EP2256334A1 - A fuel-supply system for an internal-combustion engine - Google Patents
A fuel-supply system for an internal-combustion engine Download PDFInfo
- Publication number
- EP2256334A1 EP2256334A1 EP09425198A EP09425198A EP2256334A1 EP 2256334 A1 EP2256334 A1 EP 2256334A1 EP 09425198 A EP09425198 A EP 09425198A EP 09425198 A EP09425198 A EP 09425198A EP 2256334 A1 EP2256334 A1 EP 2256334A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- open
- close element
- pressure pump
- inlet
- 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.)
- Granted
Links
Images
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
- F02M59/20—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
- 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
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
Definitions
- the present invention relates to a fuel-supply system for an internal-combustion engine.
- fuel-supply systems of the diesel-cycle type comprise a high-pressure pump that supplies fuel to a common rail, which has a predetermined volume for accumulating fuel under pressure and supplies, in turn, a plurality of injectors associated to the engine cylinders.
- the latter must be brought up to a very high pressure, in the region of 1600 bar, in the conditions of maximum power of the engine.
- the pressure of the fuel required in the common rail is in general defined by an electronic control unit as a function of the operating conditions of the engine.
- a by-pass solenoid valve set on the delivery pipe of the high-pressure pump, is controlled by the control unit for causing recirculation of the fuel that is in excess with respect to the fuel injected by the injectors, towards the usual fuel tank, before said excess fuel enters the common rail.
- the capacity of the high-pressure pumps is directly proportional to the engine r.p.m. and is calibrated so as to meet the maximum requirements in every operating condition of the engine.
- the flow of excess fuel which is discharged into the tank by the by-pass solenoid valve, is very high. Consequently, this embodiment presents the drawback of involving a waste of part of the compression work of the high-pressure pump.
- Variable-capacity high-pressure pumps have been proposed in such a way as to reduce the amount of fuel pumped when the engine functions at reduced power.
- the intake pipe of the high-pressure pump is provided with a restriction having a passage cross-section the area of which is continuously variable.
- Said passage cross-section is defined by a solenoid valve controlled by the electronic control unit as a function of the pressure required in the common rail and/or of the operating conditions of the engine.
- the restriction in the intake pipe is supplied with a constant pressure difference, equal to approximately 5 bar, determined by an auxiliary pump, or low-pressure pump, set in the tank.
- a constant pressure difference equal to approximately 5 bar, determined by an auxiliary pump, or low-pressure pump, set in the tank.
- the aim of the invention is to provide a fuel-supply system for an internal-combustion engine, which will enable limitation or elimination of the drawback set forth above in a simple and inexpensive way.
- a fuel-supply system for an internal-combustion engine 2 for example a four-stroke diesel engine.
- the engine 2 comprises a plurality of cylinders 3, for example four cylinders, which co-operate with corresponding pistons (not shown), which can be actuated to turn a drive shaft 4.
- the common rail 6 is supplied with fuel under high pressure by a high-pressure pump, designated as a whole by 7, via a delivery pipe 8.
- the high-pressure pump 7 is supplied by a low-pressure pump, for example, an electric pump 9, via an intake pipe 10 of the high-pressure pump 7.
- the electric pump 9 is in general set in the usual fuel tank 11.
- a discharge pipe 12 gives out into the tank 11 for causing recirculation of the excess fuel of the supply system 1.
- the common rail 6 is provided with a discharge solenoid valve 15, which is in communication with the discharge pipe 12 and performs a safety function in the case where there were to be an overpressure in the common rail 6.
- Each injector 5 is designed to inject, into the corresponding cylinder 3, an amount of fuel that ranges between a minimum value and a maximum value, under the control of an electronic control unit 16, which can be formed by the usual microprocessor control unit for control of the engine 2.
- the control unit 16 is designed to receive signals indicating the operating conditions of the engine 2, such as the position of the accelerator pedal and the r.p.m. of the drive shaft 4, which are generated by corresponding sensors (not shown), as well as the pressure of the fuel in the common rail 6, detected by a pressure sensor 17.
- the control unit 16 controls the instant and duration of actuation of the individual injectors 5.
- the control unit 16 controls opening and closing of the discharge solenoid valve 15. Consequently, the discharge pipe 12 conveys towards the tank 11 both the discharge fuel of the injectors 5 and the possible excess fuel in the common rail 6, discharged for safety reasons by the solenoid valve 15.
- the piston 21 is actuated by an eccentric 22 carried by an actuation shaft 23 of the high-pressure pump 7.
- the two pumping elements 18 are coaxial and opposite to one another, and are actuated by a single eccentric 22.
- the shaft 23 is connected to the drive shaft 4, via a motion-transmission device 26, such that the eccentric 22 controls a compression stroke of a piston 21 for each injection of the injectors 5 into the respective cylinders 3 of the engine 2.
- the fuel is at atmospheric pressure.
- the electric pump 9 compresses the fuel to a low pressure, for example in the region of just 2-3 bar.
- the high-pressure pump 7 compresses the fuel received from the intake pipe 10 so as to send the fuel at high pressure, for example in the region of 1600 bar, to the common rail 6, via the delivery pipe 8.
- the capacity of the high-pressure pump 7 is controlled exclusively by a solenoid valve 27 arranged on the intake pipe 10.
- the solenoid valve 27 is of the on-off type and has an effective passage cross-section that is relatively wide so as to supply fuel without causing any drop of pressure when it is open.
- the solenoid valve 27 (partially illustrated) comprises a casing 28 and a plate-like portion 31, which is coupled in a fixed position to the casing 28, for example via an externally threaded ringnut 31a screwed to a side wall 36 of the casing 28.
- the plate-like portion 31 has a hole 32, which extends along an axis 33 and defines an inlet for the fuel that arrives from the delivery of the pump 9.
- the chamber 37 houses an open/close element 40, which is defined by a ball or by a spherical portion, in the particular example shown.
- the open/close element 40 is subject to the opposite actions of a spring 42 and of an electric actuator 43.
- the actuator 43 is defined by an electromagnet comprising: a magnetic core 44 fixed with respect to the casing 28; and an armature 45, which impinges upon the open/close element 40 so as to keep it in a closing position when the electric actuator 43 is not energized, transferring onto the open/close element 40 the elastic force of the spring 42.
- the open/close element 40 is spherical, the travel allowed for the armature 45 is of a small amount so that there is no possibility for the open/close element 40 to be able to displace radially.
- the spring 42 has a pre-load and a stiffness such as to exert an action of axial thrust that tends to bring the armature 45 into a lowered position and, hence, the open/close element 40 into the closing position.
- the open/close element 40 engages in a fluid-tight way a valve seat 47 defined by a conical surface provided on the plate-like portion 31 around the hole 32 so as to close the hole 32 itself.
- the spring 42 is housed in the magnetic core 44 and acts directly on the armature 45.
- the magnetic core 44 When the magnetic core 44 is electrically supplied, it causes axial translation of the armature 45 into the raised position, and hence causes displacement of the open/close element 40 into an opening position.
- the hole 38 In the opening position, the hole 38 communicates with the hole 32 through the space or volume of the chamber 37 for supplying fuel from the pump 9 to the intake valves 25 of the high-pressure pump 7.
- FIG 3 is a partial illustration of a variant of the solenoid valve 27, the components of which are designated by the same reference numbers used in Figure 2 , wherever possible.
- the guide element 36a is a casing portion that is defined by the prolongation of the wall 36 towards the actuator (not illustrated in Figure 3 ) and is slidably coupled directly to the wall 40b of the open/close element 40.
- the wall 36 is provided with at least two radial holes 38, which are set in diametrally opposite positions with respect to one another.
- the plate-like portion 31 is fixed to the wall 36 underneath holes 38 for interference fit, for example via drive fit, and has a plane face that is orthogonal to the axis 33, faces the wall 40a, and defines the valve seat 47.
- the spring 42 is at least partially housed in the open/close element 40, is coaxial with respect to the wall 40b, and acts directly against the wall 40a.
- the wall 40a comprises an annular projection 46, which is coaxial to the hole 32, is set in a more internal position with respect to the holes 48 and has the purpose of guaranteeing fluid-dynamic sealing against the valve seat 47 so that the sealing area has the mean diameter of the projection 46.
- the open/close element 40 comprises a projection 49, which is set along the perimetral edge of the wall 40a, i.e., in a position more external respect to the holes 48 and to the projection 46, and has radial passages not visible in Figure 3 .
- the invention applies both to systems where the solenoid valve 27 is controlled in a way synchronous with the rate of rotation of the pump and to systems where the control of the solenoid valve 27 is asynchronous.
Abstract
Description
- The present invention relates to a fuel-supply system for an internal-combustion engine.
- As is known, fuel-supply systems of the diesel-cycle type comprise a high-pressure pump that supplies fuel to a common rail, which has a predetermined volume for accumulating fuel under pressure and supplies, in turn, a plurality of injectors associated to the engine cylinders.
- To obtain a good nebulization of the fuel, the latter must be brought up to a very high pressure, in the region of 1600 bar, in the conditions of maximum power of the engine. The pressure of the fuel required in the common rail is in general defined by an electronic control unit as a function of the operating conditions of the engine.
- Known to the art are injection systems in which a by-pass solenoid valve, set on the delivery pipe of the high-pressure pump, is controlled by the control unit for causing recirculation of the fuel that is in excess with respect to the fuel injected by the injectors, towards the usual fuel tank, before said excess fuel enters the common rail.
- Normally, the capacity of the high-pressure pumps is directly proportional to the engine r.p.m. and is calibrated so as to meet the maximum requirements in every operating condition of the engine. However, in certain operating conditions (for example, at the maximum r.p.m., but with a reduced power supplied by the engine), the flow of excess fuel, which is discharged into the tank by the by-pass solenoid valve, is very high. Consequently, this embodiment presents the drawback of involving a waste of part of the compression work of the high-pressure pump.
- Variable-capacity high-pressure pumps have been proposed in such a way as to reduce the amount of fuel pumped when the engine functions at reduced power. In one of these pumps, the intake pipe of the high-pressure pump is provided with a restriction having a passage cross-section the area of which is continuously variable. Said passage cross-section is defined by a solenoid valve controlled by the electronic control unit as a function of the pressure required in the common rail and/or of the operating conditions of the engine.
- In particular, the restriction in the intake pipe is supplied with a constant pressure difference, equal to approximately 5 bar, determined by an auxiliary pump, or low-pressure pump, set in the tank. By varying continuously the area of the restriction, the amount of fuel drawn in by the pumping elements of the high-pressure pump is modulated.
- According to an alternative solution, described, for example, in the European patent No.
EP1612402 , a solenoid valve of an on-off type is set between the high-pressure pump and the low-pressure pump. Said solenoid valve is controlled by the electronic control unit, once again as a function of the pressure required in the common rail and/or of the operating conditions of the engine, in synchronism with the intake strokes of two pumping elements of the high-pressure pump and in a chopped way so as to establish the effective amount of fuel taken in during said intake stroke. - Known solenoid valves of an on-off type mounted between the high-pressure pump and the low-pressure pump have an open/close element that is able to slide along an axis under the opposite actions of an electromagnet and a spring. The axial thrust of the spring tends to bring the open/close element against a valve seat for closing axially an opening from which the fuel exits towards the high-pressure pump. Experimentally, fuel-supply systems of the type just described have revealed an excessive noise coming from the on-off solenoid valve mounted between the high-pressure pump and the low-pressure pump. Said drawback arises above all in systems in which the solenoid valve is not controlled in synchronism with the high-pressure pump.
- The noise is due to phenomena of fluid hammer that arise during closing of the on-off solenoid valve. Said phenomena are due to the fact that the open/close element intercepts a flow with a value of instantaneous flowrate that is high also on account of the difference of pressure to which the solenoid valve is subjected (approximately 3 bar). In particular, the intensity of the fluid hammer is due above all to the constructional layout of the solenoid valve, where the supply pressure of the fuel coming from the low-pressure pump tends to close the open/close element of the solenoid valve.
- The aim of the invention is to provide a fuel-supply system for an internal-combustion engine, which will enable limitation or elimination of the drawback set forth above in a simple and inexpensive way.
- According to the invention, the above aim is achieved by a fuel-supply system for an internal-combustion engine as defined by Claim 1.
- For a better understanding of the invention described herein is a preferred embodiment, provided by way of example with the aid of the annexed drawings, wherein:
-
Figure 1 is a diagram of a fuel-supply system in an internal-combustion engine, according to the present invention; -
Figure 2 illustrates, partially and in cross section, a solenoid valve that forms part of the system ofFigure 1 ; and -
Figure 3 is similar toFigure 2 and shows part of a variant of the solenoid valve ofFigure 2 . - With reference to
Figure 1 , designated as a whole by 1 is a fuel-supply system for an internal-combustion engine 2, for example a four-stroke diesel engine. Theengine 2 comprises a plurality ofcylinders 3, for example four cylinders, which co-operate with corresponding pistons (not shown), which can be actuated to turn a drive shaft 4. - The supply system 1 comprises a plurality of electrically controlled injectors 5, associated to the
cylinders 3 and designed to inject the high-pressure fuel therein. The injectors 5 are connected to an accumulation volume, which has a predetermined value for one or more injectors 5. In the embodiment illustrated, the accumulation volume is formed by the usualcommon rail 6, connected to which are all the injectors 5. - The
common rail 6 is supplied with fuel under high pressure by a high-pressure pump, designated as a whole by 7, via adelivery pipe 8. In turn, the high-pressure pump 7 is supplied by a low-pressure pump, for example, anelectric pump 9, via anintake pipe 10 of the high-pressure pump 7. Theelectric pump 9 is in general set in theusual fuel tank 11. Adischarge pipe 12 gives out into thetank 11 for causing recirculation of the excess fuel of the supply system 1. - Preferably, the
common rail 6 is provided with adischarge solenoid valve 15, which is in communication with thedischarge pipe 12 and performs a safety function in the case where there were to be an overpressure in thecommon rail 6. - Each injector 5 is designed to inject, into the
corresponding cylinder 3, an amount of fuel that ranges between a minimum value and a maximum value, under the control of anelectronic control unit 16, which can be formed by the usual microprocessor control unit for control of theengine 2. Thecontrol unit 16 is designed to receive signals indicating the operating conditions of theengine 2, such as the position of the accelerator pedal and the r.p.m. of the drive shaft 4, which are generated by corresponding sensors (not shown), as well as the pressure of the fuel in thecommon rail 6, detected by apressure sensor 17. By processing said received signals by a purposely provided program, thecontrol unit 16 controls the instant and duration of actuation of the individual injectors 5. In addition, thecontrol unit 16 controls opening and closing of thedischarge solenoid valve 15. Consequently, thedischarge pipe 12 conveys towards thetank 11 both the discharge fuel of the injectors 5 and the possible excess fuel in thecommon rail 6, discharged for safety reasons by thesolenoid valve 15. - The high-pressure pump 7 comprises a pair of
pumping elements 18, each formed by acylinder 19 having acompression chamber 20, in which amobile piston 21 slides with reciprocating motion, constituted by an intake stroke and a delivery stroke. Eachcompression chamber 20 is provided with acorresponding intake valve 25 and acorresponding delivery valve 30. Thevalves intake valves 25 are in communication with theintake pipe 10 common to saidintake valves 25, whilst the twodelivery valves 30 are in communication with thedelivery pipe 8 common to saiddelivery valves 30. - In particular, the
piston 21 is actuated by an eccentric 22 carried by anactuation shaft 23 of the high-pressure pump 7. In the embodiment described here, the twopumping elements 18 are coaxial and opposite to one another, and are actuated by a single eccentric 22. Theshaft 23 is connected to the drive shaft 4, via a motion-transmission device 26, such that the eccentric 22 controls a compression stroke of apiston 21 for each injection of the injectors 5 into therespective cylinders 3 of theengine 2. - In the
tank 11, the fuel is at atmospheric pressure. In use, theelectric pump 9 compresses the fuel to a low pressure, for example in the region of just 2-3 bar. In turn, the high-pressure pump 7 compresses the fuel received from theintake pipe 10 so as to send the fuel at high pressure, for example in the region of 1600 bar, to thecommon rail 6, via thedelivery pipe 8. - The capacity of the high-pressure pump 7 is controlled exclusively by a
solenoid valve 27 arranged on theintake pipe 10. - The
solenoid valve 27 is of the on-off type and has an effective passage cross-section that is relatively wide so as to supply fuel without causing any drop of pressure when it is open. - With reference to
Figure 2 , the solenoid valve 27 (partially illustrated) comprises acasing 28 and a plate-like portion 31, which is coupled in a fixed position to thecasing 28, for example via an externally threadedringnut 31a screwed to aside wall 36 of thecasing 28. The plate-like portion 31 has ahole 32, which extends along anaxis 33 and defines an inlet for the fuel that arrives from the delivery of thepump 9. - The
wall 36 and the plate-like portion 31 define the perimeter and the bottom of achamber 37, which communicates in a permanent way with ahole 38 made on thewall 36 in a radial direction with respect to theaxis 33. Thehole 38 defines an outlet for the fuel that flows towards thevalves 25 of the high-pressure pump 7. - The
chamber 37 houses an open/close element 40, which is defined by a ball or by a spherical portion, in the particular example shown. The open/close element 40 is subject to the opposite actions of aspring 42 and of anelectric actuator 43. In particular, theactuator 43 is defined by an electromagnet comprising: amagnetic core 44 fixed with respect to thecasing 28; and anarmature 45, which impinges upon the open/close element 40 so as to keep it in a closing position when theelectric actuator 43 is not energized, transferring onto the open/close element 40 the elastic force of thespring 42. Even though the open/close element 40 is spherical, the travel allowed for thearmature 45 is of a small amount so that there is no possibility for the open/close element 40 to be able to displace radially. - In the particular example illustrated, the
armature 45 is defined by a body comprising: acentral portion 45a, which rests on the open/close element 40; and aperipheral portion 45b, which is disk-shaped and is made of ferromagnetic material. Preferably, thearmature 45 is guided by one ormore guide elements 36a, fixed with respect to thewall 36 so as to translate along theaxis 33 between a raised position and a lowered position with respect to themagnetic core 44. - As mentioned above, the
spring 42 has a pre-load and a stiffness such as to exert an action of axial thrust that tends to bring thearmature 45 into a lowered position and, hence, the open/close element 40 into the closing position. In the closing position, the open/close element 40 engages in a fluid-tight way avalve seat 47 defined by a conical surface provided on the plate-like portion 31 around thehole 32 so as to close thehole 32 itself. In the particular embodiment shown, thespring 42 is housed in themagnetic core 44 and acts directly on thearmature 45. - When the
magnetic core 44 is electrically supplied, it causes axial translation of thearmature 45 into the raised position, and hence causes displacement of the open/close element 40 into an opening position. In the opening position, thehole 38 communicates with thehole 32 through the space or volume of thechamber 37 for supplying fuel from thepump 9 to theintake valves 25 of the high-pressure pump 7. -
Figure 3 is a partial illustration of a variant of thesolenoid valve 27, the components of which are designated by the same reference numbers used inFigure 2 , wherever possible. - Unlike what is shown in
Figure 2 , the open/close element 40 is defined by a cup-shaped body (partially illustrated) comprising: abottom wall 40a orthogonal to theaxis 33, axially facing the plate-like portion 31, and provided with through holes 48; and acylindrical side wall 40b, which extends axially starting from the perimetral edge of thewall 40a in a position set facing thewall 36 and is fixed with respect to thewall 40a itself. - The
guide element 36a is a casing portion that is defined by the prolongation of thewall 36 towards the actuator (not illustrated inFigure 3 ) and is slidably coupled directly to thewall 40b of the open/close element 40. Thewall 36 is provided with at least tworadial holes 38, which are set in diametrally opposite positions with respect to one another. - The plate-
like portion 31 is fixed to thewall 36 underneathholes 38 for interference fit, for example via drive fit, and has a plane face that is orthogonal to theaxis 33, faces thewall 40a, and defines thevalve seat 47. - The
spring 42 is at least partially housed in the open/close element 40, is coaxial with respect to thewall 40b, and acts directly against thewall 40a. Towards the plate-like portion 31, thewall 40a comprises an annular projection 46, which is coaxial to thehole 32, is set in a more internal position with respect to the holes 48 and has the purpose of guaranteeing fluid-dynamic sealing against thevalve seat 47 so that the sealing area has the mean diameter of the projection 46. Once again towards the plate-like portion 31, the open/close element 40 comprises aprojection 49, which is set along the perimetral edge of thewall 40a, i.e., in a position more external respect to the holes 48 and to the projection 46, and has radial passages not visible inFigure 3 . - According to the invention, as compared to the on-off solenoid valves of a known type used for adjusting the flowrate, like the ones described in the patent No.
EP1612402 , the direction of the flow of the fuel that traverses the solenoid valve is reversed, i.e., the supply pressure tends to raise the open/close element 40, instead of closing it. This results in longer closing times of the open/close element 40, because the supply pressure is now opposite to the action of thespring 42, instead of being concordant therewith: given that the flow of fuel that traverses the solenoid valve is interrupted for a longer time as compared to what occurs in the known art, the intensity of the fluid hammer caused by closing of the open/close element 40 is lower, with consequent benefit in terms of noise emission. - It is clear that modifications and variations may be made to the system 1 described and illustrated herein, without thereby departing from the scope of protection of the present invention, as defined in the annexed claims.
- For example, it is possible to eliminate the motion-
transmission device 26, and actuate theshaft 23 of the high-pressure pump 7 at a rate independent of the r.p.m. of the drive shaft 4. Also thesolenoid valve 15 for discharge of the fuel from thecommon rail 6 can be eliminated without jeopardizing operation of the system. - In addition, the two
pumping elements 18 can be set in parallel and actuated in phase opposition by two different eccentrics, and/or theactuator 43 could be different from the one shown by way of example inFigure 2 ; and/or the shape of thesolenoid valve 27 could be different from the ones shown inFigures 1 and2 , and/or the high-pressure pump 7 could have a different number of pumping elements, for example a single pumping element, or else three pumping elements preferably actuated by a common eccentric with a phase offset of 120°. - Finally, the invention applies both to systems where the
solenoid valve 27 is controlled in a way synchronous with the rate of rotation of the pump and to systems where the control of thesolenoid valve 27 is asynchronous.
Claims (7)
- A fuel-supply system (1) for an internal-combustion engine, comprising:- a high-pressure pump (7);- a low-pressure pump (9);- a pipe (10) for supplying fuel from said low-pressure pump (9) to at least one intake valve (25) of said high-pressure pump (7);- a solenoid valve (27) of an on-off type, set along said pipe (10) and comprising:a) an electric actuator (43);b) elastic means (42) exerting a closing thrust;c) an inlet (32) for the fuel, which communicates with the delivery of said low-pressure pump (9);d) an outlet (38) for the fuel, which communicates with said intake valve (25); ande) an open/close element (40), which is mobile along an axis (33) under the opposite actions of said electric actuator (43) and of said elastic means (42) between an opening position, in which said inlet (32) communicates with said outlet (38), and a closing position, in which the passage of fuel from said inlet (32) to said outlet (38) is blocked;characterized in that said inlet (32) is made axially, and said open/close element (40) closes said inlet (32) when it is set in said closing position so as to oppose, in use, the supply pressure at said inlet to the closing thrust exerted by said elastic means (42).
- The system according to Claim 1, characterized in that said outlet (38) is provided in a radial direction with respect to said axis (33).
- The system according to Claim 2, characterized in that said outlet (38) is defined by at least two holes set at the same angular distance apart.
- The system according to any one of the preceding claims, characterized in that said elastic means (42) exert a thrust action to bring said open/close element (40) into said closing position, and said electric actuator (43) is defined by an electromagnet, which attracts said open/close element (40) into said opening position when it is electrically supplied.
- The system according to any one of the preceding claims, characterized in that said solenoid valve (27) comprises:- a side wall (36), on which said outlet (38) is made;- a plate-like portion (31) fixed with respect to said side wall (36); said inlet (32) being provided on said plate-like portion (31);- a valve seat (47) extending on said plate-like portion (31) around said inlet (32) and engaged in a fluid-tight way by said open/close element (40) when said open/close element (40) is set in the closing position; and- a chamber (37) defined laterally by said side wall (36) and axially by said plate-like portion (31).
- The system according to Claim 5, characterized in that said open/close element (40) comprises a wall (40a) orthogonal to said axis (33), facing said plate-like portion (31), and having an annular projection (46) defining the sealing area against said valve seat (47).
- The system according to Claim 5 or Claim 6, characterized in that said solenoid valve (27) comprises guide means (36a) fixed with respect to said side wall (36) for guiding said open/close element (40) and/or an armature of said electric actuator along said axis (33) between said opening position and said closing position.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT09425198T ATE556217T1 (en) | 2009-05-21 | 2009-05-21 | FUEL SUPPLY SYSTEM FOR AN COMBUSTION ENGINE |
EP09425198A EP2256334B1 (en) | 2009-05-21 | 2009-05-21 | A fuel-supply system for an internal-combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP09425198A EP2256334B1 (en) | 2009-05-21 | 2009-05-21 | A fuel-supply system for an internal-combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2256334A1 true EP2256334A1 (en) | 2010-12-01 |
EP2256334B1 EP2256334B1 (en) | 2012-05-02 |
Family
ID=41228706
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09425198A Active EP2256334B1 (en) | 2009-05-21 | 2009-05-21 | A fuel-supply system for an internal-combustion engine |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2256334B1 (en) |
AT (1) | ATE556217T1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITBO20110183A1 (en) * | 2011-04-07 | 2012-10-08 | Magneti Marelli Spa | SILENCED FUEL PUMP FOR A DIRECT INJECTION SYSTEM |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003083286A1 (en) * | 2002-03-28 | 2003-10-09 | Robert Bosch Gmbh | Adjustable pressure regulating valve for fuel injection systems |
EP1612402A1 (en) | 2004-06-30 | 2006-01-04 | C.R.F. Societa' Consortile per Azioni | A high-pressure variable-flow-rate pump for a fuel-injection system |
EP1895218A1 (en) * | 2006-09-04 | 2008-03-05 | Magneti Marelli Powertrain S.p.A. | Shut-off valve for controlling the flow rate of a fuel pump for an internal combustion engine |
EP1898084A1 (en) * | 2006-08-31 | 2008-03-12 | Hitachi, Ltd. | High-pressure fuel supply pump |
-
2009
- 2009-05-21 AT AT09425198T patent/ATE556217T1/en active
- 2009-05-21 EP EP09425198A patent/EP2256334B1/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003083286A1 (en) * | 2002-03-28 | 2003-10-09 | Robert Bosch Gmbh | Adjustable pressure regulating valve for fuel injection systems |
EP1612402A1 (en) | 2004-06-30 | 2006-01-04 | C.R.F. Societa' Consortile per Azioni | A high-pressure variable-flow-rate pump for a fuel-injection system |
EP1898084A1 (en) * | 2006-08-31 | 2008-03-12 | Hitachi, Ltd. | High-pressure fuel supply pump |
EP1895218A1 (en) * | 2006-09-04 | 2008-03-05 | Magneti Marelli Powertrain S.p.A. | Shut-off valve for controlling the flow rate of a fuel pump for an internal combustion engine |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITBO20110183A1 (en) * | 2011-04-07 | 2012-10-08 | Magneti Marelli Spa | SILENCED FUEL PUMP FOR A DIRECT INJECTION SYSTEM |
EP2508744A1 (en) * | 2011-04-07 | 2012-10-10 | Magneti Marelli S.p.A. | Silenced fuel pump for a direct injection system |
CN102734019A (en) * | 2011-04-07 | 2012-10-17 | 马涅蒂-马瑞利公司 | Silenced fuel pump for a direct injection system |
US8474436B2 (en) | 2011-04-07 | 2013-07-02 | MAGNETI MARELLI S.p.A. | Silenced fuel pump for a direct injection system |
CN102734019B (en) * | 2011-04-07 | 2015-07-15 | 马涅蒂-马瑞利公司 | Silenced fuel pump for a direct injection system |
Also Published As
Publication number | Publication date |
---|---|
EP2256334B1 (en) | 2012-05-02 |
ATE556217T1 (en) | 2012-05-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR100514275B1 (en) | High pressure pump | |
EP1072787B2 (en) | High-pressure fuel pump and cam for high-pressure fuel pump | |
EP2964949B1 (en) | Electronically controlled inlet metered single piston fuel pump | |
US6668800B2 (en) | Internal combustion engine fuel injection system | |
US7261087B2 (en) | High-pressure variable-flow-rate pump for a fuel-injection system | |
EP1598548B1 (en) | Method and system for the direct injection of fuel into an internal combustion engine | |
US20130022484A1 (en) | High-pressure pump | |
KR101608706B1 (en) | Fuel system for an internal combustion engine | |
US6581577B1 (en) | Pump arrangement for providing fuel at high pressure | |
EP1598549A1 (en) | Method for the direct injection of fuel into an internal combustion engine | |
EP1219828B1 (en) | Internal combustion engine common-rail injection system with a fuel premetering device | |
US6530363B1 (en) | Variable delivery pump and common rail fuel system using the same | |
EP3296558B1 (en) | High-pressure fuel pump | |
US7273036B2 (en) | High-pressure fuel pump with a ball valve in the low-pressure inlet | |
US7891338B2 (en) | Device for regulating pressure/flow in an internal combustion engine fuel injection system | |
US6959694B2 (en) | Fuel injection system for an internal combustion engine | |
US20030136384A1 (en) | Fuel injection system for an internal combustion engine | |
EP2256334B1 (en) | A fuel-supply system for an internal-combustion engine | |
US8464692B2 (en) | Device for supplying an internal combustion engine with fuel | |
JPH1073064A (en) | High-pressure feed pump | |
JP2002349391A (en) | High pressure fuel pump, particularly used for direct injection type internal combustion engine, fuel system, and internal combustion engine | |
JPH10306761A (en) | Solenoid valve used for high pressure fuel pump | |
KR20010019594A (en) | High pressure supply for fuel injection device | |
JPH1193803A (en) | Variable displacement high pressure pump | |
KR20040021733A (en) | High pressure supply pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA RS |
|
17P | Request for examination filed |
Effective date: 20101028 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: MAZZARELLA, CARLO Inventor name: STUCCHI, SERGIO Inventor name: GARGANO, MARCELLO Inventor name: LEPORE, DOMENICO Inventor name: DE MICHELE, ONOFRIO Inventor name: RICCO, RAFFAELE |
|
17Q | First examination report despatched |
Effective date: 20110225 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 556217 Country of ref document: AT Kind code of ref document: T Effective date: 20120515 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602009006757 Country of ref document: DE Effective date: 20120621 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20120502 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D Effective date: 20120502 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120902 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120802 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 556217 Country of ref document: AT Kind code of ref document: T Effective date: 20120502 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120903 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120803 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20130205 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120813 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120521 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602009006757 Country of ref document: DE Effective date: 20130205 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120802 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20130521 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130531 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20120502 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130521 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120521 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090521 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 9 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20210527 Year of fee payment: 13 Ref country code: FR Payment date: 20210526 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602009006757 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20221201 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230420 Year of fee payment: 15 |