EP0346607A2 - Dispositif de contrôle hydraulique pour systèmes d'injection du carburant pour machines à combustion interne - Google Patents

Dispositif de contrôle hydraulique pour systèmes d'injection du carburant pour machines à combustion interne Download PDF

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Publication number
EP0346607A2
EP0346607A2 EP19890108081 EP89108081A EP0346607A2 EP 0346607 A2 EP0346607 A2 EP 0346607A2 EP 19890108081 EP19890108081 EP 19890108081 EP 89108081 A EP89108081 A EP 89108081A EP 0346607 A2 EP0346607 A2 EP 0346607A2
Authority
EP
European Patent Office
Prior art keywords
control
piston
fuel injection
working
pump
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.)
Withdrawn
Application number
EP19890108081
Other languages
German (de)
English (en)
Other versions
EP0346607A3 (fr
Inventor
Rudolf Babitzka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0346607A2 publication Critical patent/EP0346607A2/fr
Publication of EP0346607A3 publication Critical patent/EP0346607A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston
    • 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
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the invention relates to a hydraulic control device according to the preamble of the main claim.
  • hydraulic control devices which work with closed liquid-filled rooms and in which pistons and valve surfaces are acted upon
  • the basic relationship between the surface exposed to the liquid and that of the liquid pressures and the surfaces results problems that can be derived when the time factor plays a role.
  • the same force can be achieved, for example, by a low pressure in a large area or a high pressure in a small area, the mastery of the volume, ie the amount flowing off per unit of time, being decisive for the time factor.
  • the valves used for control should on the one hand have an extremely short opening and closing time factor and on the other hand the lowest possible flow resistance, ie the largest possible control cross section.
  • Such a hydraulic control device becomes problematic when large volumes of liquid under high pressure are to be controlled in very short time periods, as is the case, for example, with fuel injection, in which the speed changes in less than a millisecond and this changes Control must run.
  • the fuel injection can be interrupted by relieving the pressure in the pump work space via a relief channel, this channel being controlled via a solenoid valve.
  • the movable valve member of the solenoid valve is un because of the high pressure of the pump work space acted upon indirectly, so that when the valve is closed, considerable locking forces must be applied in accordance with the functional surface acting in the opening direction on the movable valve member, as long as no outflow is to take place.
  • a solenoid valve that is open when de-energized as is usually used for such a purpose for safety reasons, the energy consumption of the magnet is proportional to the required locking forces.
  • a relatively large cross-section must usually be selected with the short times available, which leads to large, expensive magnets and correspondingly high power consumption.
  • a pressure line branches off from the pump work space, via which the fuel is fed to an alternative piston, which is always displaced by the delivery pressure of the injection pump when the solenoid valve is open, the one on the rear of the alternative piston existing space is relieved of pressure by the solenoid valve.
  • This piston is loaded by a return spring that this in the case of evasive fuel injected towards the end of the injection and after the end of the high-pressure delivery via the injection nozzle into the combustion chamber of the internal combustion engine. As a result, the spray duration is extended and the internal combustion engine runs quieter.
  • the hydraulic control according to the invention with the characterizing features of the main claim has the advantage that the liquid volume that has to flow through the valve for a certain displacement of the control piston within a certain time that this volume the upstream in the control piston, swallowed during the movement, is reduced by the size ratio of the working surface to the control surface. This means that if the control surface is twice as large as the working surface, the volume that has to flow through the valve is just half as large as the volume flowing through the control surface.
  • the pressure in the work area increases inversely proportional to the control room pressure, ie the pressure in the work area is greater by the ratio of the control area to the work area than in the control room.
  • This pressure in the working area in turn acts on the movable valve member of the valve, so that its closing forces must be adapted to this pressure. Due to the area ratio between the working area and the control area, the volume to be controlled by the valve can be greatly reduced, the opening cross section of the valve can also be reduced accordingly, it now advantageously being found that, with the closing force remaining the same, a time-cross-sectional gain corresponding to the area ratio can be achieved by using the stepped piston is.
  • the advantage can also be described in such a way that, due to the reduction in the volume to be controlled, despite the increase in pressure which is given, while the closing force of the movable valve member remains the same, the area ratio corresponds the time opening cross-sectional gain is available, that is, with the same amount of closing force on the valve, a faster stroke of the control piston can be achieved or, conversely, for a certain speed of the control piston, a smaller opening cross section on the valve is sufficient in the invention.
  • This advantage has a particular effect on fuel injection pumps for internal combustion engines, in which the working cycles are extremely short - for example in a four-cylinder internal combustion engine and 4000 rpm, which corresponds to approximately 66 working cycles of the alternative piston per second and this varies depending on the speed .
  • a solenoid valve is used as the control valve, so that the advantage of the invention of the lower actuating forces required has a particular effect, since the effort for generating a magnetic force not only increases disproportionately to the actuating force size, but also in terms of costs.
  • the stepped piston is spring-loaded in the direction of the pump work space, so that it is automatically pushed back into an initial position after the pressure in the pump work space has been reduced.
  • the stepped piston can serve as an escape piston or for controlling a relief channel.
  • the control piston working as an evasive piston is displaced by the pressure in the pump work space against the restoring force as soon as the valve is open, a volume being stored in front of its control surface, which volume is then returned by the control piston towards the end of the injection.
  • this return leads directly to the injection via the injection valve or that this storage quantity is supplemented by the controller of the injection pump for injection.
  • an extension of the spraying time is achieved by this device, which is particularly important when idling, in order to achieve quiet operation of the machine.
  • the control piston controls the passage of the relief channel
  • a large outflow cross section on the control piston is controlled according to the invention by the small control valve.
  • FIG. 1 shows a distributor injection pump in longitudinal section with the step piston as a pilot-operated valve
  • FIG. 2 shows a detail of the distributor pump according to FIG. 1 with the step piston as an evasive piston, on an enlarged scale.
  • a pump piston 1 which also serves as a distributor, is set into a reciprocating and simultaneously rotating movement by a drive shaft 2 and with the aid of a cam gear 3.
  • fuel is conveyed from a pump working chamber 4 via a longitudinal distribution groove 5 to one of a plurality of pressure channels 6, which are arranged around the pump piston 1 at uniform angular intervals and each lead to a combustion chamber (not shown) of an internal combustion engine.
  • the pump work chamber 4 is supplied with fuel via a suction channel 7 from a suction chamber 8 which is present in the housing of the injection pump and is filled with fuel, in that the suction channel 7 is opened by longitudinal control grooves 9 provided in the pump piston 1 during the suction stroke of the pump piston 1.
  • the number of control grooves 9 corresponds to the number of pressure channels 6 and thus to the number of pressure strokes carried out per revolution of the pump piston.
  • the quantity to be injected per stroke into one of the pressure channels 6 is determined by the axial position of a slide valve 11 arranged around the pump piston 1. This axial position is determined by a speed controller 12 and an arbitrarily actuated adjusting lever 13, evaluating the respective speed and load (the load can correspond, for example, to the position of the accelerator pedal of the motor vehicle).
  • the suction chamber 8 is supplied with fuel by a feed pump 14, which is driven by the drive shaft 2 and supplies fuel from a fuel tank 15 and a suction line 16.
  • the output pressure of the feed pump 14 and thus the pressure in the suction chamber 8 are controlled by a pressure control valve 17, this pressure also increasing the speed also increases according to a desired function.
  • the cam drive 3 and the speed controller 12 are arranged in the suction chamber 8 and are thus acted upon on all sides by this pressure and are lubricated by this fuel.
  • the cam drive 3 has a roller ring 19 carrying rollers 18, which is rotatably mounted in the housing by a certain angle and in the U-shaped cross section of which the rollers 18 are mounted.
  • This roller ring 19 is coupled in a rotationally locking manner to an injection adjustment piston 22 via an adjustment bolt 21, this injection adjustment piston 22 being shown rotated by 90 ° in the drawing, ie working perpendicular to the plane of the illustration.
  • In the inner bore of this roller ring 19 there is a claw coupling in which claws 23 on the drive side 2 of the drive shaft 2 mesh with claws 24 on the output side of the pumping and distributing piston 1, so that the pumping and distributing piston 1 independently of the drive shaft 2 exert a lifting movement while rotating can.
  • An end cam disk 25 is arranged on the pump piston 1 and runs with its end cam 26 on the rollers 18, the number of end cams in turn corresponding to the number of pressure channels 6.
  • the front cam disk 25 is supported by springs 27, only one of which is shown, pressed onto the rollers 8 with its career.
  • a high-pressure control line 28 branches off from the pump work chamber 4, which leads to a control piston 29, which is of stepped design and is axially displaceably guided in a corresponding stepped bore 30, its end face of larger diameter, which is referred to here as control surface 31, facing the pump work chamber 4 .
  • its second end face of smaller diameter, here called working surface 32 delimits a section of stepped bore 30 which is closed by a solenoid valve 33 and is called working space 42.
  • the control piston 29 is loaded by a spring 34 in the direction of the control chamber 40.
  • the solenoid valve 33 is constructed so that it is "open when de-energized". As soon as the solenoid 35 of this solenoid valve 33 is energized, the movable valve member 36 is pulled onto the valve seat 37 and the working space 42 is closed. The functional surface 43 of the movable valve member 36 which is then acted upon from the working space and acts in the opening direction is smaller than the working surface 32 and determines the maximum opening cross section of the solenoid valve 33.
  • a solenoid valve 33 with a relatively small functional surface 43 or small valve seat 37 is sufficient, since corresponding to the area ratio on the control piston 29 for a specific control piston stroke to be controlled a desired volume upstream of the control surface 31, that is to say corresponding to a relatively large amount, only a relatively small amount has to flow out of the working space 42 via the valve seat 37.
  • an input 41 of a second relief channel 44 is controlled by the piston 39 of larger diameter of the control piston 29 assigned to the control surface 31, so that after the stroke movement of the control piston 29 the pump work chamber 4 is relieved of pressure towards the suction chamber 8. The consequence of this is that no pressure can build up in the pump work chamber 4 and the internal combustion engine is switched off.
  • the second embodiment of the invention shown in Fig. 2 is in principle similar to the first example, only with the difference that the control piston 29 'serves here as an escape piston and that the solenoid valve 33' is closed when de-energized.
  • the solenoid 35 'of the solenoid valve 33' is energized, the movable valve member 36 'lifts off from the valve seat 37' and the fuel under pressure in the pump work chamber moves the control piston 29 to the right, with fuel 32 from the work chamber 42 and through its working surface the relief channel 38 'is displaced to the pump suction chamber.
  • This fuel volume which is collected in the form of a store in front of the control surface 31, is then conveyed back to the pump work chamber 4 or via the latter and one of the pressure channels 6 to the internal combustion engine and there, after the high pressure phase in the pump work chamber 4 has been stopped, during the rest of the pump piston 1 or the subsequent suction stroke injected.
  • This quantity can also be supplemented by the controller on the pump side.
  • This procedure, a certain amount during the injection between storing is known as the so-called silent running method, because it extends the spraying time and thus makes the motor silent.
  • this volume to be controlled by the solenoid valve 33 in the working space 42 is only half as large as the original volume in the control space 40, the drain cross-section of the working space or the functional surface 43 of the solenoid valve can also be reduced accordingly, and so too to reduce closing forces acting on the valve member based on the pressure in the working space 42.
  • a gain in the direction of the opening time cross section can be achieved, that is to say one higher positioning speed of the control piston is achievable than in the known systems without a stepped piston design.
  • the invention is illustrated using a numerical example.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP89108081A 1988-06-11 1989-05-05 Dispositif de contrôle hydraulique pour systèmes d'injection du carburant pour machines à combustion interne Withdrawn EP0346607A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3819996 1988-06-11
DE3819996A DE3819996A1 (de) 1988-06-11 1988-06-11 Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0346607A2 true EP0346607A2 (fr) 1989-12-20
EP0346607A3 EP0346607A3 (fr) 1990-02-14

Family

ID=6356392

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108081A Withdrawn EP0346607A3 (fr) 1988-06-11 1989-05-05 Dispositif de contrôle hydraulique pour systèmes d'injection du carburant pour machines à combustion interne

Country Status (4)

Country Link
US (1) US5007400A (fr)
EP (1) EP0346607A3 (fr)
JP (1) JPH0233462A (fr)
DE (1) DE3819996A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991002897A1 (fr) * 1989-08-23 1991-03-07 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs a combustion interne

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3934953A1 (de) * 1989-10-20 1991-04-25 Bosch Gmbh Robert Magnetventil, insbesondere fuer kraftstoffeinspritzpumpen
DE3943299A1 (de) * 1989-12-29 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US6394072B1 (en) * 1990-08-31 2002-05-28 Yamaha Hatsudoki Kabushiki Kaisha Fuel injection device for engine
GB9203636D0 (en) * 1992-02-19 1992-04-08 Lucas Ind Plc Fuel pumping apparatus
DE19713868A1 (de) * 1997-04-04 1998-10-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
JP3852753B2 (ja) * 2001-12-04 2006-12-06 株式会社デンソー 燃料噴射ポンプ
JP6411313B2 (ja) * 2015-11-26 2018-10-24 ヤンマー株式会社 燃料噴射ポンプ

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3211680A1 (de) * 1982-03-30 1983-10-06 Espenschied Helmut Dipl Ing Kraftstoffeinspritzsystem fuer brennkraftmaschinen
EP0114375A2 (fr) * 1983-01-25 1984-08-01 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air
GB2168130A (en) * 1984-11-30 1986-06-11 Lucas Ind Plc Electromagnetically operable valve
EP0193788A2 (fr) * 1985-03-06 1986-09-10 Robert Bosch Gmbh Procédé de commande de quantité de combustible injecté
EP0290797A2 (fr) * 1987-05-11 1988-11-17 Robert Bosch Gmbh Pompe d'injection de combustible

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2076561B (en) * 1980-04-26 1985-04-03 Diesel Kiki Co Distribution type fuel injection apparatus
US4480619A (en) * 1982-06-08 1984-11-06 Nippon Soken, Inc. Flow control device
JPS5951139A (ja) * 1982-09-17 1984-03-24 Nippon Soken Inc 燃料供給装置
DE3375596D1 (en) * 1982-11-25 1988-03-10 Kawasaki Heavy Ind Ltd Fuel injection timing control system
GB8406271D0 (en) * 1984-03-09 1984-04-11 Lucas Ind Plc Hydraulic mechanism
GB8417864D0 (en) * 1984-07-13 1984-08-15 Lucas Ind Plc Fuel pumping apparatus
GB8432310D0 (en) * 1984-12-20 1985-01-30 Lucas Ind Plc Liquid fuel pumping apparatus
JPH0692743B2 (ja) * 1985-04-01 1994-11-16 日本電装株式会社 流体制御用電磁弁
JPS635140A (ja) * 1986-06-24 1988-01-11 Diesel Kiki Co Ltd 燃料噴射ポンプの噴射制御方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3211680A1 (de) * 1982-03-30 1983-10-06 Espenschied Helmut Dipl Ing Kraftstoffeinspritzsystem fuer brennkraftmaschinen
EP0114375A2 (fr) * 1983-01-25 1984-08-01 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air
GB2168130A (en) * 1984-11-30 1986-06-11 Lucas Ind Plc Electromagnetically operable valve
EP0193788A2 (fr) * 1985-03-06 1986-09-10 Robert Bosch Gmbh Procédé de commande de quantité de combustible injecté
EP0290797A2 (fr) * 1987-05-11 1988-11-17 Robert Bosch Gmbh Pompe d'injection de combustible

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991002897A1 (fr) * 1989-08-23 1991-03-07 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs a combustion interne

Also Published As

Publication number Publication date
JPH0233462A (ja) 1990-02-02
US5007400A (en) 1991-04-16
DE3819996A1 (de) 1989-12-14
EP0346607A3 (fr) 1990-02-14

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