JPH07222393A - Axial vibration isolator using plate spring or laminated spring - Google Patents

Axial vibration isolator using plate spring or laminated spring

Info

Publication number
JPH07222393A
JPH07222393A JP6067323A JP6732394A JPH07222393A JP H07222393 A JPH07222393 A JP H07222393A JP 6067323 A JP6067323 A JP 6067323A JP 6732394 A JP6732394 A JP 6732394A JP H07222393 A JPH07222393 A JP H07222393A
Authority
JP
Japan
Prior art keywords
leaf spring
spring
vibration isolator
supporting base
space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP6067323A
Other languages
Japanese (ja)
Other versions
JP2665312B2 (en
Inventor
Yang-Gyu Je
ヤン−ギュ ジェ
Jong-Su Kim
ジョン−ス キム
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koria Inst Of Mach & Metals
Korea Institute of Machinery and Materials KIMM
Original Assignee
Koria Inst Of Mach & Metals
Korea Institute of Machinery and Metals KIMM
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Koria Inst Of Mach & Metals, Korea Institute of Machinery and Metals KIMM filed Critical Koria Inst Of Mach & Metals
Publication of JPH07222393A publication Critical patent/JPH07222393A/en
Application granted granted Critical
Publication of JP2665312B2 publication Critical patent/JP2665312B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
    • F16F15/073—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only leaf springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Motor Or Generator Frames (AREA)
  • Springs (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

PURPOSE: To obtain an axial vibration insulation device that has proper elasticity and attenuation, can be handled easily, has a semi-permanent life, and can simply adjust stiffness coefficient and attenuation coefficient by arranging a leaf spring or a laminated spring between an external movement ring and an internal supporting base and providing elasticity between them. CONSTITUTION: A number of leaf springs 1 or laminated springs 1' arranged on an internal supporting base 3 in a circumference direction and an external movement ring 2, is supported, thus providing a relative elasticity between the external movement ring 2 and the internal supporting base 3. Also, a proper amount of working fluid is filled into an internal fluid space 6. Therefore, when a relative movement occurs between the movement ring 2 and the supporting base 3, the volume of the space 6 is changed, a flow occurs in the space 6 through an oil path gap, and a pressure difference is generated in the space 6. In this case, the pressure difference operates on springs 1 and 1', thus generating an attenuation force between the movement ring 2 and the supporting base 3.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は板スプリング又は重板ス
プリングを利用した軸方向振動絶縁装置に関するもので
あり、もっと詳細には、エンジン、建物に設置される空
調機械、各種ターボ流体機械及び輪転機等の弾性支持マ
ウントとして軸方向の絶縁効果を高めながらも荷重支持
能力及び耐久性を増大して既存のゴム振動絶縁装置の欠
点を克服できる新しい概念の軸方向振動絶縁装置の開発
に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial vibration isolator using a leaf spring or a heavy leaf spring, and more particularly to an engine, an air conditioning machine installed in a building, various turbo fluid machines and wheels. It is related to the development of a new concept axial vibration isolator that can increase the load bearing capacity and durability while overcoming the shortcomings of the existing rubber vibration isolator while improving the axial insulation effect as an elastic support mount for a rolling machine. is there.

【０００２】[0002]

【従来の技術】弾性支持マウントとして現在まで価格の
低廉なゴム絶縁装置が多く使用されているが、ゴムの特
性上、油の中とか永い間使用すると硬化されて弾力を喪
失するので、耐久性が問題となっている。また、ゴムの
剛性が金属に比べて低いために、高荷重用として使用す
るには不適合であり、減衰効果も不足な場合が多い。従
って、近来はゴムの減衰力だけでなく、その中に流体を
封入して流体力によって減衰力を補充して大きな減衰効
果を持たせる振動絶縁装置も多く開発されて使用されて
いる。2. Description of the Related Art As an elastic support mount, inexpensive rubber insulating devices have been widely used up to now, but due to the characteristics of rubber, they lose their elasticity due to curing when used in oil or for a long time, so they are durable. Is a problem. Further, since the rigidity of rubber is lower than that of metal, it is unsuitable for use for heavy loads and the damping effect is often insufficient. Therefore, not only the damping force of rubber but also a vibration isolator that has a large damping effect by enclosing a fluid therein and supplementing the damping force by the fluid force has been developed and used recently.

【０００３】[0003]

【発明が解決しようとする課題】然しながら、この場合
にも剛性の増大は期待できないので、高荷重用には適当
でないし、またゴムの硬化又は破壊等による寿命の限界
も克服できずにいる。またゴム形振動絶縁装置の動特性
係数、即ち剛性係数及び減衰係数が振動数に従って急激
に変る非線形性によりシステムの解析が非常に難かし
い。However, in this case as well, an increase in rigidity cannot be expected, so that it is not suitable for high loads, and the life limit due to hardening or breaking of rubber cannot be overcome. In addition, it is very difficult to analyze the system due to the non-linearity in which the dynamic characteristic coefficient of the rubber vibration isolator, that is, the rigidity coefficient and the damping coefficient, changes rapidly according to the frequency.

【０００４】[0004]

【課題を解決するための手段】従って、本発明の目的は
上記のような既存のゴム形振動絶縁装置の欠点を補完す
るために、適切な弾性及び減衰を持つ振動絶縁装置であ
って、取扱いが容易であり寿命が半永久的で剛性係数及
び減衰係数の調節が簡便であってエンジニアリング設計
の容易な新しい軸方向流体減衰振動絶縁装置を開発する
ことにある。SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a vibration isolator with suitable resilience and damping in order to supplement the shortcomings of existing rubber type vibration isolators as described above. It is to develop a new axial fluid damping vibration isolation device that is easy to perform, has a semi-permanent life, is easy to adjust the rigidity coefficient and damping coefficient, and is easy to design in engineering.

【０００５】[0005]

【実施例】本発明の振動絶縁装置は図１及び図２のよう
な構造になっており、内部流体空間６には作業流体（一
般的にオイル）が適正量だけ満たされている。図１及び
図２において、板スプリング又は重板スプリング１，
１’を内部支持台３に円周方向に多数設置して外部移動
リング２を支持する構造にすることによって、外部移動
リング２と内部支持台３間に相対的な弾性を与えること
ができるようにし、また弾性係数の大きさは重板スプリ
ングの板の数、板の厚さ、板の幅、板の長さ、スプリン
グ板の材質等によって決定され、また円周方向に設置さ
れる重板スプリングの数によっても決定できる構造であ
る。従って、本発明の振動絶縁装置はゴム形振動絶縁装
置に比べて大きな剛性を与えることができるばかりでな
く、剛性係数の調節も容易であるということが非常に大
きな長所である。DESCRIPTION OF THE PREFERRED EMBODIMENTS The vibration isolator of the present invention has a structure as shown in FIGS. 1 and 2, and the internal fluid space 6 is filled with a proper amount of working fluid (generally oil). 1 and 2, a leaf spring or a heavy leaf spring 1,
By providing a large number of 1'on the inner supporting base 3 in the circumferential direction to support the outer moving ring 2, it is possible to provide relative elasticity between the outer moving ring 2 and the inner supporting base 3. The size of the elastic coefficient is determined by the number of plates of the heavy plate spring, the thickness of the plate, the width of the plate, the length of the plate, the material of the spring plate, and the like. The structure can be determined by the number of springs. Therefore, the vibration isolator of the present invention has a great advantage that not only can it provide greater rigidity, but also the rigidity coefficient can be easily adjusted, as compared with the rubber vibration isolator.

【０００６】従って、本発明の振動絶縁装置を使用する
ことによって、機械システムの固有振動数を調節できる
ので、危険速度と運転速度間の差異を大きくして、シス
テムを安定化できる設計が可能である。また、図１にお
いて内部流体空間は重板スプリングにより上側空間と下
側空間とに分離され、その間の通路が図２のオイルグル
ープ４であり、符号５は密封要素である。それゆえに、
外部移動リング２と内部支持台３間に相対運動が起こる
と、各々の内部流体空間６の体積が変わるようになり、
従って図２のオイルグループ４（油路間隙）を通して内
部流体空間６に流動が起こり、これにより内部流体空間
６に圧力差が発生されるようになる。この際、圧力差が
重板スプリングに作用するようになって、外部移動リン
グ２と内部支持台３間に減衰力が発生するようになる。
従って、減衰係数の大きさは流体の粘度とオイルグルー
プ４の大きさ等に関係される流れ抵抗係数と重板スプリ
ングの有効長さによって決定される。Therefore, since the natural frequency of the mechanical system can be adjusted by using the vibration isolator of the present invention, the design can stabilize the system by increasing the difference between the critical speed and the operating speed. is there. Further, in FIG. 1, the internal fluid space is divided into an upper space and a lower space by a heavy plate spring, a passage therebetween is an oil group 4 in FIG. 2, and a reference numeral 5 is a sealing element. Hence,
When a relative movement occurs between the outer moving ring 2 and the inner support base 3, the volume of each inner fluid space 6 changes,
Therefore, a flow occurs in the internal fluid space 6 through the oil group 4 (oil passage gap) in FIG. 2, which causes a pressure difference in the internal fluid space 6. At this time, the pressure difference acts on the heavy plate spring, and a damping force is generated between the outer moving ring 2 and the inner support 3.
Therefore, the magnitude of the damping coefficient is determined by the flow resistance coefficient related to the viscosity of the fluid and the size of the oil group 4 and the effective length of the heavy leaf spring.

【０００７】従って、本発明の振動絶縁装置は剛性係数
のように減衰係数も調節が容易であり、必要に応じて減
衰効果を充分に発揮できるばかりでなく、既存のゴム形
振動絶縁装置で得られる減衰係数よりもっと大きな減衰
係数を得ることができる。本発明の構造によって板スプ
リング又は重板スプリング１，１’を幅の一定な形態に
することができるし、図３のように円板で構成される円
板重板スプリング７を使用してもっと大きな剛性を与え
ることもできる形態に使用されることができるし、この
際、流体の移動通路は円板にオリフィス孔８を円周方向
に多数個穿孔して減衰効果を持たせることができる。Therefore, in the vibration isolator of the present invention, the damping coefficient such as the rigidity coefficient can be easily adjusted, and not only the damping effect can be sufficiently exerted if necessary, but also the existing rubber type vibration isolator can be obtained. It is possible to obtain a larger damping coefficient than the damping coefficient obtained. According to the structure of the present invention, the leaf springs or the heavy leaf springs 1 and 1'may have a constant width, and a disc heavy spring 7 composed of a disc may be used as shown in FIG. It can be used in a form that can give a great rigidity, and in this case, the fluid moving passage can have a large number of orifice holes 8 formed in the disk in the circumferential direction to provide a damping effect.

【０００８】[0008]

【発明の効果】本発明の振動絶縁装置は既存のゴム形振
動絶縁装置に比して剛性係数及び減衰係数の非線形性が
非常に弱くて、本発明の振動絶縁装置を包む機械システ
ムの振動解析が更に簡便になる効果を有するものであ
り、本発明の構造的設計変更は本発明の特許請求範囲に
包まれることは勿論のことである。EFFECTS OF THE INVENTION The vibration isolator of the present invention has much weaker non-linearity of the rigidity coefficient and the damping coefficient than the existing rubber vibration isolator, and the vibration analysis of the mechanical system including the vibration isolator of the present invention. However, the structural design change of the present invention is of course included in the scope of the claims of the present invention.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の振動絶縁装置の縦断面図である。FIG. 1 is a vertical sectional view of a vibration isolator of the present invention.

【図２】本発明の振動絶縁装置の横断平面部分である。FIG. 2 is a transverse plane portion of the vibration isolator of the present invention.

【図３】本発明の円板重板スプリングの構造である。FIG. 3 is a structure of a disc plate spring of the present invention.

【符号の説明】[Explanation of symbols]

１，１’ 板スプリング又は重板スプリング ２ 外部移動リング ３ 内部支持台 ４ オイルグループ ５ 密封要素 ６ 内部流体空間 ７ 円板重板スプリング ８ オリフィス孔 1, 1'plate spring or heavy plate spring 2 external movement ring 3 internal support 4 oil group 5 sealing element 6 internal fluid space 7 disk heavy plate spring 8 orifice hole

───────────────────────────────────────────────────── フロントページの続き (72)発明者 キム ジョン−ス 大韓民国 ブサン−シ，ブグ−ク，ハグジ ャン−ドン，グンガン アパート 104− 501 ─────────────────────────────────────────────────── --- Continuation of the front page (72) Inventor Kim Jong-su, Republic of Korea Busan-si, Buk-guk, Hagjang-dong, Gungan Apartment 104-501

Claims (3)

【特許請求の範囲】[Claims] 【請求項１】 板スプリング又は重板スプリング１，
１’を外部移動リング２と内部支持台３間に設置して相
互間に弾性を与えることを特徴とする板スプリング又は
重板スプリングを利用した軸方向振動絶縁装置。1. A leaf spring or a heavy leaf spring 1,
An axial vibration isolator using a leaf spring or a heavy leaf spring, wherein 1'is installed between the outer moving ring 2 and the inner support base 3 to give elasticity to each other. 【請求項２】 板スプリング又は重板スプリング１，
１’で内部流体空間６を上下に分割するようにし内部流
体空間６に適切な流体を封入して分割された内部流体空
間６に流体の移動による圧力差を利用して減衰効果を付
与することを特徴とする板スプリング又は重板スプリン
グを利用した軸方向振動絶縁装置。2. A leaf spring or a heavy leaf spring 1,
In 1 ', the internal fluid space 6 is divided into upper and lower parts, and an appropriate fluid is enclosed in the inner fluid space 6 to impart a damping effect to the divided inner fluid space 6 by utilizing the pressure difference due to the movement of the fluid. An axial vibration isolator using a leaf spring or a heavy leaf spring. 【請求項３】 板スプリング又は重板スプリング１，
１’は幅を一定な形態にできるし、円板で構成される円
板重板スプリング７を使用して大きな剛性を与えること
もできる形態で使用できるし、この際、流体の移動通路
は円板にオリフィス孔８を円周方向に多数個穿孔して減
衰効果を持つようにすることを特徴とする板スプリング
又は重板スプリングを利用した軸方向振動絶縁装置。3. A leaf spring or a heavy leaf spring 1,
1'can have a constant width, and can also be used in a form in which a large disc spring 7 composed of a disc can be used to give a large rigidity. An axial vibration isolator using a plate spring or a heavy plate spring, characterized in that a large number of orifice holes 8 are bored in the plate in the circumferential direction so as to have a damping effect.
JP6067323A 1994-01-18 1994-04-05 Axial vibration isolator using leaf spring or heavy leaf spring Expired - Fee Related JP2665312B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR835/1993 1994-01-18
KR1019940000835A KR950023875A (en) 1994-01-18 1994-01-18 Axial Vibration Isolation System Using Leaf Springs or Leaf Springs

Publications (2)

Publication Number Publication Date
JPH07222393A true JPH07222393A (en) 1995-08-18
JP2665312B2 JP2665312B2 (en) 1997-10-22

Family

ID=19375845

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6067323A Expired - Fee Related JP2665312B2 (en) 1994-01-18 1994-04-05 Axial vibration isolator using leaf spring or heavy leaf spring

Country Status (4)

Country Link
JP (1) JP2665312B2 (en)
KR (1) KR950023875A (en)
CN (1) CN1065034C (en)
DE (1) DE4420595C2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215440A (en) * 2007-03-01 2008-09-18 Sumitomo Heavy Ind Ltd Plate spring and refrigerator
CN109630607A (en) * 2018-12-21 2019-04-16 合肥佳恩特机械制造有限公司 A kind of sump that paves with shock-absorbing function

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103603442B (en) * 2013-11-25 2015-12-30 辽宁工业大学 The universal damper of arc memory alloy spring sheet
CN104179867B (en) * 2014-07-25 2016-04-06 哈尔滨工业大学 For the buffer limiter of electromagnetism vibration isolator
CN104534017B (en) * 2014-12-23 2016-08-24 广东宇泰减震科技有限公司 A kind of vibration abatement of practicality
DE202015002359U1 (en) * 2015-03-30 2016-07-01 Simon Winter vibration isolator
CN105729133B (en) * 2016-03-31 2017-12-26 苏州诺登德智能科技有限公司 A kind of embedded ground type lathe bidirectional damping buffering plate
CN105729134B (en) * 2016-03-31 2018-01-19 台州市智诚工业设计有限公司 A kind of lathe damping, buffering base
CN110939680B (en) * 2019-12-11 2021-08-10 北京化工大学 Damping device for axial vibration and noise reduction of shafting

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5055770A (en) * 1973-09-12 1975-05-16
JPS5427522A (en) * 1977-08-03 1979-03-01 Mitsubishi Chem Ind Ltd Preparation of maleic anhydride
JPH0415336A (en) * 1990-05-08 1992-01-20 Mazda Motor Corp Fly wheel device for engine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1641217A (en) * 1926-08-02 1927-09-06 George F Yevseyeff Shock absorber
US3145012A (en) * 1962-07-16 1964-08-18 Korfund Dynamics Corp All-directional frictional damper
DE2303543A1 (en) * 1973-01-25 1974-08-01 Schoen Christel Vehicle shock absorber unit - with housing for spring with high viscosity fluid above spring and compressible mass within spring
US3856242A (en) * 1973-03-29 1974-12-24 Gen Electric Mounting apparatus for a surge voltage arrester

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5055770A (en) * 1973-09-12 1975-05-16
JPS5427522A (en) * 1977-08-03 1979-03-01 Mitsubishi Chem Ind Ltd Preparation of maleic anhydride
JPH0415336A (en) * 1990-05-08 1992-01-20 Mazda Motor Corp Fly wheel device for engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008215440A (en) * 2007-03-01 2008-09-18 Sumitomo Heavy Ind Ltd Plate spring and refrigerator
CN109630607A (en) * 2018-12-21 2019-04-16 合肥佳恩特机械制造有限公司 A kind of sump that paves with shock-absorbing function

Also Published As

Publication number Publication date
KR950023875A (en) 1995-08-18
DE4420595C2 (en) 1997-07-03
DE4420595A1 (en) 1995-07-20
JP2665312B2 (en) 1997-10-22
CN1120134A (en) 1996-04-10
CN1065034C (en) 2001-04-25

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