can also reduce its higher harmonic frequency. The noise caused by the low vibration damping pair _ can be configured with a ratio: the vibration damping device and a vibration damping device with a vibration frequency of _2 and three or more vibration damping devices stacked together and synchronized separately. Adjust to two, two and three auto. In addition, in the case of the most suitable synchronous type, as in the case of 2 =, attenuation means such as silicon rubber 42 may be disposed between the cover portion 24 and the vibration damper of each of the vibration damping devices 103 and 10b. Negative Carcass 1 2 Next, a fourth embodiment of the present invention will be described. Fig. 6 is a schematic diagram of a vibration damping system including a synchronous vibration damping device of this embodiment. The vibration damping device 50 shown in Fig. 6 includes an actuator 52 in addition to the vibration damping device of the first embodiment. Although the detailed description of the actuating mechanism 52 is omitted, the woman wears the nut 22 of the vibration damping device 10, and the nut 22 can be rotated. ‘The actuating mechanism 52 is connected to the control device 54, and the control device 54 is connected to the vibration sensors 56, 57. The vibration sensor 5 6 can detect the vibration of a vibration-damping object (not shown) or a vibration-damping object disposed in the vicinity, and the vibration sensor 5 7 can
00P0080.ptd 第11頁 4 6 6 81 2 一1,1 — 五、發明說明（9) 檢知制振質量 振動感測器5 6 振動傳給控制 指令，使制振 關函數為零。 預定位置。 藉此，本 5 6、5 7以及控 構5 2，即使對 追蹤該改變並 頻率。因此， 低其振動。 在本實施 機構5 2。而且 場合亦可適用 制振裝置之螺 [發明效果] 根據以上 整手段大幅改 彈性構件之長 緩改變制振質 長度調整幅度 較短時間内精 合使用於控制00P0080.ptd Page 11 4 6 6 81 2 -1,1 — V. Description of the invention (9) Detecting the quality of vibration damping Vibration sensor 5 6 The vibration is transmitted to the control command to make the vibration damping related function zero. Intended location. With this, the present 56, 5 7 and the control 5 2 can track the change and frequency even for the pair. Therefore, its vibration is low. 2 in this implementing agency. Moreover, the screw of the vibration damping device can also be applied in the occasion. [Inventive effect] According to the above measures, the length of the elastic member is greatly changed. The vibration damping quality is slowly changed. The length adjustment range is used for control in a short time.
體1 2或配置 所檢知的制 裝置54。控 對象以及制 致動機構5 2 實施例之制 制裝置54， 於制振對象 轉動螺母2 2 即使制振對 例中，可使 ，如第三實 本實施例， 母轉動量， 於其附近制振質量體的振動The body 12 or the detection device 54 is provided. The control device 54 of the embodiment of the control object and the actuating mechanism 5 2 can rotate the nut 2 2 to the vibration control object. Even in the vibration control pair, it is possible to make, as in the third embodiment, the amount of female rotation in the vicinity thereof. Vibration of damping mass
振對象以及制挤曰 U 制振質量體12的檢出 '^ 送出驅動致動機構5 2之 t質量，2的檢出振動之互相相 11到該心令後’即轉動螺母2 2至 振裝置50因連接於振動感測器 備可轉動螺母22之致動機 的振動頻率會改變的場合，亦會 务5 f變更制振質量體1 2的振動 象的振動頻率改變，亦可自動減 :fI Ϊ馬達或壓電素子作為致動 歹中上下重疊兩組制振裝置之 此時，控制裝置54分別計算上 並分別予以轉動。 說明’依申請專利範圍第i項，即使利 變第二：性構件之長度’亦僅稍微改變第一 度，對應於第二彈性構件之長度變化量可徐 量體之振動頻率。，亦即，因為可對於實際: 微小地控制制振質量體之振動頻率，故可在 確地調整制振質量體之振動頻率。因此，、商 雜音。 ^The detection of the vibration object and the squeezing mass U of the vibration damping mass 12 '^ sends the t mass of the driving actuating mechanism 5 2, the detected vibrations of 2 are in phase with each other 11 after the heartbeat, that is, turning the nut 2 2 to the vibration Where the vibration frequency of the device 50 caused by the device 50 connected to the vibration sensor and the rotatable nut 22 is changed, the device 50 will also change the vibration frequency of the vibration image of the damping mass 1 2 and automatically reduce: At this time, when the fI 素 motor or piezoelectric element is used to actuate the two sets of vibration damping devices superimposed on top and bottom, the control device 54 is calculated and rotated separately. Explanation ‘According to item i of the scope of patent application, even if the second is changed: the length of the sexual member’, it only changes the first degree slightly, which corresponds to the vibration frequency of the body by the amount of change in the length of the second elastic member. That is, since the vibration frequency of the damping mass body can be controlled minutely for practical purposes, the vibration frequency of the damping mass body can be accurately adjusted. Therefore, the business noise. ^
00P0080.ptd 第12胃 466812 五、發明說明（10) 且申冑專利範圍第2工員，可獲得作為最佳同步型 ί使用於制振對象處於共振狀態時之適宜同步型制振裝 置。 妒二：：申请專利靶園第3項，因可追蹤制振質量體之 ^頻率並調整I彈性構件之長度，故即使在制振質量 體之振動頻率會產生變化之場合，亦可自動減低其振動。 i根ί申請專利範園第4及5項，藉由較小之設置面積，不 僅可減低制振質量體之基頻，還可減低高次諧波。 [圖式之簡單說明] 面圖圖-為本纟明同步型制振裝置t第一實施W的概略平 圖=為沿著圖一之I I-Ι I線之斷面圖。 圖三為本發明同步型制振裝置之第一實施 :黃以及線圈彈簧之長度改變量與彈性力之關係的曲：形 圖。圖四為本發明同步型制振裝置之第二實施例的斷面 圖。圖五為本發明同步型制振裝置之第三實施例的斷面 圖:、為本發明第四實施例’係為包含同步型制 之制振系統的概略模式圖。 裝·置 [符號說明] 10 _―制振裝置 12 一—制振質量體00P0080.ptd The twelfth stomach 466812 V. Description of the invention (10) The second worker in the scope of the patent application can obtain the best synchronous vibration damping device used when the vibration damping object is in a resonance state. Jealousy 2 :: The third item of the patent application target park, because the ^ frequency of the damping mass body can be tracked and the length of the I elastic member can be adjusted, so even if the vibration frequency of the damping mass body changes, it can be automatically reduced Its vibration. The application of items 4 and 5 of the patent application park of igentil, with a small installation area, can not only reduce the fundamental frequency of the damping mass, but also reduce higher harmonics. [Brief description of the drawings] The front view is a schematic plan view of the first implementation W of the synchronous synchronous vibration damping device t of the present invention. It is a cross-sectional view taken along line I-I-I in FIG. FIG. 3 is a curve diagram of the first embodiment of the synchronous vibration damping device according to the present invention: the relationship between the length change of the yellow and coil springs and the elastic force. Fig. 4 is a sectional view of a second embodiment of a synchronous vibration damping device according to the present invention. Fig. 5 is a cross-sectional view of a third embodiment of a synchronous vibration suppressing device of the present invention: and is a schematic diagram of a fourth embodiment of the present invention ', which is a vibration suppressing system including a synchronous vibration suppressing system. [Symbol] 10 _―Vibration damping device 12 I—Vibration damping mass
00P0080.ptd00P0080.ptd
第13頁 46 6 8 1 2 五、發明說明（11) 14a~14d碟形彈簧 16 18 20 22 24 28 基盤 支柱 彈簣推壓構件 螺母 蓋部 線圈彈簧Page 13 46 6 8 1 2 V. Description of the invention (11) 14a ~ 14d disc spring 16 18 20 22 24 28 base plate pillar impulse pushing member nut cover coil spring
00P0080.ptd 第14頁00P0080.ptd Page 14
Claims (1)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10201299A JP4279396B2 (en) | 1999-04-09 | 1999-04-09 | Synchronous vibration control device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| TW466812B true TW466812B (en) | 2001-12-01 |
Family
ID=14315863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW89106481A TW466812B (en) | 1999-04-09 | 2000-04-07 | Synchronous vibration control apparatus |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4279396B2 (en) |
| TW (1) | TW466812B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103603916A (en) * | 2013-11-06 | 2014-02-26 | 清华大学 | Control moment gyroscope vibration-isolating unit |
| CN108652797A (en) * | 2017-03-28 | 2018-10-16 | 上海交通大学 | Suppression system and combinations thereof of trembling device |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2849133B1 (en) * | 2002-12-20 | 2005-11-11 | Bosch Gmbh Robert | DISC BRAKE DEVICE WITH VIBRATION ATTENUATOR |
| JP2007040034A (en) * | 2005-08-04 | 2007-02-15 | Daiwa House Ind Co Ltd | Vibration control device using tuned mass damper |
| JP5027037B2 (en) * | 2008-03-29 | 2012-09-19 | 東海ゴム工業株式会社 | Vibration control device |
| US8261896B2 (en) * | 2008-09-18 | 2012-09-11 | Honeywell International Inc. | Tuned mass dampers and vibration isolation apparatus |
| US8727660B2 (en) | 2010-04-16 | 2014-05-20 | Ammann Schweiz Ag | Arrangement for providing a pulsing compressive force |
| CN102493572B (en) * | 2011-12-27 | 2013-12-18 | 中铁大桥局集团武汉桥梁科学研究院有限公司 | Adjustable damping energy storage type tuned mass damper and energy storage method thereof |
| CN103368086B (en) * | 2013-06-29 | 2016-01-20 | 芜湖明远电力设备制造有限公司 | A kind of switchgear damping device |
| WO2015173642A1 (en) * | 2014-05-12 | 2015-11-19 | Cgg Services Sa | Low-frequency receiver coil suspension system |
| KR101546353B1 (en) | 2015-04-08 | 2015-08-24 | (주) 서원전설 | A vibration absorber for transformer |
| CN105240434B (en) * | 2015-11-17 | 2017-11-17 | 北京理工大学 | Disk spring quasi-zero stiffness vibration isolators |
| CN110565936B (en) * | 2019-08-30 | 2021-07-06 | 广东博智林机器人有限公司 | Tuned mass damper device and suspension construction robot with same |
| CN113464603B (en) * | 2021-06-15 | 2023-02-10 | 上海工程技术大学 | Tuning dynamic damper with adjustable it is multidirectional |
-
1999
- 1999-04-09 JP JP10201299A patent/JP4279396B2/en not_active Expired - Lifetime
-
2000
- 2000-04-07 TW TW89106481A patent/TW466812B/en not_active IP Right Cessation
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103603916A (en) * | 2013-11-06 | 2014-02-26 | 清华大学 | Control moment gyroscope vibration-isolating unit |
| CN103603916B (en) * | 2013-11-06 | 2015-10-21 | 清华大学 | Control-moment gyro isolation mounting |
| CN108652797A (en) * | 2017-03-28 | 2018-10-16 | 上海交通大学 | Suppression system and combinations thereof of trembling device |
| CN108652797B (en) * | 2017-03-28 | 2023-10-31 | 上海交通大学 | Tremor suppression system and combination device thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4279396B2 (en) | 2009-06-17 |
| JP2000291725A (en) | 2000-10-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| TW466812B (en) | Synchronous vibration control apparatus | |
| JP6401761B2 (en) | Tunable vibration damper and manufacturing and tuning method | |
| JP3555035B2 (en) | Dynamic vibration absorber | |
| US6958567B2 (en) | Active/passive distributed absorber for vibration and sound radiation control | |
| US7394014B2 (en) | Apparatus, system, and method for electronically adaptive percussion instruments | |
| TW201112080A (en) | Touch sensitive device | |
| TWI695128B (en) | Active inertial damper system and method | |
| JP2002061703A (en) | Vibration control method and vibration control device using this vibration control method | |
| JP2016176555A (en) | Vibration-proof component and vibration-proof structure | |
| US4341126A (en) | Variable amplitude vibratory apparatus | |
| Sarban et al. | Active vibration control of periodic disturbances using a DEAP damper | |
| Sung et al. | Active torsional vibration control experiments using shear-type piezoceramic sensors and actuators | |
| JP2000230603A (en) | Multi-dimensionally synchronized passive vibration control device and active vibration control device | |
| JP4705653B2 (en) | Vibration control device | |
| JP2012083338A (en) | Vibrator, and oscillator and gas detector including the same | |
| JP2008202371A (en) | Active damper of building | |
| Ryaboy | Practical aspects of design, tuning and application of dynamic vibration absorbers | |
| JP6790961B2 (en) | Vibration test equipment and vibration test method | |
| RU2309435C1 (en) | Piezo-electric bending transformer with controllable resonance frequency | |
| JP4392700B2 (en) | Method for suppressing vibration of plate-like body | |
| Duong et al. | Development of a rotary inchworm piezoelectric motor | |
| CN205530759U (en) | Tuned mass damper system with adjustable | |
| JP2005261025A (en) | Ultrasonic motor, moving device and its driving method | |
| JPH03117743A (en) | Damping device | |
| Xu et al. | Piezoelectric air transducer for active noise control |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GD4A | Issue of patent certificate for granted invention patent | ||
| MM4A | Annulment or lapse of patent due to non-payment of fees |