CN102162384B - Valve device for a large two stroke diesel engine - Google Patents
Valve device for a large two stroke diesel engine Download PDFInfo
- Publication number
- CN102162384B CN102162384B CN201110044751.XA CN201110044751A CN102162384B CN 102162384 B CN102162384 B CN 102162384B CN 201110044751 A CN201110044751 A CN 201110044751A CN 102162384 B CN102162384 B CN 102162384B
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- China
- Prior art keywords
- pressure
- valve
- valve member
- room
- floating valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/16—Controlling lubricant pressure or quantity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/03—Reducing vibration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/04—Reducing noise
Abstract
The utility model provides a valve device for a large two stroke diesel engine, the valve device is used for controlled backflow from a pressure pipeline (10), the pressure pipeline (10) connects the top of an air release valve driver to an electric hydraulic control valve (5) at the top part of a cylinder housing top part far lower than the top part of the air release valve. Therefore, when pressure of the pressure pipeline (10) is reduced, a cavitation and following cavitation erosion can be prevented without a supercharger or a pressure divider between the electric hydraulic control valve (5) and the pressure pipeline (10).
Description
Technical field
The present invention relates to valve gear, more particularly to it is a kind of for controlled reflow and for keeping the minimum of valve gear upstream to press
The valve gear of power.
Background technology
Conventional check valves with the movable valve component for closing on base can not be used in rugged environment, such as large-scale
In the air bleeding valve drive system of two stroke diesel engine.
Electric hydraulic control valve drive system in large two-stroke diesel engine considers the profile of flexible operating and air bleeding valve, permits
Perhaps improved emission control and fuel efficiency.
Very big power is needed come against promoting in combustor and in the closing direction the pressure of air bleeding valve to beat in air spring
Open 400 kilograms of the air bleeding valve of weighing.Accordingly, it would be desirable to high pressure and high-power hydraulic system are opening the row of large two-stroke diesel engine
Air valve.
Conditional electronic control (electro-hydraulic) air bleeding valve drive system of large two-stroke diesel engine is included by common rail to closing on
Or the high-pressure pump of valve block transmission hydraulic fluid (hydraulic oil or lubricating oil) placed on cylinder baffle top board.Valve block carries hydraulic pressure
The ratio electric hydraulic control valve of accumulator and control hydraulic fluid stream, so as to operate fuel injector and air bleeding valve.
Each valve block is connected to pressure pipeline the air bleeding valve of each of which.Valve block is generally positioned at the top of cylinder baffle
Portion, therefore, pressure pipeline must at the top of the valve block and exhaust valve actuators between bridge sizable distance and difference in height.The height
Degree difference can be several meters.
Supercharger (substantially having big and a little active surface a piston at either end) is arranged on the top of valve block.
One end of pressure pipeline is connected to supercharger, while the other end of pressure pipeline is connected to the top of air bleeding valve.Therefore, manometer tube
Road extends to the top of air bleeding valve from valve block.
Due to the size of these electromotors, the difference in height between air bleeding valve top and valve block is it will be apparent that i.e. several meters.
When air bleeding valve is in the position closed, the pressure in pressure pipeline should be close to zero.
Supercharger between valve block and pressure pipeline lower end prevents the hydraulic fluid in pressure pipeline to be discharged and keep away
Exempt from relative in hydraulic fluid pressure pipeline be full of air.
When closing air bleeding valve has been arrived, pressure pipeline is connected to fuel tank by electric hydraulic control valve.Due to being used to for air bleeding valve
Property, air pocket (air pockets) can be formed in pressure pipeline.Can cause cavitation pitting when pressure increases again these air pockets
(cavitation), therefore, it is necessary to place supercharger or potentiometer between electric hydraulic control valve and pressure pipeline.
The content of the invention
In this context, the purpose of the application is to provide a kind of valve gear, and it avoids or at least reduce drawbacks described above.
By providing a kind of valve gear this purpose is realized, it includes shell, arrival end, in arrival end or downstream
Fixed restriction device, the movable valve component with two relative effective pressure faces being contained in the hole of the shell, one
Effective pressure face is in the face of the first pressure room being in fluid communication with the reducer, and another effective pressure face is relative in the face of being connected to
The second pressure room of low pressure source, the port of export, its by the movable valve component movable valve component a position range
It is interior to close and in another position range opening of movable valve component, so as to first pressure room is connected to into the outlet
End, in the effective pressure area to the position range that first pressure room is connected with the port of export promotes movable valve structure
Part, another in the effective pressure area promotes removable to the position range that first pressure room is not connected with the port of export
Valve member.
Valve gear allows the controlled reflow to fuel tank and keeps the minimum pressure of valve upstream.It can thus be avoided or at least
Reduce the formation of air pocket and cavitation pitting.
Conventional check valves can not be used in the adverse circumstances that there is big barometric gradient, the row of such as large two-stroke diesel engine
Air valve drive system, because the check-valves closed by base will be destroyed after the relatively little of cycle.
Valve gear can also include that first pressure room is connected to second pressure by it through the hole of the movable valve component
Room.
Preferably, the hole through the movable valve component can be provided with side opening, when the movable valve component is can
Mobile valve member is connected to first pressure room when significantly being moved in the position range of the port of export, and side opening is pressed second
Power room is connected to overfall.
In one embodiment, an effective pressure face is more than another effective pressure face.
Movable valve component can limit the edge in control edge and the hole for being accommodated therein movable valve component.
According to specific descriptions, will become more according to the further object of the valve gear of the disclosure, feature, advantage and characteristic
Substantially.
Description of the drawings
In the following concrete part of this specification, the exemplary embodiment shown in refer to the attached drawing is carried out more to the present invention
Detailed description, wherein：
Fig. 1 is the schematically partial sectional of the air bleeding valve drive system of the use valve gear according to an exemplary embodiment
Face view；
Fig. 2 is the figure of the hydraulic solution exemplified with valve drive system shown in Fig. 1；And
Fig. 3 is the cross-section details figure of valve in air bleeding valve drive system shown in Fig. 1.
Specific embodiment
Fig. 1 is the partial cross-sectional views of the air bleeding valve drive system of an exemplary embodiment according to the disclosure.Row
Air valve drive system is large two-stroke diesel engine, such as a part for crosshead type large turbocharging single current diesel engine.Greatly
Type two stroke diesel engine structurally and operationally it is widely known that therefore being not described in detail here.
Valve block (valve block) 3 is arranged on the top board of the cylinder baffle of large two-stroke diesel engine.Valve block is carried
Electronically controlled proportional hydraulic controls valve 5.The electronic control unit of electronically controlled proportional hydraulic control valve 5 and electromotor is (not
Illustrate) it is connected.Valve block 3 also carries one or more accumulators 8 and valve gear 20.One end of pressure pipeline 10 and valve block 3
A port connection.The difference in height that pressure pipeline 10 is covered can be several meters, and without corresponding measure, gravity can cause to work as pressure
When the blood pressure lowering of pipeline 10 is to allow air bleeding valve to return its base, pressure pipeline 10 is drained from and full of air.
Pressure pipeline 10 is connected to a port that proportional hydraulic controls valve 5 by the hole 7 in valve block 3, and hole 11 is by valve gear
20 are connected to another port that proportional hydraulic controls valve 5, and proportional hydraulic control valve 5 is connected to high-voltage power supply by another hole 9, its
It is in this case common rail.
The other end of pressure pipeline 10 is connected to the top of aerofluxuss valve shell 12.The main shaft of air bleeding valve is illustrate only in figure
14.Hydraulic unit driver for opening air bleeding valve is placed on the top of main shaft 14.Hydraulic unit driver includes at least one pressure chamber
16 and a piston 18, and when hydraulic unit driver pressurizes, it promotes in the direction of the opening air bleeding valve.Air spring (does not show
Go out) for promoting air bleeding valve in the closing direction in a well-known manner.
Fig. 2 is the figure of the hydraulic solution exemplified with valve drive system shown in Fig. 1.The system includes high-pressure common rail 32, its
Supplied by the high pressure pumping station of one or more electromotors.High-pressure common rail 32 keeps the pressure of hundreds of bars (bar).It is also common including low pressure
Rail 34, it is maintained at about 2.2 bars.Common rail 36 is connected under substantially atmospheric pressure with fuel tank.
Ratio electric hydraulic control valve 5 is connected to high-pressure common rail 32 by conduit 9 (being formed by the hole in valve block 3).The electro-hydraulic control of ratio
Valve processed 5 includes pilot stage, and it uses the valve element of the pressure moving ratio electric hydraulic control valve 5 on the position for needing from conduit 9.
Conduit 9 is connected as branch with several hydraulic accumulators 8, and when flow velocity increases suddenly, several hydraulic accumulators 8 are used for protecting
Hold/steady pressure.
The port of export of the ratio electric hydraulic control valve 5 being associated with fuel injection system is connected to low pressure common rail system by conduit 13
34.Conduit 11 is connected to the port of export of the ratio electric hydraulic control valve 5 being associated with air bleeding valve drive system by valve gear 20
Low pressure common rail system 34.Valve gear 20 includes reducer, non-time (non-return) function, and keeps the minimum pressure in conduit 11
Power.
Ratio electric hydraulic control valve 5 is connected to the fuel injection system 30 with its supercharger and ejector 37, also, ratio
Electric hydraulic control valve 5 is also connected to exhaust valve actuators.Fuel injection system is it is well known that just no longer doing more detailed here
Describe.
Hydraulic diagram shows and is connected to outside the exhaust valve actuators with piston 18, air spring and air bleeding valve main shaft 14
The pressure pipeline 10 of shell 12.Compressed air source 19 is also connected to aerofluxuss valve shell 12, for supplying compressed air for air spring,
Air spring promotes in the closing direction air bleeding valve.Additionally, determining that the position sensor of exhaust valve positions and air bleeding valve drive
Device is associated.
During power operation, ratio electric hydraulic control valve 5 is being sent out under the electronic control unit order of electromotor
Air bleeding valve drive system or fuel injection system are connected to high-pressure common rail by reasonable time in motivation circulation.Therefore, when arriving
When opening air bleeding valve, the electronic control unit of electromotor is by order ratio electric hydraulic control valve 5 in high-pressure common rail 32 and pressure
Connection is set up between pipeline 10.Then, air bleeding valve opens the power of the pressure headed in combustor and air spring.When having arrived again
When secondary closing air bleeding valve, order ratio electric hydraulic control valve 5 is passed through valve gear 20 by pressure pipeline 10 by electronic control unit
It is connected to low pressure common rail system 34.Air bleeding valve and exhaust valve actuators associated there have sizable inertia, if working as ratio
Pressure pipeline 10 is directly connected to fuel tank when electric hydraulic control valve 5 sets up connection, then the closing of air bleeding valve will compare pressure pipeline
Pressure drop in 10 is more slowly.Valve gear 20 includes reducer, and it guarantees that pressure drop will not be too fast, and valve gear 20 will
Minimum pressure is kept at upstream side.Thus, it is to avoid pressure drop is too fast and excessively slow in pressure pipeline 10.This will be avoided pressure
The formation of air pocket and subsequent cavitation pitting in pipeline 10.
Fig. 3 shows valve gear 20 in greater detail.In the present example embodiment, valve gear includes outer with through hole
Shell.Valve gear 20 be included in one end of through hole be arranged in or neighbouring valve gear 20 arrival end fixed restriction device 21.Valve is filled
Putting 20 arrival end can be connected to ratio electric hydraulic control valve 5 by hole 11.
Movable valve component 22 with substantially cylindrical body is slidably received in through hole.Movable valve component 22
A pressure face is provided with every one end.First pressure face is arranged in that movable valve component 22 faces arrival end and reducer 21
Side.First pressure room 23 is formed in the hole between reducer 21 and first pressure face.
Second pressure face is arranged in the opposite side of movable valve component 22.Second pressure face is in the face of being equally arranged in through hole
In second pressure room 25.Second pressure room is connected to a relatively low pressure source, such as low pressure common rail system 34.
Form running through in the part with diameter greater than formation second pressure room of the through hole in the part of first pressure room
The diameter in hole.Therefore, active surface of the active surface in first pressure face more than second pressure face.Movable valve component 22 is arranged
There is the hole 26 of the first and second pressure chamberes of connection.The diameter in hole 26 is relatively small, so as to control the flowing between two pressure chamberes.
The port of export 27 connects fuel tank 36.The port of export 27 is by movable valve component 22 in a position of movable valve component 22
In the range of close and open in another position range of movable valve component 22, it is described so as to first pressure room be connected to
The port of export 27.In the range of the open position of movable valve component 22, first pressure room 23 is connected to the port of export 27.
With reference to the direction of valve gear in Fig. 3, when movable valve component 22 is in its relatively low position range, movable valve
The connection that component 22 is closed between first pressure room 23 and the port of export 27, when movable valve component 22 is in its higher position model
When enclosing, movable valve component 22 opens the connection between first pressure room 23 and the port of export 27.
The first larger effective pressure area to the position range that the port of export 27 is connected to first pressure room 23 promotes removable
Dynamic valve member 22, and less second effective pressure area is to the connection closed between first pressure room 23 and the port of export 27
Position range promotes movable valve component 22.
Movable valve component 22 is provided with the side opening 28 being connected with the overfall 29 on the shell of valve gear 20, when described
Movable valve component 22 move up to a great extent (relative to valve gear in Fig. 3 direction upwards) when so that side opening 28
Overlap with overfall 29.Therefore, second pressure room 25 is connected to fuel tank 34, so as to the pressure of the pressure chamber below reaches peak
Pressure in allowing movable valve component 22 to fully open the port of export 27 to discharge first pressure room 23 during value.
When the flowing of first pressure room is entered not over reducer 21, behind pressure in room be less than second pressure room
In pressure coefficient be equal to effective pressure face size between ratio.Therefore, when the pressure in second pressure room is, for example, 2.2
When bar, the pressure in first pressure room can be 1.5 bars.When pressure pipeline 10 is connected to valve by ratio electric hydraulic control valve 5
When device 20, it will have a large amount of streams to become sufficiently high to first by the pressure in reducer 21 and first pressure room
The position of connection establishment promotes movable valve component 22 between pressure chamber 21 and the port of export 27 so that hydraulic fluid can be evacuated
To fuel tank.The position of movable valve component 22 will balance between the pressure in pressure chamber.
The position of valve 22 is determined by following power.The first effective pressure area × first pressure room of first pressure room 23
Pressure in second effective valve face product × second pressure room 25 of the pressure comparison second pressure room 25 in 23.Work as exhaust valve closure
When, the pressure in second pressure room 25 is about 2 bars.Dynamic balance pressure in first pressure room 23 can be 1.5 bars.The
Pressure differential between one pressure chamber 23 and second pressure room 25 will cause fluid to flow in first pressure room 23 by hole 26.
Pressure in first Room 23 increases again will the opening that move up valve member 22 and increase the port of export 27
The value of the power that pressure limit is acted in balance on movable valve component 22.
Therefore, will be identical to the stream of the port of export 27 with from room 23 by the stream in hole 26.From first pressure room 23 to the port of export
27 aperture area will be the stream for passing through hole 26 in the dP (pressure differential) between first pressure room 23 and second pressure room 25.Can
Therefore mobile valve member 22 " will float " and adjust its position to working condition.
The balance in combination with reducer 21 will provide suitable flow velocity and keep the overvoltage of valve gear upstream (if i.e.
Air bleeding valve drive system uses valve gear, then in pressure pipeline).These effects guarantee that flow velocity is controllable and enters without air
Enter.
Valve gear 20 is described as a part for the air bleeding valve drive system of large two-stroke diesel engine.However,
It is understood that valve gear 20 can use other situations that controlled reflow is needed in adverse circumstances and minimum pressure is kept
Under.
Air bleeding valve drive system is described by reference to the large two-stroke diesel engine of single cylinder.In multicylinder engine, must
Such air bleeding valve drive system must be provided for each cylinder (or being at least each air bleeding valve), except being made by multiple cylinders
Common rail.
The teaching of the disclosure has many advantages.It is following that different embodiments or embodiment can produce one or more
Advantage.It should be noted that this is not detailed list, and can also there is the further advantage not described here.Disclosure teaching
One advantage is it offers valve gear, and it allows to flow back to fuel tank under controlled conditions, so as to avoid air pocket and cavitation pitting
Produce.
Another advantage of the disclosure is it offers valve gear, and it can be in the valve member that can not be used with close on base
The function of check-valves is played in rugged environment with reference to the conventional check valves of operation.
Although teachings of the present application has been carried out for illustrative purposes detailed description, it should be appreciated that this details is only used
In the purpose, and those skilled in the art can wherein make change in the case of the scope instructed without departing from the application
Shape.
Term " including (comprising) " used in claim is not precluded from miscellaneous part or step.Claim
Used in term " (a) " or " one (an) " be not precluded from it is multiple.Uniprocessor or other units can realize claim
In the function of several means enumerated.
Claims (4)
1. a kind of valve gear, including：
Shell,
Arrival end, it is used to be connected to the first hydraulic pressure source,
Fixed restriction device (21) at the arrival end or downstream,
Be contained in the through hole of the shell, the floating valve member (22) with two relative effective pressure faces,
First pressure room (23) between the reducer and the floating valve member (22) in the housing, described first
Pressure chamber (23) receives hydraulic fluid by the fixed restriction device (21) from the arrival end,
Second pressure room (25) in the housing, the second pressure room (25) is connected to the second hydraulic pressure source,
The first effective pressure face in described two relative effective pressure faces, it faces the first pressure room (23),
Second effective pressure face, it faces the second pressure room (25),
Wherein, the first pressure room (23) is limited in side by fixed restriction device (21), effective by described first in opposite side
Pressure face is limited,
The port of export (27), its position range by the floating valve member (22) in the floating valve member (22) is closed simultaneously
And another position range in floating valve member (22) is opened, so as to the first pressure room (23) is connected to into the outlet
End (27),
First effective pressure promotes institute towards the position range that the first pressure room (23) is connected with the port of export (27)
Floating valve member (22) is stated, and second effective pressure is not connected towards the first pressure room (23) with the port of export (27)
The position range that connects promotes the floating valve member (22), and through the hole (26) of the floating valve member (22), and it is by institute
State first pressure room (23) and be connected to the second pressure room (25).
2. valve gear according to claim 1, wherein, arrange through the hole (26) of the floating valve member (22)
There is side opening (28), when the floating valve member (22) is connected to the first pressure room (23) in the floating valve member (22)
When significantly being moved in the position range of the port of export (27), the side opening (28) is by the second pressure room (25)
It is connected to overfall (29).
3. valve gear according to claim 1, wherein, the first effective pressure face is more than second effective pressure
Face.
4. valve gear according to claim 1, wherein, the floating valve member (22) limits it to be used to control the port of export
(27) edge for opening or closing, and shell is limited for accommodating the edge of the through hole of floating valve member (22).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201000153A DK177283B1 (en) | 2010-02-24 | 2010-02-24 | Valve arrangement |
| DKPA201000153 | 2010-02-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102162384A CN102162384A (en) | 2011-08-24 |
| CN102162384B true CN102162384B (en) | 2017-04-12 |
Family
ID=44463801
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110044751.XA Active CN102162384B (en) | 2010-02-24 | 2011-02-24 | Valve device for a large two stroke diesel engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5372036B2 (en) |
| KR (1) | KR101242611B1 (en) |
| CN (1) | CN102162384B (en) |
| DK (1) | DK177283B1 (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4271796A (en) * | 1979-06-11 | 1981-06-09 | The Jacobs Manufacturing Company | Pressure relief system for engine brake |
| CN1654835A (en) * | 2004-02-12 | 2005-08-17 | 沃尔沃建造设备控股（瑞典）有限公司 | Relief valve |
| CN101160457A (en) * | 2005-04-14 | 2008-04-09 | 曼狄赛尔公司 | Exhaust valve assembly for a large two-stroke diesel engine |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5423332U (en) * | 1977-07-19 | 1979-02-15 | ||
| JPS58175270U (en) * | 1982-05-20 | 1983-11-24 | 株式会社網野鉄工所 | Ultra-high pressure relief valve for opposed hydraulic molding |
| JPS58191474U (en) * | 1982-06-17 | 1983-12-20 | 株式会社トキメック | relief valve |
| JPS62253911A (en) * | 1986-03-31 | 1987-11-05 | Tech Res Assoc Highly Reliab Marine Propul Plant | Hydraulic drive valve device for reciprocating internal combustion engine |
| JPS633576U (en) * | 1986-06-25 | 1988-01-11 | ||
| JP2564216Y2 (en) * | 1991-02-26 | 1998-03-04 | 株式会社ユニシアジェックス | Oil relief device |
| DK170121B1 (en) | 1993-06-04 | 1995-05-29 | Man B & W Diesel Gmbh | Sliding valve and large two stroke internal combustion engine |
| DE19818385A1 (en) * | 1998-04-24 | 1999-10-28 | Bosch Gmbh Robert | Connecting valve for fuel injection system of internal combustion engine |
| JP2004084670A (en) | 2002-08-28 | 2004-03-18 | Man B & W Diesel As | Valve operated with hydraulic pressure |
| WO2006081829A1 (en) * | 2005-02-02 | 2006-08-10 | Man Diesel A/S | A large two-stroke diesel engine with hydraulically actuated exhaust gas valves |
| ITMI20072219A1 (en) * | 2007-11-23 | 2009-05-24 | Bosch Gmbh Robert | OVERPRESSURE VALVE AND HIGH PRESSURE PUMP INCLUDING THIS PRESSURE VALVE |
| JP4686561B2 (en) * | 2008-02-14 | 2011-05-25 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Exhaust valve actuator for large two-cycle diesel engines |
| CN102066703B (en) * | 2008-06-25 | 2013-02-13 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Hydraulic supply system of a large two-stroke diesel engine |
-
2010
- 2010-02-24 DK DKPA201000153A patent/DK177283B1/en active
-
2011
- 2011-01-27 JP JP2011014829A patent/JP5372036B2/en active Active
- 2011-02-22 KR KR1020110015694A patent/KR101242611B1/en active IP Right Grant
- 2011-02-24 CN CN201110044751.XA patent/CN102162384B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4271796A (en) * | 1979-06-11 | 1981-06-09 | The Jacobs Manufacturing Company | Pressure relief system for engine brake |
| CN1654835A (en) * | 2004-02-12 | 2005-08-17 | 沃尔沃建造设备控股（瑞典）有限公司 | Relief valve |
| CN101160457A (en) * | 2005-04-14 | 2008-04-09 | 曼狄赛尔公司 | Exhaust valve assembly for a large two-stroke diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102162384A (en) | 2011-08-24 |
| JP2011174462A (en) | 2011-09-08 |
| JP5372036B2 (en) | 2013-12-18 |
| KR101242611B1 (en) | 2013-03-19 |
| DK177283B1 (en) | 2012-10-08 |
| DK201000153A (en) | 2011-08-25 |
| KR20110097673A (en) | 2011-08-31 |
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Address after: Copenhagen Patentee after: Man energy solutions (man energy solutions, Germany Ag) branch Address before: Copenhagen Patentee before: Man Diesel AS |