CN107061007B - Large-sized turbo-charging two-stroke compression ignition type internal combustion engine with gas exhaust inspecting - Google Patents
Large-sized turbo-charging two-stroke compression ignition type internal combustion engine with gas exhaust inspecting Download PDFInfo
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- CN107061007B CN107061007B CN201710059750.XA CN201710059750A CN107061007B CN 107061007 B CN107061007 B CN 107061007B CN 201710059750 A CN201710059750 A CN 201710059750A CN 107061007 B CN107061007 B CN 107061007B
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 48
- 230000006835 compression Effects 0.000 title claims abstract description 13
- 238000007906 compression Methods 0.000 title claims abstract description 13
- 238000001816 cooling Methods 0.000 claims description 15
- 239000000446 fuel Substances 0.000 claims description 15
- 238000002347 injection Methods 0.000 claims description 8
- 239000007924 injection Substances 0.000 claims description 8
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 239000002826 coolant Substances 0.000 claims description 2
- 238000013016 damping Methods 0.000 description 8
- 230000006378 damage Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000002000 scavenging effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000010354 integration Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008450 motivation Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 239000002360 explosive Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 208000027418 Wounds and injury Diseases 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000012809 cooling fluid Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 208000014674 injury Diseases 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001141 propulsive effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000005303 weighing Methods 0.000 description 1
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
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/10—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of charging or scavenging apparatus
-
- 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
- F02B77/00—Component parts, details or accessories, not otherwise provided for
- F02B77/08—Safety, indicating, or supervising devices
- F02B77/082—Safety, indicating, or supervising devices relating to valves
-
- 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
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/12—Engines characterised by fuel-air mixture compression with compression ignition
-
- 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
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- 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
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
A kind of large-sized turbo-charging two-stroke compression ignition type internal combustion engine with crosshead, including multiple cylinders, cylinder have cylinder head, exhaust valve and exhaust pipe.Cylinder head is provided with dump valve, and the entrance of dump valve is fluidly connected to combustion chamber, and the outlet of dump valve is fluidly connected to discharge tube.Dump valve is provided with movable valve component movable within the scope of the middle position between closed position and fully open position between them.When during movable valve component is in an intermediate position any one or when being in a fully open position, dump valve allows gas to flow to from entrance to export, and when movable valve component is in the closed position, and dump valve prevents from gas from flowing to from entrance exporting.Movable valve component has the first effective pressure surface of the pressure being exposed in combustion chamber, and movable valve component has the second hydraulic effective pressure surface being exposed to for movable valve component to be pushed to closed position.
Description
Technical field
This disclosure relates to the row in the large-sized turbo-charging two-stroke compression ignition type internal combustion engine with crosshead
The control of gas event.
Background technique
The large-sized two-stroke turbocharging compression ignition type internal combustion engine of cross-head type is for example for Large ocean going vessels
Propulsive force or as the motive power in power device.Bulky dimensions are not only due to, these two-stroke diesel engines are also by structure
It is different from any other internal combustion engine for making.Their exhaust valve may weigh up to 400kg, and the diameter of piston reaches 100cm, and
Maximum working pressure (MWP) in combustion chamber is usually hundreds of bar.Related power is under these high pressure levels and piston size
It is huge.
Due to for example wrong fuel injection timing or fuel injection amount, may be generated in one of multiple cylinders once in a while
High pressure.In order to adapt to these excessively high pressure, by being connected to base plate and together holding engine knot to by cylinder head
The stay-bolt of structure applies tension, is finely controlled for making cylinder head be crushed on the power at the top of cylinder liner.Therefore, when out
When showing excessively high pressure, cylinder head is raised and discharges excessively high pressure between the top of cylinder liner and the bottom of cylinder head
Power.In the art usually using the system, but it is not that there is no problem.Cylinder head rise is that a kind of explosive gas is let out
Leakage, wherein uncontrolled gas discharges under the up to loud noise of 170db.When this lateral exhaust occurs, any onlooker
(it typically is flame forms) may be all sprayed by exposure to hot gas and by grievous injury.In addition, the gas of very high temperature high pressure
Body corrodes the precision machined matching surface of cylinder liner and cylinder head, and damages top and the cylinder head for being placed in cylinder liner
Bottom between sealing ring.Therefore, exhaust events would generally to need to process these surfaces and replace sealing
Ring is to obtain required fluid sealability.Therefore, the rehabilitation cost after being vented is significant.In addition, tension in stay-bolt by
Change in the temperature change of engine and environment, therefore can not accurately be controlled very much.If in stay-bolt
The power relatively high moment is vented, then is having resulted in major part and other expensive engine portions before to the power of piston and crankshaft
The damage of part.Such case is even more expensive compared with the exhaust preferably controlled.
Large ship insurance company (classification society) requires large-scale marine engine that must take safety measures to prevent from burning
It is damaged caused by excess pressure in room.
Therefore, the engine of some prior arts is provided with rupture disk in the wall of combustion chamber, which is designed to
It can fail the possibility damage for protecting engine from the excess pressure in combustion chamber.The shortcomings that these rupture disks, is
They are weakened over time because being exposed to the pressure fluctuated in combustion chamber, and finally in relatively small excess pressure
It fails already under (for example, since small is caught fire).Therefore, rupture disk often prematurely fails.This be it is problematic, especially
Because engine must be stopped replacing failed rupture disk with new rupture disk.Therefore, most common that there is explosion
The measure of piece is not optimal.
Other engines are provided with safety valve, so that meeting can open when occurring excessively high pressure in combustion chamber with from combustion
Burn the requirement of room discharge gas.These are spring-loaded poppets.However, due to their maximum open be not enough to it is sufficiently fast
Ground releases stress, so the explosive nature thereof of exhaust events causes these poppet relative nullities.Therefore, these safety valves cannot be
Required opening area is effectively provided in the time short enough, and only there is indicator or siren before cylinder head rise
Effect, but these known valves cannot prevent cylinder head from rising.
GB 817,018 discloses a kind of large-sized two-stroke diesel engine, has between cylinder liner and cylinder head
Separate ring, which is equipped with hole for receiving safety valve.However, the known safety valve is unreliable, and
And the safety valve is stopped using.
Therefore, it is necessary to a kind of improved exhaust controls for cross-head type large-sized two-stroke compression ignition type internal combustion engine
System processed.
Summary of the invention
The object of the present invention is to provide the cross-head type large-sized two-stroke compression ignitions for overcoming or at least reducing the above problem
Formula internal combustion engine.
Foregoing end other objects are realized by the feature of independent claims.According to dependent claims, specification and
Attached drawing, other forms of implementation are obvious.
According in a first aspect, providing a kind of large-sized turbo-charging two-stroke compression ignition type internal combustion hair with crosshead
Motivation, comprising:
Multiple cylinders as combustion chamber, the cylinder have cylinder head, the exhaust being centrally placed in the cylinder head
Valve and the exhaust pipe that the exhaust valve is connected to exhaust receiver,
The cylinder head is provided with dump valve, and the entrance of the dump valve is fluidly connected to combustion chamber, and the discharge
The outlet of valve is fluidly connected to discharge line,
The dump valve is provided with the middle position range between closed position and fully open position between them
Interior movable movable valve component,
When any place during movable valve component is in an intermediate position or when being in a fully open position, dump valve allows gas
Body is flowed to from entrance and is exported, and when movable valve component is in the closed position, dump valve prevents gas from flowing to outlet from entrance,
The movable valve component has the first effective pressure surface of the pressure being exposed in combustion chamber, so that combustion chamber
In pressure push movable valve component to fully open position,
The movable valve component has hydraulic second being exposed to for movable valve component to be pushed to closed position
Effective pressure surface,
Second effective pressure surface when movable valve component is in the closed position have first size, it is described can
There is the second size for being less than the first size, the first position range is from complete in the first position of mobile valve member
Full open position extends to predetermined intermediate position.
Have by offer and its open position is pushed to by the pressure in combustion chamber and is pushed to its pass by hydraulic
Following device may be implemented in the dump valve of the movable member of closed position: the device can be opened fast enough with sufficiently large
Mouthful open, with excess pressure in a combustion chamber in the case where provide prevent damage engine needed for release.By using hydraulic
The movable member of dump valve is balanced, the pressure of dump valve opening can be reliably controlled, and is capable of providing following knot
Structure: the structure is quick and roomily opens, to provide so that the big circulation area that the gas of combustion chamber escapes.When dump valve is beaten
When opening, the second effective pressure surface of reduction prevent due to when dump valve is opened in combustion chamber pressure decline caused by
It is undesirable to repeat to open and close.
In the first possible embodiment of first aspect, predetermined position is than fully open position closer to close stance
It sets.
In the second possible embodiment of first aspect, the second effective pressure surface pass through movable valve component the
It one surface and is formed by the second surface of movable valve component.The second surface be less than first surface and with the first table
Face is oppositely directed to.
In the possible embodiment of third of first aspect, first surface passes through in all positions of movable valve component
It is hydraulic pressurized, and wherein second surface is pressurized within the scope of first position by hydraulic.
In the 4th possible embodiment of first aspect, movable valve component opens permission within the scope of first position
Second surface passes through hydraulic pressurized port.
In the 5th possible embodiment of first aspect, movable valve component is provided with the valve disc with valve seat cooperation,
Valve seat is arranged in the tap of cylinder head.
In the 6th possible form of implementation of first aspect, the principal plane of valve seat is tilted relative to the principal direction of tap
Setting.
In the 7th possible embodiment of first aspect, movable valve component includes the valve disc connecting with valve rod and can
It is operatively coupled to the actuating piston of valve rod.
In the 8th possible embodiment of first aspect, the side of actuating piston, the second table is arranged in first surface
The opposite side of actuating piston is arranged in face.
In the 9th possible form of implementation of first aspect, tap is connected to exhaust pipe or exhaust by discharge pipe
Receiver, to bypass exhaust valve.
In the tenth possible embodiment of first aspect, the dump valve is provided with cooling device, the cooling dress
Set the path preferably included for cooling medium by dump valve.
In the 11st possible embodiment of first aspect, engine includes hydraulic system, which has
Pressure increase as engine load increases, and reduce as engine load reduces, and wherein second effective
Pressure surface passes through the hydraulic pressurized of hydraulic system.
In the 12nd possible embodiment of first aspect, hydraulic system provides power for fuel injection valve.
In the 13rd possible embodiment of first aspect, hydraulic system provides power for exhaust valve actuation system.
Detailed description of the invention
In the part in detailed below of the disclosure, it will be solved in more detail with reference to illustrative embodiments shown in the drawings
Release the present invention, in which:
Fig. 1 is the front view of large-sized two-stroke diesel engine according to illustrative embodiments；
Fig. 2 is the side view of the large-sized two-stroke engine of Fig. 1；
Fig. 3 is the schematic diagram according to the large-sized two-stroke engine of Fig. 1；
Fig. 4 is cylinder head and with the side view according to the exhaust valve of the dump valve of embodiment；
Fig. 5 is the sectional view intercepted along the line A-A of Fig. 4；
Fig. 6 is the top view according to the dump valve of embodiment；
Fig. 7 to Fig. 9 is the sectional view of the dump valve of Fig. 6, and wherein the movable valve component of dump valve is in different location；
Figure 10 is the different sectional views of the dump valve of Fig. 6；With
Figure 11 is the schematic diagram of the hydraulic system of the engine of Fig. 1 to Fig. 3.
Specific embodiment
In the following detailed description, the large-sized two-stroke turbine that will there is crosshead by illustrative embodiments description
Charge compression ignition formula (diesel oil) internal combustion engine.Fig. 1 to Fig. 3 shows the large-sized low-speed whirlpool with crankshaft 42 and crosshead 43
Wheel pressurization two-stroke compression ignition engine.Fig. 3 shows the schematic diagram of the engine with gas handling system and exhaust system.
In the illustrative embodiments, engine has six cylinders 1 being in line.Large-sized two-stroke turbocharging compression ignition
Formula internal combustion engine usually has 5 to 16 cylinders being in line, being carried by engine frame 45.The engine can example
Such as it is used as the sustainer in marine ship or as the stationary engine for operating generator in power station.Engine it is total defeated
It out can be for example in the range of 5000kW to 110000kW.
The engine is compression ignition engine of the two-stroke single to flow pattern, has the lower area in cylinder 1
In scavenging port 19 and be centrally disposed in the exhaust valve 4 in cylinder head 22 at the top of cylinder 1.The principal direction that air-flow passes through cylinder
For the exhaust valve 4 at the top from the scavenging port 19 of 1 bottom of cylinder to cylinder 1, therefore entitled " one-way flow ".Pressurized air is from pressurizing air
Gas receiver 2 (it is big, general hollow cylinder form) is transported to the scavenging port 19 of each cylinder 1.In cylinder 1
41 compressing charge air of piston, fuel then burn from the fuel injection valve (not shown) injection in cylinder head 22
And generate exhaust (exhaust gas).
When exhaust valve 4 is opened, exhaust flows into exhaust by exhaust pipe 35 associated with related cylinder 1 and receives
Device 3 (it is big hollow cylinder form), and it is advanced through the turbine 6 that first exhaust pipeline 18 flows to turbocharger 5,
Exhaust is flowed in atmosphere from it by second exhaust pipeline 7.Turbine 6 is driven by axis 8 and supplies air via air intake 10
Compressor 9.The pressurized air of pressurization is transported to the charge air duct 11 for leading to charging air receiver 2 by compressor 9.
Intercooler 12 is passed through in air inlet in pipeline 11, and the intercooler 12 at about 200 DEG C for that will leave
The pressurized air of compressor is cooled to the temperature between 36 DEG C and 80 DEG C.
Cooling pressurized air passes through (its underload in engine of auxiliary blower 16 driven by electric drive motor 17
Pressurizing air air-flow is pressurized under condition or part load condition) and enter air receiver 2.At higher engine loads,
Turbocharger compressor 9 conveys enough compressed scavenging airs, then auxiliary blower 16 via check-valves 15 by around
It crosses.
Fig. 4 and Fig. 5 illustrates in greater detail the side view and sectional view of exhaust valve 4 and cylinder head 22 respectively.4 benefit of exhaust valve
It is bolted in cylinder head 22 securely with exhasut valve stem 44, wherein during its whole valve disc is arranged in cylinder head 22
In heart opening.Exhasut valve stem 44 is shown in its closed position, and the valve disc of exhasut valve stem 44 leans against on valve seat.When exhaust valve 4
When opening, combustion chamber 27 is connected to exhaust pipe 35.In embodiments, exhaust pipe 35 is directly connected to exhaust receiver 3.
The top of the formation of cylinder head 22 combustion chamber 27.Cylinder head 22 is provided with several cooling ducts sightless in figure.
In addition, fuel injection valve (generally for single-fuel engine each cylinder there are three fuel valve and for dual fuel engine
Each cylinder there are six fuel valve) (fuel valve is not shown) be the wherein nozzle of fuel valve in the receiver hole of cylinder head 22
It is projected into combustion chamber 27.
Exhaust valve 4 is provided with hydraulic exhaust valve actuators 47 comprising the hydraulic pressure chamber 38 positioned at the top of valve rod 44.Air
Spring 37 pushes valve rod 44 (in such as Fig. 5 upwards, i.e., along closing direction) upwards, and when hydraulic actuator 47 is pressurized, it is hydraulic
Actuator 47 pushes valve rod 44 along opening direction.Therefore, exhaust valve is realized by applying hydraulic pressure to hydraulic actuator 47
The lift of bar 44, and air spring 37 ensures to make valve rod 44 back to its closed position.
Engine is provided with the discharge line (as shown in the figure) that exhaust pipe 35 is extended to from combustion chamber 27.Alternatively, it arranges
Pipeline extends to exhaust receiver 3 from combustion chamber 27 out.The cross-sectional area of discharge line is sufficiently large, to catch fire or burn
Cause sufficiently to discharge the pressure in combustion chamber 27 in the case where other events of excess pressure fastly in room 27.Dump valve 50 controls
The opening and closing of discharge line, and exhaust valve 50 can be opened fast enough with sufficiently large opening, for crossing high pressure
The pressure in combustion chamber 27 is discharged in the case where power, to prevent damage engine.
Tap 29 in cylinder head 22 forms a part of discharge line.Tap 29 is connected to exhaust by discharge pipe 36
Pipeline 35 or exhaust receiver 3.
Fig. 6 to Figure 10 illustrates in greater detail dump valve 50.Dump valve 50 can have the shell 51 of its own (as schemed institute
Show), the socket or dump valve made it possible in the suitable hole 28 (Fig. 5) for being used as and being inserted into cylinder head 22 can be
The integration section (not shown) of cylinder head 22.
Dump valve 50 is inserted into the hole 28 in cylinder head 22, and wherein bracket 68 is prominent from cylinder head 22.Bracket 68 can be with
It is bolted to shell 51 or the integration section as shell 51.Bracket 68 is provided with for receiving that dump valve 50 is fixed
The hole of bolt (Fig. 5) on to cylinder head 22.Shell 51 is provided with for allowing to be vented the big of discharge when dump valve 50 is opened
Export (opening) 58.
Dump valve 50 be provided with can be shown in Fig. 7 closed position and fully open position shown in Fig. 9 between move
Movable valve component 52, i.e., removable valve member 52 can be between the closed position of Fig. 7 and the fully open position of Fig. 9
It is moved back and forth in position range.In fig. 8, movable valve component 52 is shown at middle position.When movable valve component 52
When being not at its closed position, dump valve 50 allows gas to flow to its outlet 58 from its entrance 57.Hollow portion in valve chest 52
Entrance 57 is connected to outlet 58 by 63.Valve seat 55 is arranged around entrance 57.
Movable valve component 52 includes valve rod 53, and the valve rod 53 is provided with valve disc 54 at one longitudinal end.Valve
Another opposing longitudinal end of bar 53 is provided with damping element 69.Valve rod 53 is slidably received within vertical in shell 51
Xiang Kongzhong.
Valve rod 53, be provided with the end of valve disc 54 and extended in the hollow portion 63 in valve chest 51 from longitudinal hole.When can
When mobile valve member 52 is in its closed position, valve disc 54 is rested on valve seat 55, as illustrated in fig. 7 and fig. 10, wherein valve disc 54
, be exposed to opening 57 surface formed the first effective pressure surface 59.
When movable valve component 52 rises, as shown in Figure 8 and Figure 9, valve disc 54 is located in hollow portion 63 and provides use
The substantial flow region of outlet (opening) 58 is flowed to from entrance (opening) 57 in gas.In embodiments, the master of valve seat 55 is flat
Face Z is obliquely installed relative to the principal direction of tap 29, so that the limitation to the flowing for flowing through tap 29 minimizes.Work as row
Portal 29 when being straight, principal direction is the longitudinal direction of the flowing in hole 29.When tap 29 is curved, principal direction is
The course bearing of curve at the position that valve seat 55 intersects with tap 29.
Longitudinal hole, the guidance valve rod 53 side is arranged in hollow portion 63.It is provided in the other side of the longitudinal hole
Cylindrical chamber accommodates actuating piston 56 in cylindrical chamber.Cylindrical chamber is divided into first chamber by actuating piston 56
60 and second chamber 66.It activates piston 56 and is fixed to valve rod 53, to be operably connected to movable valve component 52.Implementing
In mode, piston 56 is also possible to the integration section of movable valve component 52.Movable valve component 52 has 61 He of first surface
The second surface 62 being oppositely directed to.First surface 61 is exposed to the pressure in the first chamber 60, and when first chamber 60 is pressurized
When, push movable valve component 52 to its closed position.Second surface 62 is exposed to the pressure in second chamber 66, and when the
When two chambers 66 are pressurized, push movable member 52 to its fully open position.The area of first surface 61 is greater than the second table
The area in face 62.Therefore, when the pressure in first chamber 60 is equal to the pressure in second chamber 66,52 quilt of movable valve component
Push closed position to.First surface 61 and second surface 62 are formed together the second effective pressure surface.First is acted on effectively to press
Pressure in combustion chamber 27 on power surface 59 and multiply with the area on the first effective pressure surface 59 and pressure in combustion chamber 27
The corresponding power of product pushes movable valve component 52 to its closed position together.
First chamber 60 is connected to the entrance 80 in dump valve 50 by supply hole 82 and damping chamber 65.In the embodiment party
In formula, entrance 80, supply hole 82 and damping chamber 65 are arranged in bracket 68, but can also be located in shell 51.
Inbound port 80 is connect with the hydraulic system 88 of the engine for the hydraulic pressure at least providing continuous floor level.It is preferred that
Ground, hydraulic system 88 provide constant pressure or provide with engine load increase and increase and with engine load reduce and
Reduced pressure.
Pressure at port 80 is applied to first chamber 60, and the pressure by damping chamber 65 and service 82
By movable valve component 52 together with power and power corresponding with the product of the pressure in first chamber 61 with the area of first surface 61
Push its closed position to.
When actuating piston 56 is in 71 top (top in the orientation of the dump valve 50 in such as Fig. 7-Figure 10) of compensation port
Position when, second chamber 66 is connected to port 80 by compensation port 71 by subsidiary conduit 64.At movable valve component 52
When its closed position as illustrated in fig. 7 and fig. 10, compensation port 71 is activated the blocking of piston 56.
As illustrated in fig. 7 and fig. 10, in this case, second chamber 66, which passes through, cools down inbound port 75 at substantially less than end
It is pressurized under the low pressure of pressure at mouth 80.Cooling inbound port 75 allows cooling oil (hydraulic fluid) to flow into chamber 66, for cold
But dump valve 50.Cooling exit port 74 allows cooling oil (hydraulic fluid) to flow out.Go out in the upstream of cooling inbound port 75 and cooling
Flow resistance (not shown) is arranged in the downstream of port 74, for allowing the pressure in second chamber 66 to be instantaneously relatively higher than cooling
Fluid pressure.
When occurring excessively high pressure in combustion chamber 27, act in the combustion chamber 27 on the first effective pressure surface 59
Pressure will be more than the reaction force of pressure generated on movable valve component 52 by first pressure chamber, movable valve component
52 will start to move towards its fully open position, as shown in Figure 8.
When movable valve component 52 rises to a certain degree, secondary ports 71 will be opened, and second pressure chamber 66 will
The elevated pressures being connected at port 80.Limited part associated with cooling inbound port 75 and cooling exit port 74 ensures chamber 66
In pressure will not be lost by these corresponding ports 74,75.Therefore, second surface 62 is added by the pressure from port 80
Pressure, and generate the additional force that movable member is pushed to its fully open position.Therefore, it acts on movable valve component 52
Closing forces are substantially reduced.When movable valve component 52 is slightly opened, the reduction of the closing forces during exhaust events for ensuring
Dump valve 50, which is stablized, to be opened.That is, in combustion chamber 27 gas pressure opening force due to hollow portion 63 pressurization and in valve
Disk 54 is significantly reduced at the time of rise from seat 55.If this opening force loss may cause in single mistake without counter-measure
It undesirably repeats to open and close dump valve 50 during high pressure event.When secondary ports 71, which are not activated piston 56, to be stopped
Closing forces reduce, to provide stable opening procedure for dump valve 50.
Therefore, second acted on along closing direction on the movable valve component 52 to be pressurizeed by the pressure of hydraulic system 88 has
Imitating pressure surface has first size when movable valve component 52 is in the closed position, and the of movable valve component 52
There is in one position range the second size less than the first size, the first position range from fully open position always
To scheduled middle position.Middle position depend on secondary ports 71 relative to actuating piston 56 position, and preferably with
Compare apart from the fully open position closer to the closed position, but this according to circumstances depending on, and art technology
Personnel will determine the optimum position that closing forces reduce.Also other devices can be used to ensure once movable valve component 52
There are some lifts to be reduced by closing forces.
When movable valve component 52 is moved towards its fully open position always, move by the free end of valve rod 53
The damping element 69 at place with damping chamber 65 cooperation and be damped.Damping element 69 is that its diameter is suitable for making it by slideably
The cylindrical elements being contained in cylindrical damping chamber 65, and ensure that movable valve component 52 slowly reaches as shown in Figure 9
Fully open position at.
Hydraulic system 88 will be described in more detail with reference to Figure 11, and including supplying pressurized hydraulic to service 45
The pump or pumping plant 41 of liquid.Pressure in service 45 can be any number between 50bar and 500bar.Service
45 can be to multiple customers (such as fuel injection valve 42, exhaust valve actuation system 48 and dump valve 50) supply pressurized hydraulic
The common rail of liquid or pseudo- common rail.Each customer of hydraulic fluid is connected to storage tank by public return wire 49.
The ME line of (brand) engine hydraulic system is pseudo- common rail, wherein local accumulator is for fitting
Answer unexpected partial spent peak value.The hydraulic system of ME engine provides power for fuel valve and exhaust valve.It is sent out in typical ME
In motivation, the pressure in hydraulic system is as follows relative to engine load:
Therefore, hydraulic pressure increases as engine load increases, and reduces as engine load reduces.Note
It anticipates, the number in upper table is only exemplary, and actual pressure value may change with the different engines of given type
And with engine type difference and change.In addition, drop forelock motivation, i.e., wherein load and speed be different from related
The engine of the L1 load of engine type, also will be with different, usually slightly lower system pressures.
Normal maximum pressure in combustion chamber 27 also with engine load increase and increase, and with engine load
Reduction and reduce, distribution with herein go up table shown in hydraulic system pressure distribution it is closely similar.Therefore, pass through phase
Size setting is carried out to the size of first surface 61 for the size on the first effective pressure surface 59, it being capable of the row of setting
The size of valve 50 makes it have higher surplus than the normal pressure in the combustion chamber 27 for actual engine load out
It is opened under pressure.Surplus can be constant differential pressure or increase as engine load increases, and vice versa.
Dump valve 50 can also be to be supplied to the constant pressure operation of port 80.In this case, which should make
Dump valve 50 is opened when maximum pressure during proper normal in combustion chamber 27 exceeds a surplus, for example, ought be most
When big expecting pressure (i.e. in 100% engine load) is 200Bar, dump valve 50 is set under the pressure of 230Bar
It opens.In view of the pressure applied at port 80, by adjusting between the first effective pressure surface 59 and first surface 61
Dump valve 50 can be set as opening under required pressure by ratio.
In embodiment (not shown), dump valve 50 couples with the controller of engine, and sends out in exhaust events
Alarm out.In this regard, in embodiments, dump valve 50 is provided with the pressure sensor of the pressure in sensing second chamber 66.Such as
Pressure in fruit second chamber 66 is more than cooling oil pressure, then dump valve 50 has already turned on, and sounds an alarm.Alternatively,
Movable valve component 52, and the hair when movable valve component 52 moves from its closed position can be monitored with motion sensor
It alarms out.
In embodiment (not shown), it can be set and push movable valve component 52 with the elasticity far from its closed position
Device (dish-type spring etc.), to operate dump valve 50 when engine is stopped work.
In embodiments, determine whether movable valve component 52 is pushed to closed position or the power of fully open position is flat
Weighing apparatus is only acted on by the hydraulic fluid of the gas pressure and supply to dump valve that are acted on movable valve component 52 in combustion chamber 27
It is determined in the balance of the pressure on movable valve component 52.Therefore, if there is operating the discharge when engine is stopped work
The elastic device of valve, then these elastic devices will have so that not having during power operation to the movement of movable valve component 52
There is any lesser intensity significantly affected.
The multiple embodiments for having been combined this paper describe the present invention.However, those skilled in the art require in practice
When the present invention of protection, by studying attached drawing, disclosure and appended claims, it is to be understood that and implement disclosed implementation
Other modifications of mode.In the claims, word " comprising " is not excluded for other element or steps, and indefinite article " one " or
"one" is not excluded for multiple.State that the pure fact of certain measures does not indicate that these are arranged in mutually different dependent claims
The combination applied cannot be advantageously used.
Appended drawing reference used in claim is not necessarily to be construed as the limitation to range.
Claims (14)
1. the large-sized turbo-charging two-stroke compression ignition type internal combustion engine that one kind has crosshead (43), comprising:
Multiple cylinders (1) as combustion chamber (27), the cylinder (1) include cylinder head (22), are centrally placed in the cylinder
Exhaust valve (4) in lid (22) and the exhaust valve (4) is connected to the exhaust pipes (35) of exhaust receiver (3),
The cylinder head (22) is provided with dump valve (50), wherein the entrance (57) of the dump valve (50) be fluidly connected to it is described
Combustion chamber (27), and the outlet (58) of the dump valve (50) is fluidly connected to discharge tube,
It is characterized in that,
The dump valve (50) is provided with movable movable valve component (52) between closed position and fully open position,
There are a series of middle positions between the closed position and fully open position,
When the movable valve component (52) is in any middle position or is in the fully open position, the row
Valve (50) allows gas to flow to the outlet (58) from the entrance (57) out, and when the movable valve component (52) is in institute
When stating closed position, the dump valve (50) prevents gas from flowing to the outlet (58) from the entrance (57),
The movable valve component (52) has the first effective pressure surface of the pressure being exposed in the combustion chamber (27)
(58), so that the pressure in the combustion chamber (27) pushes the movable valve component (52) to the fully open position,
The movable valve component (52), which has, to be exposed to for pushing the movable valve component (52) to the closed position
The second hydraulic effective pressure surface, and
Second effective pressure surface has first size when the movable valve component (52) is in the closed position,
And there is the second size less than the first size within the scope of the first position of the movable valve component (52), described the
One position range is from the fully open position until predetermined intermediate position.
2. engine according to claim 1, wherein the predetermined intermediate position and the fully open position phase apart
Than the closer closed position.
3. engine according to claim 1 or 2, wherein second effective pressure surface is by the movable valve structure
Second surface (62) formation of the first surface (61) and the movable valve component of part (52), the second surface (62) are less than
The first surface (61) and the second surface (62) is oppositely directed to the first surface (61).
4. engine according to claim 3, wherein the first surface (61) is in the movable valve component (52)
All positions are by described hydraulic pressurized, and wherein the second surface (62) passes through institute within the scope of the first position
It states hydraulic pressurized.
5. engine according to claim 4, wherein the movable valve component (52) is within the scope of the first position
Opening allows the second surface (62) to pass through the hydraulic pressurized port (71).
6. engine according to claim 1, wherein the movable valve component (52) is provided with to be cooperated with valve seat (55)
Valve disc (54), the valve seat is arranged in the tap (29) of the cylinder head (22).
7. engine according to claim 1, wherein the principal plane of the valve seat (55) is relative to the tap (29)
Principal direction be obliquely installed.
8. engine according to claim 1, wherein the movable valve component (52) includes connecting with valve rod (53)
Valve disc (54) and the actuating piston (56) for being operably connected to the valve rod (53).
9. engine according to claim 1, wherein first surface (61) setting is in actuating piston (56)
Side, and the second surface (62) setting is in the opposite side of actuating piston (56).
10. engine according to claim 1, wherein the tap (29) is connected to described by discharge pipe (36)
Exhaust pipe (35) or the exhaust receiver (3), to bypass the exhaust valve (4).
11. engine according to claim 1, wherein the dump valve (50) is provided with cooling device, the cooling dress
It sets including the path for passing through the dump valve (50) for cooling medium.
12. engine according to claim 1, wherein the engine includes hydraulic system (88), the hydraulic system
The pressure having increases as engine load increases, and reduces as engine load reduces, and wherein described
Second effective pressure surface (61,62) passes through the hydraulic pressurized of the hydraulic system.
13. engine according to claim 12, wherein the hydraulic system (88) is that fuel injection valve (42) offer is dynamic
Power.
14. engine according to claim 12 or 13, wherein the hydraulic system (88) is exhaust valve actuation system
(48) power is provided.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201670059A DK179120B1 (en) | 2016-02-03 | 2016-02-03 | A large turbocharged two-stroke compression-ignited internal combustion engine with blow-off control |
| DKPA201670059 | 2016-02-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107061007A CN107061007A (en) | 2017-08-18 |
| CN107061007B true CN107061007B (en) | 2019-06-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710059750.XA Active CN107061007B (en) | 2016-02-03 | 2017-01-24 | Large-sized turbo-charging two-stroke compression ignition type internal combustion engine with gas exhaust inspecting |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6188975B2 (en) |
| KR (1) | KR101780212B1 (en) |
| CN (1) | CN107061007B (en) |
| DK (1) | DK179120B1 (en) |
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| JP2000097004A (en) * | 1998-09-17 | 2000-04-04 | Toyota Motor Corp | Turn stopper mechanism for valve lifter for three- dimensional cam |
| CN1973114A (en) * | 2004-05-21 | 2007-05-30 | 布鲁内尔大学 | Method of operating an internal combustion engine |
| CN101275474A (en) * | 2007-03-30 | 2008-10-01 | 曼狄赛尔公司 | Cam driven exhaust valve actuating system for large two-stroke diesel engine |
| EP2425104A1 (en) * | 2009-04-27 | 2012-03-07 | Wärtsilä Finland Oy | A control arrangement for an inlet valve in a piston engine |
| CN103917762A (en) * | 2011-09-21 | 2014-07-09 | 雅各布斯车辆系统公司 | Method and system for engine cylinder decompression |
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| GB817018A (en) * | 1957-01-03 | 1959-07-22 | Burmeister & Wains Mot Mask | Improvements in and relating to an internal combustion engine |
| GB495391A (en) * | 1937-05-11 | 1938-11-11 | Myron Seiliger | Improvements in and relating to solid-injection compression-ignition engines |
| JPS5759930U (en) * | 1980-09-26 | 1982-04-09 | ||
| DE3230133A1 (en) * | 1982-08-13 | 1984-02-16 | Klöckner-Humboldt-Deutz AG, 5000 Köln | ARRANGEMENT FOR SPARK-FREE DISCHARGE OF COMBUSTION GASES |
| JPS6075644U (en) * | 1983-10-31 | 1985-05-27 | いすゞ自動車株式会社 | Internal combustion engine pressure limiting device |
| JPH0425569Y2 (en) * | 1985-09-30 | 1992-06-18 | ||
| DE102008063968B4 (en) * | 2008-12-19 | 2010-12-23 | Man Diesel Filial Af Man Diesel Se, Tyskland | Diesel engine, predetermined breaking component therefor, as well as methods for avoiding damage to a diesel engine |
| ES2387372B1 (en) * | 2010-02-01 | 2013-07-29 | Jesus Manuel Diaz Escaño | INTERNAL COMBUSTION ENGINE THAT USES FOR ITS OPERATION ALTERNATIVE FUELS |
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2016
- 2016-02-03 DK DKPA201670059A patent/DK179120B1/en active
-
2017
- 2017-01-24 CN CN201710059750.XA patent/CN107061007B/en active Active
- 2017-02-02 KR KR1020170015208A patent/KR101780212B1/en active IP Right Grant
- 2017-02-02 JP JP2017017818A patent/JP6188975B2/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000097004A (en) * | 1998-09-17 | 2000-04-04 | Toyota Motor Corp | Turn stopper mechanism for valve lifter for three- dimensional cam |
| CN1973114A (en) * | 2004-05-21 | 2007-05-30 | 布鲁内尔大学 | Method of operating an internal combustion engine |
| CN101275474A (en) * | 2007-03-30 | 2008-10-01 | 曼狄赛尔公司 | Cam driven exhaust valve actuating system for large two-stroke diesel engine |
| EP2425104A1 (en) * | 2009-04-27 | 2012-03-07 | Wärtsilä Finland Oy | A control arrangement for an inlet valve in a piston engine |
| CN103917762A (en) * | 2011-09-21 | 2014-07-09 | 雅各布斯车辆系统公司 | Method and system for engine cylinder decompression |
Also Published As
| Publication number | Publication date |
|---|---|
| DK179120B1 (en) | 2017-11-13 |
| CN107061007A (en) | 2017-08-18 |
| KR20170092472A (en) | 2017-08-11 |
| JP2017137866A (en) | 2017-08-10 |
| KR101780212B1 (en) | 2017-10-10 |
| JP6188975B2 (en) | 2017-08-30 |
| DK201670059A1 (en) | 2017-08-28 |
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