EP0974008B1 - Einspritzsystem, druckventil und volumenstromregelventil und verfahren zum regeln eines kraftstoffdruckes - Google Patents
Einspritzsystem, druckventil und volumenstromregelventil und verfahren zum regeln eines kraftstoffdruckes Download PDFInfo
- Publication number
- EP0974008B1 EP0974008B1 EP98912258A EP98912258A EP0974008B1 EP 0974008 B1 EP0974008 B1 EP 0974008B1 EP 98912258 A EP98912258 A EP 98912258A EP 98912258 A EP98912258 A EP 98912258A EP 0974008 B1 EP0974008 B1 EP 0974008B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel
- volume
- closing member
- flow
- 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
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
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
-
- 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
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic 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
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
-
- 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0047—Four-way valves or valves with more than four ways
-
- 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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/005—Pressure relief valves
- F02M63/0052—Pressure relief valves with means for adjusting the opening pressure, e.g. electrically controlled
-
- 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
- F02M63/0205—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
- F02M63/0215—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
-
- 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
Definitions
- the invention relates to an injection system for an internal combustion engine according to the preamble of claim 1, a volume flow control valve and pressure valve according to the preamble of claim 3 and a method for controlling a Fuel pressure in a fuel accumulator according to the Preamble of claim 7.
- the regulation of the fuel pressure in a fuel accumulator is particularly important in a common rail system, because with a common rail system the maximum fuel pressure for example at 1600 bar. Because of the high pressure, it is advantageous to reduce the pressure in the fuel accumulator to be regulated with as little power loss as possible.
- volume flow control valve on the inlet side of the high pressure pump to be provided and with the volume flow control valve Regulate pressure in the fuel accumulator.
- a pressure valve on the fuel accumulator to provide that quickly lower the pressure in the fuel storage can, for example, when changing from full load to Idle operation is necessary.
- the pressure control valve required to turn the fuel storage off to depressurize the internal combustion engine.
- a fuel injection system is known from US 4,884,545, in which a fuel pump fuel into a fuel accumulator which carries the fuel to injectors forwards.
- a volume flow control valve is in the inlet to the fuel pump provided that the fuel flow for Fuel pump adjusts.
- the volume flow control valve is controlled by a control unit via an actuator.
- a safety valve 13 is provided which when a predetermined pressure is exceeded, fuel is switched off allows the fuel reservoir to flow back to the fuel tank.
- the object of the invention is an inexpensive To provide pressure control for a fuel accumulator, which is also very efficient.
- a major advantage of the invention resides in the fact that with a single control valve both the volume flow in the inlet to the high pressure pump as well the pressure in the fuel reservoir is regulated.
- FIG. 1 schematically shows the structure of an injection system, that via a pre-feed pump 2 from a fuel tank 11 Feeds fuel to a high-pressure pump 1 via a control valve 10.
- the high pressure pump 1 compresses the supplied fuel and puts the high pressure fuel in the fuel accumulator 4.
- the fuel accumulator 4 stands with injectors 5 in connection through which the fuel is injected into an internal combustion engine.
- a pre-pressure control valve 3 is connected in parallel, that the fuel pressure after the feed pump 2 sets a predetermined value.
- the fuel accumulator 4 is connected via a return line 26 to the Control valve 10 connected.
- the control valve 10 is also on a tank line 27 connected to the fuel tank 11 is led.
- a pressure sensor 9 is located on the fuel accumulator 4 arranged, via a signal line with a control unit 6 communicates.
- a speed sensor 8 and an accelerator sensor 7 is provided, which is also via a signal line are connected to the control unit 6.
- the Control unit 6 has a data memory 28 and is via first control lines with the injection valves 5 and connected to the control valve 10 via a second control line.
- the arrangement according to Figure 1 works as follows:
- the control unit 6 controls depending on the speed of the internal combustion engine and the driver request the injection valves 5 according to a corresponding program that is in the data memory 28 is filed.
- the control device 6 controls the control valve 10 depending on the speed of the internal combustion engine and the fuel pressure in the fuel reservoir 4 and regulates thus the fuel pressure in the fuel accumulator 4.
- FIG. 2 shows schematically the structure of the control valve 10.
- Das Control valve 10 has an actuator 21, for example is designed as a magnet.
- the actuator 21 is directly with one Volume closure member 20 in connection that the fuel supply 24, which comes from the pre-feed pump 2, with the fuel outlet 23, which is led to the high pressure pump 1, connects.
- the volume closing member 20 stands over a spring 12 with a pressure closure member 22 in connection that the connection between the return line 26 and the tank line 27 closes with an adjustable holding pressure.
- the control device 6 In the rest position, the cross section of the connection between the fuel inlet 24 and the fuel outlet 23 through the Volume closure member 20 closed and the connection between the return line 26 and the tank line 27 is open. If the control device 6 now controls the magnet 21, this becomes Volume closing member 20 in the direction of the pressure closing member 22 moves and thus the connection cross section between the Fuel inlet 24 and the fuel outlet 23 opened. moreover is the pressure closure member 22 against the spring 12 Opening cross section of the return line 26 biased.
- the spring 12 is designed such that in the rest position the pressure closing member 22 releases the return line 26 and the return line 26 is connected to the tank line 27.
- FIG 3 shows a development of the control valve 10, in which the operative connection between the volume closure member 20 and the pressure closing member 22 via a first coupling spring 16 and a second coupling spring 17 is reached.
- the second coupling spring 17 is biased to a predetermined spring force. If the control device 6 now controls the actuator 21, this becomes Volume closing member 20 moves and the volume flow to High pressure pump flows enlarged. In addition, the pressure closure member 22 via the first coupling spring 16 against the return line 26 biased. Now the first coupling spring 16 widely compressed that the preloaded spring force of the second coupling spring 17 is reached, act on one further deflection of the volume closure member 20, the first and the second coupling spring 16.17 in series connection.
- Figure 4 shows characteristics for the holding pressure P for different Spring couplings between the volume closure member and the Pressure closing element depending on the displacement path S of the actuator 21 and depending on the opening cross section Q, the volume closure member 20 opens.
- the holding pressure P corresponds to a closing force F.
- the deflection in Range greater than S1 corresponds to a volume flow Q> 0.
- With a deflection of actuator 21 between 0 and S1 first builds the pressure closing element 22 a holding pressure before the volume closure member 20 the connection cross section between the Fuel inlet 24 and fuel outlet 23 in the first Deflection S1 opens.
- the characteristic curve A corresponds to the control valve 10 of FIG. 2, in which only one spring 12 between the volume closing member 20th and the pressure closing member 22 is provided.
- the pressure that is set by the pressure closing member 22 takes linear with the deflection s of the actuator 21. It can be seen from FIG. 4 that that the volume closure member 20 initially, i.e. for the Deflection s ⁇ S1 covers an empty path in which the fuel flow not yet connected to the fuel supply becomes.
- the pressure closing member 22 is at the first deflection S1, in which the volume closure member has the connection cross section between the fuel supply line and the fuel discharge line opens, preloaded with a holding force F0.
- the linear characteristic has the disadvantage that with large deflection s a large holding force F is built up.
- the holding pressure characteristic for the control valve of Figure 3, at a first and a second coupling spring 16, 17 between the volume closing member 20 and the pressure closing member 22 are provided are shown in the characteristic curve B.
- the volume closing member 20 In the rest position is the first coupling spring 16 relaxed and the second coupling spring 17 with the aid of a stop 18 and one Transmission disk 19 biased.
- the volume closing member 20 an empty path is provided so that it is only opens when the pressure closing member 22 already with a holding force F1 is biased against the return line 26.
- the actuator 21 is controlled and the volume closing member 20 is deflected, so increases the holding force with which the pressure closing member 22 is biased linearly up to a second deflection S2 on.
- the linear increase corresponds to the spring rate the first coupling spring 16.
- the characteristic B and C are the actual ratios of the fuel pressure in the fuel storage and the volume flow supplied adapted to the fuel storage. For a common rail system are already at low volume flows, i.e. with a small amount of fuel being injected, and low engine speed high fuel pressures necessary. Consequently characteristics B and C offer good efficiency for electrical control, as unnecessarily high holding forces can be avoided with large deflections.
- the characteristic curve forms B, C also offer the advantage that in Area between the rest position of the actuator 21 and the second Deflection S2 a large change in the holding force of the Pressure closing member 22 with a small deflection at the same time of the actuator 21 is reached, while a small Change in the deflection of the volume closing member 20 and thus takes place with little change in the volume flow. In this way, low volume flows can be set precisely become.
- the Pressure holding force F a function, preferably proportional, of the control current I with which the actuator 21 is controlled.
- the volume flow Q is also preferably proportional for deflection S.
- FIG. 5 shows a preferred embodiment of the control valve 10 with a spring combination according to Figure 3.
- Das Control valve 10 has a valve body 31, which with a Key attack 32 and a central thread 33 in a stepped bore a housing 34 is screwed.
- the housing 34 is preferably the housing of a high pressure pump.
- In the housing 34 is an inlet bore 35, an outlet bore 36, a high pressure feed bore 38 and a high pressure drain bore 37 introduced.
- the fuel inlet is at the inlet bore 35 24, to the drain hole 36 is the fuel drain 23, to the high pressure inlet bore 38 is the return line 26 and to the high pressure drain hole 37 is the tank line 27 connected.
- the inlet bore 35, the outlet bore 36 and the high pressure drain hole 37 are preferably radial Connection bores are formed and open into a corresponding one first ring channel 39, second ring channel 40 and third ring channel 41.
- first ring channel 39 and the second ring channel 40 through axially offset diameter steps in the housing 34 and in the valve body 31.
- the third ring channel 41 is a circumferential groove introduced into the valve body 31.
- Control valve 10 is generally cylindrically symmetrical to the axis of symmetry 71.
- first sealing ring 42 Between the first ring channel 39 and the central thread 33 is a first sealing ring 42, between the first ring channel 39 and the second ring channel 40 is a second sealing ring 43 and between the second ring channel 40 and the third ring channel 41, a third sealing ring 44 is introduced into the valve housing 31.
- the first, the second and the third sealing ring 42, 43, 44 are designed as radially sealing O-rings.
- first connection bore 55 In the valve body 31 there are a first connection bore 55, a second connection hole 57 and a third connection hole 64 starting from the first, the second and the third ring channel 39, 40, 41 introduced.
- the first one connect the second and third connection bores 55, 57, 64 the first, the second and the third ring channel 39, 40, 41 with a central bore 70 that is symmetrical to the axis of symmetry 71 and in the longitudinal direction of the valve body 31 in the Valve body 31 is introduced.
- a control slide 53 In the central bore 70 a control slide 53 is introduced parallel to the axis of symmetry 71, which is designed as a sleeve.
- a locking pin 51 is provided arranged symmetrically and in the longitudinal direction to the axis of symmetry 71 is.
- the locking pin 51 and the control slide 53 are fitted in the central bore 70 and in the longitudinal direction of the central bore 70 slidably arranged.
- the control valve 53 has an annular circumference and to the valve body 31 open annular space 54, which in the rest position of the Control slide 53 only connected to the first inlet bore 35 is. If the control slide 53 is actuated by the electromagnet 72 is moved into the working position, then the annular space 54 the first inlet bore 35 with the first outlet bore 36 connected. In this way, the volume flow that the High pressure pump 1 is controlled.
- the high-pressure inlet bore 38 is made in the center of the axis of symmetry 71 and at the lower end of the control valve 10.
- the central bore 70 is closed in the lower region by a head piece 45, which at the same time projects into the high-pressure inlet bore 38 with a closure piece.
- the head piece 45 is arranged in the center of the axis of symmetry 71 and has a pressure relief bore 48 in the center.
- the pressure relief bore 48 widens in the direction of the central bore 70 into a conical valve seat, in which a ball 50 is arranged, which is held by a receptacle 52 on the pressure relief bore 48.
- the receptacle 52 forms the lower end of the locking pin 51.
- annular space 63 is formed all around the locking pin 51, to which the high-pressure drain hole 37 is connected via the third connecting hole 64.
- the cylindrical continuation of the head piece 45, which projects into the high-pressure inlet 38, is surrounded by an annular support ring 47 and a sealing ring 46, which seal the high-pressure inlet bore 38.
- the sealing ring 46 and the support ring 47 offer the advantage that no axial contact force is required to the high pressure inlet bore 38 to seal.
- the axial contact force should be between the head piece 45 and the central thread 33 from the valve housing 31 are included if, for example, as a seal a metallic flat seat or cone seat or a Cutting ring would be used.
- an electromagnet 72 with a magnetic winding 73 and an associated armature guide rod 58 arranged In the upper area of the control valve 10 is an electromagnet 72 with a magnetic winding 73 and an associated armature guide rod 58 arranged, the center of the axis of symmetry 71 is guided in a guide sleeve 80.
- the anchor guide rod 58 protrudes into the central bore 70 and is over a second coupling spring 17 with the control slide 53 in operative connection.
- the second coupling spring 17 is through a transmission socket 60 biased, the transmission socket 60 on one Stop surface 62 of the control slide 53 rests and the prestresses second coupling spring 17 against a stop sleeve 74, which is designed as an end piece of the anchor guide rod 58.
- the transmission bushing 60 is adjacent to the stop 62 a retaining ring formed perpendicular to the axis of symmetry 71 75 on that with a terminating bushing 76, which is the upper end piece of the control slide 53 represents a sleeve-like second spring chamber 77 forms in the direction of the electromagnet 72 is limited by the stop sleeve 74.
- the stop sleeve 74 is firmly connected to the terminating bush 76.
- the transmission socket 60 is on the side of the electromagnet completed with an end plate 87.
- the locking pin 51 which with a Completes transfer plate 78, which corresponds to a diameter has the diameter of the transmission bush 60.
- the end plate 78 is arranged centrally to the axis of symmetry 71 and perpendicular to the axis of symmetry 71 and in the transmission socket 60 movably arranged therein. Between the Transfer plate 78 and end plate 87 is a first Coupling spring 16 introduced.
- the anchor guide rod 58 lies with one Stop plate 79 on a stop 66 of the magnet housing 81 at.
- the stop 66 is preferably over, for example Adjustment discs adjustable accordingly.
- the magnet armature 82 is on a further plate 85 and the stop plate 79 the anchor guide rod 58 adjusts.
- the locking pin 51 is not in the rest position against the Ball 50 biased.
- the pressure relief bore is 48 in the rest position, i.e. without triggering the electromagnet 72 open.
- the control slide 53 is so in the rest position arranged that the inlet bore 35 is connected to the annular space 54 is.
- the drain hole 36 is not with the Annulus 54 connected.
- the actuator guide rod 58 moves in the upward direction the locking pin 51 and thereby transmits via the second coupling spring 17 and the first coupling spring 16 a higher pressure holding force on the ball 50.
- the pressure holding force F increases linearly with the deflection S of the actuator guide rod 58, as shown in Figure 4.
- the second connecting bore 57 preferably has the shape of a rectangular longitudinal slot, which is in the direction of movement of the control slide 53 extends so that the opening cross section is directly proportional to the path S, with the the control slide 53 is moved.
- Another beneficial one Shape is a triangular opening cross-section.
- the control valve 53 provides a volume closing member 20 according to the figures 2 and 3.
- the transmission socket 60 moves together the stop sleeve 74 and the control slide 53. From the second Deflection S2 moves the transmission bush 60 in the equilibrium of forces the second coupling spring 17 and the first Coupling spring 16 opposite the stop sleeve 74 of the anchor guide rod 58. In this way, the increase in holding force kinks F onto the ball 50 from the second deflection S2 into one smaller increase per deflection unit s, as from figure 4 can be seen.
- the high pressure inlet bore 38 is then only with the high pressure outlet bore 37 connected when a larger pressure of the high pressure inlet bore acts on the ball 50 than on the ball 50 by the holding force F of the locking pin 51st acts.
Landscapes
- 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)
Abstract
Description
- Figur 1
- ein Einspritzsystem mit dem erfindungsgemäßen Regelventil,
- Figur 2
- den schematischen Aufbau des Regelventils,
- Figur 3
- eine weitere Ausführungsform des Regelventils,
- Figur 4
- eine Haltedruck- und Volumenstrom-Kennlinie und
- Figur 5
- eine bevorzugte Bauform des Regelventils.
Die zylinderförmige Fortsetzung des Kopfstückes 45, die in den Hochdruckzulauf 38 ragt, ist von einem ringförmigen Stützring 47 und einem Dichtring 46 umgeben, die die Hochdruckzulaufbohrung 38 abdichten.
Claims (11)
- Einspritzsystem für eine Brennkraftmaschine mit Einspritzventilen (5), die mit einem Kraftstoffspeicher (4) in Verbindung stehen, der an einer Kraftstoffpumpe (1) angeschlossen ist, die den Kraftstoffspeicher (4) mit Kraftstoff versorgt,mit einem Druckventil (10,22), das am Kraftstoffspeicher (4) angeschlossen ist,mit einem Drucksensor (9), der am Kraftstoffspeicher (4) vorgesehen ist und den Druck im Kraftstoffspeicher (4) mißt und einem Steuergerät (6) zuführt,wobei ein Volumenstromregelventil (10,20) im Zulauf zur Kraftstoffpumpe (1) vorgesehen ist, das den Kraftstoffstrom zur Kraftstoffpumpe (1) einstellt,daß das Steuergerät (6) das Volumenstromregelventil (10,20) über einen Aktor (21) steuert, und daß derselbe Aktor (21) die Haltekraft des Druckventils (10,22) einstellt.
- Einspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der Aktor (21) auf das Volumenschließglied (20) des Volumenstromregelventils (10,20) einwirkt, daß das Volumenschließglied (20) in Wirkverbindung mit dem Druckschließglied (22) des Druckventils (10,22) steht und die Position des Volumenschließgliedes (20) die Haltekraft des Druckschließgliedes (22) festlegt, mit der das Druckventil (10,22) den Kraftstoffspeicher geschlossen hält.
- Volumenstromregelventil und Druckventil mit einem Ventilkörper (31), in das ein Kraftstoffzulauf (35,55) und ein Kraftstoffablauf (36,57) eingebracht sind,
mit einem Regelschieber (53) als Volumenschließglied, das den Verbindungsquerschnitt zwischen dem Kraftstoffzulauf (35,55) und dem Kraftstoffablauf (3657) steuert,
mit einem Druckzulauf (48) und einem Druckablauf (64,41,37), die in das Gehäuse (31,45) eingebracht sind, mit einem Druckschließglied (50,52,51), das den Druckzulauf (48) mit einer vorgebbaren Haltekraft vom Druckablauf (64,41,37) abschließt,
mit einem steuerbaren Aktor (72,58), der die Position des Volumenschließglied (53) und die Haltekraft des Druckschließgliedes (50,51,52) festlegt. - Volumenstrom- und Druckventil nach Anspruch 3, dadurch gekennzeichnet, daß der Aktor (72,58) direkt das Volumenschließglied (53) in der Position festlegt, daß der Aktor (72,58) über Federmittel (16,17) die Haltekraft des Druckschließgliedes (50,51,52) festlegt.
- Volumenstrom- und Druckregelventil nach Anspruch 3, dadurch gekennzeichnet, daß das Volumenschließglied (53) über Federmittel (16,17) die Haltekraft des Druckschließgliedes (50,51,52) festlegt, daß die Federmittel (16,17) eine Federrate aufweisen, die mit zunehmender Auslenkung des Volumenschließgliedes (53) abnimmt.
- Volumenstrom- und Druckregelventil nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß als Federmittel eine erste und eine zweite Feder (16,17) in Reihenschaltung angeordnet sind, so daß ausgehend von einer Ruheposition, in der die erste Feder (16) entspannt und die zweite Feder (17) vorgespannt ist, bis zu einer vorgegebenen Auslenkung (S2) nur die erste Feder (16) und ab der vorgegebenen Auslenkung (S2) die erste und die zweite Feder (16,17) in Reihenschaltung zusammengedrückt werden.
- Verfahren zum Regeln des Kraftstoffdruckes in einem Kraftstoffspeicher (4) einer Einspritzanlage einer Brennkraftmaschine, bei dem der Kraftstoffspeicher (4) mit Kraftstoff versorgt wird, bei dem der Kraftstoff-Volumenstrom zum Kraftstoffspeicher (4) in Abhängigkeit vom Betriebszustand der Brennkraftmaschine., insbesondere abhängig von der zum Einspritzen benötigten Kraftstoffmenge und von dem zum Einspritzen benötigten Kraftstoffdruck geregelt wird, wobei ein Druckventil (10,22) vorgesehen ist, das den Druck im Kraftstoffspeicher (4) auf einen vorgebbaren Haltedruck begrenzt,
dadurch gekennzeichnet, daß
der Haltedruck des Druckventils (10,22) als Funktion vom Kraftstoff-Volumenstrom eingestellt wird und daß ein Volumenstromregelventil (10,20) im Zulauf zur Kraftstoffpumpe (1), das den Kraftstoff-Volumenstrom zu dieser einstellt, über denselben Aktor (21) gesteuert wird, der auch die Haltekraft des Druckventils (10,22) steuert. - Verfahren nach Anspruch 7, dadurch gekennzeichnet, daß ausgehend von einer Ruheposition, bei der kein Druck im Kraftstoffspeicher (4) herrscht und kein Volumenstrom der Kraftstoffpumpe (1) zugeführt wird, zuerst der Haltedruck des Druckventils (10,22) auf einen vorgebbaren, positiven Wert eingestellt wird, und daß erst anschließend ein Volumenstrom der Kraftstoffpumpe zugeführt wird.
- Verfahren nach Anspruch 7 oder 8, dadurch gekennzeichnet, daß der Haltedruck mit zunehmendem Volumenstrom zunimmt, vorzugsweise proportional zum Volumenstrom zunimmt.
- Verfahren nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, daß der Haltedruck ausgehend von der Ruheposition bis zu einem vorgebbaren ersten Volumenstrom mit einer ersten Steigung zunimmt, daß bei einem größeren Volumenstrom als dem ersten Volumenstrom der Haltedruck mit zunehmendem Volumenstrom mit einer zweiten Steigung zunimmt, die kleiner als die erste Steigung ist.
- Verfahren nach Anspruch 7, dadurch gekennzeichnet, daß der Haltedruck des Druckventils höher als der vorgegebene Kraftstoffdruck des Einspritzvorgangs eingestellt wird.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19714489 | 1997-04-08 | ||
DE1997114489 DE19714489C1 (de) | 1997-04-08 | 1997-04-08 | Einspritzsystem, Druckventil und Volumenstromregelventil und Verfahren zum Regeln eines Kraftstoffdruckes |
PCT/DE1998/000468 WO1998045594A1 (de) | 1997-04-08 | 1998-02-17 | Einspritzsystem, druckventil und volumenstromregelventil und verfahren zum regeln eines kraftstoffdruckes |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0974008A1 EP0974008A1 (de) | 2000-01-26 |
EP0974008B1 true EP0974008B1 (de) | 2002-05-15 |
Family
ID=7825800
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98912258A Expired - Lifetime EP0974008B1 (de) | 1997-04-08 | 1998-02-17 | Einspritzsystem, druckventil und volumenstromregelventil und verfahren zum regeln eines kraftstoffdruckes |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0974008B1 (de) |
DE (1) | DE19714489C1 (de) |
WO (1) | WO1998045594A1 (de) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006037693A1 (de) * | 2004-10-06 | 2006-04-13 | Robert Bosch Gmbh | Kraftstoffsystem für eine brennkraftmaschine |
US7302935B2 (en) | 2003-05-26 | 2007-12-04 | Siemens Aktiengesellschaft | Method for operating an internal combustion engine, fuel system, and volume flow control valve |
DE102008043237A1 (de) | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
DE102008043217A1 (de) | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
DE102010004215A1 (de) * | 2010-01-08 | 2011-07-14 | Continental Automotive GmbH, 30165 | Vorrichtung zur Verhinderung des Absterbens des Motors bei einem mit einem Dieseleinspritzsystem ausgestatteten Fahrzeug |
DE102010027858A1 (de) | 2010-04-16 | 2011-11-24 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19904341A1 (de) * | 1999-02-03 | 2000-08-10 | Mannesmann Rexroth Ag | Steuerungsverfahren |
IT1310754B1 (it) * | 1999-11-30 | 2002-02-22 | Elasis Sistema Ricerca Fiat | Sistema di valvole per il controllo della pressione di ingresso di unliquido in una pompa ad alta pressione, e relativa valvola di |
IT1310753B1 (it) * | 1999-11-30 | 2002-02-22 | Elasis Sistema Ricerca Fiat | Sistema di regolazione della portata di una pompa ad alta pressioneper l'alimentazione di combustibile ad un motore ad iniezione. |
US7270113B2 (en) | 2002-07-11 | 2007-09-18 | Siemens Automotive Hydraulics Sa | Device for controlling flow rate of a direct injection fuel pump |
DE10244551A1 (de) | 2002-09-25 | 2004-04-08 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10329331B3 (de) | 2003-06-30 | 2005-05-25 | Siemens Ag | Verfahren zur Diagnose eines Volumenstromregelventils bei einer Brennkraftmaschine mit Hochdruck-Speichereinspritzsystem |
FR2858432B1 (fr) * | 2003-08-01 | 2005-10-07 | Eaton Corp | Electrovanne de regulation de debit et de pression |
ATE337482T1 (de) | 2004-06-30 | 2006-09-15 | Fiat Ricerche | Hochdruckpumpe mit variabler förderrate für ein brennstoffeinspritzsystem |
ATE344882T1 (de) * | 2004-07-30 | 2006-11-15 | Delphi Tech Inc | Zumesseinrichtung |
IT201900017252A1 (it) * | 2019-09-25 | 2021-03-25 | Bosch Gmbh Robert | Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2653543A (en) * | 1950-05-03 | 1953-09-29 | Hobson Ltd H M | Hydraulic pump |
CH674243A5 (de) * | 1987-07-08 | 1990-05-15 | Dereco Dieselmotoren Forschung | |
DE19612413B4 (de) * | 1996-03-28 | 2006-06-29 | Siemens Ag | Druckfluid-Versorgungssystem, insbesondere für ein Kraftstoff-Einspritzsystem |
-
1997
- 1997-04-08 DE DE1997114489 patent/DE19714489C1/de not_active Expired - Fee Related
-
1998
- 1998-02-17 EP EP98912258A patent/EP0974008B1/de not_active Expired - Lifetime
- 1998-02-17 WO PCT/DE1998/000468 patent/WO1998045594A1/de active IP Right Grant
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7302935B2 (en) | 2003-05-26 | 2007-12-04 | Siemens Aktiengesellschaft | Method for operating an internal combustion engine, fuel system, and volume flow control valve |
WO2006037693A1 (de) * | 2004-10-06 | 2006-04-13 | Robert Bosch Gmbh | Kraftstoffsystem für eine brennkraftmaschine |
DE102008043237A1 (de) | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
DE102008043217A1 (de) | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
WO2010049207A1 (de) | 2008-10-28 | 2010-05-06 | Robert Bosch Gmbh | Kraftstoff-hochdruckpumpe für eine brennkraftmaschine |
DE102010004215A1 (de) * | 2010-01-08 | 2011-07-14 | Continental Automotive GmbH, 30165 | Vorrichtung zur Verhinderung des Absterbens des Motors bei einem mit einem Dieseleinspritzsystem ausgestatteten Fahrzeug |
DE102010004215B4 (de) * | 2010-01-08 | 2013-06-06 | Continental Automotive Gmbh | Vorrichtung zur Verhinderung des Absterbens des Motors bei einem mit einem Dieseleinspritzsystem ausgestatteten Fahrzeug |
DE102010027858A1 (de) | 2010-04-16 | 2011-11-24 | Robert Bosch Gmbh | Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
EP0974008A1 (de) | 2000-01-26 |
DE19714489C1 (de) | 1998-10-01 |
WO1998045594A1 (de) | 1998-10-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0974008B1 (de) | Einspritzsystem, druckventil und volumenstromregelventil und verfahren zum regeln eines kraftstoffdruckes | |
EP1772618B1 (de) | Common-Rail-Injektor | |
EP0845077B1 (de) | Kraftstoffeinspritzvorrichtung für brennkraftmaschinen | |
DE3856031T2 (de) | Elektronisch gesteuertes Brennstoffeinspritzventil | |
DE69918902T2 (de) | Brennstoffinjektor | |
EP1756415B1 (de) | Kraftstoffinjektor mit variabler aktorübersetzung | |
EP1047871A1 (de) | Kraftstoffeinspritzsystem für brennkraftmaschinen | |
DE19531652A1 (de) | Kraftstoffeinspritzventil für Brennkraftmaschinen | |
DE2742466A1 (de) | Pumpe-duese fuer luftverdichtende einspritzbrennkraftmaschinen | |
DE19816316A1 (de) | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen | |
DE19630938C2 (de) | Kraftstoffzuleitung mit einem Volumenstromregelventil und Volumenstromregelventil | |
DE102006038840A1 (de) | Kraftstoffinjektor mit Kolbenrückholung eines Druckübersetzerkolbens | |
EP1387937B1 (de) | Kraftstoffeinspritzventil für brennkraftmaschinen mit einem druckschwingungen reduzierenden dämpfungsraum | |
EP1521930A1 (de) | Druckentlastungsventil | |
DE102008032133A1 (de) | Kraftstoffeinspritzvorrichtung | |
DE19737125C2 (de) | Volumenstrom-Regelvorrichtung und Einspritzsystem mit einer solchen Regelvorrichtung | |
EP1290335B1 (de) | Kraftstoffeinspritzventil | |
EP1144842A1 (de) | Injektor für ein kraftstoffeinspritzsystem für brennkraftmaschinen mit in den ventilsteuerraum ragender düsennadel | |
EP1799999A1 (de) | Kraftstoffsystem für eine brennkraftmaschine | |
EP1276987A1 (de) | Kraftstoffeinspritzventil fur brennkraftmaschinen | |
DE10160264A1 (de) | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine | |
DE102008042531A1 (de) | Ventilanordnung zur Kraftstoffhochdruckeinspritzung | |
WO2009130063A1 (de) | Injektor | |
DE10050599B4 (de) | Einspritzventil mit einem Pumpkolben | |
DE102020209574A1 (de) | Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil |
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 |
|
17P | Request for examination filed |
Effective date: 19991005 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): FR IT |
|
17Q | First examination report despatched |
Effective date: 20010514 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): FR IT |
|
ET | Fr: translation filed | ||
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: 20030218 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20060220 Year of fee payment: 9 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20060228 Year of fee payment: 9 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20071030 |
|
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: 20070228 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070217 |