CN107762655B - The cylinder lubrication equipment of large-sized two-stroke compression-ignition engine - Google Patents
The cylinder lubrication equipment of large-sized two-stroke compression-ignition engine Download PDFInfo
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- CN107762655B CN107762655B CN201710700883.0A CN201710700883A CN107762655B CN 107762655 B CN107762655 B CN 107762655B CN 201710700883 A CN201710700883 A CN 201710700883A CN 107762655 B CN107762655 B CN 107762655B
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- cylinder
- end gear
- cylinder lubrication
- lubrication equipment
- stroke
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/20—Other cylinders characterised by constructional features providing for lubrication
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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
- F01M1/02—Pressure lubrication using lubricating pumps
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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
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
-
- 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
- F01M3/00—Lubrication specially adapted for engines with crankcase compression of fuel-air mixture or for other engines in which lubricant is contained in fuel, combustion air, or fuel-air mixture
-
- 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
- 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
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/023—Piston pumps
-
- 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
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
A kind of cylinder lubrication equipment (55), for being supplied cylinder lubrication liquid by multiple fuel injectors (24) to the inner surface (25) of the cylinder jacket (1) of large-sized two-stroke one-way flow compression-ignition engine, multiple fuel injectors (24) are distributed in the circumference of cylinder jacket (1).Cylinder jacket (1) defines a cylindrical inside, and the piston (10) of reciprocating motion is slidably disposed on cylindrical inside.The cylinder lubrication equipment includes: multiple piston pumps, each piston pump, which has, to be slidably disposed on the oil flushing plunger (70) in oil gas cylinder (71), it include each pump chamber (72) with oil gas cylinder (71), pump chamber (72) is fluidly connected with pump discharge (62) for fluidly connecting with one in multiple fuel injectors (24)；Common actuator (80), for driving all oil flushing plungers (70) simultaneously；Linear drive (83) is operatively coupled on common actuator (80)；And the device for any one of at least two scheduled discrete length (L1, L2) of stroke during operating the length adjustment of the stroke of actuator common during cylinder lubrication equipment (55) operating to cylinder lubrication equipment (55).
Description
Technical field
This disclosure relates to a kind of cylinder lubrication equipment of large-sized two-stroke one-way flow compression-ignition engine, especially relate to
And a kind of equipment of the inner surface supply cylinder lubricating fluid of the cylinder jacket to large-sized two-stroke one-way flow compression-ignition engine.
Background technique
Large-sized two-stroke one-way flow turbocharging compression ignition cross-head type internal combustion engine is often used as pushing away for large vessel
Into system or the prime mover being used as in power station.Huge size, weight and power output makes they and common burning
Machine differs widely, and it is unique for also allowing large-sized two-stroke turbocharging compression-ignition engine.
For traditionally, large-sized two-stroke compression-ignition engine is operated with liquid fuel, for example, liquid fuel is
Fuel oil, or especially heavy oil, this low cost due to latter fuel.Heavy oil will be to engine nocuousness
A large amount of particles introduce cylinder, for example, will form the sulphur of sulfuric acid in combustion process.This generates the inner surfaces of protection cylinder jacket
From the necessity that sulfuric acid corrodes, sulfuric acid is to compensate for acid (high pH) combustion gas composition and moistens the cylinder with low ph value
Synovia is applied to the inner surface of cylinder jacket and generates, and cylinder lubrication liquid is usually oil.Cylinder lubrication liquid (oil) is relatively expensive, and
And the cylinder lubricating oil for being applied to the inner surface of cylinder jacket is consumed during engine operating, in other words, is transported in engine
The cylinder lubrication liquid of continuously fresh supply is needed between refunding.The consumption of cylinder lubrication liquid is low in the large size with crosshead
It is a critically important factor in the operating of speed operation two-stroke one-way flow compression-ignition engine.Therefore, it is necessary to cylinder jacket
Inner surface carry out efficiently and accurate lubrication, it is ensured that the minimal consumption of suitable protecting and expensive cylinder lubricating oil to the latter.
According to engine loading, engine condition and fuel characteristic, the cylinder lubrication liquid of doses is sprayed.Further
Ground needs to be applied to the inner surface of cylinder jacket during the adjustment of new cylinder jacket approximately twice as the lubricating fluid of quantity.
The general timed injection of cylinder lubricating oil, so that the revolution relative to engine, injection is regular.It is rushed in compression
During journey, the injection of lubricating fluid occurs prior to or just when engine piston passes through oil spout fibre pipe (fuel injector).Fuel injector is uniform
It is distributed in the circumference of cylinder jacket.
A kind of equipment for supply cylinder lubricating fluid has multiple oil flushing plungers, passes through that Linear actuator driving is common to drive
Moving part moves these oil flushing plungers.When Linear actuator activation, oil flushing plunger does full stroke, and each oil flushing plunger pumps
The cylinder lubricating oil of fixed predetermined amount is into cylinder jacket in corresponding fuel injector out.Usually, these oil flushing plungers are connected
The common actuator being connected on Linear actuator does the reversal of stroke under the action of helical spring or other bias units.At this
In kind cylinder lubrication equipment, oil flushing plunger can only do full stroke, and can be started between cylinder lubrication oil injection event by changing
The number of machine revolution, the adjusting of Lai Shixian feed rate, the feed rate are the interior tables that cylinder lubrication liquid is fed into cylinder jacket
The rate in face.Highest feed rate is obtained by activating the Linear actuator for each engine revolution.
When merging new cylinder jacket, feed rate needs to increase about one times.Therefore, cylinder lubrication equipment will be capable of handling
Feed rate within the scope of from low feed rate to double high feed rate, the low feed rate are in the gas merged
Under the low engine loading of cylinder sleeve, which is under the maximum engine load in new cylinder jacket.
Lower feed rate is obtained by skipping the injection events of one or more engine revolutions.Especially, it is
Lower engine loading might have relatively high quantity there is no the place of cylinder lubrication liquid injection events
Dry engine revolution.However, in the ideal case, due to experience have shown that the drying between the injection of these cylinder lubrication liquid is sent out
Motivation revolution is unfavorable for the protection to the inner surface of cylinder jacket, and injection events should occur for each engine revolution.
Another kind is equipped with Linear actuator for the equipment of supply cylinder lubricating fluid, which, which can do to have, appoints
The pratial stroke of what expectation and length-controllable.In this cylinder lubrication equipment, each engine revolution would generally spray
Event is penetrated, the oil mass conveyed is the length of stroke by linear adjustment driver and the length of stroke for adjusting oil flushing plunger
It is precisely adjusted the current demand of engine.This equipment for supply cylinder lubricating fluid has the ability to provide starts all
The rate of cylinder lubrication liquid institute exact requirements under machine operating condition.However, this equipment for supply cylinder lubricating fluid with
The above-described cylinder lubrication equipment with regular length pumping stroke is compared to more expensive.
International application WO2008009291 discloses a kind of for quantitatively matching the hydrodynamic lubrication equipment of cylinder lubricating oil.This is matched
Oil system includes: fuel feeding line and oil drive back thread, is connect each by one or more valves with lubricating utensil, hydraulic for supplying
Oil；Central hydraulic oil oil-feed pump, connect with multiple hydraulic cylinders, and each hydraulic cylinder has hydraulic piston and may be passed through
The pressure of the hydraulic oil of fuel feeding line；Several oil spout elements, the multiple of the number of cylinders corresponding to engine, each oil spout element are each
It is connect from the fuel feeding line with oil gas cylinder and cylinder lubricating oil having with oil piston with them.In order to provide one kind reliably, just
The not no system of disruption risk preferably and hydraulic cylinder failure, design has oil-distributing plate in lubricating utensil, and the one of the oil-distributing plate
Side is in contact with oil piston, and the another side of the oil-distributing plate is in contact with two or more hydraulic pistons, and hydraulic piston is used for
Mobile oil-distributing plate is used to activate with oil piston.
Therefore, the purpose of the present invention is to provide a kind of equipment of supply cylinder lubricating fluid, the equipment was not only cheap but also capable
Feed rate is adjusted with the demand reduction of the engine revolution event to no cylinder injection event.
Summary of the invention
The object of the present invention is to provide a kind of cylinder lubrication equipment for overcoming or at least mitigating problem indicated above.
Above-mentioned and other purposes are realized by independent claims.Further embodiment can be wanted from appurtenance
It asks, be apparent from the description and the appended drawings.
According in a first aspect, a kind of cylinder lubrication equipment is provided, for supplying cylinder lubrication liquid by multiple fuel injectors
To the inner surface of the cylinder jacket to large-sized two-stroke one-way flow compression-ignition engine, multiple fuel injectors are distributed in the circle of cylinder jacket
Around, cylinder jacket defines a cylindrical inside, and the piston of reciprocating motion is slidably disposed on cylindrical inside, cylinder lubrication equipment
It include: multiple piston pumps, each piston pump has an oil flushing plunger, and oil flushing plunger is slidably disposed on in oil gas cylinder, each
It include pump chamber with oil gas cylinder, pump chamber is fluidly connected with pump discharge for fluidly connecting with one in multiple fuel injectors；It is common to drive
Moving part, for driving all oil flushing plungers simultaneously；Linear drive is operatively coupled on common actuator；And it uses
In by the length adjustment of the stroke of actuator common during cylinder lubrication equipment operation to stroke during cylinder lubrication equipment operation
Any one of at least two scheduled discrete length device；First solid mechanical end gear, it is determined that described common
First extended position of actuator；Piston is driven, is slidably disposed in hydraulic cylinder, drive chamber is located at driving piston and liquid
Between air cylinder；First port is arranged in the longitudinal end of hydraulic cylinder or is arranged close to the longitudinal end of hydraulic cylinder；The
Two-port netwerk, is arranged in the position along hydraulic cylinder length direction with the longitudinal end of hydraulic cylinder a distance away, and second
Port is connect with the first hydraulic valve.
By providing the cylinder lubrication equipment having for adjusting the device of the length of the stroke of common actuator, so that making
With relative ease and cheap equipment is possibly realized to convey the cylinder lubrication liquid of controlled variable.By along cylinder length direction
Second port is provided on the position of the longitudinal end of cylinder at first port a distance away, is had by control
The opening of the second port of valve, it is hydraulic by opening first that the maximum stroke of common actuator can be limited in driving piston
Valve and position by second port, first port are located in the cylinder.
According to the first possible embodiment of first aspect, which further includes the second solid mechanical end
Gear, the second solid mechanical end gear have determined the indentation position of common actuator.
According to second of possible embodiment of first aspect, wherein linear drive is single-acting formula hydraulic line
Property driver, common actuator elastic biasing to indentation position.
According to the third possible embodiment of first aspect, linear drive is that double-acting type hydraulic linear drives
Dynamic device.
According to the 4th of first aspect the kind of possible embodiment, piston is driven to be equipped with pipeline, pipeline is to drive chamber and drive
The cylindrical outer surface of piston is open.
According to the 5th of first aspect the kind of possible embodiment, the first hydraulic valve is electronic control valve, the first electronics control
Valve processed is preferably configured to be connected to hydraulic power source or fuel tank, preferably responds to control signal.
According to the 6th of first aspect the kind of possible embodiment, first port is selectively connected to pressure source or oil
Case.
According to the 7th of first aspect the kind of possible embodiment, which further includes the second hydraulic valve, is used for
First port is selectively connected to pressure source or fuel tank.
According to the 8th of first aspect the kind of possible embodiment, the second hydraulic valve is electronic control valve, is configured as ringing
First port should be connected to pressure source or fuel tank in control signal.
According to the 9th of first aspect the kind of possible embodiment, the distance between the end of cylinder and second port are less than
The distance between second solid mechanical end gear and the first solid mechanical end gear.
According to the tenth of first aspect the kind of possible embodiment, when the first hydraulic valve is opened, selecting has common drive
One shorter pump stroke in the discrete length of stroke of at least two of moving part；When the first hydraulic valve is closed, selection has
Longer one pump stroke at least two discrete lengths of stroke of common actuator.
According to a kind of the tenth possible embodiment of first aspect, which further comprises controller, controller quilt
It is configured to issue control signal after responding instruction from operator or response engine running parameter to first hydraulic
Valve is to be connected to hydraulic power source or fuel tank.
According to second aspect, a kind of cylinder lubrication equipment is provided, for supplying cylinder lubrication liquid by multiple fuel injectors
To the inner surface of the cylinder jacket to large-sized two-stroke one-way flow compression-ignition engine, multiple fuel injectors are distributed in the circle of cylinder jacket
Around, cylinder jacket defines a cylindrical inside, and the piston of reciprocating motion is slidably disposed on cylindrical inside, cylinder lubrication equipment
It include: multiple piston pumps, each piston pump has an oil flushing plunger, and oil flushing plunger is slidably disposed on in oil gas cylinder, each
It include pump chamber with oil gas cylinder, pump chamber is fluidly connected with pump discharge for fluidly connecting with one in multiple fuel injectors；It is common to drive
Moving part, for driving all oil flushing plungers simultaneously；Linear drive is operatively coupled on common actuator；And it uses
In by the length adjustment of the stroke of actuator common during cylinder lubrication equipment operation to stroke during cylinder lubrication equipment operation
Any one of at least two scheduled discrete length device；Moveable machinery end gear, moveable machinery end
Gear has at least two positions, and in first position, moveable machinery end gear is common actuator the first of common actuator
Extended position forms end gear, and in the second position, moveable machinery end gear be common actuator with common actuator
Second extended position of the different common actuator of the first extended position forms end gear.
According to the first possible embodiment of second aspect, which further comprises the second solid mechanical end gear,
Second solid mechanical end gear has determined the indentation position of common actuator.
According to second of possible embodiment of second aspect, moveable machinery end gear is operably coupled to end gear
Driver, end gear driver are configured as moving moveable mechanical end gear between the first position and the second position.
According to the third possible embodiment of second aspect, end gear driver receives control signal and end gear driver
It is configured as that mechanical end gear is moved to the second position from first position upon receiving the control signal, or end is kept off from second
It sets and is moved to first position.
According to the 4th of second aspect the kind of possible embodiment, moveable machinery end gear includes being slidably disposed on
Bar in hole, moveable end gear are configured as bar being fastened on first position or the second position.
According to the 5th of second aspect the kind of possible embodiment, the second longitudinal direction end of bar forms end and keeps off butting surface, uses
It is docked in the common actuator butting surface with common actuator.
According to the 6th of second aspect the kind of possible embodiment, bar is fastened to first by third solid mechanical end gear
Position, and the second position is fastened to by moveable bolt.
According to the 7th of second aspect the kind of possible embodiment, bolt is slidably disposed in path of navigation, bolt
It is operably coupled to end gear driver, end gear driver is configured as moving bolt between the retracted position and the extended position,
Bolt is not stretched out from path of navigation on indentation position, and bolt is stretched out from path of navigation on extended position.
According to the 8th of second aspect the kind of possible embodiment, when bolt is on its extended position, bolt setting exists
Between third solid mechanical end gear and bar.
According to the 9th of second aspect the kind of possible embodiment, path of navigation is arranged to the axis essentially through bar.
According to the tenth of second aspect the kind of possible embodiment, bolt is equipped with oblique top.
According to a kind of the tenth possible embodiment of second aspect, the bar second longitudinal direction end opposite with first longitudinal direction end is set
There is rake.
According to the 12nd of second aspect the kind of possible embodiment, bar elastic biasing to its first position.
According to the 13rd of second aspect the kind of possible embodiment, end gear driver is Linear actuator, preferably
Single-acting formula Linear actuator, but bolt elastic biasing is to its indentation position.
According to the 14th of second aspect the kind of possible embodiment, end gear driver is linear air impeller, linear
Hydraulic unit driver or linear electrical driver.
According to the 15th of second aspect the kind of possible embodiment, the second solid mechanical end gear and moveable end gear
Between common actuator maximum stroke, when movably end gear in first position when be greater than ought movably hold gear
When the second position.
The aspect of these and other of the invention will be apparent from embodiment from the description below.
Detailed description of the invention
In the following detail section of present disclosure, will with reference to exemplary embodiment shown in the drawings to the present invention into
Row is explained in more detail, in which:
Fig. 1 is the high visual angle front view according to the large-sized two-stroke diesel engine of an exemplary embodiment；
Fig. 2 is the high visual angle side view of the medium-and-large-sized two-stroke diesel engine of Fig. 1；
Fig. 3 is the graph-based according to the large-sized two-stroke engine of Fig. 1；
Fig. 4 is the longitudinal sectional drawing by Fig. 1 cylinder jacket of engine and cylinder frame into Fig. 3；
Fig. 5 is the side view of cylinder jacket in Fig. 4；
Fig. 6 is the cross-sectional view of cylinder jacket in Fig. 4；
Fig. 7 is to be used to provide the high multi-angled view of the equipment of cylinder lubrication liquid according to an exemplary embodiment；
Fig. 8 is the top view of equipment in Fig. 7；
Fig. 9 is the longitudinal sectional drawing of equipment in Fig. 7；
Figure 10 is another longitudinal sectional drawing of equipment in Fig. 7；
Figure 11 is the amplification detail view of the middle section Fig. 9；
Figure 12 is a kind of for providing the longitudinal sectional drawing of another exemplary embodiment of the equipment of cylinder lubrication liquid；
Figure 13 is another longitudinal sectional drawing of equipment in Figure 12；
Figure 14 is the high multi-angled view of amplification of the bolt of equipment in Figure 12；
Figure 15 is the graph-based of equipment in Figure 12；And
Figure 16 is a kind of for providing the graph-based of another exemplary embodiment of the equipment of cylinder lubrication liquid.
Specific embodiment
It, will be with reference to cylinder lubrication equipment in the exemplary embodiment and with the big of crosshead in following detailed description
Type two-stroke low speed turbocharging compression-ignition engine is a kind of for cylinder lubrication liquid to be provided to the gas of internal combustion engine to describe
The equipment of the inner surface of cylinder sleeve.
Fig. 1, Fig. 2 and Fig. 3 show a kind of large-sized low-speed turbocharging two-stroke diesel with crankshaft 8 and crosshead 9
Engine.Fig. 3 shows a kind of large-sized low-speed turbocharging two-stroke diesel engine with its intake and exhaust system
Graph-based.In the exemplified embodiment, there are six cylinders in line for engine tool.Large-sized low-speed turbocharging two-stroke
Diesel engine usually has there are four to the cylinder in line between 14, passes through cylinder frame 23 and supports, the cylinder frame 23
It is supported by engine frame 11.For example, engine is used as the sustainer of ship or is used as being used in power station
Operate the stationary engine of generator.For example, total output of the engine can be at 1000 kilowatts to 110000 kilowatts
In range.
In the exemplified embodiment, which is a kind of compression ignition engine of two-stroke single to streaming, tool
There is the central discharge air valve 4 in the scavenging port 18 of 1 lower area of cylinder jacket and at 1 top of cylinder jacket.Scavenging is from scavenging receiver 2
Lead to the scavenging port 18 of each cylinder 1.Piston 10 in cylinder jacket 1 compresses scavenging, passes through the fuel valve 50 on cylinder clothing 22
Fuel is sprayed, and then burns and generates exhaust gas.
When exhaust valve 4 is opened, exhaust gas passes through the exhaust duct inflow exhaust gas receiver 3 that connect with cylinder 1 and passes through first
Exhaust pipe 19 flows to forward in the turbine 6 of turbocharger 5, and exhaust gas passes through second exhaust pipe by gasoline economizer 20 from turbine 6
Outlet 21 is flowed out to, atmosphere is discharged into.By axis, turbine 6 drives compressor 7, supplies fresh air by air intlet 12.Compression
The conveying of machine 7 is pressurized scavenging to the scavenging air pipe 13 for leading to scavenging receiver 2.Scavenging in scavenging air pipe 13 passes through intercooler 14,
For cooling down scavenging.
When the compressor 7 of turbocharger 5 does not convey enough pressure to scavenging receiver 2, in other words, in hair
When the low or partial load conditions of motivation, cooling scavenging passes through by the auxiliary blower 16 driven by motor 17, is
The pressurization of scavenging stream.Under higher engine loading, the compressor 7 of turbocharger conveys enough compression scavengings, then borrows
Help check-valves 15 around auxiliary blower 16.
Fig. 4, Fig. 5 and Fig. 6 show single cylinder jacket 1 respectively with longitudinal sectional drawing, side view and top view.Cylinder clothing
22 are clamped at the upper longitudinal end of cylinder jacket 1 by the cylinder clothing stud 43 fastened by hydraulic fixing nut 44.Cylinder
The lower end of outer cover stud 43 is anchored on cylinder frame 23.Cylinder clothing 22 is equipped with the central opening for exhaust valve
46.In cylinder jacket 1 close to its relatively under longitudinal direction be equipped with row's scavenging port 18.Cylinder frame is resisted against by the shoulder of cylinder jacket 1
On the upper surface of frame 23, cylinder jacket 1 is supported by cylinder frame 23.
Other than containing the relatively small recess of nozzle of the fuel injector 24 for injection cylinder lubricating fluid, cylinder jacket
It is smooth for 1 inner surface 25 is universal.Fuel injector 24 by be essentially equal height and it is equally distributed in a manner of be arranged in gas
The circumference of cylinder sleeve 1.
Fuel injector 24 is inserted into the casing wall of cylinder jacket 1 and extends into cylinder jacket 1 from the outside of cylinder jacket 1, fuel injector 24
Nozzle on tip is housed in the dolly dimple on inner surface 25 above-mentioned.Fuel injector 24 is used to injection cylinder lubricating fluid to gas
On the inner surface 25 of cylinder sleeve 1.The cylinder lubrication liquid for being ensured to be sprayed using various technologies is finally sprayed on inner surface 25.It is pressing
Piston 10 reaches before being disposed with the height of fuel injector 24 during contracting stroke, and some technologies are directly from nozzle bore by the gas of injection
Cylinder lubricating fluid is sprayed on inner surface 25.Just piston 10 is located at the height of fuel injector 24 to another technology during compression stroke
Injection cylinder lubricating fluid at the time of upper, so that cylinder lubrication liquid is ejected between the piston ring of piston 10.Any one ensures
The technology that cylinder lubrication liquid reaches the inner surface of cylinder jacket 25 can be used in conjunction with the invention.
Fuel injector 24 is connected to a kind of equipment 55 for supply cylinder lubricating fluid by respective supply pipe 41.
Fig. 7, Fig. 8, Fig. 9, Figure 10 and Figure 11 are shown respectively with high visual angle figure, top view, longitudinal sectional drawing and amplification
It is a kind of for providing the equipment of cylinder lubrication liquid to inner surface 25 in first exemplary embodiment.Cylinder lubrication equipment 55 includes
Shell 60, in the present embodiment, shell 60 are assembled by multiple components, but can also be formed by single component.
Cylinder lubrication equipment 55 includes pump, which includes corresponding with multiple in oil gas cylinder 72 by being slidably disposed on
Oil flushing plunger 70 is formed by multiple positive-displacement pumps.Cylinder lubrication equipment 55 also includes Linear actuator, the Linear actuator
It is configured as during pumping stroke and aspiration stroke while moving all oil flushing plungers 70.The Linear actuator drives by common
Moving part 80 may be operatively connected to all oil flushing plungers 70.
Linear actuator is linear hydraulic drive 83 in the illustrated embodiment, including driving piston 82, is contained in and sets
Set the matching cylinder in shell 60.Piston 82 is driven to define drive chamber 81 together with matching cylinder in shell 60.However, can
With understanding, hydraulic unit driver 83 can also be the component being kept completely separate with the shell of their own.
Driving piston 82 may be operatively connected to common actuator 80.In the present embodiment, driving piston and common drive
Moving part 80 is single global facility.It is understood, however, that it is only necessary to can grasp for common actuator 80 and driving piston 82
Therefore isolated component can be become by being joined together with making.
Helical spring 75 is arranged in spring housing 73.Helical spring 75 is used to be resiliently biased to match by common actuator 80
In other words aspiration stroke is done in the position that oil piston 70 is fully retracted.Common 80 part of actuator is arranged in spring housing.
In the present embodiment, Linear actuator is single-acting formula linear hydraulic drive 83, is configured as driving by common
Moving part 80 starts the pumping stroke for oil flushing plunger 70, and at the same time, reply (suction) stroke of oil flushing plunger 70 is by spiral
Wire spring 75 starts.Spiral wire spring 75 can be suitably used for the common actuator 80 of elastic biasing to oil column by any other
The elastic device of the indentation position of plug 70 replaces.Alternatively, Linear actuator can be double acting linear driver, start simultaneously
The pumping stroke and aspiration stroke of oil flushing plunger 70.
Pump chamber is formed in each in oil gas cylinder 70.Each pump chamber is connected to cylinder lubrication inlet chamber by check-valves 62
65.Cylinder lubrication liquid in the room 65, which by cylinder lubrication enters port 61 and is connected to the source of cylinder lubrication liquid, (not to be shown
Out).When oil flushing plunger 70 is retracted simultaneously during aspiration stroke, pump chamber enters port 61 by cylinder lubrication liquid, cylinder moistens
Synovia inlet chamber 65 and respective check-valves 62 fill up cylinder lubrication liquid from the source of cylinder lubrication liquid again.Each pump chamber by
Access 77 is connected to outlet port 62.When oil flushing plunger 70 is extended to longest to when matching in oil gas cylinder, the volume of pump chamber is most
Small, when oil flushing plunger 70 in oil gas cylinder from being retracted to most in short-term, the volume of pump chamber is maximum.
When oil flushing plunger 70 is moved to oil gas cylinder simultaneously during pumping stroke, cylinder lubrication liquid in pump chamber by
Respective access 77, respective outlet port 62, respective supply pipe 41 are pressed out in respective fuel injector 24 from pump chamber, are changed
Yan Zhi, each oil flushing plunger is connected to single fuel injector 24 in one embodiment.
Linear drive 83 includes driving piston 82, which is slidably disposed in matching cylinder, drives
Dynamic room 81 is located between driving piston 82 and matching cylinder.The longitudinal end or close of matching cylinder is arranged in first port 84
The longitudinal end setting of matching cylinder and second port 86 are arranged in along matching cylinder length direction and the longitudinal direction that matches cylinder
The position of end a distance away.Second port 86 is doughnut or endless groove in one embodiment.
If amplified best shown in the C of section, the longitudinal end for facing the driving piston 82 of drive chamber 81 is equipped with connection
Pipeline in drive chamber 81 to the circumferential outer surface of driving piston 82.This pipeline is by 89 shape of vertical passage in the present embodiment
It is open at, vertical passage 89 to drive chamber 81 and connects one or more radial passages 88, radial passage 88 is to driving piston 82
Cylindrical outer surface opening.
First port 84 is connected to the second hydraulic valve 59 by access 85.Second hydraulic valve 59 is selectively by first end
Mouth 84 is connected to pressure source or fuel tank.When first port 84 is connected to pressure source by the second hydraulic valve 59, drive chamber 81 is increased
Pressure, driving piston 82 to common 80 applied force of actuator and and then are used 70 applied force of oil flushing plunger on the direction of pumping stroke
In doing pumping stroke.Pumping stroke is mechanically limited by the first mechanical end gear, and the first mechanical end shelves are in this exemplary implementation
It is that the first butting surface 36 of the common actuator docked by the second butting surface 37 with shell 60 is formed in example.Therefore,
First mechanical end keeps off the maximum extension position for determining oil flushing plunger 70.
When first port 84 is connected to fuel tank by the second hydraulic valve 59, driving piston 82 does not apply common actuator 80
Any significant power, therefore helical spring 70 promotes the indentation position that oil flushing plunger 70 is returned to them and then does aspiration stroke.
Helical spring 70 moves common actuator 80 until the third butting surface in common actuator 80 on the direction of aspiration stroke
38 dock with the 4th butting surface 35 of shell 60, and then form the second of the maximum indentation position for being used for oil flushing plunger 70 and fix
Mechanical end gear.
Second port 86 is connected in fuel tank by delivery pipe 87 and the first hydraulic valve 58.When the first hydraulic valve 58 is in
Second port 86 is connected in fuel tank by it by delivery pipe 87 when on first position.When the first hydraulic valve 58 is in the pumping stroke phase
Between on the second position when once the radial passage 88 in piston 82 is driven to reach 86 first hydraulic valve 58 of second port once
Drive chamber 81 is connected to fuel tank, in other words, radial passage 82 faces second port 86, and then is depressured drive chamber 81 and terminates
Pump stroke.Therefore, second port 86 formed hydraulic end gear a part, when have been carried out length be L1 short stroke length
When, by connection drive chamber 81 to fuel tank, pumping stroke is limited in the short length of length L1.
When the first hydraulic valve 58 is connected to hydraulic pressure source during pumping stroke, it is L2's that driving piston 82, which does length,
Full stroke, in other words, pumping stroke are continued until the butting surface 36 of common actuator and the second butting surface of shell 60
37 (the first solid mechanical end gears) docking.
The length of full stroke L2 is greater than the length of short stroke L1.In the longitudinal end for the matching cylinder that first port 84 is located at
Between portion and the position of second port 86, the length L1 of short stroke is together defined with radial passage 88.It is understood that by
It is non-essential that axial passageway 89, which is formed by pipeline with radial passage 88,.However, needing without this pipeline by second
Port 86 is placed on the position for being closer to first port 84 to obtain identical short stroke length L1.
Pumping stroke is initiated by mobile second hydraulic valve 59 to its position for being connected to hydraulic pressure source, and passes through movement
Second hydraulic valve 59 to its position for being connected to fuel tank terminates pumping stroke.The length of stroke is pumped by the position of the first hydraulic valve 58
Set determination.The long pumping stroke with length L2 is obtained when the first hydraulic valve 58 is connected to hydraulic pressure source, when the first liquid
Pressure valve 58 obtains the short pumping stroke with length L1 when being connected to fuel tank.In one embodiment, the first hydraulic valve 58 is
Electronic control valve, such as solenoid valve receive control signal.In one embodiment, the second hydraulic valve 59 is electronic control valve, all
Such as solenoid valve, control signal is received.
(not shown) in another embodiment, the first control valve 58 is simple valve, can only be opened or closed, and is being beaten
Second port 86 is connected to fuel tank by open position, the valve.In this embodiment, short punching is obtained by opening the first hydraulic valve 85
Cheng Changdu L1 obtains long stroke length L2 by closing the first hydraulic valve 85.
Figure 12, Figure 13, Figure 14 and Figure 15 show another on longitudinal sectional drawing, detail view and diagrammatic view respectively and show
A kind of equipment 55 for supply cylinder lubricating fluid in example property embodiment.Cylinder lubrication equipment 55 in the embodiment of Figure 12 to Figure 15
It is largely identical, identical appended drawing reference reference with the cylinder lubrication equipment 55 in the embodiment of Fig. 7 to Figure 11
Identical feature, however there is following difference.
Linear actuator 83 had both been not arranged in second port or had been not arranged on discharge-channel.Driving piston 81 is not arranged in
Drive chamber 81 is connected on the pipeline of the cylindrical outer surface of driving piston 81, and without the first hydraulic valve.
Drive chamber 81 is selectively connected to hydraulic pressure source or fuel tank by the second hydraulic valve 59.Without the second hole 86, lead to
It crosses and drive chamber 81 is depressured, the length of the stroke of oil flushing plunger 70 will not be limited in shorter length L1.Instead
In the present example embodiment, the length L1 of short stroke is by moveable mechanical end gear limitation.Moveable machinery end gear has
At least two positions.Figure 12 shows the position of the moveable mechanical end gear for the short stroke for causing to have length L1, same with this
When Figure 13 show the long stroke that can cause that there is length L2 moveable mechanical end gear position.
What movement of the oil flushing plunger 70 on the direction of aspiration stroke was docked by the 4th butting surface 35 with shell 60
The third butting surface 38 of common actuator 80 is formed by the gear limitation of the second solid mechanical end, and then is formed and be used for oil flushing plunger
Second solid mechanical end of 70 maximum indentation position is kept off.This indentation position of common actuator 80 and oil flushing plunger 70 is being schemed
It is shown in 12 and Figure 13.
Moveable machinery end gear includes end gear driver, and end gear driver may be operatively connected to moveable machinery
End gear.
End gear driver is configured as moving moveable mechanical end gear between the first position and the second position.
End gear driver receives control signal from electronic control unit 100 and end gear driver is configured as from electronics control
It is received in unit 100 processed and mechanical end gear is moved to the second position from first position after control signal, or from the second position
It is moved to first position.The control button for holding gear driver is sent signal to just simply alternatively, using by operator
Control the position of mechanical end gear.
Moveable end gear includes bar 94, and bar 94 is slidably disposed in matched hole.Bar 94 can be driven by end gear
Dynamic device is maintained at first position or the second position.
The first longitudinal direction end of bar 94 forms the second butting surface 37, and the second butting surface 37 is used for and common actuator 80
The docking of first butting surface 36.
Bar 94 is fastened to its first position by third solid mechanical end gear, and bar 94 is fastened to it by bolt 90
The second position.
Third solid mechanical end gear is formed by embolism 93.Embolism 93 is fastened in the hole of shell 60.Embolism 93 can be
The form of screw is engaged with the threaded hole screw thread of shell 60, and adjusts embolism 93 by rotation embolism 93 in this case
Position.Embolism 93 and common actuator 80, which are arranged on the same axis and are equipped with, faces the 5th axial butting surface 28.Bar
94 are arranged the embolism 93 for facing in longitudinal end and having the 6th butting surface 29 being axially facing.When bolt 90 is located at institute in Figure 13
When the position shown, bar 94 can move always the 6th butting surface 29 and embolism 93 until bar 94 on the direction of pumping stroke
The 5th butting surface 28 docking.The first position of exactly mechanical end gear to pump stroke with longer length L2.At this
A position, bolt 90 are located on the indentation position that it does not extend between bolt 94 and embolism 93.
Bolt 90 is slidably disposed on path of navigation, and the axis of path of navigation and bar 94 is substantially arranged at right angle.Spiral shell
Bolt 93 may be operatively connected to end gear driver, be configured as moving between indentation position and extended position in figure 13 illustrates
Dynamic bolt 93, bolt 93 is not stretched out from path of navigation on indentation position, and bolt is from bar 94 and bolt 93 on extended position
Between path of navigation on stretch out, and then bar 94 is forced to be located at its second position.The second position of exactly mechanical end gear provides
Pumping stroke with shorter length L1.
In the present embodiment, bolt 93 is equipped with oblique top 97, and the second longitudinal direction end opposite with first longitudinal direction end of bar 94, which is equipped with, inclines
Inclined portion 33.By interrupting lines as shown in figure 15 when end keeps off driver, and bolt 93 is moved to extended position from indentation position,
97 engagement angled portion 33 of oblique top, so on bar 94 generation have axial component power, and then force bar 94 be located at its second
Position.In its second position, the second butting surface 37 is kept off close to the second solid mechanical end, therefore when 90 positioned at its extended position
When, pumping stroke has shorter length L1, and in extended position, it forces bar 94 to be located at its second position.
In embodiment, 94 elastic biasing of bar is to its first position.
When bolt 90 is located at its indentation position, bar is located at its first position and pumping stroke has longer length L2.
End gear driver is Linear actuator, may be operatively connected to bolt 90.End gear driving in one embodiment
Device is the single-acting formula Linear actuator with bolt 90, elastic biasing to its indentation position.In the present embodiment, end gear driving
Device is linear air impeller, but it is understood that, end gear driver is also possible to linear hydraulic drive, linear electrical is driven
Dynamic device or powered actuator.
Linear air impeller includes pneumatic cylinder 95, bolt 90 serve as piston be slidably and sealingly arranged in it is pneumatic
In cylinder 95, the longitudinal end opposite with oblique top 97 is equipped with head 91.Pneumatic cylinder 95 is connected to pneumatic operated valve by pneumatic tube 96
99.In one embodiment, pneumatic operated valve 99 is solenoid valve, is connected to electronic control unit 100.Pneumatic operated valve 99 is configured as gas
Dynamic pipe 96 is connected to pneumatic pressure source or atmosphere.
When electronic control unit 100 issues shorter stroke of the signal behavior with the oil flushing plunger 70 of length L2, gas
Pneumatic tube is connected to pneumatic pressure source by dynamic valve 99.As shown in figure 12, the resulting pressure acted on bolt head 91 will
Bolt 90 is oppressed in its extended position, and then bar 94 is forced to be located at its second position.When electronic control unit 100 issues signal choosing
When selecting the longer stroke of the oil flushing plunger 70 with length L1, pneumatic tube 96 is connected to atmosphere by pneumatic operated valve 99.Such as Figure 13 institute
To show, insufficient pressure of the resulting combination elastic bias on bolt 90 forces bolt 90 to be located at its indentation position, into
And bar 94 is allowed to be moved to its first position.
Figure 16 is in third embodiment for cylinder lubrication liquid to be provided to the equipment 55 of the inner surface 25 of cylinder jacket
Diagrammatic view.According to the equipment 55 of this embodiment, in addition to bolt 90 is substituted by hydraulic wedge and pneumatic operated valve is by third liquid
Pressure valve 99 ' is instead outer, and the equipment 55 is generally identical as the equipment 55 in the embodiment of Figure 12 to Figure 15.In this embodiment
In, a part of bar 94 serves as piston in the hole of receiving bar 94.Therefore, hydraulic pressure is formd between bar 94 and embolism 93
Room 30.Hydraulic pressure room 30 is connected to third hydraulic valve 99 ' by hydraulic tube 96 '.In one embodiment, third hydraulic valve
99 be electronic control valve, is connected to electronic control unit 100.Electronic control valve 99 ' is configured as from electronic control unit 100
Hydraulic tube 96 ' is connected to hydraulic pressure source or fuel tank after the middle respective instruction of reception.When third hydraulic valve 99 ' is by hydraulic tube
96 ' when being connected to hydraulic pressure source, and the pressure increase in hydraulic pressure room 30 simultaneously forces bar 94 to be moved to refer to by interrupting lines
Its second position out, and then select the pumping stroke with shorter length for being used for oil flushing plunger 70.When third hydraulic valve
99 ' when being connected to fuel tank for mature control unit 96 ', the insufficient pressure in hydraulic pressure room 30 allow bar 94 be moved to its
One position, and then select with the pumping stroke with longer length for being used for oil flushing plunger 70.
It can be used to pump stroke to be used to supply cylinder lubrication liquid to at least two using this with various ways
Different length cylinder jacket 1 inner surface 25 equipment 55.A kind of mode using the equipment 55 is, by using having
The length pumping stroke of length L2 has the fuel injector for each engine revolution, and work as merging new cylinder jacket 1
When being run under 100% engine loading, conveyed for normal running (operation) conditions most using the short pumping stroke with length L1
Roughing feed rate has the fuel injector for each engine revolution.When running low-load, fuel injector can skip engine
Revolution, but when compared with the equipment of the pumping stroke in the prior art with single regular length, still more frequently.
While reference has been made to embodiments above is described using the length of stroke automatic control of electronic control unit,
It is understood that the length of stroke of the pumping stroke of plunger 70 can be by manually controlling respective hydraulic valve or pneumatic operated valve
It is manually controlled, for example, passing through push button.
Term " comprising " is not precluded from other elements or steps used in claims.It is used in claims
Term " one (a) " or " one (an) " be not precluded it is multiple.Electronic control unit may be implemented to enumerate in claims several
The function of a device.Appended drawing reference used in claims is not construed as the limitation to range.Although in order to say
The present invention is described in detail in bright purpose, it is to be understood that such details be entirely for that purpose,
And those skilled in the art is modified wherein without departing from the scope of the present invention.
Claims (30)
1. a kind of cylinder lubrication equipment (55), for being supplied cylinder lubrication liquid to large-sized two-stroke by multiple fuel injectors (24)
The inner surface (25) of the cylinder jacket (1) of one-way flow compression-ignition engine, multiple fuel injectors (24) are distributed in the cylinder
The circumference of (1) is covered, the cylinder jacket (1) defines a cylindrical inside, and the piston (10) of reciprocating motion is slidably disposed on
The cylindrical inside, the cylinder lubrication equipment (55) include:
Multiple piston pumps, each piston pump have oil flushing plunger (70), and the oil flushing plunger (70) is slidably disposed on oil
It include each pump chamber (72) with oil gas cylinder (71), the pump chamber (72) fluidly connects with pump discharge (62) to be used in cylinder (71)
It is fluidly connected with one in multiple fuel injectors (24)；
Common actuator (80), for driving all oil flushing plungers (70) simultaneously；
Linear drive (83) is operatively coupled on the common actuator (80)；
For length adjustment to the cylinder lubrication of the stroke of the common actuator during cylinder lubrication equipment (55) operating to be set
The device of any one of at least two scheduled discrete length (L1, L2) of stroke during standby (55) operating；
It is characterized by:
First solid mechanical end gear, it is determined that the first extended position of the common actuator；
The linear drive includes: driving piston (82), is slidably disposed in matching cylinder, is lived in the driving
It fills in and is equipped with drive chamber (81) between (82) and the matching cylinder；The longitudinal direction of the matching cylinder is arranged in first port (84)
End is arranged close to the longitudinal end of the matching cylinder；And second port (86), it is arranged long along the matching cylinder
Spend position with the longitudinal end for matching cylinder a distance away on direction, the second port and first hydraulic
Valve (58) connection.
2. cylinder lubrication equipment (55) as described in claim 1 further includes that the second solid mechanical end is kept off, and described second
Solid mechanical end gear has determined the indentation position of the common actuator.
3. cylinder lubrication equipment (55) as claimed in claim 1 or 2, wherein the linear drive is single-acting formula liquid
Press Linear actuator, the common actuator elastic biasing to indentation position.
4. cylinder lubrication equipment (55) as described in claim 1, wherein the linear drive is that double-acting type is hydraulic
Linear actuator.
5. cylinder lubrication equipment (55) as described in claim 1, wherein the driving piston is equipped with pipeline (88,89), it is described
Pipeline is to the pump chamber (81) and the cylindrical outer surface of piston (82) is driven to be open.
6. cylinder lubrication equipment (55) as claimed in claim 5, wherein first hydraulic valve (58) is electronic control valve.
7. cylinder lubrication equipment (55) as claimed in claim 6, wherein first hydraulic valve (58) is configured to respond to
Control signal and in an open position or closed position.
8. cylinder lubrication equipment (55) as described in claim 1, wherein the first port (84) is selectively connected to press
Power source or fuel tank.
9. cylinder lubrication equipment (55) as claimed in claim 8, including the second hydraulic valve (59), being used for selectively will be described
First port (84) is connected to pressure source or fuel tank.
10. cylinder lubrication equipment (55) as claimed in claim 9, wherein second hydraulic valve (59) is electronic control valve,
It is configured to respond to control signal and the first port (84) is connected to the pressure source or fuel tank.
11. cylinder lubrication equipment (55) as claimed in claim 2, wherein the end of the cylinder and the second port (86)
Between the distance be less than second solid mechanical end gear and first solid mechanical end gear the distance between.
12. cylinder lubrication equipment (55) as claimed in claim 10, wherein when first hydraulic valve (58) is located at first
When setting, one pump impulse shorter in the described at least two discrete lengths of stroke with the common actuator (38) is selected
Journey；When first hydraulic valve is located at another position, select described at least two with the common actuator discrete
Length of stroke in longer one pump stroke.
13. cylinder lubrication equipment (55) as claimed in claim 12, further comprises controller, the controller is configured as
After responding instruction or the response engine running parameter from operator, control signal is issued to first hydraulic valve
(58) to change position.
14. a kind of cylinder lubrication equipment (55) is rushed for being supplied cylinder lubrication liquid to large size two by multiple fuel injectors (24)
The inner surface (25) of the cylinder jacket (1) of journey one-way flow compression-ignition engine, multiple fuel injectors (24) are distributed in the gas
The circumference of cylinder sleeve (1), the cylinder jacket (1) define a cylindrical inside, and the piston (10) of reciprocating motion is mounted slidably
In the cylindrical inside, the cylinder lubrication equipment (55) includes:
Multiple piston pumps, each piston pump have oil flushing plunger (70), and the oil flushing plunger (70) is slidably disposed on oil
It include each pump chamber (72) with oil gas cylinder (71), the pump chamber (72) fluidly connects with pump discharge (62) to be used in cylinder (71)
It is fluidly connected with one in multiple fuel injectors (24)；
Common actuator (80), for driving all oil flushing plungers (70) simultaneously；
Linear drive (83) is operatively coupled on the common actuator (80)；
For length adjustment to the cylinder lubrication of the stroke of the common actuator during cylinder lubrication equipment (55) operating to be set
The device of any one of at least two scheduled discrete length (L1, L2) of stroke during standby (55) operating；
It is characterized in that,
Moveable machinery end gear, the moveable mechanical end gear has at least two positions, described removable in first position
Dynamic mechanical end gear is that the common actuator (80) is kept off at the first extended position formation end of the common actuator；And
The second position, the moveable mechanical end gear is the common actuator (80) described with the common actuator (80)
Second extended position of the different common actuator of the first extended position forms end gear.
15. cylinder lubrication equipment (55) as claimed in claim 14 further comprises that the second solid mechanical end is kept off, described second
Solid mechanical end gear has determined the indentation position of the common actuator (80).
16. the cylinder lubrication equipment (55) as described in claims 14 or 15, wherein the moveable mechanical end gear can operate
Ground is connected to end gear driver, and the end gear driver is configured as moving between the first position and the second position
The moveable mechanical end gear.
17. cylinder lubrication equipment (55) as claimed in claim 16, the end gear driver receives control signal and the end
Gear driver is configured as that the mechanical end gear is moved to the second from the first position upon receiving the control signal
It sets, or the end is kept off from the second position and is moved to the first position.
18. cylinder lubrication equipment (55) as claimed in claim 14, wherein the moveable mechanical end gear includes slidably
The bar (94) in hole is arranged in ground, and the moveable end gear is configured as the bar (94) being fastened on first position or second
Position.
19. cylinder lubrication equipment (55) as claimed in claim 18, wherein the first longitudinal direction end of the bar (94) forms end gear
Butting surface (37), for being docked with the common actuator butting surface (36) of the common actuator (80).
20. the cylinder lubrication equipment (55) as described in claim 18 or 19, wherein the bar (94) passes through third solid mechanical
End gear (93) is fastened to the first position, and is fastened to the second position by moveable bolt (90).
21. cylinder lubrication equipment (55) as claimed in claim 20, wherein the bolt (90) is slidably disposed on guidance
In access, the bolt (90) is operably coupled to end gear driver, and the end gear driver is configured as in indentation position
The mobile bolt between extended position, the bolt (90) is not stretched out from the path of navigation on indentation position,
The bolt (90) is stretched out from the path of navigation on extended position.
22. cylinder lubrication equipment (55) as claimed in claim 21, wherein when the bolt (90) is on its extended position,
Bolt (90) setting is between third solid mechanical end gear (93) and the bar.
23. cylinder lubrication equipment (55) as claimed in claim 21, wherein the path of navigation is arranged through the bar
(94) axis.
24. cylinder lubrication equipment (55) as claimed in claim 20, wherein the bolt (90) is equipped with oblique top (97).
25. cylinder lubrication equipment (55) as claimed in claim 19, wherein the bar (94) is opposite with the first longitudinal direction end
Second longitudinal direction end be equipped with rake (33).
26. cylinder lubrication equipment (55) as claimed in claim 18, wherein the bar (94) elastic biasing is to its first position.
27. cylinder lubrication equipment (55) as claimed in claim 16, wherein end gear driver is Linear actuator.
28. cylinder lubrication equipment (55) as claimed in claim 27, wherein end gear driver is that single-acting formula is linearly driven
Dynamic device, but bolt (90) elastic biasing is to its indentation position.
29. cylinder lubrication equipment (55) as claimed in claim 27, wherein end gear driver be linear air impeller,
Linear hydraulic drive or linear electrical driver.
30. cylinder lubrication equipment (55) as claimed in claim 15, wherein second solid mechanical end gear and described removable
The maximum stroke of the common actuator between dynamic end gear, when the moveable end gear is when the first position
Greater than when the moveable end gear is when the second position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201670630 | 2016-08-17 | ||
| DKPA201670630A DK179118B1 (en) | 2016-08-17 | 2016-08-17 | Cylinder lubrication apparatus for a large two-stroke compression-ignited internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107762655A CN107762655A (en) | 2018-03-06 |
| CN107762655B true CN107762655B (en) | 2019-07-23 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710700883.0A Active CN107762655B (en) | 2016-08-17 | 2017-08-16 | The cylinder lubrication equipment of large-sized two-stroke compression-ignition engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6461251B2 (en) |
| KR (1) | KR101959852B1 (en) |
| CN (1) | CN107762655B (en) |
| DK (1) | DK179118B1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK179482B1 (en) * | 2017-12-13 | 2018-12-14 | Hans Jensen Lubricators A/S | A large slow-running two-stroke engine, a method of lubricating it, and an injector with a hydraulic-driven pumping system for such engine and method |
| DK179521B1 (en) * | 2017-12-13 | 2019-02-05 | Hans Jensen Lubricators A/S | A large slow-running two-stroke engine, a method of lubricating it, and an injector with a step-wise hydraulic pumping system for such engine and method |
| DK179952B1 (en) * | 2018-07-06 | 2019-10-25 | Hans Jensen Lubricators A/S | A method for upgrading a lubrication system in a large slow-running two-stroke engine |
| DK179946B1 (en) * | 2018-07-06 | 2019-10-21 | Hans Jensen Lubricators A/S | A method for optimizing lubrication in a large slow-running two-stroke engine |
| DK180054B1 (en) * | 2018-10-02 | 2020-02-11 | Hans Jensen Lubricators A/S | Substitution of a valve seat for improving a lubricator pump unit and lubrication system of a large slow-running two-stroke engine, and an improved lubricator pump unit |
| DK180164B1 (en) * | 2019-05-01 | 2020-07-06 | Man Energy Solutions Filial Af Man Energy Solutions Se Tyskland | Multi-lubricant cylinder lubrication system for a large two-stroke internal combustion engine |
| WO2021213603A1 (en) * | 2020-04-22 | 2021-10-28 | Hans Jensen Lubricators A/S | Method for lubricating large slow-running marine diesel engines |
| DK181014B1 (en) | 2021-04-21 | 2022-09-23 | Man Energy Solutions Filial Af Man Energy Solutions Se Tyskland | A large turbocharged two-stroke internal combustion engine with egr system |
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| WO2008009291A1 (en) * | 2006-07-21 | 2008-01-24 | Hans Jensen Lubricators A/S | Lubricating apparatus for a dosing system for cylinder lubrication oil and method for dosing cylinder lubricating oil |
| EP2199549A1 (en) * | 2008-12-18 | 2010-06-23 | Wärtsilä Schweiz AG | Cylinder lubrication device for combustion engine |
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| JPS5925919B2 (en) * | 1975-12-29 | 1984-06-22 | ヤマハ発動機株式会社 | 2 cycle engine pump |
| JPS5848473Y2 (en) * | 1977-10-20 | 1983-11-05 | ヤマハ発動機株式会社 | diaphragm device |
| JPS5851003U (en) * | 1981-10-02 | 1983-04-06 | 三井造船株式会社 | cylinder lubricator |
| JP3114080B2 (en) * | 1992-08-10 | 2000-12-04 | ヤマハ発動機株式会社 | Separate refueling system for two-stroke engine |
| JPH07127414A (en) * | 1993-11-05 | 1995-05-16 | Yamaha Motor Co Ltd | Lubricating oil feeder for two-cycle engine |
| DK173288B1 (en) * | 1996-10-11 | 2000-06-13 | Man B & W Diesel As | Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder |
| DK176366B1 (en) * | 2005-11-21 | 2007-10-01 | Hans Jensen Lubricators As | Lubricator for a dosing system for cylinder lubricating oil and method for dosing of cylinder lubricating oil |
| KR101506313B1 (en) * | 2012-05-15 | 2015-03-26 | 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 | Cylinder lubrication device |
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2016
- 2016-08-17 DK DKPA201670630A patent/DK179118B1/en active
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- 2017-07-11 JP JP2017135303A patent/JP6461251B2/en active Active
- 2017-08-16 CN CN201710700883.0A patent/CN107762655B/en active Active
- 2017-08-16 KR KR1020170103356A patent/KR101959852B1/en active IP Right Grant
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| WO2008009291A1 (en) * | 2006-07-21 | 2008-01-24 | Hans Jensen Lubricators A/S | Lubricating apparatus for a dosing system for cylinder lubrication oil and method for dosing cylinder lubricating oil |
| EP2199549A1 (en) * | 2008-12-18 | 2010-06-23 | Wärtsilä Schweiz AG | Cylinder lubrication device for combustion engine |
| CN103422934A (en) * | 2012-05-15 | 2013-12-04 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | A cylinder lubrication device and method of operating the cylinder lubrication system |
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Also Published As
| Publication number | Publication date |
|---|---|
| DK179118B1 (en) | 2017-11-13 |
| JP2018028315A (en) | 2018-02-22 |
| DK201670630A1 (en) | 2017-11-13 |
| JP6461251B2 (en) | 2019-01-30 |
| KR20180020106A (en) | 2018-02-27 |
| KR101959852B1 (en) | 2019-03-19 |
| CN107762655A (en) | 2018-03-06 |
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