JPS6159037A - Vibration damper for marine diesel engine - Google Patents
Vibration damper for marine diesel engineInfo
- Publication number
- JPS6159037A JPS6159037A JP18230484A JP18230484A JPS6159037A JP S6159037 A JPS6159037 A JP S6159037A JP 18230484 A JP18230484 A JP 18230484A JP 18230484 A JP18230484 A JP 18230484A JP S6159037 A JPS6159037 A JP S6159037A
- Authority
- JP
- Japan
- Prior art keywords
- vibration
- flywheel
- driven
- weight
- diesel engine
- 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.)
- Pending
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
- F16F15/22—Compensation of inertia forces
- F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
- F16F15/264—Rotating balancer shafts
-
- 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
-
- 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
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は舶用ディーゼル機関の消振装置に関する。[Detailed description of the invention] [Industrial application field] The present invention relates to a vibration damping device for a marine diesel engine.
船舶がその主機関として機関室に搭載する大型低速ディ
ーゼル機関は、可動部分質量の慣性力によって、主機ク
ランク軸回転数の１倍及び２倍の周波数を持つ不平衡偶
力を発生しておシ、この不平衡偶力は通常それぞれ１次
アンバランスモーメント及び２次アンバランスモーメン
トと呼ばれる。The large low-speed diesel engine installed in the engine room as the main engine of a ship generates unbalanced couples with frequencies of one and two times the main engine crankshaft rotation speed due to the inertia of the mass of the moving parts. , this unbalanced couple is usually called the first unbalanced moment and the second unbalanced moment, respectively.
このアンバランスモーメントによって船舶に発生する振
動を消すために、電動バランサーが船尾部に搭載される
が、電動バランサーの原理は軸の回りに回転する重錘の
遠心力によって消振力を発生させるものである。An electric balancer is mounted on the stern of the ship to eliminate the vibrations generated in the ship due to this unbalanced moment, but the principle of an electric balancer is to generate vibration-absorbing force by the centrifugal force of a weight rotating around an axis. It is.
舶用電動バランサーとしては、従来、例えば第３口止面
図に示すように、１対の不平衡回転重錘０１ｂ、０１ｂ
がフライホイール０１．０ｉ内に納められ、それぞれの
回転軸Ｑ１ａ、Ｑ１ａの周りに同一回転数で互いに逆方
向に回転するように配置されている。Conventionally, as a marine electric balancer, a pair of unbalanced rotating weights 01b, 01b is used, for example, as shown in the third port stop diagram.
are housed in the flywheel 01.0i, and are arranged so as to rotate in opposite directions at the same rotation speed around their respective rotational axes Q1a, Q1a.
そして、これらは図示していない電動機によって駆動さ
れる駆動軸０２で駆動され、回転重錘０１ｂ、０１ｂ及
び駆動軸０２等はケーシング０６で囲まれ、駆動軸０２
の回転数及び位相は図示していない制御部によって制御
されている。These are driven by a drive shaft 02 driven by an electric motor (not shown), and the rotating weights 01b, 01b, drive shaft 02, etc. are surrounded by a casing 06, and the drive shaft 02 is
The rotation speed and phase of are controlled by a control section (not shown).
したがって、１対の回転重錘ｏｉｂ、ｏｉｂが回転する
と、遠心力によって上下方向の力が発生するが、水平方
向には両者の遠心力が相殺して水平起振力は発生しない
。そして、船尾部への搭載方法は第５図側面図及び第６
図横断面図に示すように、回転軸０１ａ。Therefore, when the pair of rotating weights oib, oib rotate, a vertical force is generated due to centrifugal force, but in the horizontal direction, the centrifugal forces cancel each other out and no horizontal excitation force is generated. The method of mounting on the stern section is shown in Figure 5 side view and Figure 6.
As shown in the cross-sectional view, the rotation axis 01a.
０１′ａは船の長さ方向に沿って配置するので、上記の
遠心力による力は上下振動のみを発生し、左右振動は発
生させない。Since 01'a is arranged along the length direction of the ship, the centrifugal force described above generates only vertical vibration and no horizontal vibration.
また、電動バランサー０８による消振効果は第４図で主
機関４のアンバランスモーメントによって船舶５に発生
した上下振動６と、船尾部７に搭載したバランサー０８
が発生させる上下振動０９とが相殺するように電動ノく
ランサー０８を制御することによって得られる。In addition, the vibration damping effect of the electric balancer 08 is shown in FIG.
This can be obtained by controlling the electric nozzle lancer 08 so that the vertical vibration 09 generated by the vibration cancels out the vibration.
しかしながら、このような装置では、下記のような欠点
がある。However, such a device has the following drawbacks.
（１） 水平方向の遠心力を相殺させるために、回転
重錘Ｑ１ｂ、Ｑ１’ｂは２個が１組となっているので、
電動バランサー０８の小型軽量化やコストダウンが困難
である。(1) In order to offset the centrifugal force in the horizontal direction, two rotating weights Q1b and Q1'b are used as a set, so
It is difficult to reduce the size and weight and cost of the electric balancer 08.
（２）電動バランサー〇８を据付けるために、船尾部７
に大きなスペースを必要とする。(2) In order to install the electric balancer 〇8, the stern section 7
requires large space.
本発明は、このような事情に鑑みて提案されたもので、
小型軽量化及びコストダウンを図る舶用ディーゼル機関
の消振装置を提供することを目的とする。The present invention was proposed in view of these circumstances, and
The purpose of the present invention is to provide a vibration damping device for a marine diesel engine that is smaller in size, lighter in weight, and lower in cost.
そのために本発明は、ｗＢｔａの周シに回転する１個の
７ライホイール内に軸心から偏心した位置に回転重錘を
配し、前記フライホイールを所定の回転数及び位相で駆
動せしめることを特徴とする。To this end, the present invention provides a method in which a rotary weight is disposed at a position eccentric from the axis within one 7-fly wheel that rotates around the circumference of wBta, and the flywheel is driven at a predetermined rotation speed and phase. Features.
上述の構成により、小型軽量化及びコストダウンを図る
舶用ディーゼル機関の消振装置を得ることができる。With the above-described configuration, it is possible to obtain a vibration damping device for a marine diesel engine that is smaller in size, lighter in weight, and lower in cost.
本発明の一実施例を図面について説明すると、第１図は
その電動バランサーを示す正面図、第２図は第４図の船
体振動の特性を示す線図である。An embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a front view showing the electric balancer, and FIG. 2 is a diagram showing the characteristics of hull vibration shown in FIG. 4.
上図において、第３〜６図と同一の記号はそれぞれ同図
と同一の部材を示し、１ｂは駆動軸２によって駆動され
る回転軸１ａによシ回転させられるフライホイール１の
軸心から偏心した位置に取付けられた回転重錘、２は図
示していない電動機及び制御部によって、所要の回転数
及び位相で回転する駆動軸、３は電動バランサーである
。In the above figure, the same symbols as in FIGS. 3 to 6 indicate the same members as in the same figure, and 1b is eccentric from the axis of the flywheel 1 rotated by the rotating shaft 1a driven by the drive shaft 2. 2 is a drive shaft which is rotated at a required rotation speed and phase by an electric motor and a control unit (not shown); 3 is an electric balancer.
このような装置において、駆動軸２を介して回転軸１ａ
のフライホイール１が回転すると、フライホイール１に
取付けられた回転重錘１ｂに遠心力が作用する。In such a device, the rotating shaft 1a is connected via the drive shaft 2.
When the flywheel 1 rotates, centrifugal force acts on the rotating weight 1b attached to the flywheel 1.
この遠心力の大きさは、回転重錘１ｂの偏心重量と回転
軸１ａからの偏心距離の積に比例し、またその方向は回
転重錘１ｂとともに回転するので、電動バランサー乙の
据付面には上下方向と水平方向の両方向に力が作用する
。The magnitude of this centrifugal force is proportional to the product of the eccentric weight of the rotating weight 1b and the eccentric distance from the rotating shaft 1a, and its direction rotates together with the rotating weight 1b. Forces act in both vertical and horizontal directions.
また、フライホイール１の回転数は、主機関４の軸回転
ｆｊｌＮ（Ｄ整数倍ｎＮ（ｎ＝＝１又は２）である。Further, the rotation speed of the flywheel 1 is the shaft rotation fjlN of the main engine 4 (D integer times nN (n==1 or 2).
ここで、第４図に示すような船舶の船体振動特性を調べ
ると、例えば第２図線図に示すように、ｎＮ・・・横軸
上にとった回転重錘の回転数（ｒｐｍ）、Ａ・・・縦軸
上にとった振動加速度、λ７・・・上下方向の起振力に
よる上下加速度、ＡＨ・・水平方向の起振力による水平
加速度、Ｂｙ・・・上下振動発生域、ＢＨ・・水平振動
発生域とすると、ＢｖではＡＶが大きいがＡＨは極めて
小さく、−万ＢＨではＡＨは大きいがＡＶは極めて小さ
い。Here, when examining the hull vibration characteristics of a ship as shown in Fig. 4, for example, as shown in the diagram of Fig. 2, nN...the number of rotations (rpm) of the rotating weight taken on the horizontal axis, A: Vibration acceleration taken on the vertical axis, λ7: Vertical acceleration due to vertical vibration excitation force, AH: Horizontal acceleration due to horizontal vibration excitation force, By: Vertical vibration generation area, BH ...Assuming the horizontal vibration generation area, at Bv, AV is large but AH is extremely small, and at -10,000 BH, AH is large but AV is extremely small.
すなわち、船体振動の特性は同時に上下・水平の２方向
の起振力が作用しても、いずれかの力（Ｃ選択共振する
ものであシ、例えばＢｖの範囲において水平起振力があ
っても過大な水平振動を発生する惧れは少ないことが分
る。In other words, the characteristics of ship vibration are that even if excitation forces in two directions (vertical and horizontal) act simultaneously, one of the forces (C) will selectively resonate; for example, if there is a horizontal excitation force in the range of Bv, It can be seen that there is little risk of generating excessive horizontal vibration.
したがって、本発明の電動バランサー３で生じた振動を
第４図における電動バランサー０８による振動０９と考
えれば、本発明の電動バランサー３による消去効果は理
解されよう。Therefore, if the vibration generated by the electric balancer 3 of the present invention is considered as the vibration 09 caused by the electric balancer 08 in FIG. 4, the elimination effect of the electric balancer 3 of the present invention will be understood.
また、主機関４に水平振動を発生させるアンバランスモ
ーメントがある場合には、上述の上下振動の消振原理と
同じように、本発明の電動バランサー３で生じた水平方
向の起振力による水平加速度によって消去させることが
できる。In addition, when there is an unbalanced moment that causes horizontal vibration in the main engine 4, the horizontal excitation force generated by the electric balancer 3 of the present invention can It can be erased by acceleration.
主機関に水平振動を起こすアンバランスモーメントがな
い場合には、ＢＨの区間では電動バランサー３の作用は
不要となる。したがって、この区間では電動バランサー
３を停止させておけばよい。If there is no unbalance moment that causes horizontal vibration in the main engine, the action of the electric balancer 3 is unnecessary in the BH section. Therefore, it is sufficient to stop the electric balancer 3 in this section.
このような装置によれば、下記効果が奏せられる。According to such a device, the following effects can be achieved.
舶用ディーゼル機関の不平衡偶力に基づく上下方向及び
水平方向の船体振動の対策が１個のみの回転重錘を有す
る電動バランサーでもって可能となるので、
（１）電動バランサーが小型幅量化され、かつコストダ
ウンする。Countermeasures against vertical and horizontal hull vibrations caused by the unbalanced couple of marine diesel engines can be achieved using an electric balancer with only one rotating weight. and reduce costs.
０）電動バランサー据付けのための船尾部スペースが小
さくて済む。0) The stern space for installing the electric balancer is small.
因みに、本装置と従来型とを比較すると下記のようにな
る。Incidentally, a comparison between this device and a conventional type is as follows.
従来型・・自重６．５ ｔｏｎ 、最大発生力５ｔｏｎ
。Conventional type: Weight 6.5 tons, maximum generated force 5 tons
.
巾×長さ１．５ ｍ Ｘ ２．４ ｍ
本発明・・・自重４ ｔｏｎ 、最大発生力５ ｔｏｎ
。Width x length 1.5 m x 2.4 m Invention: Own weight: 4 tons, maximum generated force: 5 tons
.
巾Ｘ長さ１．５ ｍ Ｘ １．５ ｍ
〔発明の効果〕
要するに本発明によれば、軸心の周りに回転する１個の
フライホイール内に軸心から偏心した位置に回転重錘を
配し、前記フライホイールを所定の回転数及び位相で駆
動せしめることによシ、小型幅量化及びコストダウンを
図る舶用ディーゼル機関の消振装置を得るから、本発明
は産業上極めて有益なものである。Width x Length 1.5 m x 1.5 m [Effects of the Invention] In short, according to the present invention, a rotating weight is placed at a position eccentric from the axis within one flywheel rotating around the axis. The present invention is industrially extremely useful because it provides a vibration damping device for a marine diesel engine that reduces the width and cost by driving the flywheel at a predetermined rotational speed and phase. be.
第１図は本発明の一実施例の電動バランサーを示す正面
図、第２図は船舶の船体振動の特性を示す線図、第３図
は公知の電動バランサーの正面図、第４図は第６図の電
動バランサーの原理説明図、第５図は第４図の電動バラ
ンサーを示す部分拡大図、第６図は第５図の■−■矢視
正而図面ある。
１・・・フライホイール、１ａ・・・回転軸、１ｂ・・
・回転重錘、２・・・駆動軸、３・・・電動バランサー
、ｎＮ・・横軸上にとった回転重錘の回転数（ｒ ｐｍ
）、Ａ・・・縦軸上にとった振動加速度、ＡＶ・・・
上下方向の起振力による上下加速度、ＡＩ（・・・水平
方向の起振力による水平加速度、Ｂｖ・・・上下振動発
生域、ＢＨ・・・水平振動発生域。
復代理人 弁理士 塚 本 正 文
第１図Fig. 1 is a front view showing an electric balancer according to an embodiment of the present invention, Fig. 2 is a diagram showing the characteristics of hull vibration of a ship, Fig. 3 is a front view of a known electric balancer, and Fig. 4 is a diagram showing the characteristics of hull vibration of a ship. FIG. 6 is an explanatory diagram of the principle of the electric balancer, FIG. 5 is a partially enlarged view showing the electric balancer of FIG. 4, and FIG. 1... Flywheel, 1a... Rotating shaft, 1b...
・Rotating weight, 2... Drive shaft, 3... Electric balancer, nN... Number of rotations of the rotating weight placed on the horizontal axis (r pm
), A... Vibration acceleration taken on the vertical axis, AV...
Vertical acceleration due to vertical excitation force, AI (...horizontal acceleration due to horizontal excitation force, Bv...vertical vibration generation area, BH...horizontal vibration generation area. Sub-agent Patent Attorney Tsukamoto Original text Figure 1
Claims (1)
ら偏心した位置に回転重錘を配し、前記フライホイール
を所定の回転数及び位相で駆動せしめることを特徴とす
る舶用ディーゼル機関の消振装置。A marine diesel engine characterized in that a rotary weight is disposed in a position eccentric from the axis within one flywheel rotating around the axis, and the flywheel is driven at a predetermined rotation speed and phase. Vibration damping device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18230484A JPS6159037A (en) | 1984-08-31 | 1984-08-31 | Vibration damper for marine diesel engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18230484A JPS6159037A (en) | 1984-08-31 | 1984-08-31 | Vibration damper for marine diesel engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6159037A true JPS6159037A (en) | 1986-03-26 |
Family
ID=16115946
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18230484A Pending JPS6159037A (en) | 1984-08-31 | 1984-08-31 | Vibration damper for marine diesel engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6159037A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04102644U (en) * | 1991-02-08 | 1992-09-04 | 川崎重工業株式会社 | Self-propelled crushing unit |
| US8066602B2 (en) | 2001-11-06 | 2011-11-29 | Borgwarner Inc. | Tension-reducing random sprocket |
| US8303444B2 (en) | 2001-11-27 | 2012-11-06 | Litens Automotive Partnership | Synchronous drive apparatus and methods |
-
1984
- 1984-08-31 JP JP18230484A patent/JPS6159037A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04102644U (en) * | 1991-02-08 | 1992-09-04 | 川崎重工業株式会社 | Self-propelled crushing unit |
| JPH0719556Y2 (en) * | 1991-02-08 | 1995-05-10 | 川崎重工業株式会社 | Self-propelled crushing unit |
| US8066602B2 (en) | 2001-11-06 | 2011-11-29 | Borgwarner Inc. | Tension-reducing random sprocket |
| US8303444B2 (en) | 2001-11-27 | 2012-11-06 | Litens Automotive Partnership | Synchronous drive apparatus and methods |
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