JPS61110698A - Power plant - Google Patents
Power plantInfo
- Publication number
- JPS61110698A JPS61110698A JP22898084A JP22898084A JPS61110698A JP S61110698 A JPS61110698 A JP S61110698A JP 22898084 A JP22898084 A JP 22898084A JP 22898084 A JP22898084 A JP 22898084A JP S61110698 A JPS61110698 A JP S61110698A
- Authority
- JP
- Japan
- Prior art keywords
- engine
- exhaust gas
- output
- generator
- gas turbine
- 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
Links
Landscapes
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
Abstract
Description
【発明の詳細な説明】
[産業上の利用分野1
本発明は動力プラントに係り、特に機関等の動力の一部
で運転される軸駆動発電システムを備えた動力プラント
に、機関の排ガスエネルギ等を回収して機関や発電機へ
動力を伝達する拮ガスタービン雪の補助動力源4に罎1
141.“際しく、高効率な設備配置とtl+宋的/2
省1ネル1゛化4: ’rt成する動力ブラン1へにl
!l 1ろ。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field 1] The present invention relates to a power plant, and particularly to a power plant equipped with a shaft-driven power generation system that is operated using part of the power of an engine, etc. An auxiliary power source for the gas turbine that collects snow and transmits power to the engine or generator.
141. “Excellent, highly efficient equipment layout and TL+Song style/2
Saving 1 channel 1゛ conversion 4: 'rt to form power branch 1 l
! l 1ro.
[従来の技術]
一般にvJ動力プラント殊に舶用の勤カグラントにあっ
ては、省エネルギ化を達成する!、:めに秤ノ?の方策
が講じられているが、での中に1月ガスタービンを設備
するものが捷案されている、。[Prior Art] In general, VJ power plants, especially marine power plants, achieve energy savings! , : Menibaino? Measures are being taken, and among them, the installation of a gas turbine is being devised.
一般的構成としては第3図に示すように、111進器a
を駆動するための機関すから排出される溝気ガスで排ガ
スタービンCを駆動させ、ぞの駆動力を動力伝達系dを
介して機関りの出力軸eに伝j!するようになっている
。As shown in Figure 3, the general configuration is as follows:
The exhaust gas turbine C is driven by the exhaust gas discharged from the engine for driving the engine, and its driving force is transmitted to the output shaft e of the engine via the power transmission system d. It is supposed to be done.
ところでこのような初ガスタービンCを利用した排ガス
エネルギの回収システムにあっては、排ガスタービンC
の出力軸fと機関すの出力軸eとの間に排ガスタービン
Cを設備するためにl!Ir力伝達力伝達系膜する必要
がある。また機関りの出力軸eが低速回転であるのに対
し、排ガスタービンCの出力軸fは極めて高い回転速度
で駆動されていることかI)3J:速n9の増設が必要
と<Kる。更に機関りは捩1′)振動を生じていること
から、この振動がIJIガスタービンC側へ伝達されな
いように振動を吸収ざIJるための流体継手り等をにQ
IJな1ノればならイfい。By the way, in the first exhaust gas energy recovery system using gas turbine C, exhaust gas turbine C
In order to install an exhaust gas turbine C between the output shaft f of the engine and the output shaft e of the engine l! Ir force transmission force transmission system membrane is required. In addition, while the output shaft e of the engine rotates at a low speed, the output shaft f of the exhaust gas turbine C is driven at an extremely high rotation speed. Furthermore, since the engine produces torsional vibration, a fluid coupling, etc., is installed to absorb the vibration so that this vibration is not transmitted to the IJI gas turbine C side.
If it's IJ, it's okay.
従って排ガスタービンCの設備のkめにイニシャル]ス
1〜が極めて^くなるという問題が、b−)tこ1゜と
ころで近([舶用プラントにあつlは、第4図に承りよ
うに省エネルギ化を更に111)任1tべ(軸駆動発電
シス7ノを11+AIこbのが大月1 (+)さ1′;
るに1ゝつている。Therefore, the problem that the exhaust gas turbine C equipment's kth (initial) 1 ~ becomes extremely large is b-) t is very close to 1 degree ([l in a marine plant, as shown in Figure 4). Further energy generation 111) 1t (shaft drive power generation system 7 no 11 + AI this b is Otsuki 1 (+) sa 1';
There is one in every corner.
軸駆動発電シスツム(1、機関1)にH転駆◆11さ1
1その動力を111進器al\1ム徨・;イ)Iごめの
出り回転軸eから山中シリiに」、り動力の 部を取り
出して1M動軸、N、:すλ、これに連結さ1+、 /
、−発電^kを運転さけるもので”+hる。Shaft drive power generation system (1, engine 1) is H-driven ◆11S1
1) Transfer the power from the output rotating shaft e to the Yamanaka series i, and take out the power part and write it as the 1M moving axis, N: λ, this. connected to 1+, /
, ``+h'' by avoiding the operation of power generation ^k.
この軸駆動発電システム1こに 11ば、1.Y来補機
類を駆動さlるために別個独立に必要どされていた電力
源(発wi機)を廃IIヌ1.1削減でさ、膜幅の簡略
化、ランニンゲー1ストの低減等を図ることがて・きる
。This shaft drive power generation system 1.1. Eliminates the need for power sources (generators) that were previously required separately to drive auxiliary equipment, simplifies the membrane width, reduces the number of running strokes, etc. It is possible to aim for
ぞしてこのJ、うな軸駆動発電シス7ノいにIjlガス
タービンCを装着して1月ガス■ネルギを回収し、省エ
ネルギ化を達成しようどする提案に、 f+願昭52−
67788弓がある。本提案は発電l!にのljl閏b
lI!11と反対側に、発電機Rに直列に撲ガスタービ
ンCを連結して構成されている。Therefore, in response to this proposal to install an eel-shaft drive power generation system 7-Ijl gas turbine C to recover gas energy and achieve energy savings, I received the f+ request.
There are 67,788 bows. This proposal is for power generation! ljl leap b
lI! On the opposite side to 11, a gas turbine C is connected in series to a generator R.
[発明が解決しようとする問題点] ところで排ガスタービンCをi!!1備ηる際に(ま。[Problem that the invention attempts to solve] By the way, exhaust gas turbine C is i! ! When I prepare one (ma).
上述したように排ガスタービンCのIご砧の動力伝達系
d、減速fj!o及び振動吸収のために流体継手り等の
設備が要求される(第3図)。As mentioned above, the power transmission system d of the exhaust gas turbine C, the reduction speed fj! Equipment such as fluid couplings is required to absorb vibrations and vibrations (Figure 3).
ここに第1図に示した軸駆動発電システムを備えた動力
プラントにあって(まIII)fスタービンC4設備す
る際、ムともと発電機1(への振動伝達をF/+止する
ために1幾関bl111どの間1.7配設さねる弾1り
継手り等を排ガスタービンCに兼用できる利Ij謙があ
る。Here, in a power plant equipped with the shaft-driven power generation system shown in Fig. 1, when installing the f-turbine C4, it is originally necessary to stop vibration transmission to the generator 1. There is an advantage that a tongue-and-groove joint or the like can be used for the exhaust gas turbine C as well.
しかしイ丁がら次の31うイ「四L’l’l +j、i
S tlリ−、/、−、。However, the next 31 ui ``4 L'l'l +j, i
S tl Lee, /, -,.
■発′I11機にの回転速麿と171万スクーピンCの
回転速a i、を相当安<Tるためこれら間に減速機9
を設ける必要がある。■In order to reduce the rotational speed of the 11 aircraft from the starting point and the rotational speed of the 1.71 million scoop C, the reduction gear 9 is placed between them.
It is necessary to provide
■ 減31機9が介設されることから、発電機1(側と
排ガスタービンC側とに回転軸!、[を大ノン別個に必
要とづる。■ Since the 31 engine 9 is installed, separate rotating shafts are required for the generator 1 (side) and the exhaust gas turbine C side.
■ 従って船内へ設置紬するときにこねら回転軸p。■ Therefore, when installing the pongee inside the ship, the kneading rotation axis p.
fの芯出し調整作業を全回なくされ据f=I ff業を
炉箱化させる。The centering adjustment work of f is completely eliminated and the installation f = I ff industry is converted into a furnace box.
■ また光11には機関り側−二111がスタービンC
側とに2本の回転軸m、βを、!Q備しイ目−)ればな
らない。■ Also, on the light 11, the engine side -2111 is the turbine C.
Two rotation axes m and β on the side and! Q must be prepared (A-).
■ 発電機にど111ノJスタービン04軸1) ln
l lJ肖911に配置するlこめ設備が良人化1する
。。■ Generator Nido 111 J Starbin 04 Axis 1) ln
The equipment installed at JSho 911 will be improved to 1. .
以上のように工;目16十困Hな問題がある。、1、/
J、■発電機にと機関す側及び1ガスタービンC側どの
間には、発電1ikの危急11.Sにその運転を゛佇1
1させるためのクラップn、pが介πグされる。このた
めy!電涙1(を保護するためにクラツー/11を切り
1lllnと、1lll継続して駆φカされる排ガスタ
ービンCからの■ネルギ回収を行なえなく<’iる。As mentioned above, there are 160 problems. ,1,/
J, ■ between the generator and the engine side and the gas turbine C side, there is an emergency 11. of the power generation 1ik. Let S drive that way.
Claps n and p are used to make the signal 1. For this reason y! In order to protect the electrolyte 1 (1), the exhaust gas turbine C, which is continuously driven, becomes unable to recover energy.
■ またクラッチpを切り頗すことにJ、リフ−1−ン
負荷(発電elk )が消失し、排ガスタービンCが過
回転される虞れがある。(2) Furthermore, when the clutch p is disengaged, the reflex load (power generation elk) is lost, and there is a risk that the exhaust gas turbine C may be over-rotated.
以、トのように省エネルギ化を達成する上からも不満足
なものど考えられる。The following can be considered to be unsatisfactory from the point of view of achieving energy saving, such as (g).
[発明の目的]
本発明は上述したような問題点に鑑みて創案されたもの
であり、その目的は機関等の動力の一部で運転さねる軸
駆動発電システムを備えた動力プラントに、111間の
排ガスエネルギ等を回収しU III関や発電機へ動力
を伝3t!する撲ガスタービン等の補助動力源を装備す
るに際して、高効串′/1設備配置と効果的な省エネル
ギ化を図ることができる動力プラントを提供するにある
。[Object of the Invention] The present invention was devised in view of the above-mentioned problems, and its purpose is to provide a 111 The exhaust gas energy, etc. between the two is recovered and power is transmitted to the U III engine and generator. To provide a power plant capable of achieving a highly effective skewer/1 equipment arrangement and effective energy saving when equipped with an auxiliary power source such as a gas turbine.
[発明の概要]
本発明は軸駆動発電システムを構成づる周波数制御手段
に並列に補助動力源を設け、その出力端を機関側に設G
プられた振動吸収1段の出り側と発電機側に設けられた
周波数制御手段の人力鋼との間に接続したものである。[Summary of the invention] The present invention provides an auxiliary power source in parallel with the frequency control means that constitutes the shaft drive power generation system, and the output end of the power source is provided on the engine side.
It is connected between the output side of the first stage of vibration absorption and the manual steel of the frequency control means provided on the generator side.
[実施例1
以下に本発明の好適 実施例を塩11図面にIIY−っ
で詳述する。[Example 1] A preferred embodiment of the present invention will be described below in detail with reference to the drawing IIY-1.
第1図に示づように、1 tit n閏であり、この機
関1には推進器2を駆動するために機関動りを伝達する
ための出力回転軸3が連結される。As shown in FIG. 1, the engine is a 1 tit n leap, and an output rotating shaft 3 for transmitting engine motion to drive a propulsion device 2 is connected to this engine 1.
そしてこの出力回転軸3には、これに、!H−jられた
歯車4に、機関動力の一部を取り出Jkめの動力取出歯
巾5が噛合されて上述したと同様な軸駆動発電システム
が接続される。And this output rotation shaft 3 has this! A shaft-driven power generation system similar to that described above is connected to the H-j gear 4, which is meshed with a Jk-th power extraction tooth width 5 for extracting a part of the engine power.
この軸駆動発電システムは、主として動力取出歯車5に
連結されて取り出された機関動力の一部を伝達するため
の動力伝達系6と、その動力伝達系6に連結され伝達さ
れる動力で運転される発電機7とから構成される。殊に
本発明にあっては発電11!7の入力側となる動力伝達
系6には、発電機7の周波数を制御するために動力取出
歯車5側からの入力回転数、即ち機関側回転数に対して
発電1117側への出力回転数を制御するための周波数
制御手段8が設置Jられる。この周波数制御手段8につ
いて)ボベると、発電機7は一定周波数を1rノるI、
−めに定速回転される必要があり、これに対して舶用機
関等は波浪等の外乱により回転数が頻繁に変動する。こ
のため介mtff7と機関1側とを連結Aる動力伝達系
6には発電機7の出力回転数を定)中色するように制御
し、発電機の周波数を制御4るために周波数制郊丁fi
t flが3Q l−1られる。この周波数制御手段は
第2図に示tJ、うに、n #JI 3!+111山中
機構9ど油F[回路系10ど/)口)T I=C4S’
+成さ1′+6゜差動遊?南11機構9(1内N1山中
15の外周部に形成された外歯11(こ11動回転入力
歯中12が噛合される。この入力歯車12は回転数変動
をQ 11つつ駆動力を伝達する遊甲歯中13の公転迷
1aを増減変更させて太陽南中14の出力回転数を定速
化させるために、内歯歯fl! 15を増減速したり1
F逆転駆動させるものである。This shaft drive power generation system is mainly operated by a power transmission system 6 connected to a power extraction gear 5 to transmit a part of the extracted engine power, and the power connected to the power transmission system 6 and transmitted. It consists of a generator 7. In particular, in the present invention, the power transmission system 6 which is the input side of the power generation 11!7 has an input rotation speed from the power take-off gear 5 side, that is, the engine side rotation speed, in order to control the frequency of the generator 7. A frequency control means 8 is installed for controlling the output rotation speed to the power generation 1117 side. Regarding this frequency control means 8) When the frequency control means 8 is turned, the generator 7 has a constant frequency of 1r,
- It is necessary to rotate at a constant speed, whereas the rotation speed of marine engines frequently fluctuates due to disturbances such as waves. For this reason, the power transmission system 6 that connects the intermediary mtff 7 and the engine 1 side is controlled so that the output rotation speed of the generator 7 is constant), and the frequency control system 6 is used to control the frequency of the generator 4. Ding fi
t fl is 3Q l-1. This frequency control means is shown in FIG. 2. +111 Yamanaka Organization 9 Do Oil F [Circuit System 10 Do/) Port) T I=C4S'
+Size 1'+6゜differential play? South 11 mechanism 9 (1 inside N1 External tooth 11 formed on the outer periphery of Yamanaka 15 (this 11 dynamic rotation input tooth 12 is meshed with it. This input gear 12 transmits driving force while suppressing rotational speed fluctuations Q 11 In order to increase or decrease the revolution 1a of the floating tooth middle 13 and make the output rotation speed of the sun south middle 14 constant, the internal tooth fl! 15 is increased or decelerated.
F is driven in reverse.
この内歯歯巾15を作動ざ1!る入力歯車12の駆動制
御は油圧回路系10によって行なわれる。Activate this internal tooth width 15! Drive control of the input gear 12 is performed by the hydraulic circuit system 10.
図示されない回転数検出手段によって検出され!ご発電
機7への出力回転数が検出信号として可変油圧ポンプ1
6の傾転色量1−ボユニツ1〜(図示せず)に投入され
る。ここに油圧ポンプ16は動力伝達系6から歯車22
を介して動力を与えられて駆動される構成となっており
、サーボコニツ1へにJ:り検出信号に応じて正逆運転
、吐出油■の制御が行なわれるようになっている。(の
結果油圧ポンプ16から作動油の給υ1を受けて作動さ
れる油圧モータ17が制御され入力歯車12が回転駆チ
11されるようになっている。Detected by rotation speed detection means (not shown)! The output rotation speed to the generator 7 is used as a detection signal for the variable hydraulic pump 1.
6, the tilted color amount 1-units 1~ (not shown) are inputted. Here, the hydraulic pump 16 connects the power transmission system 6 to the gear 22.
It is configured to be driven by being supplied with power via the servo unit 1, and forward/reverse operation and control of the discharged oil are performed in response to a detection signal sent to the servo unit 1. (As a result, the hydraulic motor 17, which is operated by receiving hydraulic oil υ1 from the hydraulic pump 16, is controlled, and the input gear 12 is driven to rotate 11.
このように構成された周波数制御手段8と、機関1の出
力回転軸3との間、図示例にあ−)では動力取出歯車5
どの間には、機関1側からの捩り振動を吸収させるため
に弾性継手等の振動吸収手段18が設けられる。Between the frequency control means 8 configured in this way and the output rotating shaft 3 of the engine 1, there is a power takeoff gear 5 in the illustrated example.
A vibration absorbing means 18 such as an elastic joint is provided between the two to absorb torsional vibration from the engine 1 side.
他方、周波数υl1llf段8の出力側と発?t[7と
の間には、動力伝達系6と発電llll7の入力軸7a
とを接続し切り+Wtすためのクラッチ19が設+−J
られる。以上のように構成された軸駆φ11発電システ
ムに対し、劃1にはぞの排気マニホールド1aに連結さ
れた1周ガス供給系20を介して補助IJ+ iJ−〇
−
源たる排ガスタービン21が接続i%ねる。JのIIガ
スタービン21は(層間1の171 )fスTネル1゛
4回収するものである。On the other hand, the output side of the frequency υl1llf stage 8 and the output side? t[7, there is an input shaft 7a between the power transmission system 6 and the power generation llll7.
A clutch 19 is provided to connect and disconnect +Wt.
It will be done. For the shaft-driven φ11 power generation system configured as described above, an exhaust gas turbine 21 which is an auxiliary IJ+ iJ-〇- source is connected to the auxiliary IJ+ iJ-〇- source through a one-circle gas supply system 20 connected to the exhaust manifold 1a. i%neru. The J II gas turbine 21 (interlayer 1, 171) recovers 1 to 4 fs T channels.
この排ガスタービン21は1述し!ご周波n lal
611手段8に並列に 体内に股l111さhろ1゜即
ち、籾がスタービン21 +、1周波数制till l
’ I’Q nの側部に配置されて全体どして幅乃〒1
!′liさ島!法が増加するも、長手方向(1法が延に
さねイ1い(8成Iなっている。This exhaust gas turbine 21 has been described above! Frequency n lal
611 parallel to means 8 in the body 1 11 1 degree, that is, the paddy is stirred by the turbine 21 +, 1 frequency control till l
'I'Q placed on the side of the
! 'lisa island! Although the number of methods increases, the number of methods increases in the longitudinal direction (one method increases in number (8 times)).
そしてこの」ガスタービン21の出力端21aは振動吸
収手段18の出力側で周波数制御1段Bの入力側に接続
される。図示例にあっては出力端21aは、クーピン出
力軸に設けられた歯巾で構成され、油圧ポンプ16に動
力を与えるための歯車22に噛合されて動力伝達系6に
接続される。The output end 21a of the gas turbine 21 is connected to the output side of the vibration absorbing means 18 and to the input side of the frequency control first stage B. In the illustrated example, the output end 21a is constituted by a tooth width provided on a coupin output shaft, and is connected to the power transmission system 6 by meshing with a gear 22 for providing power to the hydraulic pump 16.
従って排ガスタービン21はllI閏1側との間に振動
吸収手段18が介設された構成になっている。Therefore, the exhaust gas turbine 21 has a structure in which a vibration absorbing means 18 is interposed between the exhaust gas turbine 21 and the lllI leap 1 side.
また周波数制御手段8の出力側と発電成7との間に介設
されるクラッチ1つよりも前段で動力伝達系6に接続さ
れ、クラッチ19の断続に関わらず、常に少なくとも機
関1側に接続された構成となっている。Also, it is connected to the power transmission system 6 at a stage before one clutch interposed between the output side of the frequency control means 8 and the power generator 7, and is always connected to at least the engine 1 side regardless of whether the clutch 19 is engaged or disconnected. The configuration is as follows.
また彷ガスタービン21はイの出力端21aが、機関1
の出力回転輪3の回転速度を増速さける動力取出歯車5
により比較的高速で回転される歯車22に直接噛合され
る構成となっている。In addition, the output end 21a of the gas turbine 21 is connected to the engine 1.
A power take-off gear 5 for increasing the rotational speed of the output rotating wheel 3
The structure is such that the gear 22 is directly meshed with the gear 22 which is rotated at a relatively high speed.
尚、機関1の排気マニホールド1aには、嶺閏への吸入
空気を加圧するための排ガスターボ過給ta23が設G
Jられる。また発Wi機7に11機簡1からのり」力が
入力される側と反対側に蒸気タービン24が設番ノられ
る。蒸気タービン24は例えば機関1のIJI 1Fλ
熱で発生させた蒸気で駆動され、(の熱を回収して更に
省エネルギ化を達成するしのであるが、本発明にあって
は排ガスターボ過給機23、蒸気タービン24の設備は
必要不可欠な構成ではない。Incidentally, the exhaust manifold 1a of the engine 1 is equipped with an exhaust gas turbocharger ta23 for pressurizing the intake air to the ridge.
J is done. In addition, a steam turbine 24 is installed on the side opposite to the side where the force from the 11 machine 1 is input to the departure machine 7. The steam turbine 24 is, for example, IJI 1Fλ of the engine 1.
It is driven by steam generated by heat, and further energy saving is achieved by recovering the heat of It's not a good structure.
次に作用について述べる。Next, we will discuss the effect.
通常航行時にあってはII閏動力t;口よとんど推)1
器2に供給され出力回転軸3から一部が軸駆動発電シス
テムに供給される。これに際し、本発明にあっでは、機
関1の排ガスJネルI!轡の鋳熱を利用して駆動される
排ガスタービン21vIの補助動力源を備え、回収した
朔ガスJネルギを枡ガスタービン21から発電機7へ補
うことができる。従って機関1側から取り出さねるべき
動力を軽減させて省エネルギ化を達成できる。殊に本発
明にあっては、排ガスタービン21の出力端21aをク
ラッチ19前段の周波数制御手段8の入力側に接続した
ので、例えば発ff1lff7の危急時クラップ19を
切り離すことがあっても排ガスタービン21の出力は動
力伝達系6から出力回転軸3へと;!元され、機関動力
を補うことができ、有効に措ガスタービン21の機能を
発揮させて一!分<K省エネルギ化を達成できる。また
クラッチ19を切り離しても排ガスタービン21は機関
1側に接続さf;ているので無負荷とくすることはなく
、過回転を1口にできる。During normal navigation, II leaping power (t);
A portion is supplied to the shaft drive power generation system from the output rotating shaft 3. In this case, according to the present invention, the exhaust gas of the engine 1! An auxiliary power source is provided for the exhaust gas turbine 21vI that is driven by using the casting heat of the tank, and the collected gas J energy can be supplemented from the tank gas turbine 21 to the generator 7. Therefore, it is possible to reduce the power that must be extracted from the engine 1 side, thereby achieving energy savings. In particular, in the present invention, the output end 21a of the exhaust gas turbine 21 is connected to the input side of the frequency control means 8 at the front stage of the clutch 19, so that even if the clamp 19 is disconnected in an emergency of ff1lff7, for example, the exhaust gas turbine The output of 21 is transmitted from the power transmission system 6 to the output rotating shaft 3;! It is possible to supplement the engine power and effectively utilize the functions of the gas turbine 21! min<K energy saving can be achieved. Further, even if the clutch 19 is disengaged, the exhaust gas turbine 21 is connected to the engine 1 side, so there is no problem with no load, and overspeed can be reduced to one point.
他方、動力プラントの設備配訪としてl、■’It )
Iスタービン21を周波数制御手段8の側部に並行に配
置したことによりSQ Wkの長大化を防111・て
1ンパクトな構成となり、一体内な構造どして据付作業
性も向上できる。また従来のように、発電機7と排ガス
タービン21を直列に設けるためには別途芯出し作業を
要求されるが、本発明の構成によれば、排ガスタービン
21は歯車等で周波数制御手段8の入力側に接続すれば
良く、この面からも設置B作業を容易化できる。On the other hand, as a visit to power plant equipment,
By arranging the I turbine 21 in parallel to the side of the frequency control means 8, the length of the SQ Wk can be prevented.
It has a compact configuration, and the integrated structure improves installation workability. Furthermore, as in the past, a separate centering operation is required in order to install the generator 7 and the exhaust gas turbine 21 in series, but according to the configuration of the present invention, the exhaust gas turbine 21 is connected to the frequency control means 8 using a gear or the like. It suffices to connect it to the input side, which also simplifies installation B.
他方、発1’!!11ff7のための振動吸収手段18
を排ガスタービン用として箱用できるので設備を簡略化
できる。また、排ガスタービン21の出力端21aを比
較的高速回転される周波数l1lIIl1手段8の入力
側に連結したことにより排ガスタービン21の出力軸側
に減速機を介設することも必要としない。On the other hand, release 1'! ! Vibration absorbing means 18 for 11ff7
The equipment can be simplified because it can be used as a box for the exhaust gas turbine. Further, since the output end 21a of the exhaust gas turbine 21 is connected to the input side of the frequency l1lIIl1 means 8 that rotates at a relatively high speed, it is not necessary to provide a speed reducer on the output shaft side of the exhaust gas turbine 21.
更に、発電機7は機関1側への入力軸のみを設備すれば
良く、従来のように2軸を必要としない。Furthermore, the generator 7 only needs to be provided with an input shaft to the engine 1 side, and does not require two shafts as in the conventional case.
以上のことから、設面配置上、極れたスペースセービン
グと設備の簡略化を達成でき延いてはコストダウンを達
成できる。From the above, it is possible to achieve extreme space saving and simplification of equipment in terms of layout, and by extension cost reduction.
また振動対策上の観点から、振動吸収手段181ス降の
構成はlfl竹質■が人であることが好ましく、これに
対し排ガスタービン2が宵与し1qる。更に常に排ガス
タービン出力が補われる動力伝達系6では、負荷が軽減
され、動力取出のための動力取出歯車5等の歯車系強度
を小さくすることし可能である。Further, from the viewpoint of vibration countermeasures, it is preferable that the structure of the vibration absorbing means 181 is made of bamboo material, whereas the exhaust gas turbine 2 is provided with a material of 1q. Furthermore, in the power transmission system 6 where the output of the exhaust gas turbine is always supplemented, the load is reduced, and it is possible to reduce the strength of the gear system such as the power extraction gear 5 for extracting power.
尚、排ガスタービン21の出力軸には、クラッチを設け
ても良い。Note that a clutch may be provided on the output shaft of the exhaust gas turbine 21.
[発明の効!i!1
以上要するに本発明によれば次のごとき…ねた効果を発
揮する。[Efficacy of invention! i! 1. In summary, the present invention provides the following effects.
[111jJ閏の排ガス、1ネルギを回収する拮ガスタ
ービン等の補助動力源を機関側と発電機との間を接続す
る動力伝達系に連結1)たことにJ:す、機関動力を補
うことができ、省1ネルギ化を達成できる。殊に本発明
にあっては、動力伝達系の周波数制御手段の入力側に補
助動力源の出力端を連結したので、発電機の危急時等に
関わら・r、常に回収された排ガスTネル1′等をIf
fff前の軽減に寄与さ1遍ることができ、イj2!;
な省1ネル1゛11コを達成でさる。[111j Connecting an auxiliary power source such as a gas turbine that recovers the exhaust gas and energy of the engine to the power transmission system that connects the engine side and the generator 1) To supplement the engine power. can achieve energy savings. In particular, in the present invention, since the output end of the auxiliary power source is connected to the input side of the frequency control means of the power transmission system, regardless of the emergency situation of the generator, the recovered exhaust gas T channel 1 is always ′ etc. If
It is possible to contribute to the reduction before fff, and it is j2! ;
Achieved 11 points in one channel.
+2+ 補助チ;ノ))源は常に負荷を負う構成であ
るから、発電1幾の危急時等にあっても無負荷となるこ
とはむく過回転等補助動力源の損傷を防1にできる。+2+ Since the auxiliary power source is configured to always carry a load, damage to the auxiliary power source such as over-speeding can be prevented by preventing it from being unloaded even in times of emergency when generating power.
(3) 補助動力源を周波数制御手段に並列に配置し
!このτ゛、装置の長大化を防11−できスペースレー
ビングヘ;!成できる。殊に舶用設備にあっては1ま人
生による鉛白スペースの削減等を防止でき、極めて有効
である。(3) Place the auxiliary power source in parallel with the frequency control means! This τ゛ prevents the equipment from becoming too long and allows space raving;! Can be done. Particularly in marine equipment, it is extremely effective because it prevents the lead space from being reduced due to the single life.
(4) 補助動力源と周波数III al1丁段どの
並設により、体内な#A装構成どすることができ、また
従来番、−お(!る17列配置による発電機と補助動力
源の、iミ、出し作業等をII して可及的に据付作業
性を向I゛(゛さる。(4) By arranging the auxiliary power source and the frequency III al1 stage in parallel, it is possible to create #A configuration inside the body. I will improve the installation workability as much as possible by doing the installation work, etc.
C・I) 補助φIツカ河;を周波数制御手段の入力側
に接続+するJ、うにしたので、従来のように発?i機
を2軸(8成とりる必要がなく、]ス1〜ダウンを図れ
る。C・I) Since I connected the auxiliary φI to the input side of the frequency control means, I can't generate it as before. It is possible to make the i machine 2-axis (no need for 8-axis, 1-axis down).
6) 補助動力源の出力端を、比較的^速回転される周
波数2−制御手段の入力側に接続したので、減速Ifi
等を排して直結でき設備の簡略化を図れる。6) Since the output end of the auxiliary power source is connected to the input side of the frequency 2-control means that rotates at a relatively fast speed, the deceleration Ifi
It is possible to simplify the equipment by eliminating the need for direct connection.
(7) 補助動力源の出力端を発電機のための賑ナノ
」吸収手段の出力側に接続したので、補助動力源のため
に別途振動吸収1段の設舗轟を必要とせずコストダウン
を図れる。(7) Since the output end of the auxiliary power source is connected to the output side of the noise absorption means for the generator, there is no need to install a separate vibration absorbing stage for the auxiliary power source, reducing costs. I can figure it out.
(印 振動吸収手段の出力側−Cyl!電■、周波数制
御手段の入力側にIJIガスタービンを配置ff L
/こので、動力伝達系の慣t’l″¥!ffflを増加
さL! (Ik<動対策」二有利である。(Mark: IJI gas turbine is placed on the output side of the vibration absorption means - Cyl! Electric ■, and the input side of the frequency control means ff L
/This increases the inertia t'l''\!fffl of the power transmission system L! (Ik<dynamic countermeasure) is advantageous.
(9) 常に刊ガスタービンの出力な* 1+111
111に補λるので、動力の一部を出力回転軸か−)取
り出すための動力取出山中等のC″J荷を軒緘でさ、こ
れらの強度設計を緩やかなものに(・さる。(9) The output of the gas turbine is always 1+111.
111, the C''J load such as the power extraction mountain for extracting a part of the power from the output rotating shaft is installed in the eaves, and the strength design of these is made gentle.
【図面の簡単な説明】
第1図は本発明の好適一実施例を示す系統図、第2図は
要部拡大概略斜視図、第3図及び第4図は従来例を示す
系統図である。
図中、1は611L3は出力回転軸、7は発電機、8は
周波数か」卸手段、18は振動吸収1段、21は補助動
力源と1)で例示し1C排ガスタービンである。[Brief Description of the Drawings] Fig. 1 is a system diagram showing a preferred embodiment of the present invention, Fig. 2 is an enlarged schematic perspective view of main parts, and Figs. 3 and 4 are system diagrams showing a conventional example. . In the figure, 1 is 611L3 is an output rotating shaft, 7 is a generator, 8 is a frequency output means, 18 is a vibration absorbing stage 1, 21 is an auxiliary power source, and 1) is a 1C exhaust gas turbine.
Claims (1)
される発電機と、該発電機の入力側に設けられ該発電機
の周波数を制御するために出力回転数を制御する周波数
制御手段と、該周波数制御手段と上記出力回転軸との間
に設けられ振動を吸収するための振動吸収手段と、上記
周波数制御手段に並列に設けられその出力端が上記振動
吸収手段の出力側で上記周波数制御手段の入力側に接続
された補助動力源とを備えたことを特徴とする動力プラ
ント。A generator operated with part of the power extracted from an output rotating shaft of an engine, etc., and a frequency control means provided on the input side of the generator to control the output rotation speed in order to control the frequency of the generator. , a vibration absorbing means provided between the frequency control means and the output rotating shaft for absorbing vibration; and a vibration absorbing means provided in parallel with the frequency control means, the output end of which is provided on the output side of the vibration absorbing means to absorb the vibration. A power plant comprising: an auxiliary power source connected to the input side of the control means.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22898084A JPS61110698A (en) | 1984-11-01 | 1984-11-01 | Power plant |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22898084A JPS61110698A (en) | 1984-11-01 | 1984-11-01 | Power plant |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS61110698A true JPS61110698A (en) | 1986-05-28 |
JPH0574518B2 JPH0574518B2 (en) | 1993-10-18 |
Family
ID=16884881
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP22898084A Granted JPS61110698A (en) | 1984-11-01 | 1984-11-01 | Power plant |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS61110698A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6353200A (en) * | 1986-08-21 | 1988-03-07 | ゲブリユ−ダ− ズルツア− アクチエンゲゼルシヤフト | Marine propulsion plant with generator for supplying inboard power |
JP2010264867A (en) * | 2009-05-14 | 2010-11-25 | Mitsubishi Heavy Ind Ltd | Propulsion device and marine vessel including the same |
JP2011131692A (en) * | 2009-12-24 | 2011-07-07 | Mitsubishi Heavy Ind Ltd | Engine control system of ship |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60226393A (en) * | 1984-04-24 | 1985-11-11 | Takashi Takahashi | Urgent driving apparatus for main engine installed onto shaft generator |
-
1984
- 1984-11-01 JP JP22898084A patent/JPS61110698A/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60226393A (en) * | 1984-04-24 | 1985-11-11 | Takashi Takahashi | Urgent driving apparatus for main engine installed onto shaft generator |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6353200A (en) * | 1986-08-21 | 1988-03-07 | ゲブリユ−ダ− ズルツア− アクチエンゲゼルシヤフト | Marine propulsion plant with generator for supplying inboard power |
JP2010264867A (en) * | 2009-05-14 | 2010-11-25 | Mitsubishi Heavy Ind Ltd | Propulsion device and marine vessel including the same |
JP2011131692A (en) * | 2009-12-24 | 2011-07-07 | Mitsubishi Heavy Ind Ltd | Engine control system of ship |
Also Published As
Publication number | Publication date |
---|---|
JPH0574518B2 (en) | 1993-10-18 |
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