• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    1. INLET PUMP FOR INTERNAL COMBUSTION ENGINE, comprising a housing, a sleeve located in the housing with an inlet opening, placed in the sleeve with reciprocating movement between lower and upper dead spots (LDP and TDC) and blocking the inlet plunger forming a chassis sleeve. volume and having a cut-off edge of the end of fuel injection on the side surface, an injection nozzle with an injection valve, through which the above-plunger volume is in communication with the nozzle, cam Cam shaft connected to a rotating engine organ and a device for controlling the start of fuel injection, consisting of an overflow channel that communicates the above plunger volume with the inlet opening, which is under pressure of the fuel in the above plunger volume of the valve and the opening of the bypass channel with the element valve actuator and valve control system associated with the actuator element, so that, in order to improve efficiency by optimizing the change in the start of fuel injection in ability to control the angular position of the rotating motor, the valve control system is implemented as an angular position sensor of the rotating organ of the engine with a signal delay element, a source of control forces acting on the valve towards the bypass of the channel and having two values, 9 to one of which exceeds the magnitude of the effect on the valve of the pressure required to open the discharge valve to the nozzle, when the plunger moves from BDC and TDC, and the other exceeds the magnitude of the impact and to the valve of minimum pressure in the above plunger volume, when the plunger moves from TDC to BDC, and to the control switching unit, the rotational position sensor of the motor with a delay element connected to: a control switching unit, and the source control force with a primer valve element. 2. Pump POP.1, which differs in that the source of generation of control forces of the control system is made in the form of two hydraulic pressure sources, the control switching unit of the forces in the form of a hydraulic valve, and the element of the valve actuator in the form of a cylindrical valve.
    公开号:SU1192636A3
    申请号:SU823426508
    申请日:1982-04-15
    公开日:1985-11-15
    发明作者:Бастенхоф Дирк
    申请人:Сосьете Дъэтюд Де Машин Термик С.Э.М.Т. (Фирма)；
    IPC主号:
    专利说明:

    1 The invention relates to mechanical engineering, namely engine building, in particular to fuel injection equipment of internal combustion engines, and can be used in the design of high pressure injection fuel pumps with adjustable bypass on the high pressure engine for internal combustion engines. The aim of the invention is to increase the efficiency by optimizing the change in the start of fuel injection depending on the angular position of the rotating body of the motor. Li: i drawing schematically depicts the proposed pump, longitudinal section. The injection pump comprises a housing 1, in which an cylindrical sleeve 2 with inlet openings 3 is installed axially. In the sleeve 2, there is a possibility of direct reciprocating movement between the lower and upper dead points (LDP and TDC) of the secondary edge . 5 on its side surface. In KOiMTyce also supercharger is spaced. iilucer 6 with pressure valve, pan 7. Plunger end 4 with bushing 2 VI discharge nipple 6 forming the displacement 8, KOTopi- ic through the inlet ports 3 communicates with the supply cavity 9 and through the injection valve 7 with the engine nozzle (not shown) ). The inlets 3 are made in the zingyi1dr; the main wall of the sleeve 2 in the vicinity of the small-bore mine terminal of the end face of the plunger 4 and closed at the beginning of its stroke and TDC. In the housing 1, a camshaft with a cam (not shown) is still placed to communicate 45 the reciprocating rectilinear movement to the plunger 4. The camshaft is kinematically associated with the rotor1 1; a connecting organ 10, for example, an engine flywheel. The pump also contains a device for regulating the start of fuel injection, which consists of the bypass channel 11, communicatively the volume 8 with the Q cavity of the power supply and the outlets 55, the valve 12 to close and open the bypass channel 11 with the drive element 13 valve 12 and valve control system 12 associated with the GZ drive element. The shut-off element 14 of the valve 12 is under the action of fuel pressure in the above-plunger volume 8. The drive element 13 is made in the form of a cylindrical slide, mounted slidably in the cylindrical bore 15 and forming a control chamber 16 with a subsequent one. The valve control system 12 is made in the form of an electric sensor 17 of the angular position of the rotating member 10 of the engine with a signal delay element 18, a control force generation source 19 acting on the valve 12 toward the opening of the bypass channel 11, and the control switching unit 20, 17 the angular position of the rotating member 10 of the engine with the signal delay element 18 is connected with the control switching element 20, and the control force generation source 19 with the element 13 of the valve 12, Element 18 Derzhko signal intended for delaying the electrical signals supplied sensor 17 in dependence on one or more engine parameters such as air pressure in the engine, the angular position of the plunger, the maximum pressure of the fuel cycle or speed of the engine. The control system of the valve 12 can be equipped with a switch 21, which ensures that the pump is turned off in the event of an emergency of any engine parameter, such as its speed. The control force generation source 19 is configured as two hydraulic pressure sources 22 and 23. the amount of pressure of one of which exceeds the amount of pressure exerted on the closure element 14 of the valve 12 required to open the discharge valve 7 to the nozzle when the plunger 4 moves from BDC to TDC, and may be 20 bap, and the pressure of the other source exceeds the pressure, which acts on the locking element 14 of the valve 12 on the side of the above-plunger volume 8, when the plunger moves from TDC to BDC, and can be 1-5 bar.
    3
    The control switching unit 20 is designed as an electrically operated hydraulic valve.
    The pump works as follows.
    Plunger 4, moving from BDC to TDC, closes inlet openings 3 and continues its upward movement. During the first upstroke period of the plunger 4, the hydraulic valve of the control effort switching unit 20 is in such a position that the fluid coming from the source 22 of relatively high pressure acts through the control chamber 16 to the actuator element 13 of the valve 12, which is thus in the open position . This means that the over plunger volume 8 communicates with the supply width 9 through the bypass channel 11. Consequently, the fuel injected by the plunger 4 enters the feeding cavity 9. The pressure in the pre-plunger volume 8 remains relatively low and insufficient to open the arterial-negative valve 7, and no fuel flows to the nozzle,
    At a given time, determined by the passage of the rotating body 10 of the engine in front of the sensor 17 of the coal position, an electrical signal is applied to the electric drive of the switch assembly 20, which in this case changes its position. The drive element 13 of the valve 12 stops the high pressure fluid from the source 22 and a low pressure fluid begins to apply from the source 23. The pressure drop in the control chamber 16 causes the valve 12 to close. Considering that the plunger 4 continues to move to TDC, the pressure e in the above-plunger volume 8 increases and causes the opening of the discharge valve 7 which means the beginning of the fuel supply to the nozzle.
    The feed ends at the moment. when cutting edge 5 1 passes (Hered inlet 3).
    The valve 12 opens again during the movement of the plunger 4 from TDC to BDC, when the inlets 3 are closed by the side surface of the plunger 4. Opening the valve 12 during
    364
    the time of such movement of the plunger 4 contributes to a good filling of the above-plunger volume 8 between the fuel feed. The increased pressure acting on the drive element 13 of the valve 12 decreases and again blocks the valve 12 in its open position.
    The moment when the sensor 17 supplies the angular position of the valve control signal of the control switching unit 20 can be selected close to the moment the fuel supply starts, determined by the interaction of the plunger 4 and the inlet ports 3. So that the fuel start time can be changed in a relatively large range after the valve 12j is closed, it is sufficient to set the interval between the moment when the signal from the sensor 17 and the pressure drop over the element 13 of the valve 12 actuator by means of the signal delay element 18. This interval l can be
    selected based on speed
    engine, engine air pressure, plunger angle 4, maximum fuel cycle pressure or depending on any
    another engine parameter.
    The pump can also work in case of overspeed. In this case, it is sufficient not to allow a pressure drop over the drive element.
    13 valve 12.
    In the event of a malfunction of the valve control system 12, the system can be turned off by disconnecting
    hydraulic circuit source 22 with a relatively high pressure. In this case, the moment of fuel supply to the nozzle is determined by the interaction of the plunger 4 and the inlet ports 3,
    those. the engine is running well ahead, determined by the mechanical part of the pump.
    Numerous embodiments of individual parts of the system are possible.
    control like hydraulic
    electric or piezoelectric NOi.
    Such an implementation of the pump allows, by using relatively small values of control efforts in a wide range, to change the moment of the start of fuel injection, simplifies the system of control of the fuel supply.
    gz "
    权利要求:
    Claims (2)
    [1]
    1. SUPPLY PUMP FOR THE INTERNAL COMBUSTION ENGINE, comprising a housing located in the housing of a sleeve with an inlet located in the sleeve with the possibility of reciprocating movement between the lower and upper dead points (BDC and TDC) and blocking the inlet of the plunger above the inlet with the sleeve the volume and having a cut-off edge of the end of the fuel injection on the lateral surface, the discharge fitting with the discharge valve, through which the supra-plunger volume is in communication with the nozzle, the camshaft with cam connected to a rotating organ of the engine, and a device for controlling the beginning of fuel injection, consisting of a bypass channel communicating the plunger volume with the inlet opening, under the influence of the fuel pressure in the plunger volume of the valve for closing and opening the bypass channel with the valve actuator and control system element a valve associated with the actuator element, characterized in that, in order to increase efficiency by optimizing the change in the beginning of fuel injection depending on the angles position of the rotary organ of the engine, the valve control system is made in the form of a sensor of the angular position of the rotary organ of the engine with a signal delay element, a source of generating control forces acting on the valve towards the opening of the bypass channel and having two values, one of which exceeds the magnitude of the effect on the pressure valve required to open the discharge valve to the nozzle when the plunger moves from BDC and TDC, and the other exceeds the value of the minimum pressure in the supra-plunger volume, when the plunger moves from TDC to BDC, and the control effort switching unit, the angular position sensor of the rotating engine member with the delay element is connected to the control effort switching unit, and the control force generation source is connected to the valve drive element.
    [2]
    2. The pump according to claim 1, characterized in that the source of generating control efforts of the control system is made in the form of two hydraulic pressure sources, the switching force control unit is in the form of a hydraulic vein Qj. 1a, and the valve actuator element is in the form of a cylindrical spool.
    类似技术:
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    GB2277556A|1994-11-02|I.c.engine accumulator fuel injection system
    US4580540A|1986-04-08|Fuel injection pump for internal combustion engines
    US5113812A|1992-05-19|Valve control apparatus with magnet valve for internal combustion engines
    US4402290A|1983-09-06|Fuel injection pump
    SU1192636A3|1985-11-15|Delivery pump for internal combustion engine
    JPH02252964A|1990-10-11|Fuel feeding pump controller for internal combustion engine
    JPH10299601A|1998-11-10|Fuel injection system
    US5458103A|1995-10-17|Fuel injection arrangement for internal combustion engines
    US4625700A|1986-12-02|Plunger pump for delivering liquids especially fuels, for reciprocating internal combustion engines
    SU1135433A3|1985-01-15|Fuel-injection device and method of its operation
    US5040511A|1991-08-20|Fuel injection device for internal combustion engines, in particular unit fuel injector
    GB2265948A|1993-10-13|Fuel-injection device ,such as a pump nozzle for internal combustion engines.
    US4733645A|1988-03-29|Fuel injection pump for internal combustion engines
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    US5562428A|1996-10-08|Fuel injection pump having an adjustable inlet poppet valve
    US4458648A|1984-07-10|Fuel injection pump for internal combustion engines
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    US4345563A|1982-08-24|Fuel injection pump for internal combustion engines
    KR880010233A|1988-10-07|Fuel Injection Pumps for Internal Combustion Engines
    US3119592A|1964-01-28|Apparatus for hydraulic control of the valves of an internal combustion engine or motor compressor
    US6092514A|2000-07-25|Fuel injection system for an internal combustion engine
    US20020113140A1|2002-08-22|Fuel injection apparatus for an internal combustion engine
    GB1560100A|1980-01-30|Fuel injection nozzle for an international combustion engine
    EP0413454A1|1991-02-20|Unit injector
    同族专利:
    公开号 | 公开日
    DK155290B|1989-03-20|
    FR2504203A1|1982-10-22|
    FI821295L|1982-10-17|
    FI70300C|1986-09-15|
    ES8304266A1|1983-02-16|
    EP0063523A1|1982-10-27|
    JPS57181967A|1982-11-09|
    AT9606T|1984-10-15|
    DD202197A5|1983-08-31|
    NO156801C|1987-11-25|
    YU45861B|1992-09-07|
    AU549787B2|1986-02-13|
    EP0063523B1|1984-09-26|
    KR880001501B1|1988-08-16|
    FR2504203B1|1985-05-31|
    FI821295A0|1982-04-13|
    ES511459A0|1983-02-16|
    DE3260819D1|1984-10-31|
    AU8267482A|1982-10-21|
    CS274782A2|1988-07-15|
    JPH0413552B2|1992-03-10|
    BR8202126A|1983-03-22|
    CS261858B2|1989-02-10|
    EP0063523B2|1989-10-04|
    YU84482A|1989-02-28|
    NO156801B|1987-08-17|
    US4705006A|1987-11-10|
    FI70300B|1986-02-28|
    KR830010291A|1983-12-30|
    IN157868B|1986-07-12|
    PL236003A1|1982-11-08|
    NO821235L|1982-10-18|
    DK155290C|1989-08-07|
    DK161982A|1982-10-17|
    PL137665B1|1986-07-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE4113957A1|1991-04-29|1992-11-05|Kloeckner Humboldt Deutz Ag|FUEL INJECTION DEVICE|FR693493A|1930-04-07|1930-11-20|Usines De La Chaleassiere Soc|Fuel pump for internal combustion and mechanical injection engines|
    DE6610398U|1967-05-03|1973-11-29|Winkelhofer & Soehne Joh|CHAIN.|
    DE1917927A1|1969-04-09|1970-10-29|Bosch Gmbh Robert|Fuel injection pump for internal combustion engines|
    JPS506043B1|1969-05-19|1975-03-10|
    BE795479A|1972-02-17|1973-08-16|Sulzer Ag|FUEL INJECTION PUMP FOR DIESEL ENGINE|
    JPS5610462B2|1977-07-28|1981-03-07|
    DE2742466C2|1977-09-21|1986-11-27|Daimler-Benz Ag, 7000 Stuttgart|Pump nozzle for injecting fuel into an air-compressing internal combustion engine|
    GB2041577B|1979-01-31|1983-04-13|Lucas Industries Ltd|Fuel system for internal combustion engines|
    US4385614A|1979-04-06|1983-05-31|Robert Bosch Gmbh|Fuel injection pump for internal combustion engines|
    FR2482669B2|1979-05-28|1984-07-06|Semt|
    US4343280A|1980-09-24|1982-08-10|The Bendix Corporation|Fuel delivery control arrangement|
    US4364351A|1981-05-18|1982-12-21|General Motors Corporation|Diesel engine fuel limiting system|DE3375596D1|1982-11-25|1988-03-10|Kawasaki Heavy Ind Ltd|Fuel injection timing control system|
    DE3248086C2|1982-12-24|1986-10-16|L'Orange GmbH, 7000 Stuttgart|Fuel injection pumps for internal combustion engines, in particular for diesel engines|
    DE3506392A1|1985-02-23|1986-09-04|Motoren-Werke Mannheim AG vorm. Benz Abt. stationärer Motorenbau, 6800 Mannheim|INJECTION SYSTEM FOR A DIESEL ENGINE WITH A HIGH PRESSURE INJECTION PUMP FOR EVERY CYLINDER|
    GB8828159D0|1988-12-02|1989-01-05|Lucas Ind Plc|Fuel injection pump|
    DE4010450A1|1990-03-31|1991-10-02|Bosch Gmbh Robert|Fuel injection pump for IC engine - has grooved piston for return flow at max. pressure|
    GB9306603D0|1993-03-30|1993-05-26|Lucas Ind Plc|Fuel pump|
    JP3905282B2|2000-04-18|2007-04-18|トヨタ自動車株式会社|High pressure pump|
    JP3936119B2|2000-04-18|2007-06-27|トヨタ自動車株式会社|High pressure pump and high pressure pump assembly structure|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR8107685A|FR2504203B1|1981-04-16|1981-04-16|INJECTION PUMP FOR AN INTERNAL COMBUSTION ENGINE COMPRISING A DEVICE FOR ADJUSTING THE DELIVERY TIME OF THE INJECTION FUEL|
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