CN101818668B - Crosshead type large two-stroke diesel engine - Google Patents
Crosshead type large two-stroke diesel engine Download PDFInfo
- Publication number
- CN101818668B CN101818668B CN2010101515717A CN201010151571A CN101818668B CN 101818668 B CN101818668 B CN 101818668B CN 2010101515717 A CN2010101515717 A CN 2010101515717A CN 201010151571 A CN201010151571 A CN 201010151571A CN 101818668 B CN101818668 B CN 101818668B
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- Prior art keywords
- exhaust valve
- valve
- cylinder
- hydraulic
- cam
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Classifications
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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
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0223—Variable control of the intake valves only
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- 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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
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- 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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
- F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
Abstract
The invention discloses a crosshead type large two-stroke diesel engine, including: a plurality of cylinders each of which has at least an exhaust valve, at least a cam shaft equipped with a cam which is used to operate at least an exhaust valve correlated with the cylinder, and a hydraulic push rod. The hydraulic push rod is driven by a corresponding cam on the cam shaft. A hydraulic actuator is provided for one valve to move it in the operning direction. A hydraulic pipe is provided for one exhaust valve in order to connect the hydraulic piston pump of the actuator to the hydraulic actuator. An ultra gas exchange valve is associated with one cylinder. An actuating system is independent to the cam shaft to control opening and closing of the ultra gas exchange valve.
Description
The application is that application number is 200710097975.0, the applying date is on April 25th, 2007, denomination of invention is divided an application for the patent application of " cam driven exhaust valve actuating system that is used for large-scale two-stroke diesel engine ".
Technical field
The present invention relates to be used for the cam driven exhaust valve actuating system of internal-combustion engine, relate to the cam driven exhaust valve actuating system that is used for large-scale two-stroke diesel engine particularly.
Background technique
The large-scale two-stroke diesel engine of crosshead for example is used for the propelling of large-scale ocean ship or is used as prime mover of power station.Not only because of its overall dimensions, these two-stroke diesel engines are constructed differently with any other internal-combustion engine.Two stroke principle with use in the time of 50 ℃ viscosity to be lower than the heavy fuel oil (this fuel oil in room temperature time do not flow) of 700cSt, make these two-stroke diesel engines in engine art, constitute a class by itself.
Improve performance and the demand that reduces to discharge and caused being used for the development of the common rail mounted electrichydraulic control exhaust valve actuating system of these large-scale two-stroke diesel engines.An advantage of these systems is to have enhanced flexibility, and its reason is that exhaust valve opens and closes can freely be selected correct time, to meet the operating conditions of motor.Yet these common rail mounted electrohydraulic systems are relatively expensive and more consume energy than traditional cam drive system, and its reason is that the energy that during opening procedure, consumes exceeds required energy, and during closing closed procedure, does not reclaim.These two shortcomings have been offset many advantages of electronic-controlled engine.
Summary of the invention
Under this background, the purpose of this invention is to provide a kind of cam driven exhaust valve system that saves energy, it can be controlled the opening and closing of exhaust valve correct time flexibly.
This purpose realizes that through the large-scale two-stroke diesel engine that crosshead is provided said large-scale two-stroke diesel engine comprises: a plurality of cylinders, and each cylinder is provided with at least one exhaust valve; At least one is provided with the camshaft of cam, and said cam is used to activate said at least one exhaust valve that is associated with each said cylinder; With the hydraulic push rod that each cylinder is associated, said hydraulic push rod comprises: be provided with a hydraulic piston pump for each actuator, said hydraulic piston pump is driven by the respective cams on the camshaft; Be provided with a hydraulic actuator for each exhaust valve, be used for opening mobile this exhaust valve on the direction; Be provided with a hydraulic tubing for each exhaust valve; Be used for the hydraulic piston pump of associated actuator is connected with the related fluid hydraulic actuator, the equipment that wherein is connected with each hydraulic push rod is used for controllably adding perhaps to relevant hydraulic push rod removing hydraulic fluid from this hydraulic push rod.
Through controllably adding hydraulic fluid to this hydraulic push rod, said hydrovalve actuator can be in needed time work arbitrarily.Thereby,, can open said exhaust valve the times prior of opening that profile limited of said camshaft overhead cam through adding hydraulic fluid to said pipeline before the time point of effectively working at this cam.
Can also and after the effective time of cam section, remove hydraulic fluid in annex solution hydraulic fluid during the effective time of the cam section, closing of exhaust valve is deferred to the time point behind the exhaust valve closing time point that is limited cam profile.
Said equipment can comprise: be connected to the may command pressurized hydraulic fluid source of each hydraulic push rod and be connected to the may command fluid outlet of each said hydraulic push rod.
Said equipment can be configured to before the effective working stage at the cam that is associated with associated cylinder or during add a certain amount of hydraulic fluid to said hydraulic push rod.
Said equipment can be configured to after effective working stage of the cam that is associated with associated cylinder or during remove a certain amount of hydraulic fluid from hydraulic push rod.
The amount of said interpolation or the amount of said removal can be adjustable.
Said equipment can comprise the electrical control hydrovalve that is configured to said hydraulic push rod alternately is connected to pressurized hydraulic fluid source or fluid output.
Said equipment can also comprise the volume restrictions device between said electronic control hydrovalve and said hydraulic push rod.
Said motor can further comprise the position transducer that functionally is coupled to said exhaust valve, and wherein said electronic control hydrovalve is controlled in response to the signal of said position transducer.
Said motor can further comprise resilient member that is used on closing direction, urging this exhaust valve of each exhaust valve.
Said purpose realizes through the large-scale two-stroke diesel engine that a kind of crosshead is provided that also this large-scale two-stroke diesel engine comprises: a plurality of cylinders, and each cylinder is provided with at least one exhaust valve; At least one is provided with the camshaft of cam, and said cam is used to activate at least one exhaust valve that is associated with each cylinder; Hydraulic piston pump of each actuator, said hydraulic piston pump is driven by the respective cams on the camshaft; One of each exhaust valve is used at the hydraulic actuator of opening mobile this exhaust valve on the direction; Hydraulic tubing of each exhaust valve is used for the hydraulic piston pump of associated actuator is connected with the related fluid hydraulic actuator; The extra gas exchange valve that is associated with each cylinder; And actuating system, it is independent of said camshaft and controls the opening and closing of said extra gas exchange valve.
Through the extra gas exchange valve that can be independent of said camshaft control is provided, can keep said extra gas exchange valve to open and the compression pressure and the recoil of control cylinder through after before said exhaust valve, opening said extra gas exchange valve and/or closing said exhaust valve.
Said actuating system can be controlled the opening and closing of said extra gas exchange valve electronically.
When comparing with said exhaust valve, said extra gas exchange valve can be quite little.
Said extra gas exchange valve can be connected to associated cylinder and discharge gas container (receiver).
Said extra gas exchange valve this cylinder of can being correlated with is connected to the ventilation container.
Said actuating system can be connected to the hydraulic actuator of said extra gas exchange valve with further comprising maneuverability.
Said actuating system can be configured to control the recoil and the compression pressure of associated cylinder.
Said actuating system can be configured to exclusively control compression pressure.
According to detailed description, other purpose, characteristic, advantage and the characteristic of large-scale two-stroke diesel engine of the present invention will become more obvious.
Description of drawings
In the detailed part below this specification, will explain the present invention in more detail with reference to the illustrative embodiments shown in the accompanying drawing, in said accompanying drawing:
Fig. 1 is the cross-sectional view according to motor of the present invention;
Fig. 2 is the longitdinal cross-section diagram of a cylinder portion shown in Fig. 1;
Fig. 3 is the symbol table diagrammatic sketch according to exhaust valve actuating system first mode of execution of the present invention;
Fig. 4 is the symbol table diagrammatic sketch according to exhaust valve actuating system second mode of execution of the present invention;
Fig. 5 is the symbol table diagrammatic sketch according to exhaust valve actuating system the 3rd mode of execution of the present invention; With
Fig. 6 is the symbol table diagrammatic sketch according to exhaust valve actuating system the 4th mode of execution of the present invention.
Embodiment
Fig. 1 and 2 shows the cross-sectional view and (cylinder) longitdinal cross-section diagram of motor 1 according to the preferred embodiment of the present invention respectively.Motor 1 be the single current of crosshead to low speed two stroke cross-head diesel engines, it can be propulsion system or prime mover of power station in the steamer.These motors have 4 to 14 cylinder in lines usually.Motor 1 is built on the base 2, and base 2 has the main bearing that is used for crankshaft 3.
Connecting rod 8 is connected to cross head bearing 22 with crankshaft 3.Cross head bearing 22 is guided at vertical guide plane 23.
The A type support case 4 of Welding Design is installed on the base 2.Support case 4 is a Welding Design.At exhaust side, support case 4 is provided with the reduction valve that is used for each cylinder, and is provided with the big hinged door that is used for each cylinder at camshaft side support case 4.Crosshead guide planes and support case 4 form as one.
Piston 13 comprises piston head and piston skirt.Piston head is processed by refractory steel, and has four annular grooves, and the upper and lower surfaces of said annular groove is through the hard chrome coating processing.
Piston rod 14 is connected to crosshead by four screws.Piston rod 14 has two axial bores (invisible among the figure), and said axial bore is communicated to the cold oil pipeline, is formed for the entrance and exit of the cold oil of piston 13.
Cylinder be single current to type and have scavenge port 7, this scavenge port is arranged in gas tank (airbox), this gas tank is provided with the ventilation by turbosupercharger 10 (Fig. 1) supercharging from ventilation container 9 (Fig. 1).
The motor assembling is by one or more turbosupercharger 10, and for the 4-9 Cylinder engine, said turbosupercharger is arranged on front end, and for the motor more than 10 cylinders, said turbosupercharger is arranged on exhaust side.
The air inlet of turbosupercharger 10 is directly passed the admission air silencer (not shown) of turbosupercharger and is formed from engine compartment.Air arrives the scavenge port 7 of cylinder liner 6 through super charge pipe (not shown), air-cooler (not shown) and ventilation container 9 from turbosupercharger 10.
Motor is provided with the ventilation blower fan (not shown) of electric driving.The suction side of blower fan is connected to the ventilation space after air-cooler.Between air-cooler and ventilation container, the safety check (not shown) is installed, when auxiliary blower fan provided air, this safety check automatically cut out.Auxiliary blower fan helps turbocharger compressor under low load and intermediate load condition.
Fuel valve 40 medially is installed in the cylinder head 12.In compression stroke latter stage, injection valve 40 is ejected into fuel under high pressure in the firing chamber 15 with fine mist through its jet nozzles.Exhaust valve 11 medially is installed in the cylinder head in cylinder head 12.In expansion stroke latter stage; Exhaust valve 11 was opened before engine piston 13 is downwards through scavenge port 7; Thereby the combustion gas that are positioned at piston 13 tops in the firing chamber 15 flow out through the exhaust steam passage 16 that leads to waste gas container 17, and the pressure in the firing chamber 15 discharges.Exhaust valve 11 cuts out during piston 13 moves upward once more.Exhaust valve 11 is hydraulic actuatings.
Fig. 3 illustrates first mode of execution according to exhaust valve actuating system of the present invention.For all mode of executions, exhaust valve actuating system is described by single cylinder.In multicylinder engine, will be identical for each cylinder.Exhaust valve actuating system comprises the camshaft 28 (only illustrating) with cam 29.Advance and be connected to the piston of positive displacement pump (positivedisplacement pump) 32 in the surface that roller 30 is followed cam.Positive displacement pump 32 is connected to exhaust valve actuator 34 through pipeline 36.Exhaust valve actuator 34 acts on the bar of exhaust valve 11.Air spring 38 also is connected on the bar of exhaust valve, and the gas pressure in the pressure chamber of air spring 38 urges exhaust valve 11 on closing direction.When exhaust valve actuator 34 pressurization, it urges exhaust valve opening on direction.The position of exhaust valve is measured by the sensor that is connected to electronic engine management system 39.During operation, camshaft 28 rotates in concert along the direction of the arrow that is positioned at mark " TDC " top that marks the associated piston dead center position and the crankshaft of motor.The profile of cam 29 is confirmed the motion of positive displacement pump 32.When positive displacement pump 32 moves upward, force hydraulic fluid to enter into exhaust valve actuator 34 through pipeline 36.Exhaust valve actuator 34 forces exhaust valve 11 to be opened against the pressure in firing chamber and the air spring 38.When positive displacement pump 32 moved downward, air spring 38 urges exhaust valve and exhaust valve actuator 34 makes it to move up, thereby the fluid in the exhaust valve actuator 34 flow back in the positive displacement pump 32.Turn back to camshaft 28 through the pressure that is formed in the positive displacement pump 32 be delivered to the return stroke of most of energy at exhaust valve of exhaust valve actuator 34 between moving period opening of exhaust valve 11 during.Thereby, open in the required hydraulic energy of exhaust valve 11 and have only sub-fraction to dissipate.Cam 29 limit open profile in curve Figure 42 by the thin curve representation in bottom.
Exhaust valve system according to this mode of execution comprises that also a mouth of 3/2 valve (two-position three-way valve), 33,3/2 valves 33 is connected to pipeline 36 through volume restrictions device 41.The inlet of 3/2 valve 33 is the mouths that are connected to pressurized hydraulic fluid source 49, and the outlet of 3/2 valve 33 is connected to discharge pipe or container case.
3/2 valve 33 is controlled by electronic control system electronically.During operation, 3/2 valve 33 can name a person for a particular job that a certain amount of hydraulic fluid adds pipeline 36 to or from its removal at operation circuit needed time.Curve Figure 42 shows the possibility of adding pipeline 36 to or forming from its removal through with hydraulic fluid.Upper curve among curve Figure 42 is represented the position of exhaust valve 11 when a certain amount of hydraulic fluid has added in the pipeline 36.Through before cam 29 begins to work, a certain amount of hydraulic fluid being added in the pipeline 36, exhaust valve 11 can be early than being opened the time that profile limited of cam 29.Through changing the position of 3/2 valve 33, the amount of hydraulic fluid of interpolation can be removed before or after the time point that is limited on cam 29.Volume restrictions device 41 is guaranteed to add or the amount of the volume removed from pipeline 36 can not become excessive.If the adding quantity of hydraulic fluid was removed before the shut-in time point of exhaust valve 11 by the contour limit of cam 29, exhaust valve will cut out according to the time point that cam 29 is limited.If the adding quantity of hydraulic fluid is removed after the shut-in time point of exhaust valve 11 by the contour limit of cam 29, exhaust valve will stay open in longer a period of time.According to the exhaust valve actuating system of this mode of execution the possibility of adjustment characteristic curve (profiling) is provided, has promptly changed opening correct time and changing closing correct time of exhaust valve 11 of exhaust valve 11.Through controlling 3/2 valve 33, allow changing between the lower curve on curve Figure 42 at any needed time during the engine cycles according to the exhaust valve actuating system of this mode of execution.Can regulate the recoil and the compression pressure of cylinder through the opening and closing that change exhaust valve 11 correct time.Optimization correct time/characteristic the algorithm and the storage that are used for the opening and closing of exhaust valve 11 be in electronic control system, and use according to operating conditions and engine characteristics.
Fig. 4 shows second mode of execution according to exhaust valve actuating system of the present invention, and second mode of execution is substantially the same with the mode of execution of describing with reference to Fig. 3, but has following difference.3/2 valve is substituted by hydraulic control servovalve 35.Said servovalve is connected to pressurized hydraulic fluid source 49 and is connected to container case.Servovalve 35 is hydraulically controlled by control valve 37, and this control valve 37 is electrically controlled by the electronic control system of motor.The electronic control system of motor is used the tram of confirming servovalve 35 from the signal of position transducer 39.Curve Figure 42 shows the possibility that the characteristic curve to opening and closing exhaust valve 11 that can be obtained by this mode of execution changes.Mode of execution thus; Can obtain any position between the lower curve; Its reason is, add the amount of hydraulic fluid of pipeline 36 to and perhaps can freely select from the amount of hydraulic fluid of its removal, and said amount is confirmed by the volume restrictions device in the mode of execution of Fig. 3.Thereby this mode of execution is in the flexibility that further raising is provided aspect the characteristic curve of the opening and closing of exhaust valve 11.
Fig. 5 shows the 3rd mode of execution of the present invention.In this mode of execution, hydraulic valve actuation is also used the hydraulic push rod system, and this hydraulic push rod system comprises positive displacement pump 32, and this positive displacement pump is connected to hydrovalve actuator 34 by pipeline 36.Yet in this mode of execution, cylinder 6 is provided with extra gas exchange valve 46.Extra gas exchange valve 46 is Comparatively speaking quite little with exhaust valve 11, and the little opening that leads to exhaust duct is provided.Extra gas exchange valve 46 is opened and closed by little hydraulic actuator 44, and this little hydraulic actuator 44 is by the electronic control system control of motor.The operation of actuator 44 is totally independent of the operation of camshaft actuated exhaust valve actuating system.Thereby the opening and closing of extra gas exchange valve 46 can optimally be chosen as consistent with applicable cases correct time.Through opening extra gas exchange valve 46 before the time point of opening exhaust valve 11 in being used to of limiting on cam 29, can reduce recoil.Through keeping extra gas exchange valve 46 to open after the time point of closing exhaust valve 11 in being used to of limiting on cam 29, can reduce compression pressure.Curve Figure 42 has explained the characteristic possibility of the adjustment of this mode of execution.Continous curve is represented the motion of exhaust valve 11, and dotted line is represented the motion of extra gas exchange valve 46.
Fig. 6 shows the 4th mode of execution of the present invention, and the 4th mode of execution is substantially the same with the mode of execution of describing with reference to Fig. 5, but extra gas exchange valve 46 is connected to the ventilation container through pipeline 47.Thereby in this mode of execution, have only the compression pressure can be through extra gas exchange valve regulation.Curve 42 has been explained the adjustment characteristic curve possibility of this mode of execution.Continous curve is represented the motion of exhaust valve 11, and dotted line is represented the motion of extra gas exchange valve 46.
The term that uses in the claim " comprises " does not get rid of other element.Single or a plurality of term that do not spell out that uses in the claim is not got rid of a plurality of.
Although described the present invention for illustrative purposes and in detail, it will be appreciated that these details only are used to the purpose explained, those skilled in the art can change under the situation that does not depart from the scope of the invention within it.
Claims (7)
1. the large-scale single current of a crosshead is to the low speed two-stroke diesel engine, and it comprises:
A plurality of cylinders, each cylinder is provided with at least one exhaust valve,
At least one is provided with the camshaft of cam, and said cam is used to activate at least one exhaust valve that is associated with each said cylinder,
For each exhaust valve respectively be provided with one, be used for the hydraulic actuator that moves this exhaust valve opening on the direction,
For each hydraulic actuator respectively is provided with one hydraulic piston pump, said hydraulic piston pump is driven by the respective cams on the said camshaft,
For each exhaust valve respectively is provided with one hydraulic tubing, be used for the hydraulic piston pump of associated actuator is connected with the related fluid hydraulic actuator,
The additional gas crossover valve that is associated with each cylinder, and
Actuating system, it is independent of said camshaft and controls the opening and closing of said additional gas crossover valve,
Wherein, said actuating system is configured to control compression pressure through after closing said time of outlet valve point in being used to of being limited on said cam said additional gas crossover valve being opened.
2. motor according to claim 1, wherein said actuating system is controlled the opening and closing of said additional gas crossover valve electronically.
3. motor according to claim 2, wherein, said additional gas crossover valve is less than said exhaust valve.
4. motor according to claim 2, wherein said additional gas crossover valve is connected to the discharge gas container with associated cylinder.
5. motor according to claim 2, wherein said additional gas crossover valve is connected to the ventilation container with associated cylinder.
6. motor according to claim 2, wherein said actuating system also comprises the hydraulic actuator that is operatively connected to said additional gas crossover valve.
7. motor according to claim 1, wherein said actuating system further are configured to through opening the recoil that said additional gas crossover valve reduces associated cylinder before opening said time of outlet valve point in being used to of being limited on said cam.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007-092853 | 2007-03-30 | ||
| JP2007092853A JP2008248838A (en) | 2007-03-30 | 2007-03-30 | Cam driven exhaust valve operation system for large size two cycle diesel engine |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007100979750A Division CN101275474B (en) | 2007-03-30 | 2007-04-25 | Cross head type large two-stroke diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101818668A CN101818668A (en) | 2010-09-01 |
| CN101818668B true CN101818668B (en) | 2012-09-05 |
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ID=39974063
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007100979750A Expired - Fee Related CN101275474B (en) | 2007-03-30 | 2007-04-25 | Cross head type large two-stroke diesel engine |
| CN2010101515717A Expired - Fee Related CN101818668B (en) | 2007-03-30 | 2007-04-25 | Crosshead type large two-stroke diesel engine |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007100979750A Expired - Fee Related CN101275474B (en) | 2007-03-30 | 2007-04-25 | Cross head type large two-stroke diesel engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2008248838A (en) |
| KR (1) | KR100885456B1 (en) |
| CN (2) | CN101275474B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101495718B (en) * | 2007-09-04 | 2011-12-21 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Large-sized two-stroke diesel engine with outward mobile exhaust valve |
| WO2013000155A1 (en) * | 2011-06-30 | 2013-01-03 | Lio Pang-Chian | Hydraulic remote transmission control device |
| CN103362730B (en) * | 2012-06-13 | 2016-08-10 | 摩尔动力(北京)技术股份有限公司 | Impulse steady flow unit |
| DK177695B1 (en) * | 2012-11-16 | 2014-03-17 | Man Diesel & Turbo Deutschland | A large slow running turbocharged two-stoke uniflow internal combustion engine with crosshead and a cam driven exhaust valve actuation system |
| CN104500163B (en) * | 2014-12-16 | 2017-06-09 | 武汉科技大学 | A kind of opening and closing device of dimethyl ether engine main and auxiliary combustor channel valve |
| US9506382B2 (en) * | 2015-03-30 | 2016-11-29 | Caterpillar Inc. | Variable valve actuator |
| CN105485407A (en) * | 2015-12-29 | 2016-04-13 | 沪东重机有限公司 | Gas exhaust valve drive system with stroke capable of being compensated and regulated |
| DK179120B1 (en) * | 2016-02-03 | 2017-11-13 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A large turbocharged two-stroke compression-ignited internal combustion engine with blow-off control |
| CN111502836A (en) * | 2020-04-12 | 2020-08-07 | 哈尔滨工程大学 | Control method for exhaust valve of low-speed two-stroke diesel engine |
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| US5168848A (en) * | 1990-12-01 | 1992-12-08 | Mercedes-Benz Ag | Engine brake for a multi-cylinder internal combustion engine |
| CN2360610Y (en) * | 1998-11-19 | 2000-01-26 | 艾国富 | I. C engine distribution mechanism arranged with exhaust delay close auxiliary inlet deivce |
| US20030140876A1 (en) * | 2002-01-30 | 2003-07-31 | Zhou Yang | Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve |
| CN1657752A (en) * | 2005-03-11 | 2005-08-24 | 大连理工大学 | Low compresion ration and high expansion ratio combustion system of diesel engine |
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| US5537976A (en) * | 1995-08-08 | 1996-07-23 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
| JPH09327418A (en) * | 1996-06-12 | 1997-12-22 | Oshima Kogyo Kk | Toilet seat for toilet |
| DK173421B1 (en) | 1997-05-16 | 2000-10-02 | Man B & W Diesel As | Hydraulic system for a two-stroke cross-head motor and with single-strand high-pressure feeder |
| EP0909883B1 (en) * | 1997-10-14 | 2002-12-11 | Wärtsilä Schweiz AG | Arrangement and method for valve driving in a reversible diesel engine |
| CN2413027Y (en) * | 1999-12-16 | 2001-01-03 | 郭来顺 | Hydraulic starting or stopping device for air inlet or exhaust valve of internal combustion engine |
| JP2004084670A (en) | 2002-08-28 | 2004-03-18 | Man B & W Diesel As | Valve operated with hydraulic pressure |
| WO2004102008A2 (en) * | 2003-05-06 | 2004-11-25 | Jacobs Vehicle Systems, Inc. | System and method for improving performance of hydraulic actuating system |
| DE102005003552B4 (en) * | 2005-01-26 | 2007-05-03 | Man B & W Diesel A/S | Crosshead engine |
-
2007
- 2007-03-30 JP JP2007092853A patent/JP2008248838A/en active Pending
- 2007-04-25 CN CN2007100979750A patent/CN101275474B/en not_active Expired - Fee Related
- 2007-04-25 CN CN2010101515717A patent/CN101818668B/en not_active Expired - Fee Related
- 2007-05-23 KR KR1020070050414A patent/KR100885456B1/en active IP Right Grant
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5168848A (en) * | 1990-12-01 | 1992-12-08 | Mercedes-Benz Ag | Engine brake for a multi-cylinder internal combustion engine |
| CN2360610Y (en) * | 1998-11-19 | 2000-01-26 | 艾国富 | I. C engine distribution mechanism arranged with exhaust delay close auxiliary inlet deivce |
| US20030140876A1 (en) * | 2002-01-30 | 2003-07-31 | Zhou Yang | Engine valve actuation system and method using reduced pressure common rail and dedicated engine valve |
| CN1657752A (en) * | 2005-03-11 | 2005-08-24 | 大连理工大学 | Low compresion ration and high expansion ratio combustion system of diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101275474A (en) | 2008-10-01 |
| KR100885456B1 (en) | 2009-02-24 |
| CN101275474B (en) | 2010-09-08 |
| KR20080089123A (en) | 2008-10-06 |
| CN101818668A (en) | 2010-09-01 |
| JP2008248838A (en) | 2008-10-16 |
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