CN107061007A - Large-sized turbo-charging two-stroke compression ignition type explosive motor with gas exhaust inspecting - Google Patents
Large-sized turbo-charging two-stroke compression ignition type explosive motor with gas exhaust inspecting Download PDFInfo
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- CN107061007A CN107061007A CN201710059750.XA CN201710059750A CN107061007A CN 107061007 A CN107061007 A CN 107061007A CN 201710059750 A CN201710059750 A CN 201710059750A CN 107061007 A CN107061007 A CN 107061007A
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- 230000006835 compression Effects 0.000 title claims abstract description 13
- 238000007906 compression Methods 0.000 title claims abstract description 13
- 239000002360 explosive Substances 0.000 title claims abstract description 13
- 238000002485 combustion reaction Methods 0.000 claims abstract description 37
- 230000000740 bleeding effect Effects 0.000 claims abstract description 17
- 238000001816 cooling Methods 0.000 claims description 16
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 239000002826 coolant Substances 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 17
- 239000000446 fuel Substances 0.000 description 10
- 238000013016 damping Methods 0.000 description 8
- 230000006378 damage Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 5
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 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
- 230000008450 motivation Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 210000004209 hair Anatomy 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
- 238000005452 bending Methods 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
- 238000004880 explosion Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 208000014674 injury Diseases 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification 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
- 239000002912 waste gas Substances 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
- 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
- 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
- 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)
- Lubrication Details And Ventilation 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 explosive motor with crosshead, including multiple cylinders, cylinder have cylinder head, air bleeding valve and discharge duct.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 in the range of the centre 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, dump valve prevents gas is flowed to from entrance from 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 effective pressure surface for being exposed to the hydraulic pressure for being used to push to movable valve component closed position.
Description
Technical field
This disclosure relates to the row in the large-sized turbo-charging two-stroke compression ignition type explosive motor with crosshead
The control of gas event.
Background technology
The large-sized two-stroke turbocharging compression ignition type explosive motor of cross-head type is for example for Large ocean going vessels
Propulsive force or be used as the motive power in power set.Bulky dimensions are not only due to, these two-stroke diesel engines are also by structure
Make to be different from any other explosive motor.Their air bleeding 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.Involved power is under these high pressure levels and piston size
Huge.
Due to for example wrong fuel injection timing or fuel injection amount, it may be produced once in a while in one of multiple cylinders
High pressure.In order to adapt to the pressure that these are too high, by being connected to bedplate and together holding engine knot to by cylinder head
The stay-bolt of structure applies tension force, is finely controlled the power for making cylinder head be crushed at the top of cylinder liner.Therefore, when going out
When showing too high pressure, cylinder head is raised and too high pressure is discharged between the top of cylinder liner and the bottom of cylinder head
Power.In the art usually using the system, but its not there is no problem.It is that a kind of explosive gas is let out that cylinder head, which rises,
Leakage, wherein uncontrolled gas discharges under up to 170db loud noise.When occurring this lateral exhaust, any onlooker
All may be by exposure to hot gas injection (it typically is flame form) by grievous injury.In addition, the gas of very high temperature high pressure
Body corrodes cylinder liner and the precision machined matching surface of 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 be processed these surfaces and change sealing
Ring is with the fluid sealability needed for obtaining.Therefore, the rehabilitation cost after exhaust is notable.In addition, tension force 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
It is vented at the time of power is relatively high, then the power to piston and bent axle is having resulted in major part and other expensive engine portions before
The damage of part.Such case is even more expensive compared with the exhaust preferably controlled.
Large ship insurance company (classification society) requires that large-scale marine engine must take safety measures to prevent burning
The damage that excess pressure in room is caused.
Therefore, the engine of some prior arts is provided with rupture disk in the wall of combustion chamber, and the rupture disk is designed to
It can fail to protect engine to damage from the possibility of the excess pressure in combustion chamber.The shortcoming of these rupture disks is
They are weakened over time because of the pressure fluctuated in combustion chamber, and final in relatively small excess pressure
Failed already under (for example, because small is caught fire).Therefore, rupture disk often prematurely fails.This is problematic, is particularly
Because engine must be stopped to replace failed rupture disk with new rupture disk.Therefore, it is the most frequently used at present 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 too high pressure in combustion chamber with from combustion
Burn the requirement that gas is discharged in room.These are spring-loaded poppets.However, due to their maximum open be not enough to it is sufficiently fast
Ground discharges pressure, so the explosive nature thereof of exhaust events causes these poppet relative nullities.Therefore, these safety valves can not be
Required aperture 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 can not prevent cylinder head from rising.
GB 817,018 discloses a kind of large-sized two-stroke diesel engine, and it has between cylinder liner and cylinder head
Separate ring, the separate ring, which is provided with, to be used to receive the hole of safety valve.However, the known safety valve is unreliable, and
And stopped using the safety valve.
Accordingly, it would be desirable to a kind of improved exhaust control for cross-head type large-sized two-stroke compression ignition type explosive motor
System processed.
The content of the invention
It is an object of the invention to provide the cross-head type large-sized two-stroke compression ignition for overcoming or at least reducing above mentioned problem
Formula explosive motor.
Foregoing end other objects are realized by the feature of independent claims.According to dependent claims, specification and
Accompanying drawing, other forms of implementation are obvious.
According to first aspect, there is provided a kind of large-sized turbo-charging two-stroke compression ignition type internal combustion hair with crosshead
Motivation, including：
Multiple cylinders as combustion chamber, the cylinder has cylinder head, the exhaust being centrally placed in the cylinder head
Valve and the discharge duct that the air bleeding 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 centre position scope 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 exported, and when movable valve component is in the closed position, dump valve prevents that gas from flowing to from entrance and exported,
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 be exposed to the hydraulic pressure for being used to push to movable valve component closed position second
Effective pressure surface,
The second effective pressure surface has first size when movable valve component is in the closed position, it is described can
There is the second size less than the first size, the first position scope is from complete in the range of the first position of mobile valve member
Full open position extends to predetermined intermediate position.
Closed by providing to have to be pushed to its open position by the pressure in combustion chamber and be pushed to it by hydraulic pressure
The dump valve of the movable member of closed position, it is possible to achieve following device：The device can be opened with sufficiently large fast enough
Mouthful open, with excess pressure in a combustion chamber in the case of provide prevent damage engine needed for release.By using hydraulic pressure
To balance the movable member of dump valve, the pressure that can reliably control dump valve to open, and following knot can be provided
Structure：The structure is quick and roomily opens, to provide the big circulation area for the gas effusion for causing combustion chamber.When dump valve is beaten
When opening, the second effective pressure surface of reduction is prevented due to caused by the pressure decline in the combustion chamber when dump valve is opened
It is undesirable to repeat to open and close.
In the first possible embodiment of first aspect, precalculated position is than fully open position closer to close stance
Put.
In the second possible embodiment of first aspect, the second effective pressure surface pass through movable valve component
One surface and 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 3rd possible embodiment of first aspect, first surface passes through in all positions of movable valve component
Hydraulic pressure is pressurized, and wherein second surface is pressurized by hydraulic pressure in the range of first position.
In the 4th possible embodiment of first aspect, movable valve component opens permission in the range of first position
The port that second surface is pressurized by hydraulic pressure.
In the 5th possible embodiment of first aspect, movable valve component is provided with the valve disc coordinated with valve seat,
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
Set.
In the 7th possible embodiment of first aspect, movable valve component includes the valve disc being connected with valve rod and can
It is operatively coupled to the actuating piston of valve rod.
In the 8th possible embodiment of first aspect, first surface is arranged on the side of actuating piston, the second table
Face is arranged on the opposite side of actuating piston.
In the 9th possible form of implementation of first aspect, tap is connected to discharge duct or exhaust by discharge pipe
Receiver, so as to bypass air bleeding valve.
In the tenth possible embodiment of first aspect, the dump valve is provided with cooling device, the cooling dress
Put the path preferably included for cooling medium by dump valve.
In the 11st possible embodiment of first aspect, engine includes hydraulic system, and the hydraulic system has
Pressure increase as engine load increases, and reduce, and wherein second effective with engine load reduction
Pressure surface is pressurized by the hydraulic pressure of hydraulic system.
In the 12nd possible embodiment of first aspect, hydraulic system provides power for Fuelinjection nozzle.
In the 13rd possible embodiment of first aspect, hydraulic system provides power for exhaust valve actuation system.
Brief description of the drawings
In the part in detailed below of the disclosure, the illustrative embodiments shown in refer to the attached drawing are solved in more detail
The present invention is released, wherein：
Fig. 1 is the front view of the large-sized two-stroke diesel engine according to illustrative embodiments；
Fig. 2 is the side view of Fig. 1 large-sized two-stroke engine；
Fig. 3 is the schematic diagram of the large-sized two-stroke engine according to Fig. 1；
Fig. 4 is the side view of cylinder head and the exhaust valve with the dump valve according to embodiment；
Fig. 5 is the sectional view along Fig. 4 line A-A interception；
Fig. 6 is the top view of the dump valve according to embodiment；
Fig. 7 to Fig. 9 is the sectional view of Fig. 6 dump valve, and wherein the movable valve component of dump valve is in diverse location；
Figure 10 is the different sectional views of Fig. 6 dump valve；With
Figure 11 is the schematic diagram of the hydraulic system of Fig. 1 to Fig. 3 engine.
Embodiment
In the following detailed description, the large-sized two-stroke turbine with crosshead will be described by illustrative embodiments
Charge compression ignition formula (diesel oil) explosive motor.Fig. 1 to Fig. 3 shows the large-sized low-speed whirlpool with bent axle 42 and crosshead 43
Wheel supercharging two-stroke compression ignition engine.Fig. 3 shows the schematic diagram of the engine with gas handling system and gas extraction system.
In the illustrative embodiments, engine has six cylinders 1 being in line.Large-sized two-stroke turbocharging compression ignition
Formula explosive motor generally 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 that generator is operated in power station.Engine it is total defeated
Going 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, and it has the lower area in cylinder 1
In scavenging port 19 and the air bleeding valve 4 that is centrally disposed at the top of cylinder 1 in cylinder head 22.The principal direction that air-flow passes through cylinder
For the air bleeding valve 4 at the top from the scavenging port 19 of the bottom of cylinder 1 to cylinder 1, therefore entitled " unidirectional stream ".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
The compressing charge air of piston 41, fuel is then burnt from the Fuelinjection nozzle (not shown) injection in cylinder head 22
And produce exhaust (waste gas).
When air bleeding valve 4 is opened, it is vented and exhaust reception is flowed into by the discharge duct 35 associated with involved cylinder 1
Device 3 (its be big hollow circular cylinder form), and it is advanced through the turbine 6 that first exhaust pipeline 18 flows to turbocharger 5,
Exhaust is from it flows to air by second exhaust pipeline 7.Turbine 6 is driven by axle 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 is used to leave at about 200 DEG C
The pressurized air of compressor is cooled to the temperature between 36 DEG C and 80 DEG C.
The pressurized air of cooling 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 air inlet receiver 2.At higher engine loads,
Turbocharger compressor 9 conveys enough compressed scavenging airs, then auxiliary blower 16 via check-valves 15 by around
Cross.
Fig. 4 and Fig. 5 illustrate in greater detail air bleeding valve 4 and the side view and sectional view of cylinder head 22 respectively.The profit of air bleeding valve 4
It is bolted to securely in cylinder head 22 with exhasut valve stem 44, wherein, during its overall 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 is leaned against on valve seat.When air bleeding valve 4
During opening, combustion chamber 27 is connected to blast pipe 35.In embodiments, blast 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 some cooling ducts sightless in figure.
In addition, Fuelinjection nozzle (has three fuel valves and for dual fuel engine generally for each cylinder of single-fuel engine
Each cylinder have six fuel valves) (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.
Air bleeding valve 4 is provided with hydraulic pressure exhaust valve actuators 47, and it includes the hydraulic pressure chamber 38 positioned at the top of valve rod 44.Air
Spring 37 promotes valve rod 44 (in such as Fig. 5 upwards, i.e., along closing direction) upwards, and when hydraulic actuator 47 is pressurized, hydraulic pressure
Actuator 47 promotes valve rod 44 along opening direction.Therefore, air bleeding 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 return to its closed position.
Engine is provided with the discharge line (as shown in the figure) that blast pipe 35 is extended to from combustion chamber 27.Alternatively, arrange
Go out pipeline and extend to exhaust receiver 3 from combustion chamber 27.The cross-sectional area of discharge line is sufficiently large, to catch fire or burn
The pressure in combustion chamber 27 is fully discharged in the case of causing other events of excess pressure in room 27 soon.Dump valve 50 is controlled
The opening and closing of discharge line, and air bleeding valve 50 can fast enough open with sufficiently large opening, for crossing high pressure
The pressure in combustion chamber 27 is discharged in the case of power, to prevent from damaging engine.
A part for the formation discharge line of tap 29 in cylinder head 22.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 housing 51 of its own (such as figure institute
Show) so that it may be used as being inserted into the socket in the suitable hole 28 (Fig. 5) in cylinder head 22, or dump valve 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 its medium-height trestle 68 is protruded from cylinder head 22.Support 68 can be with
It is bolted to housing 51 or the integration section as housing 51.Support 68, which is provided with, fixes dump valve 50 for receiving
The hole of bolt (Fig. 5) on to cylinder head 22.Housing 51 is provided with for allowing the big of exhaust discharge when dump valve 50 is opened
Export (opening) 58.
Dump valve 50, which is provided with, to be moved between the closed position shown in Fig. 7 and the fully open position shown in Fig. 9
Movable valve component 52, you can mobile valve member 52 can be between Fig. 7 closed position and Fig. 9 fully open position
Moved back and forth in position range.In fig. 8, movable valve component 52 is shown at centre 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 bulb in valve chest 52
Entrance 57 is connected to outlet 58 by 63.Valve seat 55 is arranged on 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 housing 51
Xiang Kongzhong.
Valve rod 53, be provided with the end of valve disc 54 and extended to from longitudinal hole in the hollow bulb 63 in valve chest 51.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
, 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 bulb 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 puts down
Face Z is obliquely installed relative to the principal direction of tap 29, to cause the limitation of flowing of the convection current through tap 29 to minimize.Work as row
Portal 29 when being straight, its principal direction is the longitudinal direction of the flowing in hole 29.When tap 29 is bending, its principal direction is
The course bearing of curve at the position that valve seat 55 intersects with tap 29.
Hollow bulb 63 is arranged on longitudinal hole, the guiding valve rod 53 side.It is provided with the opposite 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.Activate piston 56 and be fixed to valve rod 53, so as to be operably connected to movable valve component 52.Implementing
In mode, piston 56 can also be the integration section of movable valve component 52.Movable valve component 52 has the He of first surface 61
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 more 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, the quilt of movable valve component 52
Push closed position to.First surface 61 and second surface 62 form the second effective pressure surface together.First is acted on effectively to press
The pressure in combustion chamber 27 on power surface 59 and the area with the first effective pressure surface 59 multiply with 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 support 68, but it is also possible in housing 51.
The hydraulic system 88 of the engine of hydraulic pressure of the inbound port 80 with providing at continuous floor level is connected.It is preferred that
Ground, hydraulic system 88, which provides constant pressure or provided, to be increased with engine load increase and with engine load reduction
The pressure of reduction.
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 the top (top in the orientation of the dump valve 50 in such as Fig. 7-Figure 10) of compensation port 71
Position when, subsidiary conduit 64 is connected to port 80 by compensating port 71 by second chamber 66.At movable valve component 52
When its closed position as illustrated in fig. 7 and fig. 10, compensation port 71 activated piston 56 and stopped.
As illustrated in fig. 7 and fig. 10 in this case, second chamber 66 is held being substantially less than by cooling down inbound port 75
It is pressurized under the low pressure of pressure at mouth 80.Cooling down inbound port 75 allows cooling oil (hydraulic fluid) to flow into chamber 66, for cold
But dump valve 50.Cooling down exit port 74 allows cooling oil (hydraulic fluid) to flow out.Go out in the upstream of cooling inbound port 75 and cooling
The downstream of port 74 sets flow resistance (not shown), for allowing the pressure in second chamber 66 to be instantaneously relatively higher than cooling
Fluid pressure.
When occurring too high pressure in combustion chamber 27, act in the combustion chamber 27 on the first effective pressure surface 59
Pressure by more than the reaction force of the pressure produced by first pressure chamber on movable valve component 52, 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
It is connected to the elevated pressures at port 80.The limited part associated with cooling exit port 74 with cooling inbound port 75 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 produce the additional force that movable member is pushed to its fully open position.Therefore, act on movable valve component 52
Closing forces are substantially reduced.When movable valve component 52 is somewhat opened, the reduction of the closing forces is used to ensure during exhaust events
Dump valve 50 is stable to be opened.That is, in combustion chamber 27 gas pressure tensile force due to hollow bulb 63 pressurization and in valve
Disk 54 is significantly reduced at the time of rise from seat 55.If without counter-measure, this tensile force loss may cause in single mistake
Undesirably repeat to open and close dump valve 50 during high pressure event.When secondary ports 71, which do not activated piston 56, to be stopped
Closing forces reduce, so as to provide stable opening procedure for dump valve 50.
Therefore, second acted on along closing direction on the movable valve component 52 pressurizeed by the pressure of hydraulic system 88 has
Effect 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 scope from fully open position always
To predetermined centre position.Centre position depend on secondary ports 71 relative to actuating piston 56 position, and preferably with
Compared apart from the fully open position closer to the closed position, but this according to circumstances depending on, and art technology
Personnel are possible to determine the optimum position that closing forces reduce.Other devices can also 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, it is moved by the free end of valve rod 53
The damping element 69 at place is damped with damping the cooperation of chamber 65.Damping element 69 is that its diameter is suitable to make it by slideably
The cylindrical elements in cylinder damping chamber 65 are contained in, and ensure that movable valve component 52 is slowly reached as shown in Figure 9
Fully open position at.
Hydraulic system 88 will in more detail be described 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 supply pressurized hydraulic to multiple customers (such as Fuelinjection nozzle 42, exhaust valve actuation system 48 and dump valve 50)
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 lines of (brand) engine hydraulic system are pseudo- common rails, wherein local accumulator is used to fit
Answer unexpected partial spent peak value.The hydraulic system of ME engines is that fuel valve and air bleeding valve provide power.In typical ME hairs
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
What the numeral in meaning, upper table was merely exemplary, and actual pressure value changes such as the different engines of given type
And change with the difference of engine type.In addition, drop forelock motivation, i.e., wherein load and speed is different from involved
The engine of the L1 loads of engine type, also by with different, generally lower slightly system pressures.
Normal maximum pressure in combustion chamber 27 increases also with the increase of engine load, and with engine load
Reduction and reduce, its be distributed and the pressure of the hydraulic system shown in this paper upper tables distribution it is closely similar.Therefore, phase is passed through
Size setting is carried out to the size of first surface 61 for the size on the first effective pressure surface 59, being capable of the row of setting
The normal pressure that going out the size of valve 50 makes it in than the combustion chamber 27 for actual engine load has higher surplus
Opened under pressure.Surplus can be constant differential pressure or increase as engine load increases that vice versa.
Dump valve 50 can also be to be supplied to the constant pressure operation of port 80.In this case, the pressure 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 230Bar pressure
Open.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 is sent out in exhaust events
Go out alarm.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 exceedes cooling oil pressure, then dump valve 50 has already turned on, and sends alarm.Alternatively,
Movable valve component 52 can be monitored with motion sensor, and be sent out when movable valve component 52 moves from its closed position
Go out alarm.
In embodiment (not shown), it can set and promote movable valve component 52 with the elasticity away from its closed position
Device (dish-type spring etc.), so as 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 put down
The gas pressure and supply to the hydraulic fluid of dump valve that weighing apparatus is only acted on movable valve component 52 in combustion chamber 27 are acted on
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 are by with causing the motion to movable valve component 52 during power operation not have
There is any less intensity significantly affected.
Combined this paper multiple embodiments describe the present invention.However, those skilled in the art are in practice calls
During the present invention of protection, pass through studying accompanying 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 some measures does not indicate that these are arranged in mutually different dependent claims
The combination applied can not be advantageously used.
The reference used in claim is not necessarily to be construed as the limitation to scope.
Claims (14)
1. one kind has the large-sized turbo-charging two-stroke compression ignition type explosive motor of crosshead (43), including：
Multiple cylinders (1) as combustion chamber (27), the cylinder (1) has：Cylinder head (22), it is centrally placed in the cylinder
Air bleeding valve (4) in lid (22) and the air bleeding valve (4) is connected to the discharge ducts (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,
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 centre positions between the closed position and fully open position,
When the movable valve component (52) is in any centre position or in the fully open position, the row
Going out valve (50) allows gas to flow to the outlet (58) from the entrance (57), 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, to be used to push the movable valve component (52) to the closed position
Hydraulic pressure the second effective pressure surface, and
The 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, described the in the range of the first position of the movable valve component (52)
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, the 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) is less than
The first surface (61) and it 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 pressurized by the hydraulic pressure, and wherein described second surface (62) passes through institute in the range of the first position
Hydraulic pressure is stated to be pressurized.
5. engine according to claim 4, wherein, the movable valve component (52) is in the range of the first position
Open the port (71) for allowing the second surface (62) to be pressurized by the hydraulic pressure.
6. engine according to any one of claim 1 to 5, wherein, the movable valve component (52) be provided with
The valve disc (54) that valve seat (55) coordinates, the valve seat is arranged in the tap (29) of the cylinder head (22).
7. engine according to any one of claim 1 to 6, wherein, the principal plane of the valve seat (55) is relative to institute
The principal direction for stating tap (29) is obliquely installed.
8. engine according to any one of claim 1 to 7, wherein, the movable valve component (52) includes and valve
The valve disc (54) of bar (53) connection and the actuating piston (56) for being operably connected to the valve rod (53).
9. engine according to any one of claim 1 to 8, wherein, the first surface (61) is arranged on the cause
The side of piston (56), and the second surface (62) is arranged on the opposite side of the actuating piston (56).
10. engine according to any one of claim 1 to 9, wherein, the tap (29) passes through discharge pipe (36)
The discharge duct (35) or the exhaust receiver (3) are connected to, to bypass the air bleeding valve (4).
11. engine according to any one of claim 1 to 10, wherein, the dump valve (50) is provided with cooling dress
Put, the cooling device is preferably included for for path of the cooling medium by the dump valve (50).
12. the engine according to any one of claim 1 to 11, wherein, the engine includes hydraulic system (88),
The pressure that the hydraulic system has increases as engine load increases, and reduces as engine load reduces,
And wherein described second effective pressure surface (61,62) is pressurized by the hydraulic pressure of the hydraulic system.
13. engine according to claim 12, wherein, the hydraulic system (88) is that Fuelinjection nozzle (42) offer is dynamic
Power.
14. the 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 true CN107061007A (en) | 2017-08-18 |
| CN107061007B 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 |
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| Country | Link |
|---|---|
| JP (1) | JP6188975B2 (en) |
| KR (1) | KR101780212B1 (en) |
| CN (1) | CN107061007B (en) |
| DK (1) | DK179120B1 (en) |
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 |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
-
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 JP JP2017017818A patent/JP6188975B2/en active Active
- 2017-02-02 KR KR1020170015208A patent/KR101780212B1/en active IP Right Grant
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 |
|---|---|
| KR20170092472A (en) | 2017-08-11 |
| KR101780212B1 (en) | 2017-10-10 |
| JP6188975B2 (en) | 2017-08-30 |
| DK179120B1 (en) | 2017-11-13 |
| JP2017137866A (en) | 2017-08-10 |
| DK201670059A1 (en) | 2017-08-28 |
| CN107061007B (en) | 2019-06-28 |
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