CN107435619A

CN107435619A - Petrolift or lubricating pump for large-sized two-stroke compression-ignition engine

Info

Publication number: CN107435619A
Application number: CN201710383002.7A
Authority: CN
Inventors: C·C·翁; J·霍尔斯特; R·B·尼耳森
Original assignee: MAN Diesel Filial af MAN Diesel SE
Current assignee: MAN Energy Solutions Filial af MAN Energy Solutions SE
Priority date: 2016-05-26
Filing date: 2017-05-26
Publication date: 2017-12-05
Anticipated expiration: 2037-05-26
Also published as: KR102098753B1; DK179219B1; JP2017210962A; JP2019148264A; KR20190086647A; JP6902066B2; KR20170134243A; CN115013112A; DK201670361A1; CN107435619B

Abstract

The present invention relates to the petrolift or lubricating pump for large-sized two-stroke compression-ignition engine.It is a kind of to be used to supply fuel or lubricant to the pump of large-sized two-stroke compression-ignition engine.The pump (40) includes two or more pump units (41,42,43).Each pump unit (41,42,43) includes the pump piston (62) being slidably disposed in mercury vapour cylinder (61) and the driving piston (46) for the hydraulic-driven being slidably disposed in driving cylinder (45), wherein, the driving piston (46) is connected to the pump piston (62) to drive the pump piston (62).

Description

Petrolift or lubricating pump for large-sized two-stroke compression-ignition engine

Technical field

The present invention relates to the petrolift or lubricating pump run for large-sized low-speed in two-stroke single current compression-ignition engine.

Background technology

Large-sized two-stroke single current turbocharging type compression-ignition, internal combustion engine with outside guide is often used as being used for argosy Prime mover in the propulsion system or power plant of oceangoing ship.Huge size, weight and power output causes above-mentioned internal combustion engine completely not It is same as general internal combustion engine and large-sized two-stroke turbocharging type compression-ignition engine is placed in one kind for its own.

In the past, large-sized two-stroke compression-ignition engine was run with liquid fuel (such as fuel oil or heavy fuel oil).So And focusing more in terms of environment has been caused developing trend use alternative type fuel, such as natural gas, methanol, coal slurry, Petroleum coke etc..

Some in the fuel of these alternative types have the characteristic for being difficult to use in conventional fuel pump.Some are abrasive materials, all Such as coal slurry, some have excessively poor lubricating property, such as gasoline, and other need extremely low temperature, such as liquid gas.

WO2016/015732 discloses the cylinder lubricating system with multiple cylinder oil pumps.Each cylinder oil pump has connection It is connected to the driving piston of multiple dosage plungers.

Accordingly, it is desirable to provide the pump of these alternative fuel can be handled.

The content of the invention

It is an object of the invention to provide a kind of pump for overcoming or at least reducing above mentioned problem.

Above and other purpose is realized by the feature of independent claims.According to dependent claims, specification and Accompanying drawing, further embodiment are obvious.

According to first aspect, there is provided a kind of pump including two or more pump units, each pump unit are included slidably The pump piston and the driving piston for the hydraulic-driven being slidably positioned in driving cylinder that ground is placed in mercury vapour cylinder, wherein, it is described Driving piston is connected to the pump piston to drive the pump piston.

The pump started by providing each pump piston by linear hydraulic actuator, can be independently of the limitation of crank and used Property, any suitable pump piston is driven in a manner of completely flexible, so as to allow by the operational factor of pump piston completely regulation to It is adapted to liquid to be pumped.

According to the first embodiments possible of first aspect, the pump also includes at least one hydraulic control valve, it is described extremely A few hydraulic control valve is connected to source of high pressure hydraulic fluid and is connected to storage tank, for control one in the pump unit or The flow of the hydraulic fluid flowed in and out in the driving cylinder of multiple pump units, the source of high pressure hydraulic fluid is preferably For with variable and controllable pressure grade source.

According to the second embodiments possible of first aspect, the driving cylinder includes drive chamber and return passage.

According to the 3rd embodiments possible of first aspect, the drive chamber is connected to the hydraulic control valve, Yi Jisuo State return passage and be preferably permanently joined to hydraulic fluid source, the pressure of the hydraulic fluid source is less than the high pressure hydraulic fluid The pressure in source.

According to the 4th embodiments possible of first aspect, the driving cylinder has position sensor, and the position passes Sensor is used to sense position of the driving piston in driving cylinder accordingly.

According to the 5th embodiments possible of first aspect, the fuel feed system is also included from the position sensor The electronic control unit of reception signal, wherein, at least one hydraulic control valve is to be connected to the electronic control unit Electronic control valve.

According to the 6th embodiments possible of first aspect, the electronic control unit is configured to the pump optionally The drive chamber of unit is connected to the source of high pressure hydraulic fluid or is connected to storage tank.

According to the 7th embodiments possible of first aspect, the electronic control unit is configured to the pump in a driving piston Start the pump stroke of another driving piston when stroke is close to its terminal so that between the pump stroke of end and the pump stroke of beginning With small overlapping.It is thereby achieved that making fuel or lubricant substantially steady flow out pump and without significant pressure Fluctuation.

According to the 8th embodiments possible of first aspect, the electronic control unit is configured to consider the pump stroke terminated Dynamics and start pump stroke dynamics, to obtain the substantially constant of fuel under high pressure or lubricant from the pump Flow.

According to the 9th embodiments possible of first aspect, the electronic control unit is configured to determine driving cylinder/mono- When the pump stroke of one of member must start and determine when the pump stroke of any driving cylinder must terminate.Therefore, can be with The point that control pump stroke starts and the point that especially pump stroke terminates exactly.

According to the tenth embodiments possible of first aspect, the electronic control unit is configured to substantially one after the other activate Each driving cylinder, preferably by exist it is small it is overlapping in a manner of activate each driving cylinder.

According to the 11st embodiments possible of first aspect, the electronic control unit is configured to send out in one of pump unit The driving piston of remaining pump unit to work is operated during raw failure.Therefore, redundancy is obtained, and if one of pump unit occurs Failure, then it can continue pumping behavior.

According to the 12nd embodiments possible of first aspect, the electronic control unit, which is configured to operate remaining, to work Pump unit driving piston, substantially one after the other to activate the driving cylinder of remaining pump unit to work, preferably with There is small overlapping mode to activate.

According to the 13rd embodiments possible of first aspect, the electronic control unit be configured to according to from high-pressure pump to The uninterrupted of the liquid gas of high pressure evaporator adjusts driving when drive chamber and the source of high pressure hydraulic fluid are disconnected The position of piston.Therefore, the position that can turn to pump stroke keeps identical, no matter the speed and institute of pump piston and driving piston How is the inertia of formation.

According to the 14th embodiments possible of first aspect, the electronic control unit is configured to：When from the pump Fuel or lubricant flow increase when, with drive stroke side in opposite direction be adjusted up drive piston drive chamber The position of respective drive piston when being disconnected with the high-pressure fluid source.

According to the 15th embodiments possible of first aspect, the electronic control unit is configured to：When from the pump Fuel or the flow of lubricant when reducing, be adjusted up driving drive chamber and the high-pressure spray of piston in the side of driving stroke The position of respective drive piston when body source is disconnected.

According to the 16th embodiments possible of first aspect, the electronic control unit is configured to according to algorithm, plan Or the randomly position of respective drive piston when drive chamber and the high-pressure fluid source of regulation driving piston are disconnected, so as to The position distribution that pump piston is turned to is on the stroke zone of pump piston, so as to reduce the abrasion of mercury vapour cylinder.

According to the 17th embodiments possible of first aspect, the electronic control unit is configured to be supplied to by control The pressure of the hydraulic fluid of drive chamber controls the pressure of the fuel pumped by the pump or lubricant.Therefore, realize to institute The fuel of pumping or the pressure of lubricant effective and the control to make an immediate response.

According to the 18th embodiments possible of first aspect, the electronic control unit is configured to make in feed forward function With the fuel or the desired pressure of lubricant that are pumped to control the pressure for the hydraulic fluid for being supplied to drive chamber.By using right By the feedforward control of the liquefied gas pressure of hydraulic pressure, the fuel or the pressure of lubricant pumped can be realized even more Quick and smoothly control.

According to the 19th embodiments possible of first aspect, the electronic control unit is configured to make in feedback function With the measurement pressure of the fuel or lubricant that are pumped to control the pressure for the hydraulic fluid for being supplied to drive chamber.Therefore, can be with Meet non-linear and transient behavior by control system.

According to the 20th embodiments possible of first aspect, the electronic control unit is configured to control to each driving The activation and deactivation of piston, Stress control of the control independently of the hydraulic fluid to being supplied to the drive chamber.Cause This, can optimize the control strategy for activating driving piston by electronic control unit independently of Stress control.

According to the 21st embodiments possible of first aspect, the electronic control unit is configured to using expression driving The information of the position of piston come control to drive piston activation and deactivation.

According to second aspect, there is provided a kind of large-sized two-stroke turbocharging type compression-ignition engine, the internal combustion engine have According to the pump described in first aspect and its any embodiments possible.

According to the third aspect, there is provided a kind of cargo ship, it includes the internal combustion engine according to second aspect.

According to fourth aspect, there is provided one kind be used for by fuel or lubricant pump be sent to internal combustion engine with by spraying high-pressure gas extremely Method in the internal combustion engine, methods described include：

By fuel or lubricant reservoir in storage tank；And

The fuel or lubricant pump are sent to the internal combustion engine using pump, wherein, the pump includes two or more Pump unit, each pump unit include the driving piston for the pump piston and hydraulic-driven being slidably positioned in mercury vapour cylinder, the drive Piston is connected to the pump piston to drive the pump piston,

Methods described also includes：

High pressure hydraulic fluid is supplied to driving cylinder to drive driving piston；And

The pressure that the hydraulic fluid of driving cylinder is supplied to by control leaves the fuel or lubricant of high-pressure pump to control Pressure.

According to the first embodiments possible of fourth aspect, methods described also includes：Driving is activated for driving stroke to live One of plug, hereafter deactivate the driving piston for backflow stroke.

According to the second embodiments possible of fourth aspect, pump piston and driving piston are connected to each other to transport exactly in unison It is dynamic.

According to the 3rd embodiments possible of fourth aspect, methods described also includes：Connect in the pump stroke of a driving piston Start the pump stroke of another driving piston during its nearly terminal so that have between the pump stroke of end and the pump stroke of beginning small It is overlapping.

According to the 4th embodiments possible of fourth aspect, methods described also includes：Consider the power of pump stroke terminated And the dynamics of the pump stroke started, to obtain from the pump to the fuel of the internal combustion engine or the substantially constant of lubricant Flow.

According to the 5th embodiments possible of fourth aspect, methods described also includes：Substantially one after the other activate each drive Dynamic cylinder, preferably by exist it is small it is overlapping in a manner of activate.

Embodiment from the description below, the aspects of the invention and other side will be evident.

Brief description of the drawings

In the part in detailed below of the present invention, with reference to the accompanying drawings in the illustrative embodiments that show be more fully described The present invention, in the accompanying drawings：

Fig. 1 is to regard front view according to the vertical of large-sized two-stroke diesel internal combustion engine of illustrative embodiments；

Fig. 2 is for high-pressure natural gas to be supplied to the combustion of the large-sized two-stroke diesel internal combustion engine according to Fig. 1 from LNG storage tank Expect the diagram of feed system；

Fig. 3 is the elevation view of the high-pressure pump in Fig. 2 fuel feed system；

Fig. 4 is the diagram of Fig. 3 high-pressure pump；

Fig. 5 is the detailed sectional view of the pump unit of Fig. 3 high-pressure pump；

Fig. 6 to Fig. 8 is the figure of the operation for the high-pressure pump for showing Fig. 3；

Fig. 9 is the diagram for the control system of the high-pressure pump of control figure 3；

Figure 10 and Figure 11 is the figure of the movement of the piston in various speed for the high-pressure pump for showing Fig. 3.

Embodiment

In the following detailed description, will be described with reference to illustrative embodiments for the large-sized two-stroke with crosshead The fuel feed system of low speed turbocharging type compression-ignition engine, but it is to be understood that internal combustion engine can be another species Type, for example, with or without turbocharging, with or without waste gas recycling or SCR two-stroke it is difficult to understand Support type, four stroke otto-types or diesel-type.Moreover, it will describe to be used to supply fuel or lubricant with reference to illustrative embodiments To the pump of the large-sized two-stroke low speed turbocharging type compression-ignition engine with crosshead, but it is to be understood that internal combustion engine Can be another type, for example, with or without turbocharging, with or without waste gas recycling or selective catalysis The two-stroke otto-type of reduction, four stroke otto-types or diesel-type.

Fig. 1 shows there is runner and the large-sized low-speed turbocharging type two-stroke diesel combustion engine of crosshead.In the example In property embodiment, internal combustion engine has rows of six cylinders.Large-sized low-speed turbocharging type two-stroke diesel combustion engine is usual With rows of four cylinders to 14 cylinders, the cylinder frame that the cylinder is carried by internal combustion engine frame 6 carries.The internal combustion engine The main internal combustion engine that can be used for example as in marine ship or as the fixation internal combustion engine for running the generator in power plant.It is interior Total output of combustion engine can be for example in the range of 1000kW to 110000kW.

In the illustrative embodiments, internal combustion engine is two-stroke single flow pattern compression-ignition engine, is had in cylinder 1 Scavenging port at lower area and the central discharge air valve 4 at the top of cylinder buss 1.Scavenging is sent to from scavenging container 2 The scavenging port of each cylinder 1.Piston compression scavenging in cylinder buss 1, sprays fuel under high pressure by the fuel valve in cylinder cover, Such as gaseous fuel, then occur to burn and produce waste gas.

When air bleeding valve 4 is opened, it is vented and degassing container 3 is flowed into by the discharge duct being connected with cylinder 1 and goes to whirlpool The turbine of booster 5 is taken turns, exhaust is left turbine by discharge duct and entered in air.The turbine drives warp of turbocharger 5 The compressor of the supply of fresh air is obtained by air inlet.Scavenging of pressurizeing is transported to the scavenging for leading to scavenging container 2 by compressor In pipeline.The intercooler 7 for being used for cooling down scavenging is passed through in scavenging in scavenging pipeline.

Fig. 2 is the schematic diagram of the fuel or lubricant supply system for internal combustion engine.Fuel feed system may be mounted at On marine ship, such as LNG cargo ships or container ship.

Fuel feed system includes fuel reservoir 8, kind of lubricant storage or fuel, such as fuel oil in fuel reservoir 8.Replace Selection of land, fuel are the liquefied gas stored under cryogenic.

The outlet of fuel or lubricant reservoir 8 is connected to the entrance of high-pressure pump 40 by feeding lines 9.Feed pump 10 helps will Fuel or lubricant are transported to the entrance of pump 40 from storage tank 8.

Fuel or lubricant gas are pumped into internal combustion engine by pump 40 by service 18.Valve gear 19 controls fuel/profit Connection between lubrication prescription feed system and large-sized two-stroke diesel internal combustion engine.

Pump 40 has two or more pump units 41,42,43 (showing 3 pump units in the present embodiment).Each Pump unit 41,42,43 includes：Pump piston 62, it is slidably disposed in mercury vapour cylinder 61；And the driving piston of hydraulic-driven 46, it is slidably disposed in driving cylinder 45, wherein, driving piston 46 is attached to pump piston 62, for described in driving Pump piston 62.

Pump piston 62 and mercury vapour cylinder 61 form positive-displacement pump.In one embodiment, pump piston 62 and mercury vapour cylinder 61 are formed The so-called cold end of cryopump unit, the cryopump unit have the pump chamber 63 for pump liquefied gas.

Mercury vapour cylinder 61 is connected to the driving piston of pump unit 41,42,43 by piston rod 49.Driving piston 46 will drive vapour The inside of cylinder 45 is divided into drive chamber 48 and return passage 47.

Driving cylinder 45 is connected to high-pressure hydraulic fluid source 20, such as pump or pump by high-pressure hydraulic fluid service 23 Stand.In shown embodiment, source of high pressure hydraulic fluid 20 includes electric drive motor 21, and it drives high-pressure pump 22.High pressure Pump 22 for example can be positive-displacement pump, preferably the variable positive-displacement pump of discharge capacity.In one embodiment, it is high for redundancy purpose Hydraulic fluid under pressure source includes two high-pressure hydraulic pumps 22, and each high-pressure hydraulic pump 22 is driven by the electric drive motor 21 of their own.

Fig. 3 is the elevation view of high-pressure pump 40, and the high-pressure pump 40 has three pump units 41,42,43, and these pump units have Mercury vapour cylinder 61, driving cylinder 45 and control valve 24, and supported by framework 35, the high-pressure pump 40 also has accumulator 53, and it is used for The higher pressure of balanced high-pressure pump 40 and for for return passage equilibrium compared with low pressure.Pump unit 41, pump unit 42, pump unit 43 are with compact The part that mode is arranged on framework 35 and on framework 35 does not have spark generation part and only has the electronics of ATEX certifications Part, so as to allow the unit to be installed in without any problems in ATEX environment.

Fig. 4 be with pump unit 41, pump unit 42, pump unit 43 high-pressure pump 40 diagram.Each pump unit 41,42, 43 are connected to storage tank by hydraulic fluid reflux pipeline 26 and are connected to high pressure hydraulic fluid by hydraulic fluid supply line 23 Body source, the high-pressure hydraulic fluid source include being connected to the variable positive-displacement pump 22 of discharge capacity of each pump unit 41,42 and 43.It is each Pump unit 41,42 and 43 is connected to service 18.

Each pump unit 41,42,43 includes hydraulic control valve 24, and the hydraulic control valve 24 is configured to optionally by control Each drive chamber 48 is connected to high-pressure hydraulic fluid source or is connected to storage tank by tubing giving sufficient strength 25.

Each pump unit 41,42,43 includes the driver element 44 of linear hydraulic actuator form, and the driver element 44 is by driving Dynamic cylinder 45 is formed, and driving piston 46 is slidably disposed with the driving cylinder 45.Return passage 47 is by return passage supply pipe Line 31 is permanently attached to hydraulic power source, and the hydraulic power source includes hydraulic pump 30 (such as discharge capacity variable positive-displacement pump), the return passage Supply pipeline 31 preferably includes current limiter 33 and is connected to accumulator 32, and the accumulator 32 is used to ensure the hydraulic fluid of pressurization Body stable supplying is to return passage 47.Alternatively, low pressure source is obtained from high-pressure hydraulic by pressure-reducing valve.In an embodiment In, the pressure for being supplied to the hydraulic fluid of return passage is significantly less than the pressure for the hydraulic fluid for being supplied to drive chamber 48.It is alternative Ground, being arranged in face of the effective pressure surface of the side of return passage 47 for driving piston 46 are significantly less than driving piston In face of the effective pressure surface of drive chamber 48.In the latter case, the pressure of the hydraulic fluid in return passage 47 can be basic The upper pressure for being equal to the hydraulic fluid for being supplied to drive chamber 48.

Each pump unit 41,42,43 includes the pump 60 of linear positive-displacement pump form, and the pump 60 is formed by mercury vapour cylinder 61, should Pump piston 62 is accommodated in mercury vapour cylinder 61 to form pump chamber 63.Pump chamber 63 is connected to feeding lines 9 by the first check valve 51, should First check valve 51 only allows the flowing for flowing to balancing gate pit 63.Pump chamber 63 is connected to service 18 by the second check valve 52, Second check valve 52 only allows the flowing of outflow pressure room 63.

Fig. 5 is pump unit 41, pump unit 42, the detailed cross sectional view of pump unit 43 of high-pressure pump 40.Pump unit 41, pump unit 42nd, pump unit 43 includes hydraulic linear actuator 44, and the hydraulic linear actuator 44 includes cylinder 45, is disposed with the cylinder 45 Drive piston 46.Driving piston 46 is connected to piston shaft 47, and preferably the two is formed as a unit.Piston rod 49 and driving are lived Plug 46 has the hole 58 of the bar 57 for accommodated position sensor 56.The signal of position sensor 56 is transferred to Electronic Control list Member 70.The inside for driving cylinder 45 is divided into drive chamber 48 and return passage 47 by driving piston 46.In Figure 5, return passage is not It is recognizable, because driving piston 46 reaches its end for driving stroke.Drive chamber 48 is connected to hydraulic control valve by hole 25 24.Return passage 47 is permanently attached to hydraulic power source by hole 31.

The piston rod 47 of linear hydraulic actuator 44 is connected to the piston rod 62 of cryogenic pump 60 (although pump 60 can also be used In the conventional linear positive-displacement pump of pumping non-cryogenic liquid).Piston rod 47 is established by connector block 54 as follows and lived Connection between stopper rod 62：Piston rod 47 and piston rod 62 is caused to move exactly in unison.Driving cylinder 45 is bolted Part 55 is connected to mercury vapour cylinder 61.Cryogenic pump 60 has outlet, and pump chamber 63 is connected to conveyance conduit 50 by the outlet.

Fig. 9 is the diagram of the control system of the form of the electronic control unit 70 of the operation for controlling high-pressure pump 40.

Electronic control unit 70 receives fuel or lubricant pressure setting value 71.The pressure set points 71 are transferred to summation Point 72.In the first summing junction 72, measurement pressure is subtracted, and by setting value and the difference between the measurement pressure in the exit of pump 40 Value is transferred to PI (proportional integration) controller 74, and the PI controllers 74 are a part for feedback control loop.

Pressure set points are transferred to feedforward piston proportional gain unit 78.In the second summing junction 76, feedforward will be come from and lived The signal of proportional gain unit 78 is filled in compared with the signal from PI controllers 74.

The fuel or lubricant measurement pressure for being sent to the first summing junction 72 can be based on spaces in the pipe at internal combustion engine The measured value of the pressure in (i.e. the downstream of valve gear 19).Valve gear 19 is pair that fuel or lubricant stream are received from service 18 Close double break valve gear.The fuel or lubricant measurement pressure are filtered in filter 86.

Comparative result at the second summing junction 76 is transferred to high-pressure hydraulic fluid source 20.Based on the signal, high pressure liquid Hydraulic fluid with appropriate pressure is sent to high-pressure pumping unit 40 by press liquid source 20.

Electronic control unit 70 receives the signal for the position for representing driving piston and handled in piston monitoring unit 92 The position signalling.Piston monitoring unit 92 is connected to activating piston policy unit 90.It will be shown in greater detail further below And illustrate the details of the operation of piston monitoring unit 92 and activating piston policy unit 90.The signal of activating piston policy unit 90 The control valve 24 of high-pressure pump 40 is transferred to, to activate driving piston 46.

The activation for driving piston 46 is caused to pump fuel or lubricant by service 18.

The main pressure control of electronic control unit 70 is forward-type.PI controller compensations are non-linear and aid in transition to show As.

Given by setting to pump unit 41, pump unit 42, the hydraulic cylinder feed pressure of pump unit 43, fuel or lubricant pressure It is self-contr ol.Stress control need not act in hydraulic pressure side in gas side application.In suitable control hydraulic pressure, the system It is unable to reach too high fuel or lubricant pressure.

Driving piston 46 is controlled by control strategy, the control strategy is not the live part of Stress control.

Each pump unit 41,42,43 is individually controllable.Therefore, different piston strategies and various operations can be run Condition.In addition, individually running pump unit 41, pump unit 42, the possibility of pump unit 43 provides redundancy, because can be in two punchings Become between journey from three pump units 41,42,43 and turn to two pump units.

Back-flow velocity can be more than preceding to (pump) speed, so that having weight when only running two pump units It is folded.Can adjust as desired it is overlapping between pump unit 41, pump unit 42, pump unit 43, to reduce pressure peak.

The end position of pump stroke can be changed over time so that abrasion is distributed on the region of mercury vapour cylinder 61, and this has Not in having high abrasion on the fixed position in cylinder.

The system allows the pressure excess of very little or no pressure excessive, or even when closing (piston stopping) suddenly, this is Because with low-down inertia or negatively influence the other factorses of dynamic response.

Control valve 24 can be hydraulic control valve or power control valve.In the embodiment that control valve 24 is hydraulic control valve In, there is provided there is the magnetic valve (not shown) of Electric control, the solenoid valve control goes to the hydraulic control signal of control valve 24.Electric power The magnetic valve of control receives electronic control signal from electronic control unit 70.

Electronic control unit 70 (especially activating piston policy unit 90) is configured to pump unit 41, pump unit optionally 42nd, the drive chamber 48 of pump unit 43 is connected to high-pressure hydraulic fluid source 20 or is connected to storage tank.

Electronic control unit 70 (especially activating piston policy unit 90) is configured to connect in the pump stroke of a driving piston 47 Start the pump stroke of another driving piston 47 during its nearly terminal so that have between the pump stroke of end and the pump stroke of beginning Very little it is overlapping.In one embodiment, electronic control unit 70 is configured to substantially one after the other activate each driving cylinder, excellent The overlapping of very little be present in selection of land.

Therefore, as shown in Figure 6 and Figure 7, it is possible to achieve make LNG substantially steady flow to high pressure evaporator 14 and without aobvious The pressure oscillation of work.

Fig. 6, Fig. 7 and Fig. 8 show the typical operation of high-pressure pump 40.Fine line represents pump unit 41, and heavy line represents pump Unit 42, and dotted line represent pump unit 43.Fig. 6 is the figure for showing to drive the motion of the pump piston 62 of piston 46/.As illustrated, The beginning of the pump stroke of next pump unit just starts before the end of the pump stroke of the currently active pump unit.Fig. 7 is shown By the final pressure formed by pressure output of the conveyance conduit 50 from three pump units 41,42,43.The final pressure is basic On be constant and without fluctuation.

Fig. 8 shows the rate curve of pump unit, wherein it will be clear that the speed of backflow stroke is apparently higher than pump impulse The speed of journey, it is overlapping between pump unit so as to allow, even if only two pump units only in three or more pump units exist In use.

In one embodiment, electronic control unit 70 (especially activating piston policy unit 90) is configured to consider what is terminated The dynamics of the dynamics of pump stroke and the pump stroke started, to obtain from high-pressure pump to high pressure evaporator 14 high-pressure liquefaction The substantially constant flow of gas.

In one embodiment, electronic control unit 70 (especially activating piston policy unit 90) is configured to determine pump unit 41st, when the pump stroke of one of pump unit 42, pump unit 43 must start and determine pump unit 41, pump unit 42, pump unit When one of 43 pump stroke must terminate.Therefore, the point that pump stroke starts and the point that especially pump stroke terminates can be by living Plug policy unit 90 () accurately controls preferably along with piston monitoring unit 92 together.

In one embodiment, electronic control unit 70 is configured to send out in one of pump unit 41, pump unit 42, pump unit 43 The pump unit 41, pump unit 42, the driving piston of pump unit 43 that remaining works are operated during raw failure.Therefore, redundancy is obtained, with And if one of pump unit 41, pump unit 42, pump unit 43 break down, then it can continue pumping behavior.

In one embodiment, electronic control unit 70 is configured to according to from high-pressure pump 40 to the liquefied gas of high pressure evaporator The uninterrupted of body adjusts the position of the driving piston 46 when drive chamber 48 and high-pressure hydraulic fluid source are disconnected.Therefore, may be used To control the position that pump stroke turns to, regardless of the inertia for driving the speed of piston 46 and pump piston 62 and being formed.

According to an embodiment, electronic control unit 70 is configured to：When the fuel or lubricant from high-pressure pump to internal combustion engine Flow increase when, with drive stroke side in opposite direction be adjusted up drive piston 46 drive chamber 48 and highly pressurised liquid The position of respective drive piston 46 when source 20 is disconnected, and electronic control unit 70 are configured to：When from high-pressure pump to internal combustion When the fuel of machine or the flow of lubricant are reduced, it is adjusted up driving drive chamber 48 and the high pressure of piston 46 in the side of driving stroke The position of respective drive piston 46 when fluid supply 20 is disconnected.This shows in Figure 10 and Figure 11.

Figure 10 shows the effect that driving piston 46 and pump piston 62 increase in the speed of the end position of driving/pump stroke Fruit.Fine line represents pump unit 41, and heavy line represents that pump unit 42, and dotted line represent pump unit 43.When driving piston has reached To 80mm stroke when, electronic control unit 70 signals to hydraulic control valve 24 so that drive chamber 48 is connected into storage tank no matter How is load/size of the flow of the liquid gas transmitted by high-pressure pump 40.Due to inertia and fair speed, piston 46 is driven Stopping/steering position become from the 85mm under 25% load and turn to 89mm under 50% load, become and turn under 100% load 98mm。

Figure 11 for show electronic control unit 70 under shorter stroke (now load is very high) and compared with long stroke (now Load is very low) compensate the effect pushed the speed of the driving pump piston 62 of piston 46/ by the way that drive chamber 48 is connected into storage tank Figure.Such as it was found from figure, electronic control unit 70 can control the end position of driving/pump stroke exactly in this mode.

It is negative for 25% for next driving cylinder when previous cylinder enters drive chamber 75mm in the example of the figure Lotus (that is, the 25% of the maximum capacity of high-pressure pump 40) issues the signal for drive chamber 48 to be connected to storage tank.Driven when entering During the 93mm of room, the drive chamber of " previous " driving cylinder is connected to storage tank.Next driving cylinder and high-voltage power supply are shown in table 1 below Connection " signal connection " and the connection of " previous " cylinder and storage tank " signal shut-off ".

	25% load	45% load	70% load	100% load
					Signal is connected	75mm	75mm	75mm	75mm
Signal turns off	93mm	86mm	83mm	80mm
					Stop position	97mm	97mm	97mm	97mm

Table 1

Certainly, it still can also program electronic control unit 72 and purposely change starting position, to reduce mercury vapour cylinder 61 abrasion.

In one embodiment, electronic control unit 70 is configured to according to algorithm, plan or randomly adjusts driving piston The position of respective drive piston 46 when 46 drive chamber 48 is disconnected with high-pressure fluid source 20, so as to turn to pump piston 62 Position distribution is on the stroke zone of pump piston 62, so as to reduce the abrasion of mercury vapour cylinder 61.It is known that the mill on mercury vapour cylinder 61 Damage highest on the position that pump stroke terminates.The position terminated by changing pump stroke, the abrasion of mercury vapour cylinder 61 can be distributed On large area, therefore the useful life of mercury vapour cylinder 61 can dramatically increase.

In one embodiment, electronic control unit 70 be configured to control to it is each driving piston 46 activation and deactivate Living, the Stress control of this hydraulic fluid with being supplied to drive chamber 48 is unrelated.Therefore, can be optimized by electronic control unit 70 For activating the control strategy of driving piston, this is unrelated with Stress control.

Combined this paper multiple embodiments describe the present invention.However, those skilled in the art are implementing to want When seeking the present invention of protection, according to the research to accompanying drawing, disclosure and the accompanying claims, it is possible to understand that and realize that institute is public The other modifications for the embodiment opened.In the claims, term " comprising " is not precluded from other element or steps, and indefinite Article "a" or "an" is not excluded for multiple.Electronic Control list can be formed by the combination of independent electronic control unit Member.Record in mutually different dependent claims some measures simple fact be not offered as the combinations of these measures can not It is advantageously used.The reference used in claims is not necessarily to be construed as limiting scope.

Claims

Be used to pumping the cryogenic pump (40) of low temp fuel 1. a kind of, the cryogenic pump include two or more pump units (41, 42nd, 43), each pump unit (41,42,43) includes being slidably disposed at the pump piston (62) in single mercury vapour cylinder (61) and can The driving piston (46) for the hydraulic-driven being slidably arranged in single driving cylinder (45), wherein, the driving piston (46) The pump piston (62) is connected to drive the pump piston (62).
2. cryogenic pump (40) according to claim 1, in addition at least one control valve (24), at least one control Valve (24) is connected to source of high pressure hydraulic fluid (22) and is connected to storage tank, for controlling one in the pump unit (41,42,43) The flow of the hydraulic fluid flowed in and out in the driving cylinder (45) of individual or multiple pump units, the high-pressure hydraulic fluid Fluid source (22) is preferably to have variable and controllable pressure grade source.
3. cryogenic pump (40) according to claim 1 or 2, wherein, the driving cylinder (45) include drive chamber (48) and Return passage (47).
4. cryogenic pump (40) according to claim 3, wherein, the drive chamber (48) is connected to control valve (24), and The return passage (47) is preferably connected to hydraulic fluid source (30), and the pressure of the hydraulic fluid source (30) is less than the high pressure The pressure of hydraulic fluid source (22).
5. cryogenic pump (40) according to any one of claim 1 to 4, wherein, the driving cylinder has position sensing Device (56), the position sensor (56) are used to sense position of the driving piston (46) in driving cylinder (45) accordingly.
6. cryogenic pump (40) according to claim 5, in addition to electronic control unit (70), the electronic control unit (70) from the position sensor (56) reception signal, wherein, at least one control valve is to be connected to the Electronic Control The electronic control valve of unit (70).
7. cryogenic pump (40) according to claim 6, wherein, at least one electronic control unit (70) is configured to select Selecting property the drive chamber of the pump unit is connected to the source of high pressure hydraulic fluid or is connected to storage tank.
8. the cryogenic pump (40) according to claim 6 or 7, wherein, the electronic control unit (70) is configured to drive one The pump stroke of piston close to the pump stroke terminal when start it is another driving piston pump stroke so that in the pump impulse of end Have between journey and the pump stroke of beginning small overlapping.
9. cryogenic pump (40) according to claim 8, wherein, the electronic control unit (70) is configured to consider what is terminated The dynamics of the dynamics of pump stroke and the pump stroke started, to obtain the base of fuel or lubricant from the cryogenic pump This constant flow.
10. cryogenic pump (40) according to claim 9, wherein, the electronic control unit (70) is configured to substantially phase Activate each driving cylinder after ground, preferably by exist it is small it is overlapping in a manner of activate each driving cylinder.
11. the cryogenic pump (40) according to any one of claim 6 to 10, wherein, the electronic control unit (70) is matched somebody with somebody Fuel or the uninterrupted of lubricant according to being pumped by the cryogenic pump are set to adjust drive chamber (48) and the high pressure The position of driving piston (46) when hydraulic fluid source (22) is disconnected.
12. cryogenic pump (40) according to claim 11, wherein, the electronic control unit (70) is configured to：When by institute When stating the flow increase of fuel that cryogenic pump (40) pumped or lubricant, raised in the direction in opposite direction with driving stroke The position of respective drive piston when the drive chamber of section driving piston is disconnected with the high-pressure fluid source.
13. the cryogenic pump (40) according to claim 11 or 12, wherein, the electronic control unit (70) is configured to：When When the flow of fuel or lubricant from the cryogenic pump is reduced, it is adjusted up driving the driving of piston in the side of driving stroke The position of respective drive piston when room is disconnected with the high-pressure fluid source.
14. the cryogenic pump (40) according to any one of claim 6 to 13, wherein, the electronic control unit (70) is matched somebody with somebody It is set to according to algorithm, plan or the position for randomly adjusting driving piston, so as to which the position distribution that pump piston turns to is lived in pump In a part for the stroke of plug, so as to reduce the abrasion of mercury vapour cylinder.
15. the cryogenic pump (40) according to any one of claim 6 to 14, wherein, the electronic control unit (70) is matched somebody with somebody The pressure for being set to the hydraulic fluid for being supplied to drive chamber by control leaves the fuel or lubricant of the cryogenic pump to control Pressure.
16. cryogenic pump (40) according to claim 15, wherein, the electronic control unit (70) is configured in feedforward work( In energy using leave the fuel of the cryogenic pump or the desired pressure of lubricant with control be supplied to driving piston hydraulic fluid Pressure.
17. the cryogenic pump (40) according to claim 15 or 16, wherein, the electronic control unit (70) is configured to anti- In feedback function the hydraulic pressure for driving piston is supplied to using the measurement pressure of the fuel or lubricant that leave the cryogenic pump to control The pressure of fluid.
18. the cryogenic pump (40) according to any one of claim 15 to 17, wherein, the electronic control unit (70) is matched somebody with somebody It is set to the Stress control independently of the hydraulic fluid to being supplied to drive chamber and the activation to each driving piston (46) and deactivates Work is controlled.
19. the cryogenic pump (40) according to any one of claim 15 to 18, wherein, the electronic control unit (70) is matched somebody with somebody The signal using the position for representing driving piston (46) is set to, to control activation and deactivation to driving piston.
20. a kind of large-sized two-stroke turbocharging type compression-ignition engine, including according to any one of claim 1 to 19 institute The cryogenic pump (40) stated, the cryogenic pump (40) are used to fuel or lubricant being supplied to the large-sized two-stroke turbocharging type Compression-ignition engine.
21. one kind is used for the method for controlling the activation to the pump piston of pump (40), the pump (40) includes two or more pumps Unit (41,42,43), each pump unit (41,42,43) include the pump piston (62) being slidably disposed in mercury vapour cylinder (61) With the driving piston (46) of hydraulic-driven being slidably disposed in driving cylinder (45), wherein, the driving piston (46) The pump piston (62) is connected to drive the pump piston (62), methods described includes：

Piston (46) is activated for driving stroke and hereafter deactivates the driving piston (46) for backflow stroke；And

The position of the driving piston (46) is measured during the driving stroke,

Wherein, activated when the driving piston (46) be in backwash deployment it is described drive piston (46), and wherein, depending on The opening position of the speed of the driving piston (46) deactivates the driving piston (46).
22. according to the method for claim 21, wherein, during stroke is driven, closer to the backwash deployment and institute The opening position for stating the speed increase of driving piston (46) deactivates the driving piston (46), and during stroke is driven, more The opening position that speed away from the backwash deployment and the driving piston (46) reduces deactivates the driving piston (46).
23. the method according to claim 21 or 22, wherein, the driving piston (46) is substantially one after the other activated, it is excellent Choosing just activates next driving piston (46) before the driving piston (46) being currently active is deactivated.
24. the method according to any one of claim 21 to 23, in addition to：High pressure hydraulic fluid is supplied to the drive Piston (46), wherein, by control supply to the pressure of the hydraulic fluid of the driving piston (46) come control leave it is described The fuel of pump (40) or the pressure of lubricant.
25. one kind is used for the method for controlling the activation to the pump piston of pump (40), the pump includes two or more pump units (70), each pump unit (41,42,43) includes being slidably disposed at pump piston (62) in mercury vapour cylinder (61) and slideably The driving piston (46) for the hydraulic-driven being arranged in driving cylinder (45), wherein, the driving piston (46) is connected to described To drive the pump piston (62), methods described includes pump piston (62)：

Driving piston (46) is activated for driving stroke and hereafter deactivates the driving piston (46) for backflow stroke；

High pressure hydraulic fluid is supplied to the driving piston (46)；And

By controlling supply to the pressure of the hydraulic fluid of the driving piston (46) to leave the fluids of the pump (40) to control Pressure.
26. according to the method for claim 25, wherein, the driving piston (46) is substantially one after the other activated, preferably Next driving piston (46) is activated before the driving piston (46) being currently active is deactivated.