EP1171707B1 - Pumpe mit variabler fördermenge und ihre verwendung in einem common-rail-kraftstoffeinspritzsystem - Google Patents

Pumpe mit variabler fördermenge und ihre verwendung in einem common-rail-kraftstoffeinspritzsystem Download PDF

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Publication number
EP1171707B1
EP1171707B1 EP00923379A EP00923379A EP1171707B1 EP 1171707 B1 EP1171707 B1 EP 1171707B1 EP 00923379 A EP00923379 A EP 00923379A EP 00923379 A EP00923379 A EP 00923379A EP 1171707 B1 EP1171707 B1 EP 1171707B1
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EP
European Patent Office
Prior art keywords
pump
plunger
sleeve
valve
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00923379A
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English (en)
French (fr)
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EP1171707A1 (de
Inventor
Dennis H. Gibson
Mark F. Sommars
James R. Blass
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Caterpillar Inc
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Caterpillar Inc
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Publication date
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Publication of EP1171707A1 publication Critical patent/EP1171707A1/de
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Classifications

    • 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
    • F02M59/46—Valves
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/15—By-passing over the pump

Definitions

  • This invention relates to a common rail fuel injection system and method of controlling the output from a sleeve metered pump.
  • high pressure actuation fluid is used to power electronic unit injectors, and the actuation fluid is supplied to the injectors from a high pressure fluid accumulator, which is referred to as a rail.
  • a rail high pressure fluid accumulator
  • Known common rail systems typically rely on either a single fluid pump that supplies fluid to the rail or a plurality of smaller displacement pumps that each supplies fluid to the rail.
  • the volume and rate of fluid delivery to the rail has been varied in the past by providing a rail pressure control valve that spills a portion of the delivery from a fixed delivery pump to maintain the desired rail pressure.
  • variable delivery pumps are well known in the art and are typically more efficient for common rail fuel systems than a fixed delivery actuation fluid pump, since only the volume of fluid need to attain the desired rail pressure must be pumped.
  • variable delivery has been achieved from an axial piston pump, e.g. a pump wherein one or more pistons are reciprocated by rotation of an angled swash plate, by varying the angle of the swash plate and thus varying the displacement of the pump.
  • the swash plate is referred to as a "wobble plate”.
  • Variable delivery has also been achieved in fixed displacement, axial piston pumps by a technique known as sleeve metering, in which each piston is provided with a vent port that is selectively closed by a sleeve during part of the piston stroke to vary the effective pumping portion of the piston stroke.
  • variable delivery pump designs are suitable for many purposes, known designs are not always well suited for use with modern hydraulically actuated fuel systems, which require fluid delivery to the rail to be varied with high precision and with rapid response times measured in microseconds.
  • known variable delivery pumps designs are typically complex, may be costly, and are subject to mechanical failure.
  • EP 0 307 947 A shows a variable discharge fixed displacement high pressure pump that utilizes an electronically actuated pressure latching valve in order to control output from the pump.
  • fluid from the pumping chamber can either be displaced back to the inlet or out of the outlet.
  • an electronically actuated spill valve can be actuated to close the spill passage between the pump chamber and the inlet to the pump.
  • pressure in the pumping chamber quickly rises, and the spill valve includes a closing hydraulic surface that holds it closed due to the high pressure in the pumping chamber.
  • the valve is closed, the fluid exits the pump through the outlet at high pressure.
  • the solenoid can be deenergized and the valve will remain in its closed position. While the concept of using a pressure latching valve can be beneficial from the standpoint of conserving electrical energy, the above prior art pump suffers from a number of drawbacks.
  • the spill valve must necessarily have a relatively large and heavy valve member, and a relatively long travel distance in order to have a sufficiently large flow area when the valve is in its open position. The result of this is to require a relatively large and strong solenoid, and acceptance of relatively long response times that are required to move the valve from its open position to its closed position. Because such a structure inherently causes conflicts between the control requirements and the flow requirements, the performance capabilities of the same must necessarily be compromised.
  • US 5,630,609 A shows a fixed displacement swash plate type pump that achieves variable output via sleeve metering.
  • the sleeve metering mechanism of this prior art appears to utilize a hydraulic force that is balanced against a spring force to adjust the position of the sleeve.
  • the positions of the metering sleeves are sensed and then fluid pressure is adjusted to move the sleeves to a different desired output position.
  • This prior art pump appears to suffer from several drawbacks, including its complex control strategy, which would appear to be accompanied by relatively difficult problems in calibrating control signals with desired outputs from the pump.
  • US 4 526 145 A discloses a pair of solenoids are disposed coaxially with and around a hollow cylindrical cut-off valve.
  • the valve includes an inner non-magnetic sleeve and an outer permanent magnet sleeve.
  • the cut-off valve slidably engages a fuel distributing plunger which injects fuel according to its axial reciprocation.
  • the cut-off valve controls fuel injection quantity via timing of exposure of a fuel injection cut-off port in the plunger.
  • a pair of disc-like permanent magnets may be disposed opposite either extreme of travel of the cut-off valve in spaced relationship thereto.
  • a pair of non-magnetic discs may be disposed in place of the pair of disc-like permanent magnets.
  • a biasing member may be disposed between the cut-off valve and the plunger housing to prevent the cut-off valve from being attracted by the plunger housing and for preventing rotation of the cut-off valve relative to the plunger housing.
  • the biasing member may be diaphragm, coil spring or a leaf spring.
  • US 4 480 619 A discloses a flow control device advantageously used in a fuel injection system for a diesel engine.
  • the flow control device includes a spool valve defining on its sides first and second chambers which are connected with each other by means of a throttle.
  • the second chamber is connected to a high pressure pipeline connecting a fuel pump with a fuel injector, while the first chamber is selectively opened to a relief line by means of an electrically operated valve.
  • a cylinder has an annular groove opened to the relief line. When the valve is opened, the first chamber is opened to the relief line. A pressure difference is thus created between the first and the second chambers so as to move the spool valve to open. Thus fuel injection is stopped.
  • US 5 404 855 A discloses a variable displacement high pressure pump having a plurality of high pressure pumping units which receive fuel from a low pressure fuel pump.
  • a rotary cam-driven roller tappet for producing pumping displacement of the pumping plunger of a respective pumping element, is connected to the pumping plunger by a separated link in a manner permitting the pumping plunger to float relative to the roller tappet during at least a portion of each pumping cycle.
  • the capacity of the pumping chamber can be limited to an extent that is less than the full stroke achievable by the pumping plunger being retracted to the maximum extent which is permitted by the driving cam.
  • the quantity of fuel to be pressurized and injected into the common rail does not have to be determined by a cutting-off of a spilling flow of excess metered fuel during the compression stroke of the pumping plunger, so that a low pressure solenoid valve can be used, in the case of time-stroke and time-pressure metering, and no solenoid is required to control metering in the case of pressure-time metering.
  • This invention is directed to overcoming one or more of the problems described above.
  • a fuel injection system is provided as set forth in claim 4.
  • Preferred embodiments of the present invention may be gathered from the dependent claims.
  • a fuel injection system generally designated 20 for an internal combustion engine 22 (FIG. 2) comprises a plurality of unit injectors 24, which may be conventional but are preferably unit injectors having a nozzle check valve operable independent of injection pressure.
  • the preferred unit injectors are powered by pressurized engine oil, however those skilled in the art will recognize that this invention is equally applicable to common rail systems that use high pressure fuel to power the unit injector.
  • an intensified injector system is preferred, although this invention is also equally applicable to non-intensified injector systems.
  • the fuel system 20 further includes a plurality of variable delivery, reciprocating piston unit pumps 26, which supply high pressure fluid to a common high pressure fluid accumulator or rail 28.
  • the injector actuation fluid is pressurized engine oil
  • oil is drawn from a sump or tank 30 in the engine 22 via an engine lube pump 32 and pumped through an oil filter 34 to the main engine oil gallery 36.
  • Each unit pump 26 draws oil from the engine oil gallery 36 and pumps high pressure oil to the common high pressure rail 28.
  • unit pumps 26 drawing fluid from gallery 36, they could instead draw fluid directly from sump 30 or any other suitable source of fluid.
  • oil from the sump 30 is also delivered to an elevated reservoir 38, which delivers fluid to the high pressure rail 28 via a check valve 40 for thermal make-up under low temperature conditions.
  • An associated camshaft 42 internal to the engine 22 drives each of the unit pumps 26, and the camshaft 42 is driven by the crankshaft 44 of the engine 22.
  • the illustrated camshaft 42 have three lobes 46 at the location of each unit pump 26, but it will be recognized that the camshaft 42 may be provided with more or less than three lobes 46 as appropriate for the particular application. In the illustrated embodiment, each unit pump 26 will undergo three pumping strokes per revolution of the camshaft 42.
  • Pressure in the high pressure rail 28 is monitored by a conventional pressure sensor 48, which provides an electronic pressure signal to a suitable, conventional electronic control module (ECM) 50. Based on the sensed rail pressure and the desired rail pressure, the ECM 50 determines whether to raise or lower the pressure in rail 28, as the case may be.
  • the pressure in the rail 28 is varied by varying the rate of delivery of fluid to the rail 28 from one or more of the unit pumps 26. In general, the delivery from each unit pump 26 is varied by adjusting the effective pumping stroke of the unit pump 26, which is the duration during each compression stroke thereof that fluid is pumped through the outlet of the unit pump 26 instead of back to the engine oil gallery 36 or the sump 30 as will be discussed below.
  • the effective pumping stroke of each unit pump 26 is related to the angular or rotary position of the camshaft 42 at the beginning of the effective pumping stroke and thus the angular position of the crankshaft 44 at the beginning of the effective pumping stroke.
  • the rotary position of the crankshaft 44 is provided to the ECM 50 via a conventional timing sensor 44A, and based on the required change in rail pressure, if any, determined by the ECM 50, the ECM 50 adjusts the effective pumping stroke of one or more of the unit pumps 26.
  • FIG. 2 illustrates a fragmentary portion of one cylinder of the internal combustion engine 22, which in this case is a diesel engine.
  • the engine 22 which may be conventional, includes a block 52 that defines one or more cylinders 54, only one of which is shown.
  • a piston 56 reciprocates within the cylinder 54 and drives the crankshaft 44 via a connecting rod 58.
  • the unit pump 26 is disposed within the block 54 and driven by the camshaft 42.
  • FIG. 2 also illustrates one of the unit injectors 24 mounted in the head 60 of the engine 22, in which the high pressure fluid rail 28 is formed.
  • the rail 28 may alternatively be a vessel separate from the head 60.
  • FIG. 3 illustrates one embodiment of a unit pump 26 in greater detail.
  • the unit pump 26 comprises a barrel 62 having an inlet 64 and an outlet 66 communicating with a pump chamber 68 formed within the barrel 62.
  • the pump chamber 68 includes a cylindrical portion 70 that receives a piston or plunger 72.
  • a follower guide 74 is attached to the barrel 62 concentric with the plunger 72, and a follower assembly, generally designated 76, is slidable within the follower guide 74.
  • barrel 62 and follower guide 74 can be considered the pump housing.
  • the follower assembly 76 comprises a roller follower 78 rotatably mounted to a cylindrical guide block 80. While a roller follower is preferred, other suitable followers may also be used.
  • the plunger 72 is provided with a flange 82 at its lower end, which engages the guide block 80.
  • a spring or other suitable bias member 84 is disposed between the flange 82 and the barrel 62 to bias the plunger 72 and guide block 80 downward.
  • the roller follower 78 travels along the surface of the cam lobes 46 as the camshaft 42 rotates, causing the plunger 72 to be driven upwardly within the barrel 62 as the roller follower 78 travels along the upward slope of each lobe 46.
  • the spring 84 biases the roller follower 78 against the cam lobe 46 and the plunger 72 is drawn downwardly within the barrel 62.
  • the downward stroke of the plunger 72 is the intake stroke of the unit pump 26, which draws fluid into the pump chamber 68 from the inlet 64 through a spring-biased inlet check valve 86.
  • the plunger 72 is driven upwardly through its compression or pumping stroke.
  • the inlet check valve 86 is forced closed so that fluid in the pump chamber 68 is pumped either through a spring-biased outlet check valve 88 or through solenoid-controlled, pilot operated by-pass valve, generally designated 90, which will be described below in greater detail. Oil pumped through the outlet check valve 88 is delivered through the outlet 66 to the high pressure rail 28.
  • the by-pass valve 90 is formed in part by the barrel 62, which has an outlet 92, which also serves as the primary inlet port 94 of the valve 90.
  • the inlet 94 opens to a cavity 96 defined by the barrel 62, and a passageway 98 extends from the cavity 96 to the inlet 64 of the unit pump 26.
  • the passageway 98 forms a primary outlet port 100 of the by-pass valve 90.
  • a thimble-like primary valve closure member 102 is disposed in confronting relationship with the primary inlet port 94, and upwardly extending walls of the primary closure member 102 are slidably received within a bore 104 in a secondary valve block 106, which is located atop the barrel 62 and seals the upper margin of the cavity 96.
  • the bore 104 of the secondary valve block 106 extends through the block 106 from top to bottom, and a passageway 108 in the block extends from the bore 104 back to the cavity 96.
  • a secondary closure member 110 is disposed within the bore 104 in the secondary valve block 106 between the primary valve closure member 102 and the open upper end of the bore 104.
  • the secondary valve closure member 110 includes a stem 112 extending from the bore 104 and connected with an armature 114 of a solenoid assembly, generally designated 116.
  • the solenoid assembly 116 also includes a solenoid coil 118 mounted to a housing 120 fastened to the upper end of the barrel 62.
  • a cover or cap 122 is secured to the top of the housing 120 to enclose the solenoid assembly 116.
  • Activation of the solenoid coil 118 moves the secondary closure member 110 to close the bore 104, whereby a portion of the bore 104 in the valve block 106, the primary closure member 102, and the secondary closure member 110(when the solenoid assembly 116 is activated) define a pressure chamber 124, which will be described in greater detail below.
  • An orifice 126 is provided in the face of the primary valve closure member 102 in the portion thereof that confronts the by-pass valve inlet port 94, and a spring 128 is disposed between the primary closure member 102 and a confronting wall of the bore 104 to bias the primary closure member 102 downwardly.
  • Spring 128 is preferably relatively weak, and likely could be eliminated except when the pump is oriented upside down from the orientation shown, where gravity could not be relied upon to bias it toward its seated position.
  • the orifice 126 provides a conduit from the pump chamber 68 to the pressure chamber 24, and may be replaced by a passageway (not shown) between the pump chamber 68 and the pressure chamber 124 that is separate from the primary closure member 102.
  • FIG. 3 illustrates the valve 90 in its inactivated state with plunge 72 beginning its pumping stroke, in which the primary closure member 102 is lifted to open cavity 96 to primary inlet port 94.
  • Fig. 4 shows valve 90 in its closed pumping position.
  • pressure builds within the pump chamber 68, and that pressure forces the primary closure member 102 upward, opening the primary inlet port 94 to the cavity 96 and permitting fluid from the pump chamber 68 to pass through the cavity 96, into the passageway 98, and back to the inlet 64 of the unit pump 26.
  • Fluid also flows through the orifice 126 in the primary closure member 102, around the secondary closure member 110, into the passageway 108 in the secondary valve block 106, and back to the cavity 96, where it can then travel through the passageway 98 and back to the unit pump inlet 64.
  • Orifice 126 preferably has a flow area such that when plunger 72 is undergoing its pumping stroke a pressure gradient between pump chamber 68 and pressure chamber 124 is sufficient to cause primary closure 102 to lift to its open position, as shown in Fig. 3. If orifice 126 is made to large, the pressure gradient phenomenon necessary to lift primary closure member 102 to its upper open position might not occur.
  • the flow area past secondary closure member 110 should preferably be large enough to accommodate whatever relatively small amount of fluid flow occurs through orifice 126 so that the necessary pressure gradients to cause the valve to perform in its preferred manner can develop.
  • by-pass valve 90 When by-pass valve 90 is open, no fluid is pumped through outlet check valve 88 since the path through the by-pass valve 90 is the path of least resistance.
  • the opening hydraulic surface area of the primary closure member 102 directly confronting the primary inlet port 94 is smaller than opposing or closing hydraulic surface area within the pressure chamber 124. Consequently, a greater force is applied to the primary closure member 102 from the pressure chamber 124 than from the primary inlet port 94, and the primary closure member 102 is forced downwardly to seal the primary inlet port 94.
  • the armature 114 and secondary valve closure member are biased downwardly by a spring or other bias member 115. Once the pressure within the pressure chamber 124 is sufficient to resist the spring force of spring 115, current to the solenoid coil can be interrupted.
  • Pressure within the pressure chamber 124 will then hold the Secondary closure member 110 in its raised position to close passageway 108 and hold primary closure member 102 in its downward position so that the primary inlet port 94 remains sealed even without current being applied to the solenoid coil 118.
  • the pressure within the pressure chamber 124 effectively latches the primary closure member 102 and secondary closure member 110 in their respective sealing positions.
  • the illustrated by-pass valve 90 is electrically actuated by use of a solenoid assembly 116.
  • actuators may be operably coupled to momentarily raise the secondary closure member 112 to create the pressure chamber 124 in the valve 90.
  • a suitable piezo-electric actuator (not shown) may be used in place of the solenoid assembly 116.
  • Other electrically operated actuators may also be used as well as pilot operated hydraulic actuators.
  • the secondary valve closure member 110 may itself form the armature of the solenoid assembly 116 or may be an integral part of the armature.
  • FIG. 5 illustrates another embodiment of a unit pump, generally designated 226, in accordance with this invention utilizing the electrically actuated, pilot operated by-pass valve 90 described above.
  • the by-pass valve 90 is shown diagrammatically in FIG. 5.
  • the unit pump 226 illustrated in FIG. 5 is constructed similarly to the unit pump 26 illustrated in FIG. 4, and like components, although configured differently, are identified by like reference numbers increased by 200.
  • FIG. 6 illustrates yet another embodiment of a unit pump, generally designated 326, in accordance with this invention utilizing the electrically actuated, pilot operated by-pass valve 90 substantially identical to the by-pass valve 90 described above.
  • the unit pump 326 differs from the unit pumps 26 and 226 in that the unit pump 326 utilizes a hollow plunger 372 having a cavity 372A therein open at its upper end and selectively closed by a plunger-mounted check valve 386, and the inlets 364 to the unit pump 326 open to the hollow interior 372A of the plunger 372.
  • the plunger mounted check valve 386 has a stem 386A which extends within the cavity 372A, and a spring 386B is disposed between a flange 372B extending around the inside diameter of the plunger 372 and an upwardly-facing surface at the lower end of the stem 386A.
  • the bias spring 386B normally positions the plunger mounted check valve 386 such that the sealing portion 387 is pulled downwardly against the open upper end of the plunger 372.
  • fluid is drawn into the plunger 372 and vacuum pressure in the pump chamber 368 opens the plunger mounted check valve 386.
  • fluid flows from the plunger cavity 372A to the pump chamber 368.
  • FIGS. 7 and 8 illustrate a multiple piston (plunger) radial pump, generally designated 400, that is provided with multiple electrically actuated, pilot operated by-pass valves 402 as described above with regard to valve 90, namely one by-pass valve 402 associated with each piston 404.
  • the radial piston pump 400 may be of conventional design except for the use of the by-pass valves 402 in accordance with this invention.
  • the radial pump 400 includes a pump housing 406 that defines a plurality of radially-extending cylinders 408.
  • a rotating camshaft 410 extends centrally through the housing 406.
  • the camshaft 410 includes an eccentric cam portion 412 to which a plurality of plungers 414 are attached by conventional shoe assembly 416 disposed in corresponding ones of the cylinders 408.
  • Each of the cylinders 408 is closed at its radially-outer end by a plug 310.
  • rotation of the camshaft 410 causes the plungers 414 to reciprocate within their corresponding cylinders 408.
  • the camshaft 410 has an input gear 420 connected for rotation therewith at its free, outer end 422.
  • a single radial pump 400 replaces the plural unit pumps 26 and the input gear 420 is driven by a drive gear (not shown) connected with the engine crankshaft 44.
  • a drive gear (not shown) connected with the engine crankshaft 44.
  • rotation of the crankshaft 44 is imparted to the camshaft 410 of the radial pump 40.
  • the camshaft 410 is similarly rotated by a suitable drive motor (not shown) or other input device.
  • each plunger 414 During the downward stroke of each plunger 414, that plunger 414 overlies an inlet slot 424 in the eccentric cam portion 412 that opens to a counterbore 426 in the camshaft 410.
  • the counterbore 54 is in fluid communication with a supply of fluid, such as the engine oil gallery 36 (FIG. 1) described above, so that fluid is drawn through the counterbore 426 and slot 424 and into the plunger 414 and cylinder 408.
  • the plunger 414 During the upward or compression stroke of each plunger 414, the plunger 414 is not aligned with the inlet slot so that the cylinder 408 is not open to the counterbore 426.
  • fluid previously drawn into the plunger 414 is pumped either through its associated by-pass valve 402 and back to the fluid supply via a return passageway (not shown) or to a circumferential outlet gallery 428 through an outlet check valve 430.
  • high pressure fluid from the delivery gallery 428 is then delivered through an outlet 432 to a hydraulically powered device, such as the common rail 28 of the fuel system 20.
  • each plunger 414 may have a dedicated delivery gallery, which may be selectively interconnected with other ones of the delivery galleries, so that the radial pump 400 can be operated as one multi-piston, variable delivery pump, or as plural multi-piston, variable delivery pumps, or even as plural single piston, variable delivery pumps.
  • the pump 400 may alternatively be configured such that only one or some of the plungers 414 has a by-pass valve 402 to provide variable delivery, in which case variable delivery from the pump 402 is still achieved but with a smaller delivery range.
  • FIG. 9 diagrammatically illustrates another embodiment of a pump, generally designated 500, in accordance with this invention.
  • the pump 500 is a multi-piston axial pump (with only one piston illustrated), which may be of any conventional design except that the outlet of each plunger 502 is provided with an electrically-controlled, pilot operated valve 504 as described above with respect to pump 90, including a solenoid or other actuator 506.
  • the axial pump 500 includes an angled, rotating swash plate 508 that reciprocates the plunger(s) 502 within a cylinder 510 in a well known manner.
  • the valve 504 in accordance with this invention controls flow to the outlet collector 512 through main inlet/outlet valve 514 in the manner described above.
  • the fewer than all of the plungers 502 of the axial pump 500 may be provided with by-pass valves 504, and each plunger 502 may pump fluid to a dedicated delivery gallery (not shown) that may be selectively interconnected with the delivery galleries of the other plungers 502.
  • FIG. 10 illustrates still another embodiment of a cam operated unit pump, generally designated 626.
  • the unit pump 626 comprises a barrel 662 having an inlet 664 and an outlet 666 communicating with a pump chamber 668 formed within the barrel 662.
  • the inlet 664 is normally closed by a spring-biased check valve 664A and the outlet 666 is normally closed by a spring-biased check valve 666A.
  • a hollow piston or plunger 672 is received within a portion of the pump chamber 668 and reciprocal therein.
  • a follower guide 674 is attached to the barrel 662 concentric with the plunger 672, and a follower assembly, generally designated 676, is slidable within the follower guide 674.
  • barrel 662 and follower guide 674 can be thought of as a pump housing.
  • the follower assembly 676 comprises a roller follower 678 rotatably mounted to a cylindrical guide block 680. While a roller follower is preferred, other suitable followers may also be used.
  • the plunger 672 has a flange 682 at its lower end, which engages the guide block 680.
  • a spring or other suitable bias member 684 is disposed between the flange 682 and a confronting surface of the follower guide 674 to bias the plunger 672 and guide block 680 downward.
  • the roller follower 678 travels along the surface of the cam lobes 646 as the camshaft 642 rotates, causing the plunger 672 to be driven upwardly within the barrel 662 as the roller follower 678 travels along the upward slope of each lobe 646.
  • the spring 684 biases the roller follower 678 against the cam lobe 646 and the plunger 72 is drawn downwardly within the barrel 662.
  • the plunger 672 is provided with at least one vent port 686 (two ports 686 are shown) that open to a fluid cavity 688 formed within the pump 626 around a portion of the plunger 672.
  • the cavity 688 is connected with the inlet 664 of the pump 626 via a passageway 690 in the barrel 662.
  • a metering sleeve 692 is slidably mounted concentrically with the plunger 672 and located within the cavity 688.
  • the metering sleeve 692 is biased upwardly, as viewed in FIG. 10, by a bias spring 694 trapped between the sleeve 692 and an upwardly facing wall of the follower guide 674.
  • a conventional solenoid coil 696 is disposed around the plunger 672 and the metering sleeve 692, as shown in FIG. 10.
  • the metering sleeve 692 and the solenoid coil 696 together form a solenoid assembly 698, with the metering sleeve itself forming the armature of the solenoid assembly 698.
  • the metering sleeve 692 may be a trapped between the spring 694 and an armature sleeve (not shown), in which case the metering sleeve itself is not the actual solenoid armature but does move together with the solenoid armature.
  • the unit pumps 26 are controlled by the ECM 50 to vary effective pumping stokes of at least some of the unit pumps 26.
  • the solenoid assembly 116 or other actuator of the by-pass valve 90 is supplied with current after a delay period determined by the ECM 50 based on the desired effective pumping stroke of the unit pump 26.
  • valve 90 may be pressure latched in its closed condition by only momentary activation of the solenoid assembly 116 or other actuator. Consequently, the valve 90 acts in a digital manner, in that it latches in its closed position for the remaining duration of the pumping stroke of the pump regardless of the duration for which current is applied to the actuator.
  • the valve 90 may be actuated and latched closed extremely quickly ⁇ on the order of a few microseconds. In other words, the valve changes states and latches in the closed state quickly in response to current application of any reasonable duration.
  • bypass valve 90 separates the control aspects from the fluid flow requirements so that the often conflicting requirements of these two functions do not cause compromises of the type briefly discussed in the background art section.
  • primary closure member 102 and its associated features are designed to accommodate fluid flow and the ability to change positions quickly.
  • the valve 90 may be used advantageously as described above to provide high precision, fast response variable delivery from an otherwise conventional fixed displacement piston pump.
  • the valve 90 obviates the need for sophisticated mechanical structures, such as wobble plate assemblies and/or sleeve metering assemblies, that are typically used to provide variable delivery from a piston pump.
  • the digital latching, precision delivery, and quick responsive allow rapid and precise variation of the pressure of the fluid in the common rail 28.
  • the rapid variations of the pressure in the fluid supplied to the unit injectors 22 can be achieved to vary the characteristics of each individual injection of fuel into the associated combustion chamber of the engine 22.
  • the solenoid assembly 116 or other actuator only requires momentary activation to close and latch the valve 90, sustained and/or high currents are not required. Consequently, a single current driver (not shown) may be used to control several valves 90. This is particularly useful in high speed engines in which injection events occur with high frequency.
  • the pump 400,500 may be used to drive two or more separate hydraulically powered systems.
  • the output of one or more of the piston/cylinder combinations may be used to drive a hydraulically powered fuel injection system whereas of output from other piston/cylinder combinations may be used to power, among other things, a vehicle anti-lock braking system (ABS), active suspension, engine supercharger, power steering, a hydrostatic drive mechanism, or non-propulsion related systems such as hydraulically powered machine implement systems.
  • ABS vehicle anti-lock braking system
  • active suspension active suspension
  • engine supercharger power steering
  • a hydrostatic drive mechanism a system in which plural devices are driven by a common pump is illustrated in US 5,540,203 A.
  • valve 90 is useful not only as a by-pass valve to provide variable delivery from fluid pumps, but also in any application where flow control of a fluid is desired.
  • the downward stroke of the plunger 672 is the intake stroke of the unit pump 626, which draws fluid into the cavity 688 from the inlet 664 through the spring-biased inlet check valve 664A. Fluid is further drawn into the plunger 672 through the vent ports 686, which serve as inlets ports to the pump chamber 668.
  • the plunger 672 is driven upwardly through its compression or pumping stroke.
  • the upward stroke of the plunger 672 causes fluid in the pump chamber 668 to be pumped either back out the vent ports 686 and into the cavity 688 or through the outlet check valve 666A to the outlet 666.
  • the metering sleeve 692 preferably forms the armature of the solenoid assembly 698 (or at least moves in unison with the armature), the position of the metering sleeve 692 depends on the current applied to the solenoid coil 696. If little or no current is applied to the solenoid coil 696, the metering sleeve will be pushed upwardly, as viewed in FIG. 10, until the spring 694 is uncompressed or the sleeve 692 engages the upper wall of the cavity 688. By applying current to the solenoid coil 696, the metering sleeve 692 can be driven downwardly relative to the plunger 672 against the force of the spring 694.
  • the magnitude of the applied current determines how far the metering sleeve 92 is displaced from its unactivated, resting position.
  • the position of the metering sleeve is preferably a function of the current supplied to the solenoid.
  • Minimum or zero fluid delivery from the unit pump 626 is achieved when no current is applied to the solenoid coil 696, in which case the sleeve 692 is positions such that the vent ports 686 remain uncovered during the entire plunger stroke.
  • a current corresponding to the desired output is applied to the solenoid coil 696, which drives the metering sleeve 692 downwardly.
  • the vent ports 686 are covered and sealed by the metering sleeve 692 during a portion of the upward stroke of the plunger 672, and as a result, fluid is pumped from the pump chamber 668 through the outlet check valve 666A to the outlet 666 during that portion of the plunger stroke.
  • the sleeve 692 By applying a higher current to the solenoid coil 696, the sleeve 692 can be driven further downward, which increases the duration during pumping stroke during in which the vent ports 686 are covered by the metering sleeve 692. As a result, the fluid delivery to the outlet 666 is increased, and maximum fluid delivery is achieved when the sleeve 692 is moved into contact with a stop surface on follower guide 674 to fully compress the spring 694. As apparent, a decrease in the fluid delivery to the outlet is achieved by applying a lower current to the solenoid coil 96.
  • FIG. 10 This invention of FIG. 10 is illustrated with respect to a single plunger unit pump, but those skilled in the art will recognize that the principles of this invention are equally applicable in controlling fluid delivery from a pump having a plurality of reciprocal plungers. In such a pump, one or more of the plungers would be provided with a metering sleeve that forms the armature of a solenoid assembly.
  • piston/plunger pumps in which this invention may be applied include both radial piston pumps and axial piston pumps.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (5)

  1. Verfahren zur Steuerung der Ausgangsgröße einer durch eine Hülse einstellbaren Pumpe (626), wobei die folgenden Schritte vorgesehen sind:
    Vorsehen einer mittels einer Hülse einstellbaren Pumpe (626), die mindestens einen Kolben (672) aufweist, und zwar positioniert für eine Hin- und
    Herbewegung über einen Hubabstand in einem Pumpengehäuse (674, 662), und mindestens einen Auslass (686) definierend, und ferner mit einer Elektromagnetanordnung (698) mit einer Spule (696), angeordnet um den mindestens einen Kolben (672) herum und ferner mit einer Zumessoder Einstellhülse (692), jeweils gleitbar angebracht auf jedem mindestens einen Kolben (672);
    Bestimmen eines effektiven Sollpumphubs für die durch eine Hülse einstellbare Pumpe (626);
    Bestimmen einer Elektromagnetstromgröße, die dem effektiven Sollpumphub entspricht; und
    Einstellen einer Position der Einstellhülse (692) durch Liefern von Strom an die Elektromagnetanordnung (698) mit einem der erwähnten Elektromagnetstromgröße entsprechenden Pegel, dadurch gekennzeichnet, dass dann, wenn der effektive Sollpumphub mit Null bestimmt wird, die Einstellung der erwähnten Elektromagnetstromgröße auf Null eingestellt wird, und/oder dass dann, wenn der effektive Sollpumphub einer maximalen Strömungsmittellieferung entspricht, der Einstellschritt das Liefern eines Stroms umfasst, der ausreicht, um die Einstellhülse (692) in Kontakt mit einer Anschlagoberfläche zu bewegen.
  2. Verfahren nach Anspruch 1, wobei der Einstellschritt dadurch ausgeführt wird, dass man eine Magnetkraft an die Einstellhülse (692) über die erwähnte Spule (696) anlegt.
  3. Verfahren nach Anspruch 1 oder 2, wobei die Bestimmungsschritte mit einem elektronischen Steuermodul (50) ausgeführt werden.
  4. Ein Kraftstoffeinspritzsystem (20), welches Folgendes aufweist:
    eine "Common Rail" (Sammelleiste) (28);
    eine Vielzahl von Kraftstoffeinspritzvorrichtungen (24), strömungsmittelmäßig verbunden mit der Common Rail (28);
    eine Strömungsmittelquelle (36);
    eine hülseneinstellbare Pumpe (626) mit einem Auslass (666) in Strömungsmittelverbindung mit der Common Rail (28) und einem Einlass (664) strömungsmittelmäßig verbunden mit der Strömungsmittelquelle (36), wobei die hülseneingestellte Pumpe (626) eine Elektromagnetanordnung (698) und mindestens einen Kolben (672) aufweist, der einen Ablass oder Abfluss (686) definiert und zur Hin- und Herbewegung über einen Hubabstand in einem Pumpengehäuse (674, 662) angeordnet ist, wobei die Elektromagnetanordnung (698) eine Spule (696), angeordnet um den mindestens einen Kolben (672) herum, aufweist, und ferner eine Einstell- bzw. Zumesshülse (692) gleitbar auf jeweils dem mindestens einen Kolben (672) angeordnet; und
    ein elektronisches Steuermodul (50), welches einen effektiven Sollpumphub für die hülsenzugemessene Pumpe (626) bestimmt, wobei das elektronische Steuermodul (50) ferner eine Elektromagnetstromgröße bestimmt, die dem effektiven Sollpumphub entspricht, und eine Position der Einstellhülse (692) einstellt, und zwar durch Liefern von Strom an die Elektromagnetanordnung (698) mit einem Pegel entsprechend der erwähnten Elektromagnetstromgröße, dadurch gekennzeichnet, dass das elektronische Steuermodul (50) die Elektromagnetstromgröße auf Null einstellt, wenn der effektive Sollpumphub mit Null bestimmt wird, und/oder einen Strom liefert der ausreicht um die Einstellhülse (692) in Kontakt mit einer Stopp- bzw. Anschlagoberfläche zu bewegen, wenn der effektive Sollpumphub einer maximalen Strömungsmittellieferung entspricht.
  5. System nach Anspruch 4, wobei das elektronische Steuermodul (50) eine Magnetkraft an die Einstellhülse (692) über die Spule (696) anlegt.
EP00923379A 1999-04-16 2000-04-14 Pumpe mit variabler fördermenge und ihre verwendung in einem common-rail-kraftstoffeinspritzsystem Expired - Lifetime EP1171707B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US12969999P 1999-04-16 1999-04-16
US12970099P 1999-04-16 1999-04-16
US129699P 1999-04-16
US129700P 1999-04-16
PCT/US2000/010136 WO2000063551A1 (en) 1999-04-16 2000-04-14 Variable delivery pump and common rail fuel system using the same

Publications (2)

Publication Number Publication Date
EP1171707A1 EP1171707A1 (de) 2002-01-16
EP1171707B1 true EP1171707B1 (de) 2003-09-03

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EP (1) EP1171707B1 (de)
DE (1) DE60004983T2 (de)
WO (1) WO2000063551A1 (de)

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Publication number Priority date Publication date Assignee Title
EP1101931B1 (de) * 1999-11-19 2006-08-30 CRT Common Rail Technologies AG Hochdruckeinspritzsystem mit Common Rail
GB2385386A (en) * 2002-02-15 2003-08-20 Delphi Tech Inc Pump assembly
DE602006017128D1 (de) * 2006-04-12 2010-11-04 Man B & W Diesel As Grosser Zweitakt-Kreuzkopfdieselmotor mit Gleichstromspülung
DE102013209018A1 (de) * 2013-05-15 2014-11-20 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102014200695A1 (de) * 2014-01-16 2015-07-16 Robert Bosch Gmbh Hochdruckpumpe mit einem elektromagnetischen Saugventil
CN114576058B (zh) * 2022-03-01 2022-09-30 安徽腾达汽车科技有限公司 一种汽车用油泵

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DE60004983D1 (de) 2003-10-09
EP1171707A1 (de) 2002-01-16
DE60004983T2 (de) 2004-07-15
WO2000063551A1 (en) 2000-10-26

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