CN100346065C - Two-stroke turbocharged internal combustion engine having 14 cylinders in a single row - Google Patents
Two-stroke turbocharged internal combustion engine having 14 cylinders in a single row Download PDFInfo
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- CN100346065C CN100346065C CNB2004100366476A CN200410036647A CN100346065C CN 100346065 C CN100346065 C CN 100346065C CN B2004100366476 A CNB2004100366476 A CN B2004100366476A CN 200410036647 A CN200410036647 A CN 200410036647A CN 100346065 C CN100346065 C CN 100346065C
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 27
- 238000010304 firing Methods 0.000 claims abstract description 57
- 230000002000 scavenging effect Effects 0.000 claims description 51
- 239000002912 waste gas Substances 0.000 claims description 26
- 239000007789 gas Substances 0.000 claims description 16
- 230000001914 calming effect Effects 0.000 claims description 2
- 230000008676 import Effects 0.000 claims description 2
- 230000010349 pulsation Effects 0.000 abstract description 10
- 102220212642 rs747431847 Human genes 0.000 description 10
- 230000000694 effects Effects 0.000 description 9
- 102220279244 rs1555053901 Human genes 0.000 description 9
- 238000000034 method Methods 0.000 description 8
- 230000008859 change Effects 0.000 description 7
- 230000007246 mechanism Effects 0.000 description 7
- 102220300875 rs1554026816 Human genes 0.000 description 7
- 239000000446 fuel Substances 0.000 description 6
- 230000008569 process Effects 0.000 description 6
- 102220298895 rs1025502215 Human genes 0.000 description 6
- 102220187649 rs145044428 Human genes 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000007599 discharging Methods 0.000 description 3
- 238000004590 computer program Methods 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000001788 irregular Effects 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000010408 sweeping Methods 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000000779 smoke Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
-
- E—FIXED CONSTRUCTIONS
- E03—WATER SUPPLY; SEWERAGE
- E03C—DOMESTIC PLUMBING INSTALLATIONS FOR FRESH WATER OR WASTE WATER; SINKS
- E03C1/00—Domestic plumbing installations for fresh water or waste water; Sinks
- E03C1/12—Plumbing installations for waste water; Basins or fountains connected thereto; Sinks
- E03C1/122—Pipe-line systems for waste water in building
- E03C1/1222—Arrangements of devices in domestic waste water pipe-line systems
-
- 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
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/20—Multi-cylinder engines with cylinders all in one line
-
- E—FIXED CONSTRUCTIONS
- E03—WATER SUPPLY; SEWERAGE
- E03C—DOMESTIC PLUMBING INSTALLATIONS FOR FRESH WATER OR WASTE WATER; SINKS
- E03C1/00—Domestic plumbing installations for fresh water or waste water; Sinks
- E03C1/12—Plumbing installations for waste water; Basins or fountains connected thereto; Sinks
- E03C2001/1206—Pipes with specific features for influencing flow characteristics
-
- E—FIXED CONSTRUCTIONS
- E03—WATER SUPPLY; SEWERAGE
- E03C—DOMESTIC PLUMBING INSTALLATIONS FOR FRESH WATER OR WASTE WATER; SINKS
- E03C2201/00—Details, devices or methods not otherwise provided for
- E03C2201/60—Reducing noise in plumbing systems
-
- 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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- 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
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B2075/1804—Number of cylinders
- F02B2075/1856—Number of cylinders fourteen
-
- 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
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Public Health (AREA)
- Water Supply & Treatment (AREA)
- Hydrology & Water Resources (AREA)
- Health & Medical Sciences (AREA)
- Environmental & Geological Engineering (AREA)
- Structural Engineering (AREA)
- Supercharger (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Ignition Installations For Internal Combustion Engines (AREA)
- Characterised By The Charging Evacuation (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
A two-stroke turbocharged internal combustion engine has 14 cylinders in a single row and a scavenge air system with at least one elongated scavenge air receiver. The engine has a firing sequence (n1 - n14) of the engine cylinders C1-C14, so that at least the following four requirements a) to d) are met : for the 4<th> order gas pulsation <MATH> for the 5<th> order gas pulsation <MATH> for the 6<th> order gas pulsation <MATH> for the 7<th> order gas pulsation <MATH> where n is the cylinder number, [phi]n is the firing angle for the cylinder n, F(n) is a weighting function linearly interpolated with respect to the position of the cylinder between F(1) = 1 at cylinder C1 and F(14) = -1 at cylinder C14, and PARALLEL identifies the length of the vector.
Description
Technical field
The present invention relates to a kind of turbo charged 14 cylinder two-stroke internal-combustion engines in upright arrangement, it has at least one waste gas receiver, at least two turbosupercharger, an and scavenging system, scavenging system wherein has the scavenging receiver of at least one lengthwise, each cylinder all has a scavenging import that is connected with the scavenging receiver, and exhaust passage, the exhaust passage is passed in described at least one waste gas receiver, the turbo-side of described turbosupercharger is connected with the waste gas receiver, the pusher side of calming the anger then is connected with scavenging system, and 14 cylinder C1-C14 of this motor have certain firing order (n1-n14).
Background technique
The motor that has the scavenging receiver adopts so-called constant pressure type turbosupercharging, the constant pressure type turbosupercharging is based on such principle realization: by being transported to the public waste gas receiver from the waste gas that each cylinder is discharged through the exhaust passage of correspondence, the exhaust flow average pulseization that each cylinder can be discharged, waste gas receiver wherein is the pressurized container of a lengthwise, it has enough big volume, thereby can make the high strength air-flow pulse of discharging from cylinder be expanded to the common air-flow that is under the middle pressure in sizable degree.
When engine loading is constant, the waste gas that the turbine portion branch of turbosupercharger receives also is on the constant compression force, this can improve the efficient of turbosupercharger, and make the gas compressor part of turbosupercharger stably carry air inlet to the scavenging system that is positioned at cylinder suction port one side.The pressure surge of waste gas receiver then can cause the power of turbosupercharger to fluctuate, so can change flow to gas charging system fill the cylinder air, make and fill the cylinder air and become inhomogeneous.
Carry to sweep to engine intake one side and blow air and can have influence on filling the inflation effect of cylinder air, thereby can have influence on combustion process in the cylinder and the power that sends by burning cylinder.The length of straight engine with 14 cylinders is very long, thereby also has very long scavenging receiver.The variation in pressure of filling the cylinder air of discharging from turbosupercharger can cause the pressure change the scavenging receiver to a certain extent.But, cause pressure in the scavenging receiver to take place to be then than the reason of great fluctuation process each cylinder uses sweeping in the scavenging receiver to blow/fill the cylinder air according to which type of pattern.
For the two stroke IC engine of 14 cylinders, have such problem: the fluctuation of air pressure can cause by filling the effect that the cylinder air inflates each cylinder and there are differences in described at least one scavenging receiver.Such inflation difference can appear at a distance of between two cylinders of certain distance, thereby the power that the combustion process that causes each cylinder is exported is also inequality, and this is a kind of disadvantageous situation, and inflation difference also has influence on control to cylinder-especially aspect the fuel dispensed amounts.
Summary of the invention
The objective of the invention is: when engine running in constant voltage load state following time, reduce or eliminate the fluctuation of engine air cylinder fuel dispensed amounts, wherein, the fluctuation of fuel dispensed amounts is owing to fill the cylinder air to due to the inflation effect change of cylinder.
Consider above-mentioned situation, two-stroke constant pressure type turbocharging internal-combustion engines according to the present invention is characterised in that: the firing order of 14 cylinders (n1-n14) can make following four to require a)-d) satisfied at least:
Quadravalence pulsation for gas
a)
Five rank pulsation for gas
b)
Six rank pulsation for gas
c)
Seven rank pulsation for gas
d)
In the formula, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, and this function is at cylinder C
1The time linear interpolation between the F (14)=-1 of F (1)=1 when the cylinder C14, || the mould of representation vector is long.The mould length of vector calculates in a conventional manner: the root sum square that promptly equals resultant sine value square and cosine value square.
If the firing order of 14 cylinder IC engines meets these several above-mentioned requirements, then cause the main source that pressure takes place to fluctuate in the scavenging receiver just to be reduced to very low degree, make the fuel dispensed amounts of cylinder can not be subjected to the influence of scavenging pressure fluctuation basically.The firing order that satisfies above-mentioned requirements makes each cylinder can not cause the big fluctuation of air pressure generation in the scavenging receiver to sweeping the consumption of blowing air and filling the cylinder air in the scavenging receiver successively.
In a preferred embodiment, the firing order of 14 cylinders (n1-n14) also satisfies the following e that requires):
e)
In the formula, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, for cylinder C1, and F (1)=0, and F (n)=F (n-1)+cylinder C
N-1Center line is to cylinder C
nNominal range between the distance/cylinder of center line, || the mould of representation vector is long.Nominal range is meant two distances between the cylinder that only has single main bearing each other between cylinder, and this distance typically refers to the distance between cylinder C1 center line and the C2 center line.In 14 Cylinder engines, bent axle generally is made into two sections, utilizes bolt usually, between certain two cylinder these two parts is joined to together.Thereby, between these two cylinders, just there are two main bearings, the separation distance between them is greater than described nominal range.
The elongated straight engine of 14 cylinder two-stroke motors etc. is often used as the pusher of boats and ships.By the condition e that meets the demands), can also promote further according to a) to d) requirement condition design the obtainable advantage of firing order.Require e) also have so favourable part: can reduce the so-called moment of dehiscing (nick-moment).The moment of dehiscing is the weighting sum of the vertical force of each cylinder action on pull bar and main bearing.The moment of dehiscing is tending towards making motor and hull to produce disadvantageous vibration in vertical plane.
In another embodiment, the firing order of 14 cylinders (n1-n14) also satisfies the following f that requires):
f)
In the formula, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, for cylinder C1, and F (1)=0, and F (n)=F (n-1)+cylinder C
N-1Center line is to cylinder C
nNominal range between the distance/cylinder of center line, || the mould of representation vector is long.The second order moment of dehiscing is the weighting sum of the second order vertical force of each cylinder action on pull bar and main bearing.The second order moment of dehiscing can cause disadvantageous vertical vibration.The firing order (n1-n14) of 14 Cylinder engines can also be designed to can satisfy the above-mentioned e that requires) and f), this moment influence that can reduce to dehisce to the hull vertical vibration.Preferably Vnick (2) is less than 3.0, more preferably less than 2.0.
In a highly preferred mode of execution, the firing order of 14 cylinders (n1-n14) is designed to make:
A) for 4 rank air pulsings, Vgas (4)＜1;
B) for 5 rank air pulsings, Vgas (5)＜2;
C) for 6 rank air pulsings, Vgas (6)＜2;
D) for 7 rank air pulsings, Vgas (7)＜2.2;
E) for the 1 rank moment of dehiscing, Vnick (1)＜1.5;
F) for the 2 rank moment of dehiscing, Vnick (2)＜1.5,
The firing order that satisfies these conditions makes the scavenging receiver obtain uniform pressure distribution in its length range, relevant therewith, the operational situation of motor is good especially, and in addition, it is highly beneficial that level of vibration becomes on the whole, on this meaning, common all vibration levels of considering all are in the acceptable limit.Reach in 6227020800 kinds of possible even firing orders at 14 Cylinder engines, only satisfy these above-mentioned conditions less than 600 kinds of even firing orders.
Firing order can be uniformly, and on this meaning, the crank angle between two order cylinders are got angry successively is 360 °/14.All cylinders in the angle motor of this fixed size all are suitable for.If there is special problem in the installation of certain specific engines, then also can come the characteristic curve of vibration is finely tuned by employing and uneven firing order, on this meaning, at least two pairs of crank angles of getting angry successively between the cylinder are not equal to 360 °/14.
Description of drawings
Below with reference to some highly the accompanying drawing of signal several mode of executions of the present invention are explained in detail, in the accompanying drawings:
Fig. 1 is the sectional view according to two-stroke 14 Cylinder engines of the present invention;
Fig. 2 is the side view of motor shown in Figure 1;
Axonometric drawing among Fig. 3 has been represented the bent axle of motor shown in Figure 1;
Schematic representation among Fig. 4 is represented the cylinder firing order relevant with bent axle shown in Figure 3;
Fig. 5 has represented the different mode of air pulsing in the scavenging receiver; And
Fig. 6 has expressed each active force that forms the moment of dehiscing.
Embodiment
Fig. 1 is the sectional view that a large cross-head formula two stroke IC engine is done, and this internal-combustion engine belongs to the constant voltage turbocharged type, and it has 14 cylinders.This motor for example can be by MAN B﹠amp; MC or ME diesel engine that W Diesel A. S. makes, or Sulzer RT-flex or the Sulzer RTA type unit made by W rtsil company.The cylinder diameter of cylinder for example between 60 to 120cm, is preferably 80 to 120cm, more preferably between 95 to 120cm.The power of motor for example be every cylinder 3000kW to 8500kW, be preferably 4000kW to the every cylinder of 8000kW/, for example be at least every cylinder 5000kW.Usually, all have a row scavenging port 2 on the lower end of each cylinder C1-C14 cylinder sleeve 1, the top of cylinder then is provided with a cylinder cap 3 that has outlet valve 4.
A piston 5 is installed on piston rod 6, and piston rod 6 is connected with a crank pin 9 on the bent axle 10 by a crosshead 7 and a connecting rod 8.The axle journal 11 of bent axle is positioned at main bearing, and main bearing is installed in the support 12.
Described crosshead is being supported by slide block 13 in the horizontal, and slide block 13 slides on vertically extending guide surface.Guide surface is fixed on the internal-combustion engine on the fixed frame type A 14.At the top of frame type A cylinder block 15 is installed.
Location at the outlet valve place, exhaust manifolds 18 are drawn from each cylinder, and are passed in the waste gas receiver 19, and this waste gas receiver is that all cylinders are shared.Motor can only have one by the shared waste gas receiver of all cylinders, perhaps also can have a plurality of waste gas receivers-for example two or three, they can be arranged in delegation end to end, and utilize air-flow path to be interconnected usually.
The waste gas receiver is that cross section is the pressurized container of drum.Waste gas duct 18 extend in the waste gas receiver 19, and when outlet valve was opened, it transferred out waste gas from relevant firing chamber.In the waste gas receiver, the pressure surge that produces owing to the waste gas of discharging pulsation from waste gas duct 18 is more average pressure by equilibrium.
Four turbosupercharger 20 on waste gas receiver 19, have been connected according to certain mode, so that waste gas can flow through the turbine part 22 of turbosupercharger through exhaust steam passage 21, in the turbine part, waste gas is as the driving working medium of turbine wheel, turbine is installed on the live axle of a compressor impeller, and compressor impeller is arranged in the gas compressor part 23 of turbosupercharger.Gas compressor part 23 can be carried pressurized air along the direction shown in the arrow A, make air stream through an air passageways 24 and also flow through a charge air cooler 25 if possible and enter into scavenging system 26.
Scavenging system comprises at least one scavenging receiver 27, it is shared by several cylinders or all cylinders, and all be provided with an air-flow path 28 for each cylinder, this passage is communicated with a suction chamber 29 with the scavenging receiver, thereby air inlet can be filled in the suction chamber in the direction of arrow B, and fall these air by cylinders consume.The scavenging receiver is that a cross section is circular cylindrical pressure vessel.Suction port place in scavenging receiver 27 bottoms is provided with check valve 31.
Air inlet both had been called as to sweep blows air, is also referred to as and fills the cylinder air.Two titles all are meant same things-be the air inlet of motor.But, for two stroke engine, when outlet valve is opened, need utilize air inlet to come the firing chamber carried out to sweep to blow (cleaning) and work, so that products of combustion is blown out, and after exhaust valve closure, air inlet is used to cylinder is inflated, and is used to next time combustion process to get ready.Suction chamber 29 has the bottom of scavenging port 2 around cylinder sleeve 1.
In the combustion stroke of two stroke cycle, piston 5 moves downward, and is positioned at the lower dead point position place of the lower portion of cylinder sleeve until arrival, and on lower dead centre, the upper surface of piston is lower than scavenging port 2.In the process that piston moves downward, when piston process scavenging port, air flow in the cylinder from suction chamber 29, thereby the pressure in the described suction chamber is descended, and make in the scavenging receiver regional area near air flow channel 28 pressure also occur to fall that air flow channel 28 wherein leads to cylinder.
Partial pressure associated in the consumption of air and the scavenging receiver reduced appearing at each bar air flow channel 28 place, these air flow channels 28 are to arrange along the length direction of scavenging receiver.Each cylinder consumed cabin air successively on each time point, time point wherein depends on the firing order of motor.Owing to the situation of carrying air inlet to cylinder changes with the change of position in time, so the air in the scavenging receiver is fluctuateed.Except some other factor, the natural frequency of vertical pressure waves depends on the length of receiver in the scavenging receiver.
Scavenging receiver shown in Figure 5 is shared by all cylinders in the motor, thereby its extended length reaches the total length of motor.The minimum natural frequency of airwaves is corresponding to so-called single order air pulsing in the scavenging receiver, and in this rank pattern, the pressure at place, receiver two end part is anti-phase, and the position of velocity variations maximum is the midpoint at receiver.In Fig. 5, the single order air pulsing is represented by curve a.Second order air pulsing pattern is then represented by the curve b among Fig. 5.Obviously, single order air pulsing pattern only has individual node 32, and second order air pulsing pattern then has two nodes 32, and the like, the every increase one-level of exponent number, just other increases by one to node.
Can the process of consumed cabin air excite the ability of air generation dynamic oscillation in the scavenging receiver to depend on the firing order of motor and current engine speed successively.If the air pressure wave frequency is consistent with the natural frequency of a certain specific rank air pulsing, then just sizable air pressure fluctuation may appear.These disadvantageous air pressure fluctuations may influence inflation effect to cylinder-especially for those node 32 cylinders farthest apart from the coupled vibration rank.
Certainly, the scavenging receiver can be divided into the receiver section of several end-to-ends.Even now makes to change the length of single scavenging receiver, but can not solve the problem of pressure surge, reason is: at first, pressure surge still can occur, secondly, receiver is segmented in the air quantity that may cause each turbosupercharger output simultaneously takes place to change more significantly, and such variable quantity can't obtain equilibrium in the single scavenging receiver shared by all cylinders.
By a)-d) selecting firing order according to above-mentioned requirements, the order of each cylinder from scavenging receiver input air can be designed to like this: make the cylinder charge effect be subjected to the influence of scavenging fluctuation and the degree that changes is very little, the amount of fuel of each cylinder is regulated so that can not disturb.
Listed below and satisfied above-mentioned requirements a) to f) some examples of firing order:
Sequence number C1 is to the firing order of C14 cylinder
1 1-4-9-14-7-2-6-11-12-5-3-8-10-13
2 1-4-9-14-7-2-6-12-11-5-3-8-10-13
3 1-5-8-14-7-2-6-11-12-4-3-9-10-13
4 1-5-8-14-7-2-6-11-13-4-3-9-10-12
5 1-5-8-14-7-2-6-13-11-4-3-9-10-12
6 1-5-9-14-7-2-6-11-12-4-3-8-10-13
7 1-5-11-12-6-2-8-10-13-3-4-7-14-9
8 1-6-9-14-5-2-7-12-11-4-3-8-13-10
9 1-6-9-14-5-2-7-13-11-3-4-8-12-10
10 1-6-10-14-2-5-7-12-11-3-4-9-13-8
11 1-6-11-13-2-5-7-14-9-3-4-10-12-8
12 1-6-11-14-2-5-7-12-10-3-4-9-13-8
13 1-6-11-14-2-5-7-12-10-4-3-9-13-8
14 1-6-11-14-2-5-7-13-9-3-4-10-12-8
15 1-6-11-14-2-5-7-13-10-3-4-9-12-8
16 1-6-13-11-4-2-8-14-7-5-3-12-10-9
17 1-6-13-11-4-2-9-14-7-5-3-12-10-8
18 1-7-10-14-2-5-6-12-11-3-4-9-13-8
19 1-7-13-11-4-2-9-14-6-5-3-12-10-8
20 1-8-10-13-2-4-9-14-7-3-5-11-12-6
21 1-8-11-12-2-4-9-14-7-3-5-10-13-6
22 1-8-11-12-2-5-7-13-9-3-4-10-14-6
23 1-8-12-9-5-2-10-13-7-4-3-14-11-6
24 1-8-12-10-4-2-11-13-6-5-3-14-9-7
25 1-8-12-10-5-2-9-14-7-4-3-13-11-6
26 1-8-13-9-2-4-11-12-6-5-3-14-10-7
27 1-8-13-9-4-2-11-12-6-5-3-14-10-7
28 1-9-12-8-5-2-11-13-7-4-3-14-10-6
29 1-9-12-10-2-3-13-11-6-4-5-14-8-7
30 1-9-12-10-2-3-13-11-6-5-4-14-8-7
31 1-9-12-10-3-2-13-11-6-4-5-14-8-7
32 1-9-12-10-4-2-11-13-6-3-5-14-8-7
33 1-10-11-9-4-2-12-13-5-3-6-14-8-7
34 1-10-11-9-4-2-13-12-5-3-6-14-8-7
35 1-10-12-9-2-4-13-11-5-3-6-14-8-7
36 1-10-13-8-2-4-12-11-7-3-5-14-9-6
37 1-11-10-9-4-2-12-13-5-3-6-14-8-7
38 1-12-10-9-2-4-13-11-5-3-7-14-8-6
39 1-12-11-8-2-4-13-10-7-3-6-14-9-5
40 1-12-11-8-2-5-13-10-6-3-7-14-9-4
41 1-13-10-8-2-5-12-11-6-3-7-14-9-4
42 1-13-10-8-2-6-12-11-5-3-7-14-9-4
43 1-14-10-8-2-6-12-11-5-3-7-13-9-4
44 1-14-11-6-2-8-12-10-4-3-9-13-7-5
Other firing order also can satisfy above-mentioned requirement condition, thereby the firing order of listing above should be counted as the preferred but firing order example of indefiniteness of 14 Cylinder engines.
Following firing order can satisfy in the claim 5 condition a)＜1, b)＜2, c)＜2, d)＜2.2, e)＜1.5, f)＜1.5:
45 1-9-14-8-2-4-11-13-5-3-7-12-10-6
46 1-5-10-14-6-2-7-12-11-4-3-8-13-9
47 1-6-14-10-5-2-9-13-8-3-4-11-12-7
48 1-5-11-12-7-2-6-14-10-4-3-8-13-9
49 1-5-11-12-6-2-7-14-10-3-4-8-13-9
50 1-8-13-9-4-2-10-14-6-3-5-12-11-7
51 1-6-11-12-5-2-7-14-10-3-4-9-13-8
52 1-5-12-11-6-2-7-13-10-3-4-8-14-9
Following firing order can satisfy condition a)＜1, b)＜1, c)＜1, d)＜1, e)＜1, f)＜1:
53 1-8-14-9-2-4-11-12-7-3-5-13-10-6
54 1-8-13-9-4-2-11-14-5-3-6-12-10-7
55 1-8-14-9-2-4-12-11-7-3-5-13-10-6
In first kind of above-mentioned firing order, C1 lights a fire according to 149 14 726 111 2538 10 13 order to the C14 cylinder.Abide by the corner pattern that can realize this firing order by bent axle 10 being made the sensing that makes its each throw of crank 33, just can in motor, realize this firing order.This firing order is by the decision of the structural design of bent axle.Fig. 3 has represented to realize first kind of bent axle pattern that firing order is required, and this firing order is that the angle intervals between twice ignition is regular (average) in this firing order of a kind of average firing order-promptly, and it equals 360 °/14.Each throw of crank 33 all comprises two crankwebs 34 and crank pin 9, and crankshaft journal 11 is connected into a complete bent axle with each throw of crank.Crankshaft journal is arranged along the center line 35 of bent axle, and is supported in the main bearing of support 12.
For bent axle shown in Figure 3, the distance L 2=L+L1 between cylinder C7 and C8, distance L between the whole bent axle scope inside cylinder all is identical, the nominal range that distance between cylinder C7, the C8 equals between cylinder adds another one distance L 2, distance L 2 is caused by two main bearings and a bent axle transition joint, the transition joint of bent axle for example is a flange connector, and two sections bent axles get up with bolted joints at this link place.Bent axle can be divided into two sections suitably, so that alleviate the weight of single hop bent axle.Motor is being carried out in the process of assembling, and such design will help bent axle is lifted by crane on the support, but also help the manufacturing of bent axle, and reason is that the weight of whole bent axle of much the same 14 Cylinder engines of size can reach 250t.Distance L 2 between two cylinders of joint is greater than the distance L between other cylinder.The bent axle joint can also be arranged between cylinder C8 and the C9.
Motor can be the electric-control motor that does not have the camshaft that is used to drive fuel pump and outlet valve, and for example the ME h type engine h is this type of type.If motor is the general type that has camshaft, then can pass through a chain drive mechanism or gear mechanism by this camshaft of crank-driven, driving mechanism can be arranged between the two bigger cylinders of separation distance L2 suitably.
Fig. 4 has expressed each corner between the throw of crank 33 on the bent axle shown in Figure 3.Also can adopt irregular firing order-be that firing order is uneven, this is meant that at least two angle interval that (may be several to) be got angry between the cylinder successively are not equal to 360 °/14.Several years that deviation average is very little will cause motor to have different mode of vibration.For the final vibration characteristics of vernier, this irregular firing order is useful.For the air pulsing in the scavenging receiver, as will be in order advantageously to obtain low-level air pulsing, then firing order be very important, and the significance of rule then can't be in contrast to this for firing order.
Generally, be to utilize a computer program to come electronization to calculate a certain specific firing order whether to meet above-mentioned requiring a)-d) and further require e) and/or f), computer program wherein for example is by MAN B﹠amp; The PROFIR program that W Diesel A. S. develops or be disclosed in specification procedure in the document " Die Verbrennungskraftmashing ", document is wherein shown by H.Maass/H.Klier and K.E.Hafner/H.Maass, and is published by the Springer-Verlag publishing house in Wien place, New York.
To illustrate this computational process at 14 Cylinder engines shown in Figure 2 below.This motor is MAN B﹠amp; The product of W Diesel A. S. belongs to the MC type, more specifically is the 14K98MC type, and its cylinder diameter is 0.98 meter, and cylinder is 1.75 meters apart from the nominal value of L.Total length between cylinder C1 median vertical line and the C14 median vertical line is 23.99 meters, and is provided with chain drive mechanism between cylinder C7 and C8.
The length L1 that adds in addition between cylinder C7 and the C8 is 1.24 meters, thereby makes the total distance L 2 between cylinder C7 and the C8 equal 2.99 meters.Adopt above-mentioned first kind of firing order: 149 14 72 6 11 12 538 10 13, can calculate following numerical value.
Cylinder C1 is followed successively by to the ignition angle of C14: 0 °, 128.6 °, 257.1 °, 25.7 °, 231.4 °, 154.3 °, 102.9 °, 282.9 °, 51.4 °, 308.6 °, 180.0 °, 205.7 °, 334.2 ° and 77.1 °.
For the pulsation to air-flow is calculated, utilize approach based on linear interpolation to try to achieve the following numerical value of F (n), interpolation arithmetic is the position with respect to cylinder, carry out between the F (14)=-1 of the F (1)=1 of cylinder C1 and cylinder C14, the result is as follows: F (1)=1, F (2)=0.85411, F (3)=0.70821, F (4)=0.56232, F (5)=0.41642, F (6)=0.27053, F (7)=0.12464, F (8)=-0.1246, F (9)=-0.2705, F (10)=-0.4164, F (11)=-0.5623, F (12)=-0.7082, F (13)=-0.8541, and F (14)=-1.The position of cylinder is calculated as: cylinder Cn motor vertically at a distance of the distance/cylinder C1 center line of cylinder C1 and the total distance between the C14 center line.Thereby F (n) equals 1-2 * (distance/cylinder C1 is to the C14 total length between cylinder Cn and the C1).
With respect to equation a) to f) in the numerical value ω t of vector summation formula because that the mould of vector is tried to achieve by institute is long irrelevant with time t, so it is long to calculate vectorial mould when t=0.
With respect to by a) numerical value of 4 rank gas forces of defined of requirement condition, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=0.37058, C3=-0.5537, C4=0.54822, C5=-0.1807, C6=-0.2637, C7=0.09744, C8=-0.0974, C9=0.11738, C10=-0.1807, C11=0.0000, C12=-0.6905, C13=0.83269 and C14=0.78138, and the summation of sinusoidal component is 0.7814.
For each cylinder, cosine component after equation multiplies each other with F (n) in a) is as follows: C1=1, C2=-0.7695, C3=0.44156, C4=-0.1251, C5=-0.3752, C6=-0.0602, C7=0.07771, C8=-0.0777, C9=0.24374, C10=0.37518, C11=-0.56232, C12=0.15759, C13=0.19006 and C14=-0.6235, and the summation of cosine component is-0.108.The long square root for (0.7814 * 0.7814+-0.108 *-0.108) of mould of the vector of trying to achieve-promptly equal 0.789, this numerical value is much smaller than 2.5.
With respect to by requirement condition b) numerical value of 5 rank gas forces of defined, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=-0.8327, C3=-0.3073, C4=0.43964, C5=0.40598, C6=0.21151, C7=0.05408, C8=0.0541, C9=0.26375, C10=-0.406, C11=0.0000, C12=0.5537, C13=0.6678 and C14=-0.4339, and the summation of sinusoidal component is 0.6707.
For each cylinder, equation b) cosine component after multiplying each other with F (n) in is as follows: C1=1, C2=0.19006, C3=-0.6381, C4=-0.3506, C5=0.09266, C6=0.16867, C7=-0.1123, C8=-0.1123, C9=0.0602, C10=0.09266, C11=0.56232, C12=-0.4416, C13=0.53253 and C14=-0.901, the summation of a plurality of cosine components is 0.1433.The mould length of the vector of trying to achieve is 0.6858, and this numerical value is much smaller than 2.0.
With respect to by requirement condition c) numerical value of 6 rank gas forces of defined, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=0.66777, C3=0.69046, C4=0.24398, C5=-0.3256, C6=-0.1174, C7=-0.1215, C8=0.12151, C9=0.21151, C10=-0.3256, C11=0.0000, C12=-0.3073, C13=0.37058 and C14=-0.9749, the summation of a plurality of sinusoidal components is 0.1336.
For each cylinder, equation c) cosine component after multiplying each other with F (n) in is as follows: C1=1, C2=0.53253, C3=-0.1576, C4=-0.5066, C5=0.25964, C6=-0.2437, C7=-0.0277, C8=0.02773, C9=-0.1687, C10=-0.2596, C11=-0.5623, C12=0.63808, C13=0.76952 and C14=0.22252, the summation of each cosine component is 1.5237.The mould length of the vector of trying to achieve is 1.5295, and this numerical value is much smaller than 2.1.
With respect to by requirement condition d) numerical value of 7 rank gas forces of defined, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=0.0000, C3=0.0000, C4=0.0000, C5=0.0000, C6=0.0000, C7=0.0000, C8=0.0000, C9=0.0000, C10=0.0000, C11=0.0000, C12=0.0000, C13=0.0000 and C14=0.0000, the summation of a plurality of sinusoidal components is 0.00.
For each cylinder, equation d) cosine component after multiplying each other with F (n) in is as follows: C1=1, C2=-0.8541, C3=0.7082, C4=-0.5623, C5=-0.4164, C6=0.2705, C7=0.1246, C8=0.12464, C9=-0.2705, C10=-0.4164, C11=0.5623, C12=-0.7082, C13=0.85411 and C14=1.0, the summation of each cosine component is 1.4164.The mould length of the vector of trying to achieve is 1.4164, and this numerical value is much smaller than 2.2.
In order to calculate and requirement condition e) and f) the relevant moment of dehiscing, calculate the numerical value of function F (n) according to following mode: F (n)=F (n-1)+(cylinder C
N-1Center line is to cylinder C
nNominal range between the distance/cylinder of center line).Nominal range is meant the horizontal equivalent between the median vertical line of adjacent and middle two cylinders that chain drive mechanism is not set between cylinder.If for camshaft is provided with chain drive mechanism, then this chain drive mechanism is usually located at the neutral position of motor on the motor.Thereby, under normal conditions, between cylinder in nominal range and the motor end regions distance between two cylinders identical, it for example equals the distance between cylinder C1 and the C2.For above-mentioned motor, can try to achieve following numerical value: F (1)=0, F (2)=1, F (3)=2, F (4)=3, F (5)=4, F (6)=5, F (7)=6, F (8)=7.70857, F (9)=8.70857, F (10)=9.70857, F (11)=10.70857, F (12)=11.70857, F (13)=12.70857 and F (14)=13.70857.
With respect to by requiring e) the dehisce numerical value of moment of 1 rank of defined, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=0.78183, C3=-1.94499, C4=1.30165, C5=-3.1273, C6=2.1694, C7=5.84957, C8=-7.5153, C9=6.8086, C10=-7.5905, C11=0.0000, C12=-5.0802, C13=-5.514 and C14=13.3649, and the summation of a plurality of sinusoidal components is-0.501.
For each cylinder, equation e) cosine component after multiplying each other with F (n) in is as follows: C1=0, C2=-0.6235, C3=-0.445, C4=2.70291, C5=-2.49396, C6=-4.50484, C7=-1.3351, C8=1.71532, C9=5.42971, C10=6.0532, C11=-10.7086, C12=-10.549, C13=11.45 and C14=3.0504, the summation of each cosine component is-0.258.The mould length of the vector of trying to achieve is 0.5639, and this numerical value is much smaller than 2.5.
With respect to by requirement condition f) the dehisce numerical value of moment of 2 rank of defined, at each cylinder, sinusoidal component after multiplying each other with F (n) is respectively: C1=0, C2=-0.9749, C3=0.86777, C4=2.34549, C5=3.8997, C6=-3.90916, C7=-2.6033, C8=-3.3446, C9=8.4902, C10=-9.4652, C11=0.0000, C12=9.15413, C13=-9.936 and C14=5.9479, the summation of a plurality of sinusoidal components is 0.4721.
For each cylinder, equation f) cosine component after multiplying each other with F (n) in is as follows: C1=0, C2=-0.2225, C3=-1.8019, C4=1.87047, C5=-0.89008, C6=3.1174, C7=-5.4058, C8=-6.9452, C9=-1.9378, C10=-2.1604, C11=10.70857, C12=7.30017, C13=7.92366 and C14=-12.351, the summation of each cosine component is-0.794.The mould length of the vector of trying to achieve is 0.9241, and this numerical value is much smaller than 6.0.
In Fig. 6, expressed the active force that produces the moment of dehiscing.When cylinder 14 is carried out combustion process, acting on power on the cylinder cap, that direction makes progress causes four pull bars to be subjected to an active force that makes progress 36, and pull bar couples together cylinder portion and support, meanwhile, is subjected to the thrust 37 of effect downwards with these cylinder 14 pairing main bearings.When other cylinder is got angry, also similar active force can appear.Active force on these Vertical direction produces the so-called moment of dehiscing, and it acts on motor and the engine support structure, and its mode of action can cause vertical vibration.These vertical vibrations can bring negative effect, especially are used as under the situation of main propeller machine group of cargo-container ship at motor, and the reason moment that is to dehisce will cause hull and produces the totally unfavorable vibration of characteristic.According to the firing order of motor of the present invention can suppress the to dehisce amplitude of moment, thereby this motor is specially adapted to its hull very long Container ship usually, this boats and ships need be equipped with the high main frame of power, so that make boats and ships have the necessary high speed of a ship or plane of transportation high value goods.The problem that motor according to the present invention there are differences except the inflation effect that can solve each cylinder of motor (this problem is especially relevant with high output engine), can also solve one of them in the principal oscillation problem relevant simultaneously with the cargo-container ship propulsion system.
Thereby, motor according to the present invention is particularly suitable for the propelling main frame as cargo-container ship, especially be suitable for the Container ship that its freight volume is at least 10000TEU (standard case), the Container ship in for example from 10200TEU to the 14000TEU scope, the TEU of unit is equal to 20 feet shipping container.TEU is the standard unit that is used to weigh the Container ship carrying capacity.
Following table 1 has been listed coupled vibration value of some other order in the above-mentioned firing order.These firing orders are marked as labels such as FS1 according to above-described order.This form has been listed according to each requirement condition a) to f) mould of the vector that obtained is long.
Table 1
| FS NO. | a) G4 | b) G5 | c) G6 | d) G7 | e) N1 | f) N2 |
| 2 | 0.97 | 0.67 | 1.26 | 1.71 | 0.364 | 0.52 |
| 5 | 0.88 | 0.56 | 1.31 | 2 | 1.148 | 1.137 |
| 9 | 0.56 | 0.35 | 1.42 | 1.12 | 0.589 | 1.499 |
| 13 | 0.97 | 0.67 | 1.26 | 1.71 | 0.364 | 0.52 |
| 14 | 0.57 | 0.72 | 1.2 | 2 | 0.384 | 1.264 |
| 21 | 0.44 | 0.74 | 1.06 | 1.42 | 0.702 | 1.015 |
| 27 | 0.44 | 0.62 | 1.87 | 1.42 | 1.402 | 0.762 |
| 31 | 0.87 | 0.72 | 1.99 | 1.42 | 0.246 | 1.335 |
| 45 | 0.833 | 0.735 | 0.419 | 0.833 | 0.724 | 1.057 |
| 46 | 0.31 | 0.212 | 0.867 | 0.541 | 0.997 | 1.468 |
| 47 | 0.371 | 0.355 | 0.755 | 0.249 | 1.002 | 1.318 |
| 48 | 0 | 0.948 | 0 | 0.541 | 1.044 | 0 |
| 49 | 0.323 | 0.902 | 0.402 | 0.249 | 1.151 | 1.227 |
| 50 | 0.401 | 0.875 | 0.846 | 0.833 | 1.155 | 0.894 |
| 51 | 0.102 | 0.628 | 0.513 | 0.541 | 1.413 | 1.082 |
| 52 | 0.445 | 0.964 | 0.247 | 0.334 | 1.429 | 1.357 |
| 53 | 0.682 | 0.376 | 0.748 | 0.833 | 0.35 | 0.93 |
| 54 | 0.909 | 0.976 | 0.978 | 0.833 | 0.429 | 0.474 |
| 55 | 0.909 | 0.492 | 0.978 | 0.541 | 0.741 | 0.474 |
Can change above-mentioned mode of execution.For example, can on motor, use other number turbosupercharger, for example can adopt two or three turbosupercharger, also can adopt, for example five to eight turbosupercharger more than four turbosupercharger.The frame of motor can be any suitable shape, and cylinder block can be integrally formed on the entablature.The cross-sectional configurations of scavenging receiver (waste gas receiver also can) if possible can be other shape except that circle, for example can be polygonal or the part-circular that combines with one or more straightways.Except above-mentioned element, scavenging system also can comprise the water smoke trap etc. of some other element-for example.Be not to be C1 and the cylinder numbers that will be positioned at the rear end is C14 with the cylinder numbers that is positioned at motor head yet.Can be C1 equally also, and be C14 the cylinder numbers of front end with the cylinder numbers of rear end.As alternative, this motor also can be used in fixedly unit of power station conduct except as the marine engine.
Also can be different from above-mentioned criterion, and set every requirement condition more strict.For example, aspect air pulsing, can a) be set at Vgas (4)＜1.2 or Vgas (4)＜0.9 with requiring, also can be with the requirement condition b of relevant air pulsing) be restricted to Vgas (5)＜1.2 or Vgas (5)＜1.0, requirement condition c with relevant air pulsing) be restricted to Vgas (6)＜1.2 or Vgas (6)＜1.0, and with the requirement condition d of relevant air pulsing) be restricted to Vgas (7)＜2.0 or Vgas (7)＜1.5.Can will require e) be defined as Vnick (1)＜1.3 or Vnick (1)＜1.0, and require f) can be restricted to Vnick (2)＜1.3 or Vnick (2)＜1.0.Can adopt these more strict requirements as required individually or in combination.Require strictly more, the firing order number that satisfies this requirement condition is few more, but at the same time, also can make the vibration characteristics of 14 Cylinder engines more favourable.
Claims (10)
1. turbo charged 14 cylinder two-stroke internal-combustion engines in upright arrangement, it has at least one waste gas receiver, at least two turbosupercharger, an and scavenging system, scavenging system wherein has the scavenging receiver of at least one lengthwise, each cylinder all has a scavenging import that is connected with the scavenging receiver, and exhaust passage, the exhaust passage is passed in described at least one waste gas receiver, the turbo-side of described turbosupercharger is connected with the waste gas receiver, the pusher side of calming the anger then is connected with scavenging system, 14 cylinder C1-C14 of this motor have certain firing order n1-n14, it is characterized in that: the firing order n1-n14 of 14 cylinders can make following four to require a)-d) satisfied at least simultaneously:
A) pulse for the quadravalence of gas
B) pulse for five rank of gas
C) pulse for six rank of gas
D) pulse for seven rank of gas
In the formula, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, linear interpolation the F (14)=-1 of the F (1)=1 from cylinder C1 time the during to cylinder C14, || the mould of representation vector is long.
2. two-stroke turbocharging internal-combustion engines according to claim 1 is characterized in that: the firing order n1-n14 of 14 cylinders can also satisfy the following e that requires):
e)
In the formula, V
Nick(1) for 1 rank of getting by the Vertical direction active force that acts on cylinder cap and the main bearing relevant value of moment of dehiscing, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, for cylinder C1, and F (1)=0, and F (n)=F (n-1)+cylinder C
N-1Center line is to cylinder C
nNominal range between the distance/cylinder of center line, || the mould of representation vector is long.
3. two-stroke turbocharging internal-combustion engines according to claim 1 is characterized in that: the firing order n1-n14 of 14 cylinders can also satisfy the following f that requires):
f)
In the formula, V
Nick(2) for 2 rank of getting by the Vertical direction active force that acts on cylinder cap and the main bearing relevant value of moment of dehiscing, n is the cylinder number of cylinder,
nBe the ignition angle of n cylinder, F (n) is a weighting function, for cylinder C1, and F (1)=0, and F (n)=F (n-1)+cylinder C
N-1Center line is to cylinder C
nNominal range between the distance/cylinder of center line, || the mould of representation vector is long.
4. according to the described two-stroke turbocharging internal-combustion engines of one of claim 1 to 3, it is characterized in that: the firing order n1-n14 of 14 cylinders is designed to make:
A) for 4 rank air pulsings, Vgas (4)＜2;
B) for 5 rank air pulsings, Vgas (5)＜2;
C) for 6 rank air pulsings, Vgas (6)＜2;
D) for 7 rank air pulsings, Vgas (7)＜2.2;
E) for the 1 rank moment of dehiscing, Vnick (1)＜2;
F) for the 2 rank moment of dehiscing, Vnick (2)＜3,
5. two-stroke turbocharging internal-combustion engines according to claim 4 is characterized in that: the firing order n1-n14 of 14 cylinders is designed to make:
A) for 4 rank air pulsings, Vgas (4)＜1;
B) for 5 rank air pulsings, Vgas (5)＜2;
C) for 6 rank air pulsings, Vgas (6)＜2;
D) for 7 rank air pulsings, Vgas (7)＜2.2;
E) for the 1 rank moment of dehiscing, Vnick (1)＜1.5;
F) for the 2 rank moment of dehiscing, Vnick (2)＜1.5,
6. according to the described two-stroke turbocharging internal-combustion engines of one of claim 1 to 3, it is characterized in that: described firing order is uniformly, and the crank angle between two order cylinders are got angry successively is 360 °/14.
7. according to the described two-stroke turbocharging internal-combustion engines of one of claim 1 to 3, it is characterized in that: described firing order is uneven, and at least two pairs of crank angles of getting angry successively between the cylinder are not equal to 360 °/14.
8. according to the described two-stroke turbocharging internal-combustion engines of one of claim 1 to 3, it is characterized in that: this internal-combustion engine is the main propeller machine group of Container ship.
9. two-stroke turbocharging internal-combustion engines according to claim 8 is characterized in that: the peak output of this internal-combustion engine is every cylinder 5000kW at least.
10. two-stroke turbocharging internal-combustion engines according to claim 8 is characterized in that: this internal-combustion engine is the propelling main frame of Deadweight cargo capacity greater than the Container ship of 10000TEU.
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| DK1739296T3 (en) * | 2005-06-30 | 2013-06-03 | Waertsilae Nsd Schweiz Ag | Method for optimizing an operating parameter in a piston combustion engine and piston combustion engine |
| EP1845250A1 (en) * | 2006-03-29 | 2007-10-17 | Wärtsilä Schweiz AG | Initial learning process |
| JP2006348947A (en) * | 2006-08-18 | 2006-12-28 | Kazuo Oyama | Internal combustion engine with exhaust pressure regenerator |
| AT507464B1 (en) * | 2008-09-29 | 2011-01-15 | Ve Vienna Engineering Forschungs Und Entwicklungs Gmbh | OPERATIONAL MANAGEMENT OF A SECONDARY MOTOR WITH TURBO CHARGER |
| DE102011003909B4 (en) | 2011-02-10 | 2018-05-30 | Man Diesel & Turbo Se | Two-stroke internal combustion engine and method of operating the same |
| JP6451485B2 (en) * | 2015-05-11 | 2019-01-16 | 株式会社Ihi | Crosshead engine |
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- 2004-02-12 DE DE202004002185U patent/DE202004002185U1/en not_active Expired - Lifetime
- 2004-03-15 JP JP2004072451A patent/JP3991039B2/en not_active Expired - Lifetime
- 2004-04-02 KR KR1020040022922A patent/KR100589766B1/en active IP Right Grant
- 2004-04-28 DE DE602004000001T patent/DE602004000001T2/en not_active Expired - Lifetime
- 2004-04-28 PL PL04076262T patent/PL1496217T3/en unknown
- 2004-04-28 AT AT04076262T patent/ATE287493T1/en not_active IP Right Cessation
- 2004-04-28 DK DK04076262T patent/DK1496217T3/en active
- 2004-04-28 EP EP04076262A patent/EP1496217B1/en not_active Expired - Lifetime
- 2004-04-29 CN CNB2004100366476A patent/CN100346065C/en not_active Expired - Lifetime
- 2004-05-13 KR KR20-2004-0013332U patent/KR200363267Y1/en not_active IP Right Cessation
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105587432A (en) * | 2014-10-07 | 2016-05-18 | 温特图尔汽柴油公司 | Piston type internal combustion engine, exhaust distributing pipe and particularly combined exhaust distributing device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2005214191A (en) | 2005-08-11 |
| EP1496217B1 (en) | 2005-01-19 |
| EP1496217A1 (en) | 2005-01-12 |
| ATE287493T1 (en) | 2005-02-15 |
| KR200363267Y1 (en) | 2004-10-01 |
| DE602004000001D1 (en) | 2005-02-24 |
| DK1496217T3 (en) | 2005-05-23 |
| KR100589766B1 (en) | 2006-06-21 |
| KR20050077708A (en) | 2005-08-03 |
| JP3991039B2 (en) | 2007-10-17 |
| DE602004000001T2 (en) | 2006-03-02 |
| DE202004002185U1 (en) | 2004-07-22 |
| PL1496217T3 (en) | 2005-06-30 |
| CN1648443A (en) | 2005-08-03 |
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Owner name: MAN DIESEL ENGINES AND TURBINE GERMAN SUBSIDIARY, Free format text: FORMER NAME: MAN DIESEL AS Owner name: MAN DIESEL AS Free format text: FORMER NAME: MAN B + W DIESEL AS. Owner name: MAN DIESEL AS Free format text: FORMER NAME: MAN DIESEL AS |
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Address after: Copenhagen, Denmark Patentee after: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address before: Copenhagen, Denmark Patentee before: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address after: Copenhagen, Denmark Patentee after: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address before: Copenhagen, Denmark Patentee before: MAN DIESEL filial af MAN Diesel SE Tyskland Address after: Copenhagen, Denmark Patentee after: MAN DIESEL filial af MAN Diesel SE Tyskland Address before: Copenhagen, Denmark Patentee before: MAN B & W DIESEL A/S |
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