JPH08285014A - Dynamic vibration absorber for longitudinal and torsional vibration of rotation shaft - Google Patents
Dynamic vibration absorber for longitudinal and torsional vibration of rotation shaftInfo
- Publication number
- JPH08285014A JPH08285014A JP11653495A JP11653495A JPH08285014A JP H08285014 A JPH08285014 A JP H08285014A JP 11653495 A JP11653495 A JP 11653495A JP 11653495 A JP11653495 A JP 11653495A JP H08285014 A JPH08285014 A JP H08285014A
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- longitudinal
- torsional
- absorber
- crankshaft
- 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.)
- Withdrawn
Links
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 15
- 238000013016 damping Methods 0.000 claims abstract description 9
- 239000003921 oil Substances 0.000 claims description 18
- XUIMIQQOPSSXEZ-UHFFFAOYSA-N Silicon Chemical compound [Si] XUIMIQQOPSSXEZ-UHFFFAOYSA-N 0.000 claims description 2
- 229910052710 silicon Inorganic materials 0.000 claims description 2
- 239000010703 silicon Substances 0.000 claims description 2
- 230000001603 reducing effect Effects 0.000 abstract description 6
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
Landscapes
- Vibration Prevention Devices (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はディーゼル機関のクラン
ク軸の縦及び捩り振動に適用される動吸振器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic vibration absorber applied to longitudinal and torsional vibrations of a crankshaft of a diesel engine.
【０００２】[0002]
【従来の技術】従来例を図４、５によって説明する。図
４は従来例のオイルダンパの断面図、図５は従来例のオ
イルダンパの振動低減効果の説明図である。エンジン軸
１の端にピストン軸２を取付け之にピストン３をキーで
取付けエンジン架構４に取付けられた作動オイル８を満
たしたシリンダ５に嵌合させている。６はカバーでシリ
ンダ５をふさぐ。７はオリフィスでピストン３の両側の
空間を連通する狭い通路である。2. Description of the Related Art A conventional example will be described with reference to FIGS. FIG. 4 is a cross-sectional view of a conventional oil damper, and FIG. 5 is an explanatory diagram of a vibration reducing effect of the conventional oil damper. The piston shaft 2 is attached to the end of the engine shaft 1, and the piston 3 is attached with a key, and the piston 3 is fitted to the cylinder 5 filled with the working oil 8 attached to the engine frame 4. 6 is a cover for closing the cylinder 5. Reference numeral 7 denotes an orifice, which is a narrow passage that communicates the spaces on both sides of the piston 3.
【０００３】前記従来例の作用を説明する。エンジン軸
１の縦振動（軸方向振動）によりシリンダ５内の作動油
をオリフィス７を通して往復させオリフィス部で作動油
に乱流を生じさせて、振動エネルギを熱エネルギに変換
させることによりエンジン軸の縦振動を低減させる。The operation of the conventional example will be described. The longitudinal vibration (axial vibration) of the engine shaft 1 causes the working oil in the cylinder 5 to reciprocate through the orifice 7 to generate a turbulent flow in the working oil, thereby converting the vibration energy into heat energy. Reduces vertical vibration.
【０００４】[0004]
【発明が解決しようとする課題】従来の縦振動の制振用
として用いられている油圧ダンパはオリフィスを有する
ため、軸の縦振動（軸方向振動）によるピストンの軸方
向の変位により作動油の圧力がオリフィスに作用する。
すなわち、軸の縦振動の圧力がシリンダ及び油圧ダンパ
が取り向けられているエンジン架構を介して船体に伝達
される。この振動伝達力は減衰を大きくして、軸の縦振
動を低減しようとすればする程大きくなる。また、一般
に舶用ディーゼルエンジンのクランク軸振動において
は、縦振動と共に捩り振動が問題になるが、縦振動に対
しては第４図に示す縦振動用ダンパが用いられるが、捩
り振動に対しては、捩り振動用のダンパを更に取り付け
る必要がある。Since the conventional hydraulic damper used for damping vertical vibration has an orifice, hydraulic oil is generated by axial displacement of the piston due to vertical vibration of the shaft (axial vibration). Pressure acts on the orifice.
That is, the pressure of longitudinal vibration of the shaft is transmitted to the hull via the engine frame to which the cylinder and the hydraulic damper are directed. This vibration transmission force increases as the damping is increased and the longitudinal vibration of the shaft is reduced. Generally, in the crankshaft vibration of a marine diesel engine, torsional vibration becomes a problem along with longitudinal vibration. For longitudinal vibration, the longitudinal vibration damper shown in FIG. 4 is used, but for torsional vibration, , It is necessary to additionally install a damper for torsional vibration.
【０００５】本発明の目的はディーゼル機関のクランク
軸の縦振動ばかりでなく捩り振動も１個の動吸振器で低
減することによりディーゼル機関を主機としている船体
への加振力を低減することができる回転軸縦及び捩り振
動用動吸振器を提供するにある。It is an object of the present invention to reduce not only longitudinal vibration of a crankshaft of a diesel engine but also torsional vibration with a single dynamic vibration reducer to reduce an exciting force to a hull whose main engine is a diesel engine. It is possible to provide a dynamic vibration absorber for longitudinal and torsional vibration of a rotating shaft.
【０００６】[0006]
【課題を解決するための手段】本発明に係る回転軸縦及
び捩り振動用動吸振器は、円周方向に多重の円弧状切欠
穴１８を有する円板の外周にリング状の重錘１４を設け
た振動円板１３をダンピングオイル１７（シリコンオイ
ル等）の中に封入したことを特徴としている。A dynamic vibration absorber for longitudinal and torsional vibration of a rotary shaft according to the present invention has a ring-shaped weight 14 on the outer circumference of a disk having multiple arcuate cutout holes 18 in the circumferential direction. The vibrating disk 13 provided is enclosed in damping oil 17 (silicon oil or the like).
【０００７】[0007]
【作用】エンジンのクランク軸が縦方向（軸方向）及び
捩り方向（円周方向）に、それぞれの固有振動数でもっ
て振動すると、これらの固有振動数に一致するように調
整された振動円板１３の外周に取り付けられたカウンタ
リング１４も振動し、結果的に２自由度系の振動系を構
成する。この時、カウンタリング１４の質量及び慣性能
率は、クランク軸の等価質量及び等価慣性能率に比べて
小さいため、カウンタリングはクランク軸より大きく振
動し、まわりのダンピングオイル１７との間に相対変位
が生じ振動エネルギが熱エネルギになって消散する。従
って、図３に示すように、図５に示す従来のオイルダン
パよりクランク軸の振動が大幅に低減する。この際、カ
ウンタリングを支えている振動円板１３には円弧状の切
欠穴１８があるため、振動円板１３の面外方向（軸方
向）及び円周方向に撓み易く、大きな変位を許容しつつ
振動円板に発生する応力を小さく保つことができる。When the crankshaft of the engine vibrates in the longitudinal direction (axial direction) and the torsional direction (circumferential direction) at respective natural frequencies, a vibrating disk adjusted to match these natural frequencies. The counter ring 14 attached to the outer periphery of 13 also vibrates, and as a result, forms a two-degree-of-freedom vibration system. At this time, since the mass and inertial coefficient of the counter ring 14 are smaller than the equivalent mass and equivalent inertial coefficient of the crankshaft, the counterring vibrates more than the crankshaft, and the relative displacement with the surrounding damping oil 17 occurs. The generated vibration energy becomes heat energy and is dissipated. Therefore, as shown in FIG. 3, the vibration of the crankshaft is significantly reduced as compared with the conventional oil damper shown in FIG. At this time, since the vibrating disc 13 supporting the counter ring has the arcuate notch hole 18, the vibrating disc 13 is easily bent in the out-of-plane direction (axial direction) and the circumferential direction, and a large displacement is allowed. At the same time, the stress generated in the vibrating disk can be kept small.
【０００８】[0008]
【実施例】本発明に係る第１実施例を図１〜３によって
説明する。図１は本発明に係る第１実施例の回転軸縦及
び捩り用動吸振器の断面図、図２は図１のII−II断面
図、図３は本発明の回転軸縦及び捩り用動吸振器による
振動低減効果の説明図である。図１に示すようにエンジ
ン軸１の端部に吸振器軸１２を取付ける。前記吸振器軸
に図２に示すように同心円上に多重に円弧状の切欠穴１
８を有する振動円板１３がキーにより固定されその外周
にカウンタリング１４が取付けられている。エンジン架
構４にケーシング１５がボルトにより固定され更にカバ
ー１６が同吸振器軸１２、振動円板１３及びカウンタリ
ング１４を覆うようにケーシング１５に取付られその中
にシリコンオイル等のダンピングオイル１７を封入して
いる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment according to the present invention will be described with reference to FIGS. FIG. 1 is a sectional view of a rotary shaft vertical and torsional dynamic absorber according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. It is explanatory drawing of the vibration reduction effect by a vibration absorber. As shown in FIG. 1, the vibration absorber shaft 12 is attached to the end of the engine shaft 1. As shown in FIG. 2, a plurality of arcuate cutout holes 1 are formed on the vibration absorber shaft in a concentric circle.
A vibrating disk 13 having a number 8 is fixed by a key, and a counter ring 14 is attached to the outer circumference thereof. A casing 15 is fixed to the engine frame 4 with bolts, and a cover 16 is attached to the casing 15 so as to cover the vibration absorber shaft 12, the vibration disk 13 and the counter ring 14, and a damping oil 17 such as silicone oil is enclosed therein. are doing.
【０００９】次に作用について述べると、エンジンのク
ランク軸が縦方向（軸方向）及び捩り方向（円周方向）
に、それぞれの固有振動熱でもって振動すると、これら
の固有振動数に一致するように調整された振動円板１３
の外周に取り付けられたカウンターリング１４も振動
し、結果的に２自由度系の振動系を構成する。この時、
カウンターリング１４の質量及び慣性能率は、クランク
軸の等価質量及び等価慣性能率に比べて小さいため、カ
ウンターリング１４はクランク軸より大きく振動し、ま
わりのダンピングオイル１７との間に相対変位が生じ振
動エネルギが熱エネルギになって消散する。従って、図
３に示すように、図５に示す従来のオイルダンパよりク
ランク軸の振動が大幅に低減する。Next, the operation will be described. The crankshaft of the engine is longitudinal (axial direction) and twisting direction (circumferential direction).
Further, when vibrating by the respective natural vibration heat, the vibrating disk 13 adjusted to match these natural frequencies.
The counter ring 14 attached to the outer periphery of the vibrator also vibrates, and as a result, a two-degree-of-freedom vibration system is formed. This time,
Since the mass and inertial coefficient of the counter ring 14 are smaller than the equivalent mass and equivalent inertial coefficient of the crankshaft, the counterring 14 vibrates more than the crankshaft, causing relative displacement with the surrounding damping oil 17 and vibrating. The energy becomes heat energy and is dissipated. Therefore, as shown in FIG. 3, the vibration of the crankshaft is significantly reduced as compared with the conventional oil damper shown in FIG.
【００１０】この際、カウンターリング１４を支えてい
る振動円板１３には円弧状の切欠穴があるため、振動円
板１３の面外方向（軸方向）及び円周方向に撓み易く、
大きな変位を許容しつつ振動円板１３に発生する応力を
小さく保つことができる。At this time, since the vibrating disc 13 supporting the counter ring 14 has arcuate notch holes, it is easy to bend in the out-of-plane direction (axial direction) and the circumferential direction of the vibrating disc 13.
The stress generated in the vibrating disk 13 can be kept small while allowing a large displacement.
【００１１】[0011]
【発明の効果】本発明は前記のとおり構成されているの
で次の効果がある。 （１）ディーゼル機関のクランク軸の振動を低減するこ
とにより、ディーゼル機関を主機としている船舶等への
加振力すなわち振動を低減することが出来、船舶の各構
造部材の振動疲労クラックを防止すると共に、乗客及び
乗組員への乗り心地を改善することができる。 （２）ディーゼル機関のクランク軸のダンパの設置場所
は限られているが、本発明によりクランク軸の縦振動ば
かりでなく捩り振動も１個の動吸振器で対応することが
可能となり、取付コストが低減するばかりでなく、クラ
ンク軸の振動を大幅に改善することができる。Since the present invention is constructed as described above, it has the following effects. (1) By reducing the vibration of the crankshaft of the diesel engine, it is possible to reduce the vibrational force, that is, the vibration, to a ship or the like having the diesel engine as the main engine, and to prevent vibration fatigue cracks of each structural member of the ship. At the same time, the ride comfort for passengers and crew can be improved. (2) The installation place of the damper of the crankshaft of the diesel engine is limited, but the present invention makes it possible to handle not only the longitudinal vibration of the crankshaft but also the torsional vibration with one dynamic vibration absorber, thus reducing the installation cost. Is not only reduced, but also the vibration of the crankshaft can be significantly improved.
【図１】本発明に係る第１実施例の回転軸縦及び捩り用
動吸振器の断面図。FIG. 1 is a cross-sectional view of a dynamic vibration absorber for vertical rotation and torsion of a rotary shaft according to a first embodiment of the present invention.
【図２】図１のII−II断面図。FIG. 2 is a sectional view taken along line II-II of FIG.
【図３】本発明の回転軸縦及び捩り用動吸振器による振
動低減効果の説明図。FIG. 3 is an explanatory view of a vibration reducing effect by the dynamic vibration absorber for vertical and torsional axes of the present invention.
【図４】従来例のオイルダンパの断面図。FIG. 4 is a cross-sectional view of a conventional oil damper.
【図５】従来例のオイルダンパの振動低減効果の説明
図。FIG. 5 is an explanatory diagram of a vibration reduction effect of the oil damper of the conventional example.
１…エンジン軸、２…ピストン軸、３…ピストン、４…
エンジン架構、５…シリンダ、６…カバー、７…オリフ
ィス、８…作動オイル、１２…動吸振器軸、１３…振動
円板、１４…カウンタリング、１５…ケーシング、１６
…カバー、１７…ダンピングオイル、１８…切欠穴。1 ... Engine shaft, 2 ... Piston shaft, 3 ... Piston, 4 ...
Engine frame, 5 ... Cylinder, 6 ... Cover, 7 ... Orifice, 8 ... Working oil, 12 ... Dynamic vibration absorber shaft, 13 ... Vibrating disc, 14 ... Counter ring, 15 ... Casing, 16
... cover, 17 ... damping oil, 18 ... notch hole.
Claims (1)
を有する円板の外周にリング状の重錘（１４）を設けた
振動円板（１３）をダンピングオイル（１７）（シリコ
ンオイル等）の中に封入したことを特徴とする回転軸縦
及び捩り振動用動吸振器。1. A circular arc-shaped notch hole (18) which is multiple in the circumferential direction.
Rotating shaft longitudinal and twisting, characterized in that a vibrating disc (13) having a ring-shaped weight (14) provided on the outer periphery of the disc having the is enclosed in damping oil (17) (silicon oil or the like). Dynamic vibration absorber for vibration.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11653495A JPH08285014A (en) | 1995-04-18 | 1995-04-18 | Dynamic vibration absorber for longitudinal and torsional vibration of rotation shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11653495A JPH08285014A (en) | 1995-04-18 | 1995-04-18 | Dynamic vibration absorber for longitudinal and torsional vibration of rotation shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08285014A true JPH08285014A (en) | 1996-11-01 |
Family
ID=14689511
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11653495A Withdrawn JPH08285014A (en) | 1995-04-18 | 1995-04-18 | Dynamic vibration absorber for longitudinal and torsional vibration of rotation shaft |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08285014A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001039656A (en) * | 1999-05-26 | 2001-02-13 | Toshiba Corp | Hoisting device, its assembling method and elevator |
| KR20020047607A (en) * | 2000-12-13 | 2002-06-22 | 이계안 | Torsional damper of manual transmission |
| JP2019027469A (en) * | 2017-07-27 | 2019-02-21 | 本田技研工業株式会社 | Vibration inhibition device and electric vehicle |
-
1995
- 1995-04-18 JP JP11653495A patent/JPH08285014A/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001039656A (en) * | 1999-05-26 | 2001-02-13 | Toshiba Corp | Hoisting device, its assembling method and elevator |
| KR20020047607A (en) * | 2000-12-13 | 2002-06-22 | 이계안 | Torsional damper of manual transmission |
| JP2019027469A (en) * | 2017-07-27 | 2019-02-21 | 本田技研工業株式会社 | Vibration inhibition device and electric vehicle |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20020702 |