CN102162384A - Valve device for a large two stroke diesel engine - Google Patents
Valve device for a large two stroke diesel engine Download PDFInfo
- Publication number
- CN102162384A CN102162384A CN201110044751XA CN201110044751A CN102162384A CN 102162384 A CN102162384 A CN 102162384A CN 201110044751X A CN201110044751X A CN 201110044751XA CN 201110044751 A CN201110044751 A CN 201110044751A CN 102162384 A CN102162384 A CN 102162384A
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- China
- Prior art keywords
- pressure
- valve member
- pressure chamber
- valve
- control valve
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/03—Reducing vibration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/04—Reducing noise
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Safety Valves (AREA)
- Fuel-Injection Apparatus (AREA)
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 control valve unit, relate in particular to a kind of control valve unit that is used for controlled backflow and is used for the pressure minimum of maintaining valve device upstream.
Background technique
Conventional check valves with the removable valve member that closes on base can not be used in rugged environment, in the outlet valve drive system such as large two-stroke diesel engine.
Electro-hydraulic control valve drive system in the large two-stroke diesel engine is considered the profile of flexible operating and outlet valve, allows improved emission control and fuel efficiency.
Need very big power come against in the firing chamber and the pressure that on closing direction, promotes outlet valve in the pneumatic spring open 400 kilograms the outlet valve of weighing.Therefore, need high pressure and high-power hydraulic system to open the outlet valve of large two-stroke diesel engine.
Conditional electronic control (electric liquid) outlet valve drive system of large two-stroke diesel engine comprises by be total to the high-pressure service pump of rail to the valve block movement hydraulic fluid (hydraulic oil or lubricant oil) that closes on or place on the cylinder baffle top board.The valve piece carries the ratio electro-hydraulic control valve of hydraulic accumulator and control flow of hydraulic fluid, thus operation oil sprayer and outlet valve.
Pressure piping is connected to their outlet valves separately with each valve piece.The valve piece is placed on the top of cylinder baffle usually, therefore, pressure piping must be between valve piece and exhaust valve actuators top sizable distance of cross-over connection and height difference.This height difference can be several meters.
Pressurized machine (being essentially the piston that has a big and little effective drying surface at arbitrary end) is installed in the top of valve piece.One end of pressure piping is connected to pressurized machine, and the other end of pressure piping is connected to the top of outlet valve simultaneously.Therefore, pressure piping extends to the top of outlet valve from the valve piece.
Because the size of these motors, the height difference between outlet valve top and the valve piece is clearly, promptly several meters.
When outlet valve in the position of closing, the pressure in the pressure piping should approach zero.
Valve piece and pressure piping prevent that than the pressurized machine between the low side hydraulic fluid in the pressure piping is discharged from and avoids with respect to being full of air in the hydraulic fluid pressure pipeline.
When to when closing outlet valve, electro-hydraulic control valve is connected to fuel tank with pressure piping.Because the inertia of outlet valve can form air pocket (air pockets) in the pressure piping.Cavitation pitting (cavitation) can be caused when pressure increases these air pockets again, therefore, pressurized machine or voltage divider must be between electro-hydraulic control valve and pressure piping, placed.
Summary of the invention
Under this background, the application's purpose provides a kind of control valve unit, and it is avoided or reduces above-mentioned defective at least.
By providing a kind of control valve unit to achieve this end, it comprises shell, entry end, fixed restriction device in entry end or its downstream, be contained in the removable valve member that has two relative effective pressure faces in the hole of described shell, first pressure chamber of effective pressure face in the face of being communicated with described flow controller fluid, another effective pressure face is in the face of being connected to second pressure chamber in relatively low pressure power source, outlet end, it is closed in a position range of removable valve member by described removable valve member and opens at another position range of removable valve member, thereby first pressure chamber is connected to described outlet end, a position range that is connected with outlet end to first pressure chamber in the described effective pressure area promotes removable valve member, and another position range that is not connected with outlet end to first pressure chamber in the described effective pressure area promotes removable valve member.
Control valve unit allows to the controlled backflow of fuel tank and the pressure minimum of maintaining valve upstream.Therefore, can avoid or reduce at least the formation of air pocket and cavitation pitting.
Conventional check valves can not be used and have the rugged environment of big pressure gradient, and the outlet valve drive system of large two-stroke diesel engine for example is because will destroy the safety check of closing by base after few relatively cycle.
Control valve unit can also comprise the hole of running through described removable valve member, and it is connected to second pressure chamber with first pressure chamber.
Preferably, the hole of running through described removable valve member can be provided with side opening, when described removable valve member carries out in removable valve member is connected to first pressure chamber position range of outlet end when significantly mobile, side opening is connected to flow-off with second pressure chamber.
In one embodiment, an effective pressure face is greater than another effective pressure face.
The edge that removable valve member can limit the control edge and removable valve member is contained in hole wherein.
According to specific descriptions, will become more obvious according to further purpose, feature, advantage and the characteristic of control valve unit of the present disclosure.
Description of drawings
In the following concrete part of this specification, the present invention will be described in more detail for the exemplary embodiment shown in reference to the accompanying drawings, wherein:
Fig. 1 is the summary part viewgraph of cross-section according to the outlet valve drive system of the use control valve unit of an exemplary embodiment;
The figure of the hydraulic solution of valve drive system shown in Fig. 1 that Fig. 2 has been an illustration; And
Fig. 3 is the cross-section details figure of valve in the drive system of outlet valve shown in Fig. 1.
Embodiment
Fig. 1 is the part viewgraph of cross-section according to the outlet valve drive system of an exemplary embodiment of the present disclosure.The outlet valve drive system is a large two-stroke diesel engine, such as the part of crosshead type large turbosupercharging single current diesel engine.The structure of large two-stroke diesel engine and operation are well-known, therefore do not do detailed description here.
Valve piece (valve block) 3 is installed on the top board of cylinder baffle of large two-stroke diesel engine.The valve piece carries electronically controlled ratio hydraulic control valve 5.Electronically controlled ratio hydraulic control valve 5 is connected with the electronic control unit (not shown) of motor.Valve piece 3 also carries one or more accumulators 8 and control valve unit 20.One end of pressure piping 10 is connected with a port of valve piece 3.The height difference that pressure piping 10 covers can be several meters, does not have corresponding measure, and gravity can cause when pressure piping 10 step-downs are returned its base with the permission outlet valve, and pressure piping 10 is drained and is full of air.
Hole 7 in the valve piece 3 is connected to pressure piping 10 port of ratio hydraulic control valve 5, hole 11 is connected to control valve unit 20 another port of ratio hydraulic control valve 5, another hole 9 is connected to high-voltage power supply with ratio hydraulic control valve 5, and it is in this case for being total to rail.
The other end of pressure piping 10 is connected to the top of outlet valve shell 12.Only show the main shaft 14 of outlet valve among the figure.The hydraulic unit driver that is used to open outlet valve is placed on the top of main shaft 14.Hydraulic unit driver comprises at least one pressure chamber 16 and a piston 18, and when hydraulic unit driver pressurizes, and it promotes outlet valve opening on direction.The pneumatic spring (not shown) is used for promoting in a well-known manner outlet valve on closing direction.
The figure of the hydraulic solution of valve drive system shown in Fig. 1 that Fig. 2 has been an illustration.This system comprises high-pressure common rail 32, and its high pressure pumping plant by one or more motors is supplied with.High-pressure common rail 32 keeps the pressure of hundreds of crust (bar).Also comprise low pressure rail 34 altogether, it remains on about 2.2 crust.Rail 36 roughly is being connected with fuel tank under the atmospheric pressure altogether.
Conduit 9 (being formed by the hole in the valve piece 3) is connected to high-pressure common rail 32 with ratio electro-hydraulic control valve 5.Ratio electro-hydraulic control valve 5 comprises pilot stage, and it uses the spool from pressure moving ratio electro-hydraulic control valve 5 on the position of needs of conduit 9.Conduit 9 is connected with several hydraulic accumulators 8 as branch, and when flow velocity increased suddenly, several hydraulic accumulators 8 were used for maintenance/steady pressure.
The outlet end of the ratio electro-hydraulic control valve 5 that conduit 13 will be associated with fuel injection system is connected to low pressure rail 34 altogether.Conduit 11 is connected to low pressure rail 34 altogether by the outlet end of the ratio electro-hydraulic control valve 5 that control valve unit 20 will be associated with the outlet valve drive system.Control valve unit 20 comprises flow controller, non-time (non-return) function, and keeps the pressure minimum in the conduit 11.
Ratio electro-hydraulic control valve 5 is connected to the fuel injection system 30 that has its pressurized machine and sparger 37, and ratio electro-hydraulic control valve 5 is also connected to exhaust valve actuators.Fuel injection system is well-known, has just no longer done more detailed description here.
Hydraulic diagram shows the pressure piping 10 that is connected to the exhaust valve actuators shell 12 that has piston 18, pneumatic spring and outlet valve main shaft 14.Source of compressed air 19 also is connected to outlet valve shell 12, is used to pneumatic spring supply pressurized air, and pneumatic spring promotes outlet valve on the direction of closing.In addition, determine that the position transducer of exhaust valve positions is related with exhaust valve actuators.
In the process of power operation, ratio electro-hydraulic control valve 5 under the electronic control unit order of motor in engine cycles reasonable time outlet valve drive system or fuel injection system are connected to high-pressure common rail.Therefore, when to when opening outlet valve, the electronic control unit of motor will order ratio electro-hydraulic control valve 5 to connect between high-pressure common rail 32 and pressure piping 10.So outlet valve will head on pressure in the firing chamber and the power of pneumatic spring is opened.When to when closing outlet valve once more, electronic control unit will order ratio electro-hydraulic control valve 5 by control valve unit 20 pressure piping 10 to be connected to low pressure rail 34 altogether.Outlet valve and the exhaust valve actuators that is associated with it have sizable inertia, if pressure piping 10 is directly connected to fuel tank when ratio electro-hydraulic control valve 5 connects, then closing of outlet valve descends slowly the pressure in the specific pressure pipeline 10 many.Control valve unit 20 comprises flow controller, and it guarantees that pressure decline can be not too fast, and control valve unit 20 is incited somebody to action at its upstream, and side keeps pressure minimum.Thus, it is too fast and slow excessively to have avoided in the pressure piping 10 pressure to descend.This will be avoided the formation of air pocket in the pressure piping 10 and cavitation pitting subsequently.
Fig. 3 shows control valve unit 20 in greater detail.In this exemplary embodiment, control valve unit comprises the shell with penetration hole.The end that control valve unit 20 is included in penetration hole is arranged in or the fixed restriction device 21 of the entry end of proximate valves device 20.The entry end of control valve unit 20 can be connected to ratio electro-hydraulic control valve 5 by hole 11.
Have substantially and be contained in the penetration hole slidably for cylindrical removable valve member 22.Removable valve member 22 is provided with a pressure side at each end.First pressure side is arranged in the side of removable valve member 22 in the face of entry end and flow controller 21.First pressure chamber 23 is formed in the hole between the flow controller 21 and first pressure side.
Second pressure side is arranged in the opposite side of removable valve member 22.Second pressure side is in the face of being arranged in second pressure chamber 25 in the penetration hole equally.Second pressure chamber is connected to a low relatively pressure source, and for example low pressure is total to rail 34.
Form the diameter of the diameter of the penetration hole in the part of first pressure chamber greater than the penetration hole in the part that forms second pressure chamber.Therefore, the effective drying surface of first pressure side is greater than the effective drying surface of second pressure side.Removable valve member 22 is provided with the hole 26 that connects first and second pressure chambers.The diameter in hole 26 is relatively little, thereby controls flowing between two pressure chambers.
With reference to control valve unit among the figure 3 towards, when removable valve member 22 is in its lower position range, removable valve member 22 is closed the connection between first pressure chamber 23 and the outlet end 27, when removable valve member 22 was in its higher position range, removable valve member 22 was opened the connection between first pressure chamber 23 and the outlet end 27.
The first bigger effective pressure area promotes removable valve member 22 to the position range that outlet end 27 is connected to first pressure chamber 23, and the position range of the less connection closed of the second effective pressure area between first pressure chamber 23 and outlet end 27 promotes removable valve member 22.
When not entering first pressure chamber mobile by flow controller 21, the coefficient that the pressure in the chamber, back is lower than the pressure in second pressure chamber equals the ratio between the effective pressure face size.Therefore, when the pressure in second pressure chamber for example was 2.2 crust, the pressure in first pressure chamber can be 1.5 crust.When ratio electro-hydraulic control valve 5 is connected to pressure piping 10 control valve unit 20, to become enough high by the pressure in the flow controller 21 and first pressure chamber and promote removable valve member 22 having a large amount of streams, and make hydraulic fluid can be dispersed into fuel tank between first pressure chamber 21 and outlet end 27, to connect the position of setting up.The position of removable valve member 22 will the pressure in the pressure chamber between balance.
The position of valve 22 is decided by following power.Pressure in the first effective pressure area of first pressure chamber 23 * first pressure chamber 23 contrasts the pressure in long-pending * the second pressure chamber 25 of second effective valve face of second pressure chamber 25.In the time of exhaust valve closure, the pressure in second pressure chamber 25 is about 2 crust.Equilibrium of forces pressure in first pressure chamber 23 can be 1.5 crust.Pressure difference between first pressure chamber 23 and second pressure chamber 25 will cause fluid to pass through in 26 inflows, first pressure chamber 23, hole.
Pressure increase in first Room 23 will move up valve member 22 and opening that outlet end 27 is increased once more with pressure limit in the value that is equilibrated at the power of effect on the removable valve member 22.
Therefore, the stream by hole 26 will be with 23 identical to the stream of outlet end 27 from the chamber.Opening area from first pressure chamber 23 to outlet end 27 will be the stream of dP (pressure difference) by hole 26 that is in first pressure chamber 23 and second pressure chamber 25.Removable valve member 22 will be therefore " floating " and adjust its position to operating conditions.
This balance that combines with flow controller 21 will provide the overvoltage (being that the event exhaust valve drive system is used control valve unit, then in pressure piping) of suitable flow velocity and maintaining valve device upstream.These effects are guaranteed that flow velocity is controlled and are not had air to enter.
The outlet valve drive system has been described with reference to the large two-stroke diesel engine of single cylinder.In multicylinder engine, be necessary for each cylinder (or being at least each outlet valve) such outlet valve drive system is provided, except the common rail that can use by a plurality of cylinders.
Instruction of the present disclosure has many advantages.Different embodiments or mode of execution can produce one or more following advantages.It should be noted that this is not detailed tabulation, and also can have other advantage of not describing here.An advantage of disclosure instruction is that it provides control valve unit, and it allows to reflux to fuel tank under controlled condition, thereby has avoided the generation of air pocket and cavitation pitting.
Another advantage of the present disclosure is that it provides control valve unit, and it can play the function of safety check in the rugged environment that can not use the conventional check valves that combines operation with the valve member that closes on base.
Although the application's instruction is described in detail for illustrative purposes, should be appreciated that this details only is used for this purpose, and those skilled in the art can make distortion therein under the situation of the scope that does not break away from the application's instruction.
The term that uses in the claim " comprises (comprising) " and does not get rid of miscellaneous part or step.The term that uses in the claim " one (a) " or " one (an) " do not get rid of a plurality of.The function of some kinds of means enumerating in the claim can be realized in uniprocessor or other unit.
Claims (4)
1. control valve unit comprises:
Shell,
Entry end,
Fixed restriction device (21) in described entry end place or its downstream,
Be contained in the hole of described shell, have a floating valve member (22) of two relative effective pressure faces,
First pressure chamber (23) in the described effective pressure face in the face of being communicated with described flow controller fluid,
Second pressure chamber (25) of in the described effective pressure face another in the face of being connected with the source of relatively low pressure,
Outlet end (27), it is closed and opens at another position range of removable valve member (22) at a position range of described removable valve member by described removable valve member (22), thereby described first pressure chamber (23) is connected to described outlet end (27)
Described position range that is connected with outlet end (27) to described first pressure chamber (23) in the described effective pressure face promotes described removable valve member (22), and another in the described effective pressure face promotes described removable valve member (22) to the position range that described first pressure chamber (23) is not connected with outlet end (27), and the hole (26) of running through described removable valve member (22), it is connected to described second pressure chamber (25) with described first pressure chamber (23).
2. control valve unit according to claim 1, wherein, the described hole (26) of running through described removable valve member (22) is provided with side opening (28), when described removable valve member (22) carries out in described removable valve member (22) is connected to described first pressure chamber (23) position range of described outlet end (25) when significantly mobile, described side opening (28) is connected to flow-off (29) with described second pressure chamber (25).
3. control valve unit according to claim 1, wherein, in the effective pressure face described one greater than the effective pressure face described another.
4. control valve unit according to claim 1, wherein, described removable valve member (22) limits the control edge and described removable valve member (22) is contained in the edge in hole wherein.
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 true CN102162384A (en) | 2011-08-24 |
| CN102162384B 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 (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5423332U (en) * | 1977-07-19 | 1979-02-15 | ||
| US4271796A (en) * | 1979-06-11 | 1981-06-09 | The Jacobs Manufacturing Company | Pressure relief system for engine brake |
| 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 |
| 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 |
| WO2009065761A1 (en) * | 2007-11-23 | 2009-05-28 | Robert Bosch Gmbh | Safety valve and high-pressure pump comprising said safety valve |
| WO2009155915A1 (en) * | 2008-06-25 | 2009-12-30 | Man Diesel Filial Af Man Diesel Se, Tyskland | Hydraulic supply system of a large two-stroke diesel engine |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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 |
| CN100554652C (en) * | 2005-02-02 | 2009-10-28 | 曼狄赛尔公司 | Crosshead type large two-stroke diesel engine and control valve thereof and purposes |
| 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 |
-
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 (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5423332U (en) * | 1977-07-19 | 1979-02-15 | ||
| US4271796A (en) * | 1979-06-11 | 1981-06-09 | The Jacobs Manufacturing Company | Pressure relief system for engine brake |
| 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 |
| 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 |
| WO2009065761A1 (en) * | 2007-11-23 | 2009-05-28 | Robert Bosch Gmbh | Safety valve and high-pressure pump comprising said safety valve |
| WO2009155915A1 (en) * | 2008-06-25 | 2009-12-30 | Man Diesel Filial Af Man Diesel Se, Tyskland | Hydraulic supply system of a large two-stroke diesel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20110097673A (en) | 2011-08-31 |
| DK177283B1 (en) | 2012-10-08 |
| DK201000153A (en) | 2011-08-25 |
| JP2011174462A (en) | 2011-09-08 |
| KR101242611B1 (en) | 2013-03-19 |
| JP5372036B2 (en) | 2013-12-18 |
| CN102162384B (en) | 2017-04-12 |
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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 |
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