CN1256742A - Method for operation of hydraulically actuated fuel pump for internal combustion engine, and hydraulically actuated fuel pump - Google Patents
Method for operation of hydraulically actuated fuel pump for internal combustion engine, and hydraulically actuated fuel pump Download PDFInfo
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- CN1256742A CN1256742A CN98805230A CN98805230A CN1256742A CN 1256742 A CN1256742 A CN 1256742A CN 98805230 A CN98805230 A CN 98805230A CN 98805230 A CN98805230 A CN 98805230A CN 1256742 A CN1256742 A CN 1256742A
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- piston
- pump
- fuel
- cylinder
- petrolift
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/24—Fuel-injection apparatus with sensors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
A hydraulically actuated fuel pump (1) for an internal combustion engine has a pump piston (39), which is driven forwards in a delivery stroke by means of an actuator piston (36). Between each injection sequence the pump piston (39) is returned to a fixed starting position by the action of the fuel pressure on the end surface (61, 62) of the pump piston in the pump chamber (52). The delivery volume of the fuel pump is electronically controlled by the supply of hydraulic fluid to the pressure chamber being cut off by the control valve (11) at the moment when the pump piston has delivered the desired volume. The pump cylinder (25) and the actuator cylinder (24) are separate units, which are mutually separated by an intermediate spacing member (26).
Description
The present invention relates to internal-combustion engine, the operating method of the hydraulic actuating petrolift of one or two stroke crosshead motor particularly, this petrolift has at backing pump depresses the high-voltage tube that the hydraulic fluid that is different from fuel of fuel being distributed to a fuel pipe of petrolift and will pressurizeing is distributed to petrolift; Pump piston in petrolift, this piston is driven forwards by the actuator piston in the actuator cylinder in a delivery stroke, meanwhile from a pump chamber, extrude fuel, and in a return stroke to rear driving, meanwhile inject fuel to pump chamber from fuel pipe; With the actuator piston of being controlled by an electronically actuated control valve, the pressure chamber in the actuator cylinder can provide hydraulic fluid or be connected to an eduction gear from high-voltage tube thus.
A kind of method like this can learn that according to this patent, the quantity delivered of petrolift is to be controlled by the rotation of pump piston, and pump piston links to each other with actuator piston for No. 151145 by claimant's Danish Patent.At the end of delivery stroke, pump piston can be retracted by the actuator piston, meanwhile refills fuel by a pressure spring that forces actuator piston to retreat to pump chamber.This pump has the structure (design) of a complexity, has many independently parts, and many in these parts all must very accurately be processed, so that pump piston and actuator piston are correctly worked.
From the petrolift (No. the 41046th, the Danish Patent of claimant's nineteen twenty-eight) of just learning a hydraulic actuating very early, this petrolift is used as hydraulic fluid with fuel, and the quantity delivered of pump is to be carried by the transfer pump of cam control in one embodiment, and be to determine by the control valve of cam control in another embodiment, both do not provide a concrete start position to pump piston, one concrete quantity delivered is not provided yet, because the camshaft actuated of control valve makes it differently act on according to the instantaneous velocity of motor, and motor (petrolift) under high speed than under low speed provides more energy.Carry out injection by hydraulic coupling or by the negative pressure that causes by actuator piston, and pump piston is pushed back backward by a spring to petrolift.
U. S. Patent has represented that a petrolift, the injection of fuel are by electronic valve control for No. 3516395, and the actuating of spraying be by with the one second valve control of the rotational synchronization of bent axle.Fuel is as the hydraulic driving fluid.
Existing many years all can not be used as hydraulic fluid with fuel in large-scale diesel engine, because the characteristic of this fuel makes it be unsuitable for the hydraulic pressure purposes.Typical fuel is heavy fuel oil, and it needs preheating and comprises corrosivity and the mixture of abrasion.Nearest motor also can adopt liquid gas to act as a fuel, but this gas also is not suitable as hydraulic fluid, because have the dangerous of blast and form ice when cooling.
In at present known hydraulically powered pump, fuel keeps separating fully with hydraulic fluid, and the dosage of fuel is to be finished by the rotation of pump piston in these pumps, changes thereby its position that tilts to cut off the edge cuts off the hole with respect to one in the pumping cylinder sidewall.Except above-mentioned Danish Patent, also can mention the example of a U.S. Pat 4907555 as this pump.In this case, be used to carry the control valve of high pressure hydraulic fluid both can be cam-actuated, also can be electronically actuated.In addition, can learn an electronically actuated control valve that is used for a hydraulic driving petrolift by claimant's Danish Patent 170121, this control valve is accurate and response fast.
The objective of the invention is aspect structure (design), Operation and maintenance, to simplify the petrolift of hydraulic actuating, and obtain high pump reliability.
Given this, the feature of the method according to this invention is: in each emission sequence (injectionsequence), effect by the fuel pressure on the end face of the pump piston in the pump chamber, pump piston turns back to a fixing initial position, and the quantity delivered of petrolift is by when pump piston has been carried required capacity, and control valve cuts off the control electronically that transports to the hydraulic fluid of pressure chamber.
By make fuel have backing pump pressure with pump piston turn back to a fixing initial position and by the accurate moment of having carried required fuel quantity at pump cut off hydraulic fluid transport the control quantity delivered, can obtain some advantages.Therefore can regulate break time, the moment of cutting off takes place up to reality.When quantity delivered changed, new setting can be worked immediately and can the cylinder that spray be exerted an influence, and the ensuing injection in other cylinder in the same rotary course of motor is exerted an influence.The electronic control of this quick response that pump is carried can produce emission sequence, and these emission sequence can change from continuous being ejected into closely-spaced a series of injection or so-called interrupted injection as required.
In addition, the invention provides to save and be used for the advantage mechanically returning and inject fuel and be used to control the known mechanical component of quantity delivered, thereby can cause the multiple choices of fuel pump design.Also can save fuel oil accumulation of energy accumulator commonly used, also be called vibration damper.Another advantage is to turn back to initial position in a time cycle of growing relatively, because this injection is to produce in the time of lacking of engine cycle.Between pump piston and pumping cylinder or actuator piston, need not a specific angle of swing.Operational simplification and the simplification mechanically that is obtained greatly reduce the danger that pump lost efficacy.
In addition, this method has important effect, promptly with pump operated relevant energy loss minimum, this part is because the consumption of pump piston and high pressure hydraulic fluid is to stop at fuel to carry when finishing, rather than in the known pump the common the sort of pressure that discharges pump chamber continuously simultaneously, in part because fixing initial position makes it can make the interior useless capacity minimum of pressure chamber of actuator, and make the capacity minimum that after opening control valve, at once needs the hydraulic fluid of pressurization thus.
The fuel of known road internal-combustion engine can mix with water, forms undesirable NO to reduce in combustion process
xCompound.A problem that exists in known petrolift is, motor must or with the fixing proportions of ingredients running of regulation water gaging, perhaps must shut down and reset to carry out the not operation of additional water.The method according to this invention, it can change the quantity delivered of petrolift as required in operating process, therefore can advantageously be used, thereby electronic control unit opens or closes pump, carrying 1%～60% additional capacity of under described engine load fuel quantity under the identical engine load, and meanwhile fuel mixes with water corresponding to additional capacity.In engine running, just be implemented to low NO easily
xThis change of operator scheme, and in operating process, can change the percentage that additional capacity accounts for fuel quantity as required, thus can be according to required NO
xMinimizing and engine load and other operational condition such as the temperature and humidity that sucks air regulate the additional of water continuously.When motor as regular passage in water and be subjected to NO
xDuring the propelling engine of one steamer of emission limit set, this flip-flop is particularly favourable to the possibility of another kind of operator scheme.
The invention still further relates to be used for an internal-combustion engine, the petrolift of a hydraulic actuating of a two-stroke diesel engine particularly, comprise a pump piston, it can longitudinally move in a pump chamber and have a front-end face, this front-end face limits a pump chamber with pumping cylinder; With an actuator piston, it is positioned at the extended position of pump piston and can longitudinally moves in actuator cylinder, and have a piston face, this piston face is positioned at a pressure chamber, deviates from pump piston and has an area more much bigger than the cross sectional area of pump piston; At least one the fuel input channel that has an one-way valve is led to pump chamber; Draw and lead at least one exhaust port from pump chamber with at least one fuel output channel.
When adopting method of the present invention, because the setting of carrying at the fuel aspect capacity and time two can not bring common restriction to the design of petrolift, so this can advantageously be simplified.Petrolift according to the present invention is characterised in that: pumping cylinder and actuator cylinder are unit independently, they are spaced from each other by annular intermediate isolating parts, and pumping cylinder has a lower section that projects in the isolating part downwards, with with respect to this lower section upper segment of projection radially, and they are installed by bonnet bolt.
Two cylinders are as independently unit manufacturings, and they are stacked on the pump assembly, separated and the axis of cylinder has rough relatively mutual degree of registration by intermediary element, and need not consider to a great extent whether the axis of cylinder is radially moving mutually.The fact that two cylinders need not very accurately to be assembled together has just been simplified the manufacturing and the installation of part greatly.Pump case is divided into two cylinders and intermediary element and the bonnet bolt by for example longitudinal bolt comes constituent components, and this has such advantage: when power that pump chamber pressurization and the upper wall effect one in the chamber make progress, housing can avoid producing tensile stress.Fixing between intermediary element and described element and two piston-cylinder units can be relative slight, because this intermediary element only need be born the compression load that comes from assembly.
In delivery stroke, by the pressure forward on the piston face that acts on actuator piston two pistons are pushed toward each other, and in return stroke, by coming from a relatively little power of the pressure backward that flows into the fuel in the pump chamber, these two pistons keep close mutually.In addition, in operating process, can by pump piston to back end with respect to actuator piston one forward a little radial displacement of end face this two pistons are set mutually, thereby the variation of temperature and pressure between each part of compensated pump automatically, and reduce the wearing and tearing of pump and improve its reliability.Can be to a certain extent come at control piston radially by the element between two pumping cylinders, for example, can pump piston mutually towards end face between some pressure meters that relevant current pump chamber pressure data sent to an electronic control unit are set.
Have two independently the petrolift built of the module type of pumping cylinder one favourable possibility also further is provided: the actuator cylinder that promptly only will have the piston that matches is replaced by other unit, wherein the diameter of actuator piston is greater than or less than the diameter of former unit, changing the peak injection pressure of pump, this jet pressure depend on the pressure of hydraulic fluid in the high-voltage tube and depend on actuator piston and pump piston between the area ratio.
In a preferred embodiment of the advantage of having utilized separate piston fully, pump piston is radially carrying out unique guiding by the cylinder hole that matches in the pumping cylinder, and actuator piston is radially carrying out unique guiding by the cylinder hole in the actuator cylinder that matches, and these two pistons can radially freely regulated mutually.This embodiment comprises minimum element, thereby makes that manufacturing is simple, reliability is high.
In one embodiment, actuator cylinder is an annular element that has a cylinder hole that axially connects, and petrolift is installed on the end face of a distributor block, the cylinder hole of actuator cylinder is positioned at the middle extending part of an exhaust port of distributor block end face, thereby pressure chamber is radially limited by actuator cylinder and axially limited by the piston face of actuator piston and the end face of distributor block respectively.The cylinder hole of the axial perforation in the actuator cylinder makes that the structure (design) of actuator is extremely simple at manufacture view, because it only comprises two major parts, i.e. and the piston-cylinder unit at Huan Xing the no end and columniform actuator piston.The pressure chamber of actuator is by producing on the end face that petrolift is installed in distributor block, because the end face of distributor block has constituted the axial qualification bottom surface in chamber.Meanwhile, the end face of distributor block can be used as a block of these two piston move toward one another and determines their initial position thus.There is not hydraulic fluid to a great extent at this position pressure chamber.Because electronically actuated control valve is installed on the distributor block usually or in, therefore have only short passage to lead to exhaust port in the end face of distributor block, make the capacity of the hydraulic fluid between control valve and the actuator piston optimally reduce, thereby provide such advantage: when control valve when the pressure in the high-voltage tube is opened when a delivery stroke begins, can ignore the energy consumption of this Fluid Volume that is used to pressurize.Simultaneously, in the pressure chamber useless capacity minimize the fast response characteristic that can be used to improve electronically actuated control valve because can ignore valve because of setting up the time lag that desired pressure activates.
Bonnet bolt can be fixed to tripartite pump case on the end face of distributor block, and this is providing some advantages aspect maintenance of petrolift.When unclamping bonnet bolt, can recommend out the pumping cylinder that has the piston that matches together in company with intermediary element, the actuator cylinder that will have the piston that matches is simultaneously stayed on the distributor block.Though dismantled pump, actuator can prevent that dust from entering under the hydraulic system.Because most maintenance only relates to the pumping cylinder that is subjected to the fuel influence, therefore aspect maintenance and security of system two, can recommend out the pump piston that has the cylinder that matches is a main advantage.
If petrolift is used to overhaul liquid gas, then do not need heat pump.Though pump of the present invention is much simpler than the known pump that is used for heavy fuel oil, when using preheating can flow through the heavy fuel oil of pump later and when motor was in the ready to start pattern, this also was an advantage.For this reason, the outer surface of the lower section of pumping cylinder can be provided with an annular notch, this outer surface its top and bottom with respect to around the internal surface wiper seal of isolating part, and the fuel inlet in the wall of intermediate member can be introduced in the annular chamber that is formed by recess and intermediate member, and a discharge route that has a current-limiting apparatus that reduces pressure can be connected to this annular chamber continuously.Therefore fuel circulates to discharge route through annular chamber from inlet, and current-limiting apparatus prevents that the pressure in the annular chamber from reducing, and the fuel of preheating provides heating by circulation to pumping cylinder.
The above-mentioned advantage that actuator is given over to a kind of loose dust cover on the hydraulic part sensitive in distributor block also can further be improved by following measure: be provided with a upright annular wall on the end face of actuator cylinder, this annular wall has an internal diameter bigger than the cylinder hole of actuator cylinder, and one upwards the cup-shaped guard shield of sealing be arranged on the lower end with a certain distance from the lower surface of the pumping cylinder that extends around annular wall of pump piston downwards.When mentioning pumping cylinder and piston, upright wall around the actuator cylinder hole prevents that dust particle from entering the actuator piston top, (otherwise) continuous operation will move in the gap between cylinder and the piston dust particle from this position, thereby cause damage because of wearing and tearing to slip surface.The cup-shaped guard shield of pump piston is provided in the operating process with wall fuel is down leaked into protection on the actuator piston, because the fuel quantity that leaks through the annular space between pump piston and the cylinder can be fallen on the end face of guard shield.Because guard shield extends downwards around wall, the fuel that therefore comes from the guard shield end face only moves downward on the outer surface of wall, and wall prevents that fuel from arriving actuator piston.Fuel eduction gear in the cave, chamber between actuator and the pump can prevent to assemble a large amount of fuel quantities around wall.
Cup-shaped guard shield is positioned at by the formed chamber of the height of intermediate member, and this chamber makes pump piston can move and make fuel and hydraulic system to produce the aforementioned isolation except the space is provided to guard shield, there is no other practical use.Therefore the structure of being made up of three parts provides the possibility that the chamber can be used as other purpose.Owing to be used for coming mechanically to determine that by rotating pump piston all known elements of pump duty are all replaced to the capacity regulating of the conveying of the hydraulic fluid of actuator based on time control by warp, therefore actually, when control valve is connected to the pressure chamber of actuator on the high-voltage tube, because the small variation of pump between the hydraulic fluid transporting velocity, the quantity delivered of pump also small variation can occur.By measuring the one or more combustion parameters in the cylinder continuously, can discern this variation of the quantity delivered of pump, and compensate by electronically actuated control valve then.Interchangeablely be, the free space in the chamber can be used for designing petrolift, thereby makes the wall thickness of cup-shaped guard shield reduce downwards, and at least two sensors are installed in the opposite side that is positioned at guard shield in the intermediate member, with the present position of testing pump piston.These two relative sensors are measured position of piston simultaneously, and the electronic control unit of reception measurement signal can compensate, and the measurement that may occur changes because piston can freely be arranged on radially in the sensor.These sensors are known, and can for example location-based measurement of inductance.
The electronic control of the petrolift quantity delivered of the delivery stroke by stopping petrolift since a fixing lower end initial position can provide the further a kind of favourable possibility of improving the pump reliability, the measure of being taked is: pumping cylinder is had with the lower section of a pressure-tight mode around the pump piston assembling, with a chamber section with internal diameter bigger than this lower section, the fuel input channel is led to the sidewall of chamber section, and at least two fuel output channels are drawn from the sidewall of chamber section.As everyone knows, for having fuel output channel and/or pressure relief vent, and by the pump that opens or closes the prior art in described passage or hole by the edge on the piston in this passage or hole, the unexpected variation of the pressure in the passage at the control edge on the piston can cause bubble phenomenon and to other erosive wear of piston and cylinder.According to this preferred embodiment of the invention, by the internal diameter than the wiper seal Duan Gengda of lower end is provided to the chamber section, move in the radial distance of the cylinder surfaces of pump piston in the sidewall of chamber section.The input and output passage that is used for fuel ends at or originates in the sidewall of chamber section, this means, continuously and no matter position of piston, fuel enters in the interior access portal of pump chamber fully, because have an annular region at least, be filled with the fuel between piston cylinder surface and the chamber section sidewall in this annular region at opening.The reliability that this has just eliminated the variation in pressure of unexpected abrasion and has improved petrolift.In addition, because therefore wearing and tearing may appear in the abrasion particle in the fuel at the edge of opening place of passage.Opening be positioned at cylinder surfaces one radial distance from pump piston just prevented because of in the wearing and tearing at bore edges place with the damage of the form of cut to the piston diffusion, this has further improved reliability.
In one embodiment, the upper segment of the increase diameter of pumping cylinder is used for further simplifying fuel pump structure (design).In this embodiment, the fuel output channel is connected to exhaust port upwards, and is used for company is installed in end face from the upper segment of pumping cylinder to the flange of the pressure tube of fuel injector.This is convenient to the setting pressure pipe and allows such structure (design), does not promptly have bending near the mounting point on the pump.The space of the abundance on the pumping cylinder end face makes can install nearly 4 pressure tubes on end face.
One embodiment allows the interior pumping cylinder in zone on the section of chamber to have a portion's section than minor diameter, this section constitutes a damping cavity of upwards sealing, and pump piston has a portion's section that goes up most, the diameter that its height is slightly less than damping cavity corresponding to height and its external diameter of damping cavity.Damping cavity has been improved the reliability of petrolift, because postpone or lost efficacy when making high pressure to the pressure chamber of actuator not stop when the electronic switch signal that for example is stuck or gives control valve owing to control valve, has reduced the danger that pump is damaged.If owing to this inefficacy makes pump piston always by the top-driving to pump chamber, it will continue to enter in the damping cavity and can form an annular space with the sidewall in the chamber of this sealing, fuel in the damping cavity is extruded through this annular space, pressure in the damping cavity increases simultaneously, impels the motion of piston to slow down significantly.Therefore the damping cavity formation prevents a pump piston hydraulic bjuffer at impact cavity top fiercely.The topmost part section of pump piston occupies the capacity almost same with damping cavity, thereby such advantage is provided: when piston during in its initial position, the total capacity of fuel can not increase owing to having added damping cavity to a great extent in the pumping cylinder.Before beginning fuel sprays, thereby when the cracking pressure of the pressurized acquisition of the total capacity of fuel sparger, by making the minimum saving that has obtained energy of this capacity,, thereby make the consumption minimum of high pressure hydraulic fluid because reduced the stroke that pump piston is used to pressurize.
Owing to actuator piston stretches into and obtained service advantages in this groove having a groove near its lower surface place and be installed in a retainer in the actuator casing wall.When recommending cylinder, this retainer prevents that actuator piston from dropping out outside the cylinder.When long period of operation is dismantled actuator afterwards, there is not the unskilled employee at the end to dismantle if know actuator cylinder, then this feature is even more important.
Below in conjunction with accompanying drawing one example of a preferred implementation of the present invention is described in more detail, wherein
Fig. 1 represents the side view according to the profile of the petrolift on the cylinder that is installed in an internal-combustion engine of the present invention;
One longitudinal sectional view of the petrolift of Fig. 2 presentation graphs 1; With
Fig. 3 represents the plan view of petrolift.
One petrolift 1 is installed on the end face of a distributor block 2, and distributor determines 2 by a carriage 3 supportings.This carriage is connected to a high-voltage tube that is used for hydraulic fluid, and this high-voltage tube is supplied with from a unshowned pumping plant the hydraulic fluid of pressure in from 125 to 325 crust scopes for example.This pressure can be fixed, but preferably can regulate according to engine load.Pumping plant can be carried from a fuel reserve tank, and hydraulic fluid can be the hydraulic oil of a standard for example, but preferably with the lubricant oil of motor as hydraulic fluid, and system carries from the oil sump of motor.
Internal-combustion engine can be a middling speed four stroke engine, but generally is a low speed two stroke crosshead motors, and this motor can advance fixing prime mover of an engine or a power station as one on the steamer.This motor can be designed to cylinder output from 400kw (kilowatt) to the various sizes of 5500kw, and its for example under full load, can have 200rpm from the minimum dimension motor (rev/min) to the various speed of the 60rpm scope of overall dimensions motor.Under the specific fuel consumption in usually from 160g/kwh (gram/kilowatt hour) to the 185g/kwh interval, about 250g variation that the required fuel quantity of each emission sequence can be from about 6g (gram) of minimum dimension motor to the overall dimensions motor under full load.Petrolift according to the present invention is particularly suitable for jumbo injection, and for example each sequence surpasses the injection of 30g fuel capacity under full load.
The high-voltage tube that connects from pumping plant is installed in the side of carriage 3, and in the end face upper support distributor block 2 of carriage 3.One pressure tube 4 extends to the actuator of outlet valve from distributor block.Several, for example 3 pressure tubes 5 extend to sparger 6 from petrolift 1, these spargers 6 inject fuel in the burning cavity of engine cylinder 7.The lower protruding edge 8 of pressure tube is threadingly attached on the pump 1.
Each cylinder of motor all links to each other with an electronic control unit 9, and wherein electronic control unit 9 receives total synchronous and control signal through electric wire 10, and these electronic control signals are sent to a for example control valve 11 through an electric wire 12.Control unit can receive the signal of relevant controlling valve present position from control valve through an electric wire 13.Cylinder can have a control unit 9, and each or several cylinder can link to each other with same control unit.This control unit also can receive come from all these cylinders the signal of a shared Master Control Unit.
On carriage, the hydraulic fluid of pressurization is transported to a high-pressure mouth on the control valve 11 from a passage 14 of high-voltage tube branch.Passage 14 is provided with a plurality of fluid accumulation of energy accumulator 15, and these accumulation of energy accumulator 15 are carried most of Fluid Volumes when control valve is opened, and can carry from the high-voltage tube secondary when control valve is closed.On the control valve the one control relatively short passage 16 mouthful in distributor block is connected to the exhaust port on the end face 17 of piece.
Control valve also has a reservoir port, and this reservoir port is connected to a return tube that is used for hydraulic fluid through a passage 18.Pressure in the return tube can be in being pressed onto residual pressure (overpressure) scope of several crust from atmosphere.
When the petrolift starting fuel is carried, from a control signal of control unit 9 with regard to actuator control valve 11 to the position that high-pressure mouth and control mouth are linked to each other, thereby high-pressure liquid can freely arrive exhaust port through passage 16.When the delivery stroke of pump stopped, control valve was actuated to the position that reservoir port is linked to each other with the control mouth, thereby released the high pressure in the passage 16.
Therefore, control valve 11 has at least 3 mouths and at least 2 positions.It can have rapid-action elder generation slider guide, and a master slider is set on this guide's slide block hydraulic ground.Control valve can be the type described in for example claimant's No. the 170121st, the Danish Patent.
The end face of petrolift 1 is lifted to and engine cylinder cover 19 about same height by carriage 3, thereby the length of pressure tube 5 can shorten, and thereby can advantageously only need a spot of fuel of pressurization when each injection of starting.Petrolift keeps from a fuel pipe 20 transfer the fuels, and wherein fuel pipe 20 distributes fuel by a backing pump to petrolift, and this backing pump has a residual pressure in from 4 to 15 crust scopes usually, generally is residual pressure at 8 crust.One branched pipe 21 extends to a fuel inlet 22 shown in Figure 2 from fuel pipe.Pump is also connected to an eduction gear 23 of removing fuel leak.
Petrolift comprises two piston-cylinder units, i.e. an actuator cylinder 24 and a pumping cylinder 25, they are spaced from each other by an intermediary element 26, and the lower surface of this intermediary element 26 is resisted against on the ring surface that makes progress of end face of actuator cylinder, and its lower surface then is resisted against on the downward ring surface of pumping cylinder.This intermediary element is annular and general cylindrical shape, and has the relative small wall thickness less than half of the wall thickness of two cylinders.This intermediary element is fixed on two cylinders by the screw 27 of less processing, thereby these three parts that will constitute housing when pump moves link together.
Pumping cylinder 25 has the cylindrical lower part section 28 and a upper segment 29 of a circular, and this upper segment 28 has a remarkable external diameter greater than lower section.Be used to be resisted against downward ring surface on the intermediary element 26 and be that lower surface by the radially projection of upper segment forms and adjacent the outside that is positioned at lower section 28, thereby, make the top of the Duan Zaiqi of this cylindrical external surface and bottom locate wiper seal on the internal surface of intermediary element by two O shape circles 29 in the groove that is arranged at the lower section outer surface.
Between these two axially spaced pressure seals, the outer surface of lower section has a recess, the common annular chamber 30 that limits of the internal surface of itself and intermediary element, this annular chamber partly links to each other with fuel delivery port 22, partly link to each other with discharge route 31, this discharge route 31 is connected to a unshowned Circulation pipe from annular chamber, with pre-heating fuel.One throttling arrangement 32 is positioned at the joint of Circulation pipe and is provided with a current-limiting apparatus of fuel limitation circulating load.
Installation position at the end face 17 of distributor block is provided with petrolift, thus actuator cylinder around the exhaust port setting of passage 16, and pumping cylinder is fixed on the distributor block by bonnet bolt 33, wherein bonnet bolt 33 inserts in the through hole 34 of projection of upper segment of cylinders.
One vertically movably pump piston 39 insert in the pumping cylinders, this pumping cylinder is installed around pump piston in a pressure-tight mode in its underpart section 40.This lower section through a tapered portion section continuous transition to have the internal diameter bigger than lower section 40 one above chamber section 41, and the cylinder hole the top of chamber section continuous transition to above a damping cavity 42.
Actuator piston has the upper-end surface 43 perpendicular to a plane shape of actuator longitudinal axis, and pump piston have be resisted against shown in a lower end surface 44 on the end face 43 at piston start position place.Two end faces can radially motion independently of one another between pump piston 39 and cylinder portion section 40 and under the influence of the guiding force between actuator piston 36 and the cylinder hole 35.Be to be understood that indication upwards, downward direction is for clarity sake to use, and be used for shown in the installation of petrolift, other installation method, for example side direction are installed on the vertical surface and also are fine.Direction finder also can be forward and backward or preceding and after, forward with the moving direction of preceding expression pump piston in the delivery stroke that is started.
In the chamber 45 that produces by intermediary element 26, at the top of actuator cylinder 24, a upright annular wall 46 is installed, this annular wall has the internal diameter bigger than cylinder hole 35.In the lower end of pump piston, a upwards closed cup-shaped guard shield 47 is installed, its sidewall 48 extends downwards and stretches out downwards around the outer surface of wall 46.This guard shield and wall prevent to enter in the end face of actuator piston such as the fuel and the impurity the dust particle that leak.Replace the installation (mode) of the guard shield 47 shown in the figure, wherein the guard shield among this figure is to be pressed on the taper guide face by twisting a nut that is screwed on the pump piston end, also this guard shield 47 can be tightened (interference) and be coupled on the cylindrical guide face of pump piston.A unshowned drain openings that is close to the actuator cylinder end face links to each other chamber 45 with eduction gear 23.
The thickness of guard shield sidewall 48 reduces downwards.In intermediary element 26, at the radially opposite side of sidewall 48 two sensors 49 are installed, these two sensors 49 send signal to control unit 9 through electric wire 50.These signals can be a voltage for example, and its size depends on the distance between sensor and sidewall 48 outer surfaces.Because this wall tilts, therefore when pump piston moves upward distance with regard to increase, and sensor thereby the feedback signal of relevant piston present position is provided to control unit.
One fuel input channel 51 links to each other pump chamber 52 through discharge route 31 with annular chamber 30.In the runner between discharge route 31 and pump chamber, one unidirectional (non-return) valve 53 is set, it only permits fuel to flow in the pump chamber.During backing pump pressure in the pressure in the pump chamber surpasses annular chamber 30, one-way valve is just closed, thereby and in case when the pressure in the delivery stroke end pump chamber of pump piston descends, fuel inflow under the backing pump pressure is opened and allowed to this one-way valve once more.This one-way valve is twisted to be screwed in the sidewise hole 54 of upper segment 29, brings this one-way valve can not occupy the advantage in space on the pumping cylinder end face.
Pump piston has the front-end face of a stepped shape, and this front-end face has portion's section 61 of radially outermost of an annular and radially interior portion's section 62 of central authorities, and wherein radially interior portion's section 62 is arranged on portion's section 61.Described thus pump piston has a portion's section 63 that goes up most between these two portion's sections, its height is corresponding to the height of damping cavity 42, and its external diameter then is slightly less than the internal diameter of damping cavity.
The following operation of petrolift: when control valve 11 makes pressure chamber 60 maintenances and eduction gear in the actuator, is the reservoir port of valve when linking to each other that the hydrodynamic pressure in the pressure chamber reduces to for example residual pressure of 0.5 crust.In this article, eduction gear is meant a kind of general possibility of draining employed hydraulic fluid.Therefore, this eduction gear need not have atmospheric pressure.The eduction gear that is connected to the reservoir port of valve can be pressurized to a little residual pressure, for example aforesaid 0.5 crust.When the chamber is connected to eduction gear, one-way valve opens and allow backing pump pressure fuel down to flow in the pump chamber 52, thus the pressure in the described chamber is 8 residual pressures that cling to for example.When drainage pressure is set at barometric pressure when above, the ratio of actuator piston and pump piston area must be less than the ratio of the drainage pressure in the pressure chamber of the backing pump pressure in the pump chamber and actuator, so that the downward power that acts on the pump piston surpasses the power that makes progress that acts on the actuator piston.In an illustrated embodiment, the ratio of piston area is 4: 1, and the ratio of pressure absolute value is about 6: 1.
As long as control valve is in described position, pump piston and actuator piston will be pushed away downwards by the pressure in the pump chamber, and so and the initial position shown in being moved back into, piston abut against each other and the lower surface 59 of actuator piston against the end face 17 of distributor block.
When control valve activated and when making its high-pressure mouth be connected to passage 16, the pressure in the pressure chamber 60 will increase to the pressure in the high-voltage tube suddenly, for example increase to 250 crust.Actuator piston is pushed away forward by this pressure and pump piston is driven in the pump chamber 52, wherein the increase of pressure can cause one-way valve 53 close and pressure tube 5 in pressure increase.After one of piston short motion, the fuel pressures in the pipe 5 reach the cracking pressure of sparger, and it can be 400 crust for example, and beginning fuel sprays.
Interrupt and send one when activating signal and coming switchover control valve 11 when control unit 9 makes to spray, passage 16 just reconnects on the reservoir port, and the pressure in the pressure chamber is reduced to drainage pressure fast, and the pressure in the pump chamber also is reduced to primary pump pressure simultaneously, and pump piston stops.Then, one-way valve 53 is opened, and fuel begins again in the feed pressure chamber, thereby pump piston and actuator piston are back into their initial position, can repeat this process subsequently and carry out emission sequence next time.
It should be noted that, in the return movement process, pump chamber only need be supplied with the fuel quantity corresponding to the emitted dose in preceding subsequence, and in a two-cycle engine, normally in 1/15 process of changeing of motor, spray, keep 14/15 of motor subsequently and transfer return piston, perhaps influence by same pump the injection in other cylinder.Even have less relatively total downward active force on piston, the time that piston also has abundance turns back to its fixing initial position.
Certainly, can make multiple modification to the foregoing description.For example, by to actuator cylinder setting lead to a transfer passage of pressure chamber, can design the bottom of a sealing to actuator cylinder.Can also come to provide different project organizations without further step to the end face of actuator piston, stepped shape for example, and the upright bolt of one on the actuator piston can support cup-shaped guard shield 47, loosely is resisted against effect on the guard shield end face with the lower surface that obtains pump piston.When need not the signal of relevant position, pump piston can be designed to not have guard shield.Can but do not wish can absorb in a conventional manner a housing of tension force to fuel pump design.In addition, two pumping cylinders can become whole and not have a cave, chamber of a reality, and the cylinder hole of actuator is cascade ground or tapered the cylinder hole that carries out the transition to pump for example, and to obtain short petrolift, this petrolift had not both had upright inwall, did not have guard shield in yet.If pump will be to 4 sparger transfer the fuels, then current-limiting apparatus can be similar to one-way valve and is arranged on like that in the sidewise hole.In addition, exhaust port 56 can be a side direction, thereby pressure tube 5 is installed on the sidewall of pump.And, petrolift can be mounted to actuator cylinder is positioned on the pumping cylinder, and can omit annular wall 46 and cup-shaped guard shield 47 simultaneously, because can be to possibility dirty and that mix with the hydraulic fluid that leaks without any the fuel oil that leaks, wherein the fuel oil of Guo Louing be excreted in the oil sump of diesel engine usually.Petrolift also can be arranged under the distributor or be other or other is local, for example is arranged on the cylinder cap 19.
Claims (12)
1. be used to operate an internal-combustion engine, a kind of method of the petrolift (1) of a hydraulic actuating of one or two stroke crosshead motor especially, wherein petrolift has a fuel pipe (20) that is used under backing pump pressure fuel being distributed to petrolift; With a high-voltage tube that is used for a pressurized hydraulic fluid that is different from fuel is distributed to petrolift; Pump piston (39) in petrolift, it drives forwards by the actuator piston (36) in an actuator cylinder (24) in a delivery stroke, meanwhile from a pump chamber (52), extrude fuel, and in a return stroke to rear driving, meanwhile inject fuel to pump chamber from fuel pipe; With the actuator piston of being controlled by an electronically actuated control valve (11), the pressure chamber in the actuator cylinder can provide hydraulic fluid or be connected to an eduction gear from high-voltage tube thus, it is characterized in that:
Between each emission sequence, end face (61 by the pump piston in the pump chamber (52), the effect of the fuel pressure 62), pump piston (39) turns back to a fixing initial position, and the quantity delivered of petrolift is by when pump piston has been carried required capacity, and control valve (11) cuts off the control electronically that transports to the hydraulic fluid of pressure chamber.
2. the method for claim 1 is characterized in that:
One electronic control unit (9) opens or closes petrolift and carry an additional capacity under same engine load, should additional capacity be under described engine load fuel quantity 1～60%, and meanwhile this fuel mixes with water corresponding to additional capacity.
3. be used for an internal-combustion engine, the petrolift of a hydraulic actuating of a two-stroke diesel engine particularly, comprise a pump piston (39), it can longitudinally move in a pump chamber (29) and have a front-end face, this front-end face limits a pump chamber (52) with pumping cylinder; With an actuator piston (36), it is positioned at the extended position of pump piston and can longitudinally moves in actuator cylinder (24), and has a piston face (59), this piston face is positioned at a pressure chamber, deviates from pump piston and has an area more much bigger than the cross sectional area of pump piston, and this pump piston relaxes with respect to actuator piston; At least one the fuel input channel (51) that has an one-way valve (53) is led to pump chamber; Draw and lead at least one exhaust port from pump chamber with at least one fuel output channel (55), it is characterized in that:
Pumping cylinder (25) and actuator cylinder (24) are unit independently, they are spaced from each other by annular intermediate isolating parts (26), and pumping cylinder has a lower section (28) that projects in the isolating part downwards, with with respect to this lower section upper segment (29) of projection radially, and they are installed by bonnet bolt (33).
4. the petrolift of hydraulic actuating as claimed in claim 3 is characterized in that:
Pump piston (39) is radially carrying out unique guiding by the cylinder hole that matches in the pumping cylinder (25), actuator piston (36) is radially carrying out unique guiding by the cylinder hole (35) in the actuator cylinder that matches, and these two pistons can radially freely regulated mutually.
5. as the petrolift of claim 3 or 4 described hydraulic actuatings, it is characterized in that:
Actuator cylinder (24) is an annular element that has a cylinder hole (35) that axially connects, and petrolift is installed on the end face (17) of a distributor block (2), the cylinder hole (35) of actuator cylinder is positioned at the middle extending part of an exhaust port of distributor block end face, thereby pressure chamber is radially limited by actuator cylinder and axially limited by the piston face of actuator piston and the end face of distributor block respectively.
6. as the petrolift of arbitrary described hydraulic actuating of claim 3～5, it is characterized in that:
The outer surface of the lower section of cylinder (28) is provided with an annular notch, this outer surface its top and bottom with respect to around the internal surface wiper seal of intermediate member (26), fuel inlet (22) in the wall of intermediate member is introduced in the annular chamber (30) that is formed by recess and intermediate member, and a discharge route (31) that has a current-limiting apparatus that reduces pressure is connected to this annular chamber continuously.
7. as the petrolift of arbitrary described hydraulic actuating of claim 3～6, it is characterized in that:
On the end face of actuator cylinder (24), has a upright annular wall (46), this annular wall has an internal diameter bigger than the cylinder hole of actuator cylinder, and one upwards the cup-shaped guard shield (47) of sealing be arranged on the lower end with a certain distance from the lower surface of the pumping cylinder that extends around annular wall of pump piston (39) downwards.
8. the petrolift of hydraulic actuating as claimed in claim 7 is characterized in that:
The wall thickness of cup-shaped guard shield (47) reduces downwards, and at least two sensors (49) are installed in the opposite side that is positioned at guard shield in the intermediate member, with the present position of testing pump piston (39).
9. as the petrolift of arbitrary described hydraulic actuating of claim 3～8, it is characterized in that:
Pumping cylinder has with the lower section (40) of a pressure-tight mode around pump piston (39) assembling, with a chamber section (41) with internal diameter bigger than this lower section, fuel input channel (51) is led to the sidewall of chamber section, and at least two fuel output channels (55) are drawn from the sidewall of chamber section.
10. the petrolift of hydraulic actuating as claimed in claim 9 is characterized in that:
Fuel output channel (55) is connected to exhaust port (56) upwards, and the flange (8) that is used to lead to the pressure tube (5) of fuel injector (6) is installed in the end face of the upper segment of pumping cylinder.
11. the petrolift as claim 9 or 10 described hydraulic actuatings is characterized in that:
The above zone of the chamber section (41) of pumping cylinder (25) has a portion's section than minor diameter, it constitutes a damping cavity (42) of upwards sealing, and pump piston has a portion's section (63) that goes up most, the diameter that its height is slightly less than damping cavity corresponding to height and its external diameter of damping cavity.
12. the petrolift as arbitrary described hydraulic actuating of claim 3～11 is characterized in that:
Actuator piston (36) has the groove (37) near its lower surface, and a retainer (38) that is installed in the wall of actuator cylinder stretches in this groove.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK199700611A DK173815B1 (en) | 1997-05-28 | 1997-05-28 | Hydraulically activated fuel pump for an internal combustion engine |
| DK0611/97 | 1997-05-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1256742A true CN1256742A (en) | 2000-06-14 |
| CN1089401C CN1089401C (en) | 2002-08-21 |
Family
ID=8095544
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98805230A Expired - Fee Related CN1089401C (en) | 1997-05-28 | 1998-05-27 | Method for operation of hydraulically actuated fuel pump for internal combustion engine, and hydraulically actuated fuel pump |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1015758B1 (en) |
| JP (1) | JP3519089B2 (en) |
| KR (1) | KR100440829B1 (en) |
| CN (1) | CN1089401C (en) |
| AU (1) | AU7639398A (en) |
| DK (1) | DK173815B1 (en) |
| WO (1) | WO1998054461A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107435619A (en) * | 2016-05-26 | 2017-12-05 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Petrolift or lubricating pump for large-sized two-stroke compression-ignition engine |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1143138A1 (en) * | 2000-04-03 | 2001-10-10 | Wärtsilä NSD Schweiz AG | Fuel injection pump |
| JP4318266B2 (en) * | 2007-03-30 | 2009-08-19 | エムエーエヌ・ディーゼル・フィリアル・アフ・エムエーエヌ・ディーゼル・エスイー・ティスクランド | Cam-driven fuel injection system for large two-cycle diesel engines |
| DE102013214484A1 (en) * | 2013-07-24 | 2015-01-29 | Bayerische Motoren Werke Aktiengesellschaft | Fuel pump unit |
| JP6193291B2 (en) | 2015-04-13 | 2017-09-06 | 三井造船株式会社 | Fuel supply device |
| JP5934409B1 (en) * | 2015-04-13 | 2016-06-15 | 三井造船株式会社 | Fuel supply device |
| JP5953395B1 (en) * | 2015-04-13 | 2016-07-20 | 三井造船株式会社 | Fuel supply device |
| DE102015016925A1 (en) * | 2015-12-24 | 2017-06-29 | Audi Ag | Fuel pump |
| JP6568613B1 (en) * | 2018-03-09 | 2019-08-28 | 株式会社ジャパンエンジンコーポレーション | Water injection pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1522293A (en) * | 1967-02-22 | 1968-04-26 | Fuel injection device for internal combustion engines | |
| DE2617841A1 (en) * | 1976-04-23 | 1977-11-03 | Kloeckner Humboldt Deutz Ag | FUEL INJECTION DEVICE |
| US4418670A (en) * | 1980-10-10 | 1983-12-06 | Lucas Industries Limited | Fuel injection pumping apparatus |
| DK170121B1 (en) * | 1993-06-04 | 1995-05-29 | Man B & W Diesel Gmbh | Sliding valve and large two stroke internal combustion engine |
-
1997
- 1997-05-28 DK DK199700611A patent/DK173815B1/en not_active IP Right Cessation
-
1998
- 1998-05-27 KR KR10-1999-7010871A patent/KR100440829B1/en not_active IP Right Cessation
- 1998-05-27 AU AU76393/98A patent/AU7639398A/en not_active Abandoned
- 1998-05-27 WO PCT/DK1998/000217 patent/WO1998054461A1/en active IP Right Grant
- 1998-05-27 JP JP50012699A patent/JP3519089B2/en not_active Expired - Fee Related
- 1998-05-27 CN CN98805230A patent/CN1089401C/en not_active Expired - Fee Related
- 1998-05-27 EP EP98924062A patent/EP1015758B1/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107435619A (en) * | 2016-05-26 | 2017-12-05 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Petrolift or lubricating pump for large-sized two-stroke compression-ignition engine |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20010012904A (en) | 2001-02-26 |
| JP2001526755A (en) | 2001-12-18 |
| WO1998054461A8 (en) | 1999-04-08 |
| EP1015758B1 (en) | 2003-09-17 |
| JP3519089B2 (en) | 2004-04-12 |
| WO1998054461A1 (en) | 1998-12-03 |
| DK61197A (en) | 1997-06-24 |
| DK173815B1 (en) | 2001-11-12 |
| AU7639398A (en) | 1998-12-30 |
| CN1089401C (en) | 2002-08-21 |
| EP1015758A1 (en) | 2000-07-05 |
| KR100440829B1 (en) | 2004-07-19 |
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