EP0989297B1 - Hubkolbenbrennkraftmaschine - Google Patents

Hubkolbenbrennkraftmaschine Download PDF

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Publication number
EP0989297B1
EP0989297B1 EP99810529A EP99810529A EP0989297B1 EP 0989297 B1 EP0989297 B1 EP 0989297B1 EP 99810529 A EP99810529 A EP 99810529A EP 99810529 A EP99810529 A EP 99810529A EP 0989297 B1 EP0989297 B1 EP 0989297B1
Authority
EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
accordance
control
fuel
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.)
Revoked
Application number
EP99810529A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0989297A1 (de
Inventor
Rolf André Bill
Jens Damitz
Stefan Fankhauser
Klaus Heim
Robert Hofer
Erwin Matter
Hameed Kazi
Marcel Weder
Alfred Wunder
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8236339&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0989297(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP99810529A priority Critical patent/EP0989297B1/de
Priority to DK99810529T priority patent/DK0989297T3/da
Publication of EP0989297A1 publication Critical patent/EP0989297A1/de
Application granted granted Critical
Publication of EP0989297B1 publication Critical patent/EP0989297B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
    • F02D41/26—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using computer, e.g. microprocessor
    • F02D41/266—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using computer, e.g. microprocessor the computer being backed-up or assisted by another circuit, e.g. analogue
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • 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
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N9/00—Starting of engines by supplying auxiliary pressure fluid to their working chambers
    • F02N9/04—Starting of engines by supplying auxiliary pressure fluid to their working chambers the pressure fluid being generated otherwise, e.g. by compressing air

Definitions

  • the invention relates to a reciprocating internal combustion engine with several Cylinders, especially a two-stroke diesel engine.
  • WO-A-98/11334 is a reciprocating internal combustion engine known in which an electronic Central unit controls the machine and one for each cylinder individual control module hydraulic gas exchange system.
  • the invention is based on the object Reciprocating piston engine with multiple cylinders while avoiding the to improve the disadvantages mentioned.
  • Fig. 1 shows a two-stroke - diesel engine e.g. has four cylinders, not shown, and at which the interaction between gas exchange valve movement, Fuel supply and piston position is controlled electronically.
  • the machine has a first gear wheel 1 and one mounted on the crankshaft second gear 2, which meshes with the first gear.
  • the second gear 2 is available for a mechanical drive for auxiliary energy and can at certain numbers of cylinders to drive the compensation of Second order mass forces are used.
  • the machine contains High pressure pumps 3, preferably variable suction throttle pumps Delivery pressure for the fuel, a pressure regulator actuator 4, accumulators 5 for the fuel, which via pipes 6 with the high pressure pumps in Connect, pressure pumps 7, 107 for control oil and accumulators 8,108 for control oil, which is connected to the pressure pump 107 via a pipe 109 Connected, with only one pump, one accumulator and one Pipeline are shown.
  • the high pressure pump 3 for the fuel driven by the second gear 2 and the pump 107 for the control oil is powered by an auxiliary motor.
  • an injection system 11 is for a cylinder the accumulator 5 as well as the second accumulator 108 in connection stands and a gas exchange system 12 is provided, which with a third Accumulator 8 is connected.
  • the accumulators 5, 108 are tube-like components with or without Internals. In the case of the accumulators without internals, the Volume storage is preferably based solely on the elasticity of the storing media.
  • a Safety valve 16 At the accumulator 5 for the fuel is a Safety valve 16, the pressure in the accumulator on a fixed The maximum value is limited and a pressure sensor 17 is provided which measures the pressure in Accumulator detects.
  • the pressure pumps 7, 107 of the accumulator 8, 108 for working oil or control oil and pilot valves 14 each form a hydraulic system Control of the injection system and the gas exchange system, each Pump upstream of a filter 13 and each accumulator 8, 108 with one Pressure sensor 18, 19 is provided.
  • valves 40, 41, 42 are installed, which allow the Disconnect the injection system of each cylinder from the engine so that Repairs to the injection system are carried out with the engine running can.
  • the machine has an electronic control device. To the Determine the speed of the crankshaft and the crank angle Angle encoder 25 slip and mechanical means with the crankshaft backlash-free connected, between the second gear 2 and A gear (not shown) can be provided for angle sensors 25, so that the angle encoders rotate at the motor speed. There are two Reference encoder 26 is provided to ensure synchronism between the Monitor crankshaft and the angle encoder.
  • the control device contains at least one central unit 21, Control module 22 for each cylinder, a remote control 23 and one Speed controller 24.
  • the central unit 21 and the control modules 22 are over a data bus networked form independent control units with one firmly assigned area of responsibility.
  • the remote control 23 is with the Central unit connected to transmit signals.
  • the pressure sensors 17, 18 and 19 are connected to central unit 21.
  • the central unit 21 is also connected to the Pressure regulator actuator or pressure regulator actuators 4 of the high pressure pumps 3 for fuel and the pressure actuator or pressure actuators High pressure pump or pressure pumps 7 connected for working oil.
  • the Control module 22 is connected to pilot valves 14 of injection system 11 and of the gas exchange system 12 and a measuring system 71 of the Gas exchange system and a measuring system 36 for volumetric Injection connected (Fig. 7).
  • the central unit 21 contains a memory in which all the engine relevant functions are stored.
  • the control modules included also a memory in which those relating to the cylinder Functions are stored.
  • the central unit 21 forms the interface of the engine-relevant sensors, the speed controller and the remote control (operator interface) to the Control units of the cylinders. It is also used for regulating the pressures responsible for the various media.
  • the current and the desired operating state of the engine are communicated to the control modules 22 via the bus.
  • the control modules 22 determine this data in accordance with the Injection time, the injection quantity and the gas exchange control times taking into account the cylinder-specific offsets and dead times. Out For reasons of safety, the central unit 21 is in this embodiment provide redundant form. The failure of a control module 22 is shown in Purchased because, despite the failure of one cylinder, the maintenance is guaranteed.
  • each of the four Cylinders e.g. three fuel nozzles 31 and one injector 32 comprises and one or more pilot valves 14 are assigned.
  • the injection device 32 contains a metering piston 34, a valve slide 35 and a displacement sensor system 36 for monitoring the position of the metering piston in order to realize a volumetric injection.
  • the metering piston 34 is designed as a differential piston.
  • the metering piston 34 is arranged in a metering chamber 37, into which a connection channel to the accumulator 5 opens on the one hand and which is connected to a channel 140 on the other hand.
  • This channel connects a chamber 141 and a chamber 142, the length of the channel advantageously being designed to be short in order to keep dynamic pressure differences small and to prevent the valve slide opening automatically.
  • a blind bore 143 opens into the chamber 141.
  • a spring 145 is arranged in the chamber 141, which is supported on the one hand on the valve slide 35 and on the other hand in the chamber 141 and is intended to hold the valve slide in the basic position.
  • a valve seat 38 I and two control edges 38 II and 38 IV are formed on the valve slide 35.
  • the valve spool 35 is arranged in the housing and forms gap seals 38 III , 38 V and 39 with it.
  • the valve spool 35 has a piston 144 which projects into the blind bore.
  • a return duct for fuel branches off into the injection channel and is provided with an orifice 30, so that when the nozzle needle is stuck, no fuel is injected because the fuel flows through the orifice into the unpressurized space.
  • the pilot valve is designed as a changeover valve and must be one have positive overlap between the switch positions to a
  • the second accumulator 108 is idling when it is stuck To prevent valve pistons.
  • a unit is provided to each cylinder in Dependence of the load and / or the crank angle with lubricant supply.
  • valve slide 35 In the basic position of the valve slide 35, fuel flows from the accumulator 5 via the control edge 38 IV of the valve slide 35 into the metering chamber 37. Because of the area difference, the metering piston 34, which is charged with battery pressure on both sides, runs into its defined end position. The metering piston 34 and the valve slide 35 block the flow of fuel from the accumulator 5 to the fuel nozzles 31 and prevent the accumulator 5 from leaking if, for example, the nozzle needle of a fuel nozzle is stuck. Furthermore, fuel flows via the channel 140 into the chambers 141 and 142, so that the same pressure prevails in these. This has the advantage that the valve slide can only be actuated on the basis of a control command.
  • the pilot valve 14 is switched by the control module 22, so that control oil from the accumulator 108 reaches the control piston 39 of the valve spool 35 and displaces it. Because of the positive overlap between the valve seat 38 I and the control edge 38 II, 38 IV closes before 38 II opens. When the control edge 38 II is open, there is a connection between the metering chamber 37 and the fuel nozzles 31. By displacing the valve slide 35, the piston 144 is displaced into the blind bore 143, the braking edge of the movement of the valve slide being initiated by the control edge 147 and in a particularly advantageous manner damping is achieved.
  • the rear of the metering piston is connected to the accumulator 5 and the pressure in the latter shifts fuel to the fuel nozzle 31 until the fuel volume corresponds to the product of the metering piston area times the metering piston stroke in order to obtain the speed value specified by the speed controller, ie a volumetric fuel metering is realized.
  • the displacement of the metering piston 34 is detected by means of the knife system 36 and the control module 22 switches the pilot valve 14 over, so that in the valve slide 35 the control edge 38 II closes first and then the control edge 38 IV opens. As a result, the fuel supply to the fuel nozzle 31 is interrupted.
  • a valve slide 35 is assigned to each fuel nozzle 31, so that the Fuel nozzles for each cylinder controlled independently and all injection options, such as easy Injection - single or multiple interrupted injection - injection times of different lengths at the individual fuel nozzles can also be carried out with cyclic or stochastic swapping (Fig.2). It is advantageous if the fuel nozzle is damped for the nozzle needle is provided. For this purpose there is a chamber 148 and a channel 149 formed in the housing, which connects the chamber with the leak line. The nozzle needle is at the end facing away from the valve seat with a piston 150 provided that protrudes into the chamber. As a low-cost version, a only valve slide 35 all fuel nozzles of an engine cylinder serve. With the system described, these can also be used Heavy and residual oils usual for engines are used.
  • the gas exchange system 12 contains a device 51 with a separating piston 56 and a control piston 52, each one Gas exchange valve 53 are assigned.
  • the separating piston 56 is intended to separate the hydraulic system (working oil) from the lubricating oil circuit and the movement of the outlet valve 53 in the area of the end positions dampen.
  • the pilot valve 14 draws working oil in a switching position from the accumulator 8 and switches the control piston 52 into one of two possible positions in which the gas exchange valve 53 due to a Valve air spring 61 reaches the "closed" position. In doing so, a Drive piston 54 displaced over the valve stem and displaces oil in a pipe 55, which in turn displaces a piston 56 and almost in a defined starting position.
  • the piston 56 in turn displaces working oil via the control piston 52 into the line 57 to one Collection tank.
  • the piston 56 displaces working oil via the control piston 52 into the line 57 to one Collection tank.
  • pilot valve 14 If the pilot valve 14 is placed in the other position, one moves Compression spring 60, the control piston 52 in the other position, so that Working oil can flow through the pilot valve 14, and connects via the control piston 52 the side of the piston 56, that of the pipeline 58 is turned away, with the accumulator 8.
  • the piston 56, the Pipeline and the drive piston 54 flowing working oil opens it Gas exchange valve against the one that is still in the cylinder of the engine Gas pressure and the valve air spring 61.
  • the Drive piston 54 is designed as a stepped piston 65, 66.
  • the larger piston 65 With its larger cross-sectional area and generates the force that is necessary Open gas exchange valve 53.
  • a smaller force is sufficient to complete the gas exchange valve 53 To have the stroke carried out.
  • the larger piston 65 moves against you Stop 67, the movement shortly before reaching this stop is braked by a damping, not shown. With this arrangement the piston 65 and 66 is removed from the second accumulator 8 Minimized amount of working oil.
  • the measuring system 71 contains a step cone 72 and redundant sensors 78 to detect and move the gas exchange valve Generate measurement signal that is sent to the control module 22.
  • the controller detects whether the gas exchange valve movements meet the setpoints intervenes in the event of incorrect switching and prevents e.g. the next Fuel injection on the cylinder in question. That way ensures that e.g. an n-cylinder engine operated with (n-1) cylinders can be.
  • the step cone 72 has a first one conical section 79, an adjacent cylindrical Section 76 and a subsequent second conical section 77 on, the cone angle of the first and second section as possible is chosen large in order to fully utilize the measuring range of the sensors.
  • the first section 79 detects the opening behavior of the valve and enables assess the damping while opening the valve.
  • the second Section 77 records the closing behavior of the valve and enables it Assess damping while closing the valve.
  • the control device can have two central units 21 have, one as a main unit and the other as a reserve unit is operated.
  • the central units 21 are with each control module 22 and the sensors 25, 26 connected by means of a bus system.
  • the sensors 25, 26 are like this arranged that all at a certain angular position of the crankshaft Encoder signals are checked for their validity via logic. Becomes a If a fault is found, the defective encoder can also be found.
  • each Control unit 22 controls this using the data from central unit 21 Injection system, the gas exchange system, and the start air valves 28. Falls an inlet controller 27, water injection or sequential Piston lubrication is provided, this is also from the Control module 22 controlled. In normal operation, the two share in FIG.
  • Pulse control shaft 91 are provided, which the electrical Control signals for the pilot units 14 on the duty cycle of the engine generated coordinated.
  • the pulse control shaft 91 is a separate unit that is mechanically connected to the crankshaft of the machine.
  • FIG. 6 shows another embodiment of the injection device.
  • the Pressure pump 7, the accumulator 8 and pilot valves 14 form one hydraulic system for controlling the injection and actuating the Gas exchange.
  • the injection device contains a metering piston 81, a valve slide 82, a control valve 83 and a displacement sensor system 84 for monitoring the position of the metering piston in order to achieve volumetric injection realize.
  • the metering piston is designed as a pressure booster.
  • a Pressure pump 86 pumps the fuel into the pressure booster 81 and that Control valve 83 blocks flow to the injectors.
  • the reciprocating piston internal combustion engine contains an injection system volumetric injection for each cylinder, one or more High pressure pumps to supply fuel, at least one Pressure pump for supplying control medium, one for each Fuel, tax and working oil, which with the pumps as well as with the Gas exchange system communicates with a hydraulic system Organs for controlling the injection and actuation of the gas exchange, one or more angle encoders and a control device with one Central unit and several electronic control modules to the Starting air supply, injection, gas exchange and central lubrication to control.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP99810529A 1998-09-21 1999-06-16 Hubkolbenbrennkraftmaschine Revoked EP0989297B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP99810529A EP0989297B1 (de) 1998-09-21 1999-06-16 Hubkolbenbrennkraftmaschine
DK99810529T DK0989297T3 (da) 1998-09-21 1999-06-16 Stempelforbrændingsmotor

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP98810944 1998-09-21
EP98810944 1998-09-21
EP99810529A EP0989297B1 (de) 1998-09-21 1999-06-16 Hubkolbenbrennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0989297A1 EP0989297A1 (de) 2000-03-29
EP0989297B1 true EP0989297B1 (de) 2004-09-29

Family

ID=8236339

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99810529A Revoked EP0989297B1 (de) 1998-09-21 1999-06-16 Hubkolbenbrennkraftmaschine

Country Status (7)

Country Link
EP (1) EP0989297B1 (ja)
JP (1) JP2000104612A (ja)
KR (1) KR100689947B1 (ja)
CN (1) CN1204337C (ja)
DE (1) DE59910639D1 (ja)
DK (1) DK0989297T3 (ja)
PL (1) PL335359A1 (ja)

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Publication number Priority date Publication date Assignee Title
DE59910639D1 (de) * 1998-09-21 2004-11-04 Waertsilae Schweiz Ag Winterth Hubkolbenbrennkraftmaschine
KR20000030467A (ko) * 2000-02-26 2000-06-05 김원봉 유압 엔진
KR20000036673A (ko) * 2000-03-21 2000-07-05 김원봉 유압엔진 자동차
ITTO20030939A1 (it) * 2003-11-25 2005-05-26 Fiat Ricerche Dispositivo di comando di elettroattuatori induttivi.
GB2410060A (en) * 2004-01-14 2005-07-20 Lotus Car A two-stroke compression-ignition internal combustion engine
EP1561935B1 (de) 2004-02-05 2010-05-05 Wärtsilä Schweiz AG Dieselmaschine, insbesondere Grossdieselmotor, mit einem elektronischen Steuerungssystem
EP1591649B1 (de) * 2004-04-26 2007-03-21 Wärtsilä Schweiz AG Dieselmaschine mit einem elektonische Module umfassenden Steuerungssystem
DE102004035301B4 (de) * 2004-07-21 2015-12-03 Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland Dieselmotor
JP2007085214A (ja) * 2005-09-21 2007-04-05 Nabtesco Corp 機関用流体供給装置の計量機構
PL1767751T3 (pl) * 2005-09-23 2009-01-30 Waertsilae Nsd Schweiz Ag Układ smarowania cylindra w silniku o posuwisto-zwrotnym ruchu tłoka
KR100852546B1 (ko) * 2007-01-29 2008-08-18 대우조선해양 주식회사 오일압력을 이용한 잠수함용 디젤기관의 폐기밸브자동제어구조
US20110308493A1 (en) * 2010-06-17 2011-12-22 Mitchell Robert L Pre start friction protection system
DE102011080736A1 (de) * 2011-08-10 2013-02-14 Schaeffler Technologies AG & Co. KG Dichteinrichtung für ein Schaltventil einer Hydraulikeinheit
JP5552146B2 (ja) * 2012-08-29 2014-07-16 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド 大型２サイクルディーゼルエンジンのためのカム駆動型排気弁作動システム
SE537454C2 (sv) * 2013-10-16 2015-05-05 Freevalve Ab Förbränningsmotor samt gashanteringssystem för pneumatisk drivning av en ventilaktuator

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DE3100725A1 (de) * 1980-12-16 1982-07-01 Gebrüder Sulzer AG, 8401 Winterthur "einrichtung zur gesteuerten foerderung des brennstoffs in einer brennkraftmaschine"
DK167076B1 (da) * 1991-03-26 1993-08-23 Man B & W Diesel Gmbh Krydshoved og stempelstang til en stempelmotor
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KR100350875B1 (ko) * 1997-03-21 2002-11-18 기아자동차주식회사 디젤엔진의 연료 분사펌프
DE59910639D1 (de) * 1998-09-21 2004-11-04 Waertsilae Schweiz Ag Winterth Hubkolbenbrennkraftmaschine

Also Published As

Publication number Publication date
PL335359A1 (en) 2000-03-27
CN1204337C (zh) 2005-06-01
KR20000023307A (ko) 2000-04-25
KR100689947B1 (ko) 2007-03-08
EP0989297A1 (de) 2000-03-29
CN1248671A (zh) 2000-03-29
JP2000104612A (ja) 2000-04-11
DE59910639D1 (de) 2004-11-04
DK0989297T3 (da) 2004-10-25

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