JPS62294724A - Turbine casing cooler for turbocharger - Google Patents
Turbine casing cooler for turbochargerInfo
- Publication number
- JPS62294724A JPS62294724A JP61138200A JP13820086A JPS62294724A JP S62294724 A JPS62294724 A JP S62294724A JP 61138200 A JP61138200 A JP 61138200A JP 13820086 A JP13820086 A JP 13820086A JP S62294724 A JPS62294724 A JP S62294724A
- Authority
- JP
- Japan
- Prior art keywords
- cooling water
- turbine
- turbocharger
- low
- temperature
- 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
- 239000000498 cooling water Substances 0.000 claims abstract description 61
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 25
- 238000001816 cooling Methods 0.000 claims description 14
- 238000001514 detection method Methods 0.000 claims 1
- 230000008646 thermal stress Effects 0.000 abstract description 10
- 239000000446 fuel Substances 0.000 description 19
- 210000004027 cell Anatomy 0.000 description 13
- 239000007789 gas Substances 0.000 description 11
- 210000005056 cell body Anatomy 0.000 description 3
- 238000010248 power generation Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000001590 oxidative effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000035882 stress Effects 0.000 description 2
- 239000002918 waste heat Substances 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000007800 oxidant agent Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/50—Fuel cells
Landscapes
- Fuel Cell (AREA)
Abstract
Description
【発明の詳細な説明】
３、発明の詳細な説明
［発明の目的］
（産業上の利用分野）
本発明は、例えば燃料電池発電プラントに用いられる２
段方式の昇圧用ターボチャージャシステムにおける改良
したターボチャージャのタービンケーシング冷却装置に
関する。[Detailed Description of the Invention] 3. Detailed Description of the Invention [Object of the Invention] (Field of Industrial Application) The present invention is directed to
The present invention relates to an improved turbocharger turbine casing cooling device in a stage-type boosting turbocharger system.
（従来の技術）
一般に燃料電池発電プラントにおいては、低圧タービン
および高圧タービンを備えた２段方式の昇圧用ターボチ
ャージャで低圧空気圧縮機よ３よび高圧空気圧縮機を駆
動し、その両圧縮機で昇圧した高圧の空気を酸化剤ガス
として燃料電池本体に供給することが行われている。(Prior Art) In general, in a fuel cell power plant, a two-stage boosting turbocharger equipped with a low-pressure turbine and a high-pressure turbine drives a low-pressure air compressor 3 and a high-pressure air compressor. Pressurized high-pressure air is supplied to the fuel cell main body as an oxidizing gas.
そして２段方式の昇圧用ターボチャージ髪・は、燃料電
池から排出された空気を燃焼器で燃料と混合して燃焼さ
−Ｕて１ｑられた高温高圧ガスを駆動源として使用する
もので、その燃焼器から出た高温高圧ガスを高圧タービ
ンで膨張させて仕事させて高圧空気圧縮機を駆動し”、
さらに高痒タービンを通過したガスを低圧タービンで再
度膨張させて仕事をさせて低圧空気圧縮機を駆動するよ
う系統構成され、低圧タービンで膨張し終った高温の排
熱は大気中へ放出される。The two-stage booster turbocharger uses the high-temperature, high-pressure gas produced by mixing the air discharged from the fuel cell with fuel in a combustor and burning it as a driving source. The high-temperature, high-pressure gas that comes out of the combustor is expanded in a high-pressure turbine to do work and drive a high-pressure air compressor.
Furthermore, the system is configured so that the gas that has passed through the high-pressure turbine is expanded again in the low-pressure turbine to do work and drive the low-pressure air compressor, and the high-temperature waste heat that has been expanded in the low-pressure turbine is released into the atmosphere. .
ターボチャージャが通常の運転状態に入った場合、高圧
タービンおよび低圧タービンケーシングは高温に暉され
る。このタービンケーシングの高温を防止するため（、
貯水タンクの冷却水を移送ポンプによって高圧タービン
および低圧タービンのケーシングに送って水冷すること
が行なわれている。そしてこの冷却後の高温になった冷
却水は、途中の冷却器で常温近くまで冷却されて貯水タ
ンク内に戻される。When the turbocharger enters normal operating conditions, the high pressure turbine and low pressure turbine casing are heated to high temperatures. To prevent this turbine casing from getting too hot (
Cooling water in a water storage tank is sent to the casings of a high-pressure turbine and a low-pressure turbine using a transfer pump for water cooling. After this cooling, the high-temperature cooling water is cooled down to near room temperature by an intermediate cooler and then returned to the water storage tank.
一方、２段ターボタヤージャの低圧空気圧縮機と高温空
気圧縮機との間に中間冷却器を設け、燃料電池本体に供
給される空気は、低圧空気圧縮機を出たあとに中間冷却
器で温度が下げられてから次段の高圧空気圧縮機へ送ら
れる。ところでこの中！冷却器の冷却水は、前記貯水タ
ンクより移送ポンプによって中間冷却器に入り、熱交換
による受熱後に前記途中の冷却器によって常温近くまで
下げられて再び貯水タンクに回収される。On the other hand, an intercooler is installed between the low-pressure air compressor and the high-temperature air compressor of the two-stage turbocharger, and the air supplied to the fuel cell body is cooled at the intercooler after leaving the low-pressure air compressor. After being lowered, it is sent to the next stage, a high-pressure air compressor. By the way, in this! The cooling water of the cooler enters the intercooler from the water storage tank by a transfer pump, receives heat through heat exchange, is lowered to near normal temperature by the intermediate cooler, and is recovered into the water storage tank again.
このようにターボチャージャのタービンケーシングの冷
却水系と中間冷却器の冷却水系を同一貯水タンク系によ
って構成している場合、ターボチャージャの高圧圧縮機
の効率を上げるためには、中間冷却器の冷却水入口温度
がなるべく低い方が良いため、タービンケーシングおよ
び中間冷却器から排出される冷却水を冷やす途中の冷却
器の冷却水設定温度はターボチャージャのタービンケー
シングの冷却水の最適温度より低い。すなわち、貯水タ
ンクの冷却水の温度は、タービンケーシングの冷却水と
しては低過ぎると云える。If the cooling water system for the turbocharger's turbine casing and the cooling water system for the intercooler are configured in the same water storage tank system, in order to increase the efficiency of the turbocharger's high-pressure compressor, it is necessary to Since it is better for the inlet temperature to be as low as possible, the cooling water setting temperature of the cooler in the middle of cooling the cooling water discharged from the turbine casing and intercooler is lower than the optimum temperature of the cooling water of the turbine casing of the turbocharger. That is, it can be said that the temperature of the cooling water in the water storage tank is too low to be used as cooling water for the turbine casing.
（発明が解決しようとする問題点）
しかして、このような燃料電池発電プラントに用いられ
る２段式の昇圧用ターボチャージャにおいては、タービ
ンケーシングの冷却水は、中間冷却器に使用される低温
の冷却水が直接使用されてケーシングを冷却することに
より、、タービンケーシング温度と冷却水温度との間に
１５０℃前後の温度差が存在することになり、この茗し
い温度差によってタービンケーシングに対して非常な熱
応力が生じていた。(Problem to be solved by the invention) However, in the two-stage boosting turbocharger used in such a fuel cell power generation plant, the cooling water of the turbine casing is the low-temperature water used in the intercooler. When cooling water is used directly to cool the casing, there is a temperature difference of around 150°C between the turbine casing temperature and the cooling water temperature, and this large temperature difference causes the turbine casing to Extreme thermal stress was occurring.
またターボチャージャの負荷の変化により、タービン入
口温度が上昇したり下降したりした場合でも、冷却水温
度は一定のためタービンケーシングと冷却水との温度差
に変化が生じ、タービンケーシングに熱応力が発生して
低サイクル疲労によるクラックが発生することがある。Furthermore, even if the turbine inlet temperature rises or falls due to changes in the turbocharger load, the cooling water temperature remains constant, so the temperature difference between the turbine casing and the cooling water changes, causing thermal stress to the turbine casing. Cracks may occur due to low cycle fatigue.
さらに低圧タービンより排出される排熱は、１５０℃前
後の温度がありながら、そのまま大気へ放出しているの
で熱が有効に利用されていなかった。Furthermore, the exhaust heat discharged from the low-pressure turbine has a temperature of around 150°C, but it is directly released into the atmosphere, so the heat is not used effectively.
本、発明の目的は、タービンケーシングと冷却水との温
度差を小さくし、タービンケーシングに付加される熱応
力による低サイクル疲労を軽減したターボチャージャの
タービンケーシング冷却装置を提供するにある。An object of the present invention is to provide a turbine casing cooling device for a turbocharger that reduces the temperature difference between the turbine casing and cooling water and reduces low cycle fatigue due to thermal stress applied to the turbine casing.
［発明の構成］
（問題点を解決するための手段および作用）本発明によ
るターボチャージャのタービンケーシング冷却装置は、
タービンで空気圧縮機を駆動する２段昇圧方式のターボ
チャージャにおいて、前記低圧タービンの排気、側に熱
交換器を設け、この熱交換器で熱交換後の冷却水をター
ビンケーシングに冷却水として通すことを特徴とするも
のである。[Structure of the Invention] (Means and Effects for Solving the Problems) The turbine casing cooling device for a turbocharger according to the present invention has the following features:
In a two-stage boosting turbocharger that uses a turbine to drive an air compressor, a heat exchanger is provided on the exhaust side of the low-pressure turbine, and the heat exchanger passes cooling water after heat exchange to the turbine casing as cooling water. It is characterized by this.
本発明においては、低圧タービンの排気側に設けた熱交
換器から出た熱交換器の冷却水をタービンケーシングに
冷却水として通すことにより、タービンケーシングと冷
却水との温度差を少なくして熱応力を軽減し、それによ
って熱応力による低サイル疲労を軽減することができる
。In the present invention, by passing the cooling water from the heat exchanger provided on the exhaust side of the low-pressure turbine through the turbine casing as cooling water, the temperature difference between the turbine casing and the cooling water is reduced and heat is generated. It can reduce stress and thereby reduce low sile fatigue due to thermal stress.
（実施例）
以下本発明の一実施例を燃料電池発電プラントに適用し
たターボチャージャの系統を示す第１図および第２図に
基づいて説明する。まず第１図に示す実施例において、
燃料電池発電プラントは低圧空気圧縮機１１および低圧
タービン１５よりなる第１段ターボチャージャＴ１．高
圧空気圧縮機１２および高圧タービン１４よりなる第２
段ターボチャージャＴ２および燃料電池本体１６を具備
し、燃料電池本体１６の酸化剤ガスとなる空気は、通常
の運転時において低圧空気圧縮機１１で加圧されたのち
、中間冷却器２０で温度が下げられ、さらに高圧空気圧
縮機１２で再加圧されて燃料電池本体１６に供給される
。(Embodiment) An embodiment of the present invention will be described below with reference to FIGS. 1 and 2 showing a system of a turbocharger applied to a fuel cell power generation plant. First, in the embodiment shown in FIG.
The fuel cell power plant includes a first stage turbocharger T1. A second unit consisting of a high pressure air compressor 12 and a high pressure turbine 14
Equipped with a stage turbocharger T2 and a fuel cell main body 16, the air that becomes the oxidant gas of the fuel cell main body 16 is pressurized by the low pressure air compressor 11 during normal operation, and then the temperature is lowered by the intercooler 20. The air is lowered, further pressurized again by the high-pressure air compressor 12, and then supplied to the fuel cell main body 16.
燃料電池本体１６から排出された高温高圧ガスは、燃焼
器１３で燃料と混合して燃焼せられ、高圧タービン１４
で膨張仕事に変換して高圧空気圧縮機１２に仕事を支え
、ざらに高圧タービン１４を通過したガスは、低圧ター
ビン１５で再度膨張仕事を行なって低圧空気圧縮機１１
に仕事を支える。そして低圧タービン１５で膨張し終っ
た高温の排熱は大気中へ放出される。The high-temperature, high-pressure gas discharged from the fuel cell body 16 is mixed with fuel and burned in the combustor 13, and the high-pressure turbine 14
The gas that has passed through the high-pressure turbine 14 undergoes expansion work again in the low-pressure turbine 15 and is then transferred to the low-pressure air compressor 11.
to support work. The high-temperature exhaust heat that has been expanded in the low-pressure turbine 15 is released into the atmosphere.
なお、以上の通常運転に入る前の起動時には、燃料電池
本体１６のバイパス回路のバイパス弁１６ａを開き、高
圧空気圧縮機１２で加圧された空気をバイパス弁１６ａ
から燃焼器１３に通し、この燃焼器１３で燃料と混合し
て高温高圧ガスとし、これをターボチャージャＴ１．Ｔ
２の駆動源として高圧タービン１４および低圧タービン
１５に供給する。そして空気系が運転条件に達するとバ
イパス弁１６ａを調整して高圧空気圧縮機１２から出た
空気の大部分を燃料電池本体１６に供給して通常の運転
状態に入る。In addition, at the time of startup before starting the above normal operation, the bypass valve 16a of the bypass circuit of the fuel cell main body 16 is opened, and the air pressurized by the high-pressure air compressor 12 is passed through the bypass valve 16a.
The gas is passed through the combustor 13, where it is mixed with fuel to form high-temperature, high-pressure gas, which is then fed into the turbocharger T1. T
The high-pressure turbine 14 and the low-pressure turbine 15 are supplied as a driving source for the high-pressure turbine 14 and the low-pressure turbine 15. When the air system reaches operating conditions, the bypass valve 16a is adjusted to supply most of the air discharged from the high-pressure air compressor 12 to the fuel cell main body 16, and the system enters a normal operating state.
一方ターボチャージャＴ１．Ｔ２の通常の運転状態に入
ると、高圧タービン１４および低圧タービン１５のケー
シングは高温にさらされる。そこで本発明においては、
低圧タービン１５の下流側に冷却水の温度を上昇させる
熱交換器１９を設け、この熱交換器１９に貯水タンク１
７の冷却水を移送ポンプ１８で送って高温の排熱ガスと
熱交換させる。そして熱交換器１９から出た冷却水と移
送ポンプ１８から出た冷却水を混合して低圧タービン１
５および高圧タービン１４のケーシングに送り、熱交換
したのちの冷却水を熱交換器２５で常温に低下させて貯
水タンク１７に回収するよう構成されている。On the other hand, turbocharger T1. Upon entering normal operating conditions at T2, the casings of the high pressure turbine 14 and the low pressure turbine 15 are exposed to high temperatures. Therefore, in the present invention,
A heat exchanger 19 for increasing the temperature of cooling water is provided downstream of the low-pressure turbine 15, and a water storage tank 1 is connected to this heat exchanger 19.
The cooling water from No. 7 is sent by a transfer pump 18 to exchange heat with the high-temperature exhaust gas. The cooling water discharged from the heat exchanger 19 and the cooling water discharged from the transfer pump 18 are then mixed to form a low-pressure turbine 1.
5 and the casing of the high-pressure turbine 14 for heat exchange, the cooling water is lowered to room temperature by a heat exchanger 25 and then collected in a water storage tank 17.
すなわち、移送ポンプ１８から出た冷却水は、熱交換器
１９を出てから流量調整弁２１から温度センサ２２を通
って低圧タービン１５のケーシングに送られる。ケーシ
ングで熱交換したのらの冷却水は、温度センサ２４を経
て熱交換器２５から貯水タンク１７に回収される。この
時低圧タービン１５のケーシングの入口には、熱交換器
１９から出た冷却水とは別に移送ポンプ１８から出た直
接の冷却水を流量調整弁２９を通して送られるようにな
っている。この両流ω調整弁２１．２９は温度センサ２
２．２４の信号を受けて制御装置２６からの指令によっ
て開度調整される。That is, the cooling water discharged from the transfer pump 18 exits the heat exchanger 19 and is then sent to the casing of the low pressure turbine 15 through the flow control valve 21 and the temperature sensor 22 . The cooling water that has undergone heat exchange with the casing passes through the temperature sensor 24 and is recovered from the heat exchanger 25 to the water storage tank 17. At this time, direct cooling water from the transfer pump 18 is sent to the inlet of the casing of the low-pressure turbine 15 through a flow rate regulating valve 29, in addition to the cooling water from the heat exchanger 19. This double-flow ω adjustment valve 21.29 is connected to the temperature sensor 2.
The opening degree is adjusted by a command from the control device 26 in response to the signal of 2.24.
同様に高圧タービン１４に対する冷却水系も、熱交換器
１９を出た冷却水を流量調整弁２３を通して送る系と、
移送ポンプ１８から出た冷却水を直接流量調整弁３０を
介して送る系とが並列にあり、この両流量調整弁２３．
３０は温度センサ２８．２７の信号を受けて制御装置２
６の指令によって開度調整される。Similarly, the cooling water system for the high-pressure turbine 14 includes a system that sends cooling water exiting the heat exchanger 19 through a flow rate adjustment valve 23;
There is a system in parallel with which the cooling water from the transfer pump 18 is directly sent via the flow rate adjustment valve 30, and both flow rate adjustment valves 23.
30 receives the signals from the temperature sensors 28 and 27 and controls the control device 2.
The opening degree is adjusted by the command No. 6.
また低圧空気圧縮）幾１１と高圧空気圧縮）幾１２の間
にある熱交換器２０に対する冷却水は、移送ポンプ１８
から送られ、熱交換した冷却水を熱交換器２５で常温に
してから貯水タンク１７に回収される。Cooling water for the heat exchanger 20 located between the low-pressure air compressor) 11 and the high-pressure air compressor 12 is supplied to the transfer pump 18.
Cooling water sent from the water tank 17 is cooled to room temperature in a heat exchanger 25 and then collected in a water storage tank 17.
次に本発明によるターボチャージャのケーシング冷却装
置の作用について説明する。第１図において、燃料電池
本体１６の通常運転状態において、ターボチャージャＴ
１ の低圧タービン１５で膨張し終った排気の温度は、
１５０℃前後である。この排熱が熱交換器１９８通過す
るとき、冷却水と熱交換を行なって大気に放出される。Next, the operation of the turbocharger casing cooling device according to the present invention will be explained. In FIG. 1, in the normal operating state of the fuel cell main body 16, the turbocharger T
The temperature of the exhaust gas that has finished expanding in the low pressure turbine 15 of 1 is:
The temperature is around 150°C. When this waste heat passes through the heat exchanger 198, it exchanges heat with the cooling water and is released to the atmosphere.
したがって貯水タンク１７の冷却水は、移送ポンプ１８
によって熱交換器１９へ送られ、熱交換されて温度上昇
下のちに、高圧タービン１４および低圧タービン１５の
それぞれのケーシングへ送られて冷却を行なう。この間
にタービンケーシングの入口および出口の冷却水温は温
度センサ２２．２４および２７゜２８で検出され、制御
装置２６を介して冷却水の流量および温度を予め決めた
値に設定し、各流量調整２１、２９および２３．３０に
よってタービンケーシングに入る冷１１水の温度を調整
する。Therefore, the cooling water in the water storage tank 17 is transferred to the transfer pump 18.
The water is sent to the heat exchanger 19, where it is heat exchanged and the temperature rises, and then sent to the respective casings of the high-pressure turbine 14 and the low-pressure turbine 15 for cooling. During this time, the temperature of the cooling water at the inlet and outlet of the turbine casing is detected by temperature sensors 22, 24 and 27, 28, and the flow rate and temperature of the cooling water are set to predetermined values via the control device 26, and each flow rate adjustment 21 , 29 and 23.30 to regulate the temperature of the cold 11 water entering the turbine casing.
いま、タービン１４および１５の出口）帰度が」二昇し
。Now, the return power at the exits of turbines 14 and 15 has increased by 2.
た場合、温度センサ２７．２８および２２．２４がそれ
を検知して制御装置２６を動作させ、その制御装置２６
の指令によってそれぞれの流量調整弁２３．３０および
２１．２９を調整し、冷却水の流量および温度を設定値
になるようケーシングに入る冷却水温度を調整する。temperature sensors 27.28 and 22.24 detect this and operate the controller 26,
The flow regulating valves 23.30 and 21.29 are adjusted according to the command, and the temperature of the cooling water entering the casing is adjusted so that the flow rate and temperature of the cooling water become the set values.
したがって、タービンケーシングは温度差の小さい冷却
水で冷却されることから、熱応力は軽減され、熱応力に
よる低サイクル疲労の度合を小さくすることができる。Therefore, since the turbine casing is cooled with cooling water having a small temperature difference, thermal stress is reduced, and the degree of low cycle fatigue due to thermal stress can be reduced.
またタービン１４および１５のケーシングに冷却水が入
ってから通過するまでの冷却水温度が１００℃以上にな
らないように温度センサ２７．２Ｂおよび２２゜２４で
検知し、流量調整弁３０および２９で冷却水の流量を調
整してベーパライズを防止するようになっている。In addition, temperature sensors 27.2B and 22.24 detect the temperature of the cooling water from when it enters the casings of the turbines 14 and 15 to when it passes through the turbines, and the flow rate adjustment valves 30 and 29 are used to cool the water. The water flow rate is adjusted to prevent vaporization.
次に第２図に示す他の実施例においては、ターボチャー
ジャＴ１の低圧タービン１５の排気側に２つの熱交換器
１９および３１を設け、その一方の熱交換器１９の冷却
水を低圧タービン１５のケーシングに供給するようにし
、他方の熱交換器３１の冷却水を高圧タービン１４のケ
ーシングに供給するようにしたものである。Next, in another embodiment shown in FIG. 2, two heat exchangers 19 and 31 are provided on the exhaust side of the low pressure turbine 15 of the turbocharger T1, and the cooling water of one of the heat exchangers 19 is transferred to the low pressure turbine 15. The cooling water of the other heat exchanger 31 is supplied to the casing of the high pressure turbine 14.
この他の実施例においては、低圧タービン１５および高
圧タービン１４のタービンケーシングに入る冷却水量を
それぞれ調整することができることにより、それぞれの
タービンケーシングの温度に適した冷却水温度を供給す
ることができ、ざらにタービンケーシングに生じる□熱
応力を軽減し、低サイクル疲労を軽減することができる
。In this other embodiment, by being able to adjust the amount of cooling water entering the turbine casings of the low-pressure turbine 15 and the high-pressure turbine 14, it is possible to supply a cooling water temperature suitable for the temperature of each turbine casing, □Thermal stress generated in the turbine casing can be reduced and low cycle fatigue can be reduced.
なお、第１図および第２図に示す実施例では燃料電池発
電プラントの２段方式のターボチャージャシステムにつ
いて説明したが、他のプラントに使用されるターボチャ
ージャのタービンケーシングの冷却システムも同様に実
施することができる。In addition, although the embodiment shown in FIGS. 1 and 2 describes a two-stage turbocharger system for a fuel cell power generation plant, the cooling system for the turbine casing of a turbocharger used in other plants can be similarly implemented. can do.
［発明の効ｆＡ］
以上のように本発明によれば、ターボチャージャの低圧
タービンの後流側に熱交換器を設け、この熱交換器で熱
交換したあとの冷却水と貯水タンクからの冷却水とを混
合して冷却水温を調整した冷却水をタービンケーシング
に供給するよう構成したことにより、タービンケーシン
グと冷却水との温度差が少なくなって熱応力自体を軽減
させることができ、また熱応力による低サイクル疲労も
低減させることができ、併せて有効な排熱回収を行なう
ことができる。[Effects of the Invention fA] As described above, according to the present invention, a heat exchanger is provided on the downstream side of the low-pressure turbine of the turbocharger, and the cooling water and cooling water from the water storage tank after heat exchange with the heat exchanger are By supplying cooling water whose temperature has been adjusted by mixing it with water to the turbine casing, the temperature difference between the turbine casing and the cooling water is reduced, reducing thermal stress itself. Low-cycle fatigue due to stress can also be reduced, and at the same time, effective exhaust heat recovery can be performed.
第１図および第２図は本発明によるターボチャージャの
タービンケーシング冷却装置のそれぞれ異なる実施例を
示す系統図である。
Ｔ１ ・・・低圧ターボチャージャ
Ｔ２・・・高圧ターボチャージャ
１１・・・低圧空気圧縮機
１２・・・高圧空気圧縮機
１３・・・燃焼器
１４・・・高圧タービン
１５・・・低圧タービン
１６・・・燃料電池本体
１７・・・貯水タンク
１８・・・移送ポンプ
１９、２５．３０・・・熱交換器
２０・・・中間熱交換器
２１、２３．２９．３０．・・流量調整弁２２、２４．
２７．２８・・・温度センサ２６・・・制御装置
（８７３３）代理人 弁理士 猪 股 祥 晃（ばか
１名）1 and 2 are system diagrams showing different embodiments of a turbine casing cooling device for a turbocharger according to the present invention. T1...Low pressure turbocharger T2...High pressure turbocharger 11...Low pressure air compressor 12...High pressure air compressor 13...Combustor 14...High pressure turbine 15...Low pressure turbine 16... ...Fuel cell body 17...Water tank 18...Transfer pump 19, 25.30...Heat exchanger 20...Intermediate heat exchanger 21, 23.29.30. ...Flow rate adjustment valves 22, 24.
27.28...Temperature sensor 26...Control device (8733) Agent Patent attorney Yoshiaki Inomata (Idiot)
1 person)
Claims (3)
ターボチャージャにおいて、前記低圧タービンの排気側
に熱交換器を設け、この熱交換器で熱交換後の冷却水を
タービンケーシングに冷却水として通すことを特徴とす
るターボチャージャのタービンケーシング冷却装置。(1) In a two-stage boost type turbocharger in which a turbine drives an air compressor, a heat exchanger is provided on the exhaust side of the low-pressure turbine, and the heat exchanger transfers the cooling water after heat exchange to the turbine casing. A turbine casing cooling device for a turbocharger, which is characterized in that it passes through as a cooling device.
水とを混合してタービンケーシングに冷却水として通す
ことを特徴とする特許請求の範囲第１項記載のターボチ
ャージャのタービンケーシング冷却装置。(2) A turbine casing of a turbocharger according to claim 1, characterized in that the cooling water after heat exchange in a heat exchanger and the cooling water in a water storage tank are mixed and passed through the turbine casing as cooling water. Cooling system.
水との混合は、その系に設けた流量調整弁をタービンケ
ーシングの入口水温との温度センサの検知結果で決まる
設定値水温になるよう開度調整して行なうことを特徴と
する実用新案登録請求の範囲第２項記載のターボチャー
ジャのタービンケーシング冷却装置。(3) The cooling water after heat exchange in the heat exchanger and the cooling water in the water storage tank are mixed at a set water temperature determined by the flow rate adjustment valve installed in the system and the detection result of the temperature sensor at the inlet water temperature of the turbine casing. A turbine casing cooling device for a turbocharger according to claim 2, characterized in that the opening degree is adjusted so that
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61138200A JPS62294724A (en) | 1986-06-16 | 1986-06-16 | Turbine casing cooler for turbocharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61138200A JPS62294724A (en) | 1986-06-16 | 1986-06-16 | Turbine casing cooler for turbocharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62294724A true JPS62294724A (en) | 1987-12-22 |
Family
ID=15216421
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61138200A Pending JPS62294724A (en) | 1986-06-16 | 1986-06-16 | Turbine casing cooler for turbocharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62294724A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006260855A (en) * | 2005-03-15 | 2006-09-28 | Aisin Seiki Co Ltd | Fuel cell system |
| US20120003082A1 (en) * | 2010-06-30 | 2012-01-05 | Mazda Motor Corporation | Cooling device of turbocharger of engine for vehicle |
| US8365526B2 (en) * | 2006-03-15 | 2013-02-05 | Man Truck & Bus Ag | Vehicle or stationary power plant having a turbocharged internal combustion engine as a drive source |
| CN109372775A (en) * | 2018-11-20 | 2019-02-22 | 势加透博（北京）科技有限公司 | A kind of two stages of compression air supply system of fuel cell |
| WO2019166122A1 (en) * | 2018-02-27 | 2019-09-06 | Robert Bosch Gmbh | Fuel cell system |
-
1986
- 1986-06-16 JP JP61138200A patent/JPS62294724A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006260855A (en) * | 2005-03-15 | 2006-09-28 | Aisin Seiki Co Ltd | Fuel cell system |
| US8365526B2 (en) * | 2006-03-15 | 2013-02-05 | Man Truck & Bus Ag | Vehicle or stationary power plant having a turbocharged internal combustion engine as a drive source |
| EP3591200A1 (en) * | 2006-03-15 | 2020-01-08 | MAN Truck & Bus SE | Vehicle or stationary power station with a charged combustion engine as a drive source |
| EP3591189A1 (en) * | 2006-03-15 | 2020-01-08 | MAN Truck & Bus SE | Vehicle or stationary power station with a charged combustion engine as a drive source |
| US20120003082A1 (en) * | 2010-06-30 | 2012-01-05 | Mazda Motor Corporation | Cooling device of turbocharger of engine for vehicle |
| US8590306B2 (en) * | 2010-06-30 | 2013-11-26 | Mazda Motor Corporation | Cooling device of turbocharger of engine for vehicle |
| WO2019166122A1 (en) * | 2018-02-27 | 2019-09-06 | Robert Bosch Gmbh | Fuel cell system |
| CN109372775A (en) * | 2018-11-20 | 2019-02-22 | 势加透博（北京）科技有限公司 | A kind of two stages of compression air supply system of fuel cell |
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