WO2009125836A1 - 過給装置 - Google Patents
過給装置 Download PDFInfo
- Publication number
- WO2009125836A1 WO2009125836A1 PCT/JP2009/057346 JP2009057346W WO2009125836A1 WO 2009125836 A1 WO2009125836 A1 WO 2009125836A1 JP 2009057346 W JP2009057346 W JP 2009057346W WO 2009125836 A1 WO2009125836 A1 WO 2009125836A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- exhaust turbine
- turbine supercharger
- supercharger
- exhaust
- turbine
- Prior art date
Links
- 238000010397 one-hybrid screening Methods 0.000 claims abstract description 6
- 238000000034 method Methods 0.000 claims description 7
- 238000010248 power generation Methods 0.000 claims description 4
- 230000011664 signaling Effects 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 21
- 230000003584 silencer Effects 0.000 description 9
- 238000004519 manufacturing process Methods 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 3
- 238000004080 punching Methods 0.000 description 3
- 239000000567 combustion gas Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
- F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
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- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D23/00—Controlling engines characterised by their being supercharged
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/04—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using kinetic energy
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- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a supercharging device having a plurality of superchargers for boosting the charge using exhaust gas, and particularly to a supercharging device suitable for being mounted on a marine diesel engine, a diesel engine for an onshore generator, or the like. It is.
- Patent Document 1 As a supercharging device including a plurality of superchargers that increase the pressure of air supply using exhaust gas, for example, the one disclosed in Patent Document 1 is known.
- Japanese Patent Laid-Open No. 60-166716 (FIG. 1)
- the present invention has been made in view of the above circumstances, and can control the rotational speed of a hybrid exhaust turbine supercharger with a simple configuration without using an expensive control device that instantaneously processes complex calculations.
- An object of the present invention is to provide a supercharging device that can suppress the manufacturing cost and prevent surging of the hybrid exhaust turbine supercharger.
- a supercharging device includes a turbine unit that is driven by exhaust gas guided from an engine body, and a compressor unit that is driven by the turbine unit and pumps outside air to the engine body.
- At least one exhaust turbine supercharger that is always in operation, a turbine section driven by exhaust gas guided from the engine body, and the engine driven by the turbine section
- a compressor unit that pumps outside air to the main body, and a generator having a rotating shaft coupled to the turbine unit and a rotating shaft of the compressor unit, and in parallel with the exhaust turbine supercharger during operation of the engine body
- At least one hybrid exhaust turbine supercharger that is in operation; and the exhaust turbine supercharger attached to the exhaust turbine supercharger.
- a command signal is issued to the generator of the hybrid exhaust turbine supercharger in response to the signal, and the rotation of the hybrid exhaust turbine supercharger
- a controller for controlling the power generation amount of the generator so that the number and the rotation speed of the exhaust turbine supercharger coincide with each other.
- the rotational speed of the hybrid exhaust turbine supercharger can be changed to the rotational speed of the exhaust turbine supercharger with a simple configuration without using an expensive control device that instantly performs complicated calculations. Since they can be matched, the manufacturing cost can be suppressed and surging of the hybrid exhaust turbine supercharger can be prevented.
- the diesel engine equipped with the supercharging device According to the diesel engine equipped with the supercharging device according to one aspect of the present invention, surging of the hybrid exhaust turbine supercharger constituting the supercharging device is prevented, so that the supply constituting the diesel engine can be prevented.
- the supercharged air (outside air) at the optimum pressure is always supplied (accumulated) in the air manifold and cylinder, the engine output can be stably improved, and the reliability of the entire engine is improved. Can do.
- An operation method of a supercharging device includes a turbine unit that is driven by exhaust gas guided from an engine body, and a compressor unit that is driven by the turbine unit and pumps outside air to the engine body. And at least one exhaust turbine supercharger that is always in an operating state during operation of the engine body, a turbine section driven by exhaust gas guided from the engine body, and driven by the turbine section A compressor unit for pumping outside air to the engine body, and a generator having a rotating shaft connected to the turbine unit and a rotating shaft of the compressor unit, and during operation of the engine body, the exhaust turbine supercharging At least one hybrid exhaust turbine supercharger in parallel operation with the engine and attached to the exhaust turbine supercharger And a controller that receives a signal from a rotation sensor that detects the rotational speed of the exhaust turbine supercharger and issues a command signal to the generator of the hybrid exhaust turbine supercharger in response to the signal.
- a method of operating a supercharger, wherein the amount of power generated by the generator is set so that the rotational speed of
- the rotational speed of the hybrid exhaust turbine supercharger can be reduced with a simple configuration without using an expensive control device that instantaneously performs complicated calculations. Since it can be made to correspond to the rotation speed of a feeder, manufacturing cost can be suppressed and surging of a hybrid exhaust turbine supercharger can be prevented.
- the supercharging device According to the supercharging device according to the present invention, it is possible to control the rotational speed of the hybrid exhaust turbine supercharger with a simple configuration without using an expensive control device that instantly processes complicated calculations, Costs can be suppressed and surging of the hybrid exhaust turbine supercharger can be prevented.
- FIG. 3 is a partially cut perspective view of the hybrid exhaust turbine supercharger shown in FIG. 2 as viewed from the silencer side.
- FIGS. 1 to 3 is a schematic configuration diagram of a marine diesel engine equipped with a supercharging device according to the present embodiment
- FIG. 2 is a longitudinal sectional view of a hybrid exhaust turbine supercharger shown in FIG. 1
- FIG. 3 is a hybrid exhaust turbine shown in FIG. It is the partial cutaway perspective view which looked at the supercharger from the silencer side.
- the marine diesel engine 1 includes a diesel engine body (for example, a low-speed two-cycle diesel engine) 2 and a supercharging device 3.
- a screw propeller (not shown) is directly or indirectly connected to a crankshaft (not shown) constituting the diesel engine main body (hereinafter referred to as “engine main body”) 2 via a propeller shaft (not shown). It is attached.
- the engine body 2 is provided with a cylinder portion 4 including a cylinder liner (not shown), a cylinder cover (not shown), and the like, and a piston connected to a crankshaft is provided in each cylinder portion 4. (Not shown) is arranged.
- an exhaust port (not shown) of each cylinder portion 4 is connected to an exhaust manifold 5, and the exhaust manifold 5 is connected to an exhaust turbine excess constituting the supercharging device 3 via a first exhaust pipe L1.
- an air supply port (not shown) of each cylinder portion 4 is connected to an air supply manifold 8, and the air supply manifold 8 is a compressor of the exhaust turbine supercharger 6 via a first air supply pipe L3. It is connected to the part 6b and is connected to the compressor part 7b of the hybrid exhaust turbine supercharger 7 via the second air supply pipe L4.
- the exhaust gases that have passed through the turbine sections 6a and 7a are guided to funnels (not shown) via exhaust pipes L5 and L6 connected to the outlet sides of the turbine sections 6a and 7a, respectively, and then outside the ship. It is supposed to be discharged.
- a silencer (not shown) is disposed in each of the supply pipes L7 and L8 connected to the inlet side of the compressor units 6b and 7b, and the outside air that has passed through the silencer is supplied to the compressor units 6b and 7b, respectively. It has come to be guided.
- air coolers (intercoolers) 9, 10 and a surge tank (not shown) are connected in the middle of the supply pipes L3, L4 connected to the outlet side of the compressor units 6b, 7b. The outside air that has passed through 7b passes through the air coolers 9, 10 and the surge tank, and is then supplied to the air supply manifold 8 of the engine body 2.
- the supercharger 3 includes at least one (one in this embodiment) exhaust turbine supercharger 6 and at least one (one in this embodiment) hybrid exhaust turbine supercharger.
- a machine 7 and a controller C are provided.
- the exhaust turbine supercharger 6 is driven by an exhaust gas (combustion gas) guided from the engine main body 2 via the first exhaust pipe L1, and the engine main body 2 is driven by the turbine section 6a.
- the main component is a compressor unit 6b that pumps outside air and a casing (not shown) that is provided between and supports the turbine unit 6a and the compressor unit 6b.
- the casing is inserted with a rotating shaft 6c having one end projecting toward the turbine section 6a and the other end projecting toward the compressor section 6b.
- One end portion of the rotating shaft 6c is attached to a turbine disk (not shown) of a turbine rotor (not shown) constituting the turbine portion 6a, and the other end portion of the rotating shaft 6c is connected to the compressor portion 6b. It is attached to a hub (not shown) of a compressor impeller (not shown).
- the hybrid exhaust turbine supercharger 7 is driven by exhaust gas (combustion gas) 11 guided from the engine body 2 via the second exhaust pipe L2 (see FIG. 1).
- the casing 15 is inserted with a rotating shaft 16 having one end protruding toward the turbine portion 7a and the other end protruding toward the compressor portion 7b.
- the rotary shaft 16 is supported by a bearing 17 provided in the casing 15 so as to be rotatable about an axis.
- the casing 15 is provided with a lubricating oil supply path 18 for supplying lubricating oil from a lubricating oil reservoir (not shown) to the bearing 17.
- the lower end portion of the casing 15 supports the casing 15 at one point in the axial direction of the rotating shaft 16 (may be supported at two or more points in a direction orthogonal to the axial direction of the rotating shaft 16).
- the leg portion 15a is fixed to a base (not shown) installed on the floor surface. That is, the weight of the hybrid exhaust turbine supercharger 7 is transmitted to the base via the leg portion 15a.
- the symbol P is a punching plate. One end of the punching plate P is fixed to the lower end of the turbine portion 7 a, and the other end is fixed to the base in the same manner as the leg portion 15 a of the casing 15.
- the punching plate P is not mainly intended to support the weight of the hybrid exhaust turbine supercharger 7 like the leg portion 15a.
- the hybrid exhaust turbine supercharger 7 is connected to the base. The main purpose is to prevent shaking.
- the turbine section 7a is connected to the outlet end of the second exhaust pipe L2 and receives the exhaust gas passage 20 to which the exhaust gas 11 is supplied, and rotates in response to the flow of the exhaust gas 11 supplied into the exhaust gas passage 20. And a turbine 21 to be driven.
- the turbine 21 includes a turbine rotor 22 and a turbine nozzle 23.
- the turbine rotor 22 includes a disk-shaped turbine disk 22a provided at one end of the rotary shaft 16, and a plurality of turbine blades having an airfoil cross section attached on the outer periphery of the turbine disk 22a. 22b.
- the turbine nozzle 23 is configured by annularly arranging a plurality of nozzle guide vanes 23a, and is disposed upstream of the turbine blade 22b.
- the exhaust gas passage 20 is connected to the outlet end of the second exhaust pipe L2 to supply the nozzle guide vane 23a and the turbine blade 22b with the exhaust gas 11, and toward the radially outer side of the turbine 21.
- a delivery path 20b that is provided and guides the exhaust gas 11 that has passed through the turbine 21 to a funnel (not shown) via an exhaust pipe L6 (see FIG. 1).
- the compressor unit 7b is driven to rotate, and a compressor impeller 24 that sends outside air 13 radially outward and a spiral chamber that surrounds the compressor impeller 24 and compresses the outside air 13 sent by the compressor impeller 24. 25.
- the compressor impeller 24 is attached to the other end of the rotary shaft 16 and has a substantially disc-shaped hub 24a.
- the compressor impeller 24 extends radially outward from the outer surface of the hub 24a, and is provided annularly along the circumferential direction. And a plurality of blades 24b.
- a silencer (silencer) 26 connected to the air supply system of the engine body 2 is disposed adjacent to the upstream side of the compressor unit 7 b, and the outside air 13 that has passed through the silencer 26 passes through an inflow path 27. It is guided to the blade 24 b of the compressor impeller 24.
- An air cooler (intercooler) 10 and a surge tank (not shown) are connected to the second air supply pipe L4 arranged on the downstream side of the compressor unit 7b, and the outside air 13 that has passed through the spiral chamber 25 is After passing through the air cooler 10 and the surge tank, the air supply manifold 8 is supplied.
- a shell housing 28 having a recess 28a formed so as to taper toward the end surface of the hub 24a is provided in the center of the silencer 26, and in the recess 28a, A (high speed induction) generator 29 is accommodated.
- the shell housing 28 is fixed to the compressor portion 7 b (the radially outer wall surface forming the inflow passage 27) via a plurality of (for example, four) supports 30 provided in the inflow passage 27.
- the outer surface of the shell housing 28 forms a radially inner wall surface that forms the inflow passage 27.
- the rotating shaft 29a of the generator 29 is disposed so as to be positioned on the same rotating axis as the rotating shaft 16, and has one end of the rotating shaft 16 protruding through the hub 24a and projecting toward the silencer 26. Are coupled via a coupling 31. That is, the rotating shaft 29 a of the generator 29 rotates with the rotating shaft 16.
- the generator 29 is electrically connected to a switchboard or the like separately installed in the ship (in this embodiment, the engine room), and the generator 29 uses (utilizes) the power generated as the generator as the ship power. Can be done.
- the controller C is attached to the exhaust turbine supercharger 6 and receives a signal from a rotation sensor (not shown) that detects the rotational speed of the exhaust turbine supercharger 6, and in response to the signal, the hybrid exhaust turbine turbocharger.
- a command signal is sent (issued) to the generator 29 of the charger 7 so that the rotational speed of the hybrid exhaust turbine supercharger 7 and the rotational speed of the exhaust turbine supercharger 6 are the same (match). The amount of power generation of 29 is controlled.
- the output of the hybrid exhaust turbine supercharger 7 is equal to the amount of power generated by the generator 29. Is set to be large.
- the flow rate of the exhaust gas 11 flowing into (passing through) the turbine portion 7a is larger than the flow rate of the exhaust gas 11 flowing into the turbine portion 6a (
- the flow rate of the outside air 13 flowing into (passing through) the exhaust gas 11 flowing into the turbine unit 6a is 1.25 times smaller than the flow rate of the outside air 13 flowing into the compressor unit 6b. (For example, 0.8 times the outside air 13 flowing into the compressor section 6b) can be given as a specific example.
- the rotational speed of the hybrid exhaust turbine supercharger 7 can be set to the exhaust turbine supercharger 6 with a simple configuration without using an expensive control device that instantaneously performs complicated calculations. Therefore, the manufacturing cost can be suppressed, and surging of the hybrid exhaust turbine supercharger 7 can be prevented.
- the marine diesel engine having one exhaust turbine supercharger 6 and one hybrid exhaust turbine supercharger 7 has been described.
- the present invention is not limited to this, and the exhaust The present invention can also be applied to a marine diesel engine provided with two or more turbine superchargers 6 and / or two or more hybrid exhaust turbine superchargers 7.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
しかしながら、発電機を備えたハイブリッド排気タービン過給機と、発電機を備えていない排気タービン過給機とが混在する過給装置では、排気タービン過給機はディーゼル機関の負荷に応じて最適な回転数で運転され、ハイブリッド排気タービン過給機は発電機で動力が食われる(消費される)分、最適な回転数よりも低い回転数で運転されることとなる。そのため、排気タービン過給機を単にハイブリッド排気タービン過給機に置き換えただけでは、ハイブリッド排気タービン過給機のコンプレッサ部を通過する流量が減って、ハイブリッド排気タービン過給機にサージングが発生してしまうおそれがある。
このようなサージングが発生しないように、ハイブリッド排気タービン過給機の回転数を制御するには、複雑な演算を瞬時に処理することのできる高価な制御装置が必要となり、製造コストの高騰化を招いてしまうといった問題点もある。
本発明の一態様に係る過給装置は、エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部とを有し、前記エンジン本体の運転中、常に運転状態とされる少なくとも1台の排気タービン過給機と、前記エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部と、前記タービン部および前記コンプレッサ部の回転軸と連結される回転軸を有する発電機とを有し、前記エンジン本体の運転中、前記排気タービン過給機と並列運転状態とされる少なくとも1台のハイブリッド排気タービン過給機と、前記排気タービン過給機に取り付けられて前記排気タービン過給機の回転数を検出する回転センサからの信号を受けて、その信号に応じて前記ハイブリッド排気タービン過給機の前記発電機に指令信号を発し、前記ハイブリッド排気タービン過給機の回転数と前記排気タービン過給機の回転数とが一致するように、前記発電機の発電量を制御する制御器とを備えている。
2 エンジン本体
3 過給装置
6 排気タービン過給機
6a タービン部
6b コンプレッサ部
7 ハイブリッド排気タービン過給機
7a タービン部
7b コンプレッサ部
11 排気ガス
13 外気
16 回転軸
29 発電機
29a 回転軸
C 制御器
図1は本実施形態に係る過給装置を具備した舶用ディーゼル機関の概略構成図、図2は図1に示すハイブリッド排気タービン過給機の縦断面図、図3は図2に示すハイブリッド排気タービン過給機を消音器の側から見た一部切開斜視図である。
ディーゼルエンジン本体(以下「エンジン本体」という。)2を構成するクランク軸(図示せず)には、プロペラ軸(図示せず)を介してスクリュープロペラ(図示せず)が直接的または間接的に取り付けられている。また、エンジン本体2には、シリンダライナ(図示せず)、シリンダカバー(図示せず)等からなるシリンダ部4が設けられており、各シリンダ部4内には、クランク軸と連結されたピストン(図示せず)が配置されている。さらに、各シリンダ部4の排気ポート(図示せず)は、排気マニホールド5と接続されており、排気マニホールド5は、第1の排気管L1を介して、過給装置3を構成する排気タービン過給機6のタービン部6aの入口側と接続され、第2の排気管L2を介して、過給装置3を構成するハイブリッド排気タービン過給機7のタービン部7aの入口側と接続されている。一方、各シリンダ部4の給気ポート(図示せず)は、給気マニホールド8と接続されており、給気マニホールド8は、第1の給気管L3を介して排気タービン過給機6のコンプレッサ部6bと接続され、第2の給気管L4を介してハイブリッド排気タービン過給機7のコンプレッサ部7bと接続されている。
コンプレッサ部6b,7bの入口側に接続された給気管L7,L8にはそれぞれ、消音器(図示せず)が配置されており、この消音器を通過した外気が、コンプレッサ部6b,7bにそれぞれ導かれるようになっている。一方、コンプレッサ部6b,7bの出口側に接続された給気管L3,L4の途中には、空気冷却器(インタークーラ)9,10や図示しないサージタンク等が接続されており、コンプレッサ部6b,7bを通過した外気は、これら空気冷却器9,10やサージタンク等を通過した後、エンジン本体2の給気マニホールド8に供給されるようになっている。
排気タービン過給機6は、第1の排気管L1を介してエンジン本体2から導かれた排気ガス(燃焼ガス)によって駆動されるタービン部6aと、このタービン部6aにより駆動されてエンジン本体2に外気を圧送するコンプレッサ部6bと、これらタービン部6aとコンプレッサ部6bとの間に設けられてこれらを支持するケーシング(図示せず)とを主たる要素として構成されたものである。
ケーシングには、一端部をタービン部6a側に突出させ、他端部をコンプレッサ部6bに突出させた回転軸6cが挿通されている。回転軸6cの一端部は、タービン部6aを構成するタービン・ロータ(図示せず)のタービン・ディスク(図示せず)に取り付けられており、回転軸6cの他端部は、コンプレッサ部6bを構成するコンプレッサ羽根車(図示せず)のハブ(図示せず)に取り付けられている。
一方、ケーシング15の下端部は、回転軸16の軸線方向においてケーシング15を一点で支持する(回転軸16の軸線方向と直交する方向においては、二点以上で支持する場合もある)脚部15aとなっており、この脚部15aは、床面に設置された基台(図示せず)に固定されるようになっている。すなわち、ハイブリッド排気タービン過給機7の重量は、この脚部15aを介して基台に伝達されるようになっている。
なお、図中の符号Pはパンチング・プレートである。このパンチング・プレートPは、その一端部がタービン部7aの下端部に固定されているとともに、その他端部がケーシング15の脚部15aと同様、基台に固定されている。そして、このパンチング・プレートPは、脚部15aのようにハイブリッド排気タービン過給機7の重量を支持することを主たる目的とするものではなく、ハイブリッド排気タービン過給機7が基台に対して動揺(振動)しないようにすることを主たる目的とするものである。
タービン21は、タービン・ロータ22と、タービン・ノズル23とを備えている。タービン・ロータ22は、回転軸16の一端部に設けられた、円盤状のタービン・ディスク22aと、このタービン・ディスク22aの外周上に取り付けられた、翼型断面を有する複数枚のタービン・ブレード22bとを備えている。
また、タービン・ノズル23は、複数枚のノズル・ガイド・ベーン23aを環状に配置して構成されたものであり、タービン・ブレード22bの上流側に配置されている。
コンプレッサ羽根車24は、回転軸16の他端部に取り付けられた、略円盤状のハブ24aと、このハブ24aの外表面から半径方向外側に向かって延びるとともに、周方向に沿って環状に設けられた複数枚の羽根24bとを備えている。
コンプレッサ部7bの上流側には、エンジン本体2の給気系統に接続された消音器(サイレンサ)26が隣接配置されており、この消音器26を通過した外気13は、流入路27を介してコンプレッサ羽根車24の羽根24bに導かれるようになっている。また、コンプレッサ部7bの下流側に配置された第2の給気管L4には、空気冷却器(インタークーラ)10や図示しないサージタンク等が接続されており、渦巻き室25を通過した外気13は、これら空気冷却器10やサージタンク等を通過した後、給気マニホールド8に供給されるようになっている。
発電機29は、船内(本実施形態では機関室内)に別途設置された配電盤等と電気的に接続されており、発電機29が発電機として発生した電力を船内電源として使用(利用)することができるようになっている。
Claims (3)
- エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部とを有し、前記エンジン本体の運転中、常に運転状態とされる少なくとも1台の排気タービン過給機と、
前記エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部と、前記タービン部および前記コンプレッサ部の回転軸と連結される回転軸を有する発電機とを有し、前記エンジン本体の運転中、前記排気タービン過給機と並列運転状態とされる少なくとも1台のハイブリッド排気タービン過給機と、
前記排気タービン過給機に取り付けられて前記排気タービン過給機の回転数を検出する回転センサからの信号を受けて、その信号に応じて前記ハイブリッド排気タービン過給機の前記発電機に指令信号を発し、前記ハイブリッド排気タービン過給機の回転数と前記排気タービン過給機の回転数とが一致するように、前記発電機の発電量を制御する制御器とを備えている過給装置。 - 請求項1に記載の過給装置を備えるディーゼル機関。
- エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部とを有し、前記エンジン本体の運転中、常に運転状態とされる少なくとも1台の排気タービン過給機と、
前記エンジン本体から導かれた排気ガスによって駆動されるタービン部と、このタービン部により駆動されて前記エンジン本体に外気を圧送するコンプレッサ部と、前記タービン部および前記コンプレッサ部の回転軸と連結される回転軸を有する発電機とを有し、前記エンジン本体の運転中、前記排気タービン過給機と並列運転状態とされる少なくとも1台のハイブリッド排気タービン過給機と、
前記排気タービン過給機に取り付けられて前記排気タービン過給機の回転数を検出する回転センサからの信号を受けて、その信号に応じて前記ハイブリッド排気タービン過給機の前記発電機に指令信号を発する制御器とを備えた過給装置の運転方法であって、
前記エンジン本体の運転中、前記ハイブリッド排気タービン過給機の回転数と前記排気タービン過給機の回転数とが一致するように、前記発電機の発電量を前記制御器により制御するようにした過給装置の運転方法。
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CN2009801013063A CN101896706B (zh) | 2008-04-11 | 2009-04-10 | 增压装置 |
US12/744,692 US8359859B2 (en) | 2008-04-11 | 2009-04-10 | Turbocharger device |
EP09731059.3A EP2261483B1 (en) | 2008-04-11 | 2009-04-10 | Supercharging device |
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EP (1) | EP2261483B1 (ja) |
JP (1) | JP4875654B2 (ja) |
KR (1) | KR101116455B1 (ja) |
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Also Published As
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KR101116455B1 (ko) | 2012-03-08 |
US20100281863A1 (en) | 2010-11-11 |
EP2261483A4 (en) | 2012-02-29 |
US8359859B2 (en) | 2013-01-29 |
KR20100089099A (ko) | 2010-08-11 |
CN101896706A (zh) | 2010-11-24 |
EP2261483A1 (en) | 2010-12-15 |
EP2261483B1 (en) | 2013-10-02 |
CN101896706B (zh) | 2012-12-05 |
JP2009257098A (ja) | 2009-11-05 |
JP4875654B2 (ja) | 2012-02-15 |
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