DE102005057526B4 - Control valve and fuel injector with this - Google Patents

Control valve and fuel injector with this

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Publication number
DE102005057526B4
DE102005057526B4 DE200510057526 DE102005057526A DE102005057526B4 DE 102005057526 B4 DE102005057526 B4 DE 102005057526B4 DE 200510057526 DE200510057526 DE 200510057526 DE 102005057526 A DE102005057526 A DE 102005057526A DE 102005057526 B4 DE102005057526 B4 DE 102005057526B4
Authority
DE
Germany
Prior art keywords
valve
cylinder
valve body
control
pressure
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 - Fee Related
Application number
DE200510057526
Other languages
German (de)
Other versions
DE102005057526A1 (en
Inventor
Shigeiku Nishio Enomoto
Hirokuni Nishio Tomita
Yoshihisa Kariya Yamamoto
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.)
Denso Corp
Soken Inc
Original Assignee
Denso Corp
Soken Inc
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
Priority to JP2004-349966 priority Critical
Priority to JP2004349966A priority patent/JP4286770B2/en
Application filed by Denso Corp, Soken Inc filed Critical Denso Corp
Publication of DE102005057526A1 publication Critical patent/DE102005057526A1/en
Application granted granted Critical
Publication of DE102005057526B4 publication Critical patent/DE102005057526B4/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00Fuel-injectors combined or associated with other devices
    • F02M57/02Injectors structurally combined with fuel-injection pumps
    • F02M57/022Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027Electrically actuated valves draining the chamber to release the closing pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0003Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0014Valves characterised by the valve actuating means
    • F02M63/0028Valves characterised by the valve actuating means hydraulic
    • F02M63/0029Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0038Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details rotary

Abstract

Control valve (3) with:
a valve housing (61, 62) including a first cylinder (30a), a second cylinder (30b) coaxial with the first cylinder (30a), a communication passage (30c) including the first cylinder (30a) and the second cylinder (30b ), a first port (28) opening to the first cylinder (30a), a second port (22) opening to the second cylinder (30b), and a control port (14a, 15a) leading to the communication passage (30c) opens a first valve seat (63) for allowing and preventing communication between the first cylinder (30a) and the control port (14a, 15a) and a second valve seat (64) for allowing and preventing communication between the second Cylinder (30b) and the control port (14a, 15a) has;
a first valve body (31) slidably installed in the first cylinder (30a) to open and close the first valve seat (63);
a second valve body (32) slidably mounted in the second cylinder ...

Description

  • The The present invention relates to a generic term of claim 1
  • Fener The invention relates to a fuel injection valve according to the claim 15th
  • Industrial attention is given to a common rail system in which a conventional pressure accumulator (a common rail) supplies fuel. Recently, it has been demanded to increase a fuel injection pressure in order to improve an output of the engine, to improve fuel consumption performance, and to purify exhaust gas. WO-00-055496-A discloses an amplifying apparatus for a fuel injection valve that realizes the above requirement in a simple manner.
  • Usually, the fuel injection valve reinforcing device is provided with a pressure increasing piston for pressurizing the fuel supplied from the common rail to increase the fuel injection pressure. 5 shows a structure of the amplifying apparatus according to WO-00-055496-A which is an example of this type of the fuel injection valve reinforcing device. The common rail 10 accumulates the fuel, which is supplied from a fuel tank T and is pressurized by a high-pressure pump P to the fuel at a certain pressure to an oil pressure accumulator 101 of the fuel injection valve 100 supply. A reinforcing element between the common rail 10 and the oil pressure accumulator 101 puts the fuel under pressure, that of the pressure-increasing chamber 104 is to be supplied, using the pressure increasing piston 103 , and then leads the fuel to the oil pressure accumulator 101 to. The pressure booster piston 103 is achieved by increasing and decreasing the fuel pressure in the pressure chamber 106 using an electromagnetically driven gain control valve 105 actuated.
  • The fuel in the common rail 10 also becomes a back pressure chamber 108 a needle 109 fed, which opens and closes an injection hole. When an injection control valve 107 opens to the fuel pressure in the back pressure chamber 108 To decrease, the needle moves 109 up to the fuel in the common rail 10 or inject the fuel pressurized by the reinforcing member. The boosting device allows the fuel to be injected at an even higher pressure to realize a desired fuel injection ratio by performing accurate controls according to a driving state.
  • The reinforcing element control valve 105 To control the pressurizing process is a two-position three-way valve. The reinforcing element control valve 105 increases and decreases the fuel pressure in the pressure chamber 106 by switching a seating position of a venil body to selectively the pressure chamber 106 with the common rail 10 or a return passage. In general, the valve body of the two-position three-way valve is a spool valve having a cylindrical seal portion, or a valve having two tapered seat portions. JP-3452850-B2 discloses a control valve for controlling a nozzle of a fuel injection valve having a valve element provided with a tapered seat and a tubular, flat seat. This control valve has an advantage in that one of the valve seat portions is flat, so that an excessively large alignment accuracy in assembling is not required.
  • In general, the control valve, which has a large seat diameter to control a large amount of fuel flow, needs a high driving power. In the three-way valve according to JP-3452850-B2 For example, an upper seat diameter and a lower seat diameter are equal to each other to balance the fuel pressure, and to reduce the driving force of the control valve, however, accurate machining is necessary when machining the three-way valve to prevent fuel from the pipe seat escapes. Further, an oil layer in the pipe seat generates a valve opening force in a valve closing time, so that a relatively large valve closing force is necessary to prevent this valve opening force.
  • WO 2004/088121 A1 shows a servo valve according to the preamble of claim 1. The control valve has a first and a second valve housing, which form two interconnected cylinder chambers. In the cylinder chambers an integrally formed valve piston is slidably received, such that with this a first valve seat, which is formed on the first valve housing, or a second valve seat, which is formed on the second valve housing, can be opened or closed.
  • DE 103 15 015 A1 discloses a servo valve with a valve housing in which an integrally formed valve piston is slidably received. Valve seats formed on the valve housing can be opened or closed by means of the valve piston.
  • It is the object of the present invention To provide a simple to install control valve, which allows a smooth valve closure reliable.
  • The The object of the invention is provided with a control valve according to claim 1 solved.
  • advantageous Further developments of the invention are the subject of the dependent claims.
  • Other Objects, features and advantages of the present invention as well as working procedures and the function of the associated parts, from a study of the following detailed description, the attached Claims and of the drawings, all of which form part of this application. In the drawings:
  • 1 is a schematic diagram showing an overall structure of a common rail fuel injection apparatus according to the present invention.
  • 2 an explanatory diagram showing a structure and an operation of a hydraulic servo valve of the pressure-increasing common rail fuel injection element according to a first embodiment of the invention.
  • 3A FIG. 12 is a cross-sectional view showing a detailed construction of the hydraulic servo valve according to the first embodiment of the present invention; FIG.
  • 3B a cross-sectional view showing a detailed structure of a hydraulic servo valve according to a second embodiment of the invention;
  • 3C FIG. 10 is a cross-sectional view showing a detailed structure of a hydraulic servo element according to a third embodiment of the present invention; FIG.
  • 3D FIG. 10 is a cross-sectional view showing a detailed structure of a hydraulic servo valve according to a fourth embodiment of the present invention; FIG.
  • 3E shows a plan view of a valve body of the hydraulic servo valve according to the first embodiment of the present invention;
  • 4A FIG. 10 is a cross-sectional view showing a detailed structure of a hydraulic servo valve according to a fifth embodiment of the invention; FIG.
  • 4B FIG. 10 is a cross-sectional view showing a detailed structure of a hydraulic servo element according to a sixth embodiment of the present invention; FIG.
  • 4C FIG. 10 is a cross-sectional view showing a detailed construction of a hydraulic servo valve according to a seventh embodiment of the present invention; FIG.
  • 5 is a schematic diagram showing an overall structure of a conventional common rail fuel injection device.
  • First Embodiment
  • In the following, a first embodiment of the present invention will be described with reference to the drawings. 1 shows a structure of a common rail fuel injection device 1 for a diesel engine that uses a hydraulic servo valve 3 is provided, that is, with a three-way control valve, which applies the present invention. In 1 is the fuel injection device 1 over a high pressure fuel passage 21 , which is a high pressure fluid passage, with the common rail 2 for an accumulation of high-pressure fuel in this connected. The common rail 2 is with a conventional high-pressure feed pump 23 connected, which is provided with a variable Auslassmengenmechanismus. The feed pump 23 puts the fuel in the fuel tank 24 under pressure and supplies the pressurized fuel to the common rail 2 to.
  • The fuel injection device 1 has a reinforcement device 4 for pressurizing the fuel in the common rail 2 , and an injector 7 for injecting the fuel passing through the reinforcing device 4 is pressurized. An electromagnetic valve 5 and a hydraulic servo valve 3 control operations or operation of the amplification device 4 and the injector 7 , The electromagnetic valve 5 is a two-position two-way valve. The electromagnetic valve 5 increases and decreases a pressure of a control fluid in a servo valve control chamber 13 , which is a hydraulic chamber, by opening and blocking a connection between a return passage 27 , which is a low-pressure fluid passage associated with the fuel tank 24 connected, and the hydraulic servo valve 3 , The electromagnetic valve 5 has a conventional structure in which an electric actuator such as a solenoid controls a valve body to open and close the valve. The hydraulic servo valve 3 is a characteristic part of the present invention and will be described in detail below.
  • A pressure booster piston 44 is in a stepped cylinder 45 installed, which has two (one big and one small) diameter to slidable in a vertical direction in the drawing. That is the stepped cylinder 45 has an upper cylinder 30a which has the large diameter, and a lower cylinder 30b which has the small diameter. The pressure booster piston 44 has a booster chamber 41 at a lower end portion of the stepped cylinder 45 , The reinforcing device 4 increases and decreases a pressure in the pressure-increasing chamber 41 by the sliding movement of the pressure increasing piston 44 , The pressure booster piston 44 has a stepped shape with two (one large and one small) diameters, that is, with an upper piston with the large diameter and a lower piston with the small diameter. The upper piston slides in the upper cylinder 30a and the lower end portion of the lower piston slides in the lower cylinder 30b to ensure an oil seal in between. A lower end surface of the lower piston and an inner peripheral surface of the stepped cylinder 45 define a chamber wall of the pressure increasing chamber 41 , The pressure booster piston 44 also has a high pressure chamber 42 at an upper end portion of the stepped cylinder 45 , Specifically, an upper end surface of the upper piston and the inner peripheral surface of the stepped cylinder define 45 the chamber wall of the high pressure chamber 42 , The high pressure chamber 42 is about the high pressure fuel passage 21 with the common rail 2 connected.
  • In the top cylinder 30a of the cylinder 45 is a gain control chamber 11 trained to the lower piston of the pressure booster piston 44 to surround. The gain control chamber 11 is through a gain control passage 14 that the mouth or opening 141 has, with the hydraulic servo valve 3 connected, and through a passage which the check valve or check valve 16 has, with the pressure booster chamber 41 , The gain control chamber 11 has a spring in it 43 installed to the pressure booster piston 44 to push up. In this state, the upper end surface of the pressure-increasing piston becomes 44 a fuel pressure in the high pressure chamber 42 exposed, and the lower end surface of the pressure increasing piston 44 becomes a resultant force of fuel pressure in the boost control chamber 11 and a restoring force of the spring 43 subjected. A pressure decrease in the gain control chamber 11 moves the pressure booster piston 44 down to pressurize the fuel leading to the booster chamber 41 should be supplied.
  • The injector 7 has a nozzle body 72 and a nozzle needle 71 Slidable in the nozzle body 72 is installed. The nozzle needle 71 is by a command piston 73 driven to an injection hole 74 to open and close, at a front end portion of the nozzle body 72 is provided. The oil pressure accumulator 75 is through a passage 17 with the pressure booster chamber 41 connected. Above the command piston 73 is an injection control chamber 12 intended. The injection control chamber 12 is through an injection control passage 15 that the mouth or opening 151 has, with the hydraulic servo valve 3 connected. The command piston 73 has a larger diameter than the nozzle needle 71 , A feather 76 is arranged to form a connecting section between the command piston 73 and the nozzle needle 71 to surround the command piston 73 to push up and around the nozzle needle 71 to push down. In this construction, a pressure decrease in the injection control chamber raises 12 the command piston 73 and the nozzle needle 71 up to inject the fuel from the oil pressure accumulator 75 is supplied.
  • In the following is a structure of the hydraulic servo valve 3 , which is a characteristic part of the present invention, with reference to 2 described. As in 2 shown has the hydraulic servo valve 3 a cylinder 65 provided in a valve housing and an upper valve 31 and a lower valve 32 in the cylinder 65 are installed. The upper valve 31 serves as a first valve element of the present invention, and the lower valve 32 serves as a second valve element of the present invention. The upper valve 31 has a roughly cylindrical shape and its upper end is closed. The upper valve 31 has an upper half portion serving as a sliding portion and a lower half portion having a smaller diameter than the upper half portion. The lower half section of the upper valve 31 has an upper valve head 33 which has a tapered surface (a tapered surface) whose diameter gradually decreases toward an opening end portion of the lower half portion. The lower valve 32 has a roughly cylindrical shape. An upper half section of the lower valve 32 is in the cylinder of the upper valve 31 installed and supported by this. A lower end portion of the lower valve 32 has a lower valve head 33 which has a tapered surface (a tapered surface) whose diameter gradually increases toward a lower end portion thereof. The cylinder 65 has a stepped shape, in which an elongated middle section 30c has a smaller diameter than other sections. A step portion at an upper end of the central portion 30c serves as an upper valve seat 63 , which is a first valve seat according to the present invention, to which the upper valve 31 sitting. Another step section at a lower end of the central section 30c serves as a lower valve seat 64 , which is a second valve seat according to the present invention, to which the lower valve 32 sitting. The lower valve 32 extends from the middle section 30c of the cylinder 65 downward. The lower end portion of the lower valve 32 , with the lower valve head 33 is provided in the lower end portion of the cylinder 65 Installed.
  • A valve housing consists of a seat surface element 61 in which the middle section 30c of the cylinder 65 is formed, the valve seats 63 . 64 has, and from a housing element 62 , in which the lower end portion of the cylinder 65 is trained. The seat surface element 61 and the housing element 92 bump against each other. The seat surface element 61 is with a return port 28 provided as a first terminal according to the present invention. One end of the return connection 28 opens to a side surface of the cylinder 65 at its section above the upper valve seat 63 To connect to a space around the lower half section of the upper valve 31 to be connected. The other end of the return port 28 is with the return passage 27 connected. The seat surface element 61 is further provided with a gain control passage 14 and an injection control passage 15 Mistake. One end of the gain control passage 14 or the injection control passage 15 opens to the side surface of the cylinder 65 at its section between the valve seats 63 . 64 to use a space around the middle section of the lower valve 32 to be connected. The other ends of the gain control passage 14 or the injection control passage 15 are with the gain control chamber 11 the reinforcing device 4 or the injection control chamber 12 the injector 7 connected. The housing element 62 is with a high pressure connection 22 provided as a second terminal according to the present invention. The high pressure connection 22 opens to a center at a lower end surface of the cylinder 65 and is with a space around the lower end portion of the lower valve 31 connected around. The lower end surface of the lower valve 32 that the high pressure connection 22 is provided with a hemispherical recess, so that a fuel flow from the high pressure port 22 inflows, not throttled when the lower valve 32 opens.
  • The servo valve control chamber 13 is provided at an upper end portion of the cylinder, which slidably in the upper valve 31 Has. An upper end surface of the upper valve 31 and the inner wall surface of the cylinder 65 define a chamber wall of the servo valve control chamber 13 , The servo valve control chamber 13 is through a passage that opens to the side surface of her and with a Einströmöffnung or inlet 25 is provided with the high pressure chamber 42 the reinforcing device 4 connected. The servo valve control chamber 13 is further characterized by a passage that opens to the upper surface of it and with a Ausströmöffnung or outflow opening 26 is provided with the return passage 27 via the electromagnetic valve 5 connected. By driving or operating the electromagnetic valve 5 becomes a connection between the servo valve control chamber 13 and the return passage 27 controlled to the upper valve 31 and the lower valve 32 to move in one piece up and down. In particular, as in 3A and 3E is shown, the upper end surface of the upper valve 31 depressed at their central section. An outer peripheral portion of the upper end surface of the upper valve 31 which projects upwards is with a radially extending groove 311 at a position provided by him. The groove 311 is constructed so that the fuel from the inlet opening 25 to the servo valve control chamber 13 can flow, even if the upper valve 31 is at an upper position.
  • In the hydraulic servo valve 3 is a surface A1 of the upper end surface of the upper valve 31 larger than an area A4 of the lower end surface of the lower valve 32 , The hydraulic servo valve 3 is with a low pressure portion between the sliding portion and the upper valve head 33 fitted to the return port 28 to be connected. In the present embodiment, the area of the upper valve head is the area 33 and the area or area of the lower valve head 32 set to be equal to each other; however, they may be different from each other provided that the area A4 of the lower end surface is larger than the upper valve head 33 , By this construction, the pressure in the servo control chamber switches 13 a sitting position around. A big pressure in the servo valve control chamber 13 increases a downward acting hydraulic force to the upper valve seat 33 of the hydraulic servo valve 3 close. A low pressure in the servo control chamber 13 increases an upward hydraulic force to the lower valve head 33 close.
  • In the following is the operation of the hydraulic servo element 3 and the fuel sprayer 1 with reference to the 1 and 2 described. As in 1 is shown is the electromagnetic valve (two-position two-way valve) 5 configured to close in a non-energized state to a connection between the discharge port 26 and the return passage 27 in the hydraulic servo valve 3 to interrupt. In this state, as in 2 shown, makes a pressure of the common rail 25 passing through the inlet opening 25 is transmitted, the pressure in the servo valve control chamber 13 large. Thus, the upper valve head 33 of the upper valve 33 on the upper valve seat 63 set and the lower valve head 33 of the lower one valve 32 gets from the lower valve head 33 lifted away or moved away. As a result, the gain control passage 14 and the injection control passage 15 with the high pressure connection 22 connected, and the pressure in the gain control chamber 11 and the injection control chamber 12 is big. Thus, the nozzle needle 71 the injector 7 at a lowermost position so as not to inject the fuel.
  • At the fuel injection start time, the electromagnetic valve becomes 5 energized to the electromagnetic valve 5 to open so that the outflow opening 26 and the return passage 27 in the hydraulic servo valve 3 interconnected to the fuel pressure in the servo valve control chamber 13 make small ("switching on" of the electromagnetic valve in the 2 ). During this time, a following relationship is fulfilled: Upward force (= (A2 + A4) × Fp)> downward force (= A5 × Fp) (1)
  • Thus, the upper and lower valves move 31 . 32 in the drawing up by a difference between a hydraulic pressure above the valves 31 . 32 and below the valves 31 . 32 , As a result, the upper valve head moves 33 of the upper valve 31 from the upper valve seat 63 away, and then the lower valve head sits down 33 of the lower valve 32 on the lower valve seat 64 to fulfill a relationship: Upward force (= A4 × Fp)> downward force (= A5 × Fp) (2)
  • Thus, the lower valve head 33 of the lower valve 32 kept closed.
  • As a result, the gain control passage 14 and the injection control passage 15 with the return connection 28 connected, and the fuel in the gain control chamber 11 and the injection control chamber 12 flows through the upper valve head 33 of the hydraulic servo valve 3 to the return passage 27 , When the fuel pressure in the injection control chamber 12 decreases and the valve opening hydraulic pressure the restoring force of the spring 76 exceeds, opens the nozzle needle 71 to allow a fuel to the injection hole 74 flows. When the pressure in the gain control chamber 11 decreases, the pressure booster piston moves 44 in the drawing, down to equalize an upper hydraulic pressure with a lower hydraulic pressure to the fuel in the pressure-increasing chamber 41 to pressurize and send the fuel to the fuel pressure accumulator 75 , Thus, it is possible to inject the pressure-increased fuel.
  • The gain control passage 14 connected to the gain control chamber 11 is independent of the injection control passage 15 connected to the injection control chamber 12 is connected, so that it is possible, a flow amount of the gain control passage 14 through the mouth 141 regardless of the flow rate of the injection control passage 15 through the mouth 151 to control. In the present embodiment, the pressure in the injection control chamber decreases 12 first, so that the valve opening operation of the nozzle needle 71 is fast to improve an injection response behavior. In this case, the injection pressure at the common rail pressure is at an initial injection time. The injection pressure reaches a superhigh (very high) pressure during injection by the pressure increasing piston 44 to the fuel in the booster chamber 41 to put pressure on. Thus, it is possible to obtain a delta-shaped injection ratio waveform in which an initial injection ratio is small and a later injection ratio is large. This is effective for reducing emissions and increasing output power.
  • At the fuel injection start time, supply of electric power to the electromagnetic valve becomes 5 stopped the electromagnetic valve 5 to open the connection between the outlet 26 and the return passage 27 in the hydraulic servo valve 3 to interrupt. Thus, the fuel pressure in the servo valve control chamber increases 13 again to be a high pressure ("turn off" the electromagnetic valve in 2 ). At this time, a following relationship is fulfilled: Upward force (= A4 × Fp) <downward force (= (A1 + A5) × Fp) (3)
  • Thus, the upper and lower valves move 31 . 32 in the drawing down by a difference between the hydraulic pressure above the valves 31 . 32 and below the valves 31 . 32 , As a result, the upper valve head moves 33 of the upper valve 32 from the upper valve seat 64 away, and then the upper valve head settles 33 of the upper valve 31 on the upper valve seat 63 to fulfill a relationship: Upward force (= (A2 + A4) × Fp) <downward force (= (A1 + A3) × Fp) (4)
  • Thus, the upper valve head 33 of the upper valve 33 kept closed.
  • As a result, the gain control passage 14 and the injection control passage 15 with the high pressure connection 22 connected, and the fuel at the common rail pressure passes through the lower valve head 33 of the hydraulic servo valve 3 to the gain control chamber 11 and the injection control chamber 12 to the pressure in the gain control chamber 11 and the injection control chamber 12 to increase again. Then the nozzle needle moves 71 the injector 7 down to the injection hole 74 close to the pressure booster piston 44 the reinforcing device 4 attributed to the original position.
  • As described above, it is possible to have a flow amount of the gain control passage 14 through the mouth 141 regardless of the flow rate of the injection control passage 15 through the mouth 151 to control. The present is constructed so that the fuel pressure in the injection control chamber 12 increased in advance. As a result, the pressure in the injection control chamber becomes 12 first big, and then the difference between the area and the area of the command piston leads 73 and the area or area of the nozzle needle 71 Very quickly a valve closing the nozzle needle 71 to realize a sharp cut (quick stop) of the fuel injection. Subsequently, the pressure in the gain control chamber 11 big, and the spring 43 moves the pressure booster piston 44 in a return direction (upward in the drawing). At this time, the fuel flows from the check valve 16 in the pressure booster chamber 41 to keep the common-rail pressure in it.
  • In this way saves according to the present invention, the hydraulic pressure valve 6 a drive energy of the electromagnetic valve 5 and reduces a constant escape amount of the fuel without a high accuracy machining accuracy and alignment accuracy. Furthermore, there is the hydraulic servo valve 3 from a plurality of valve elements, ie the upper valve 31 that the upper valve head 33 has, and the lower valve 32 that the lower valve head 32 has, so the upper and lower valve 63 . 64 in the seat element 61 including the upper and lower valve seats 63 . 64 has, from both sides can be used to the hydraulic servo valve 3 easy to assemble. As in 3A is shown, the lower valve 32 through the central hole of the upper valve 31 coarsely guided, and is set to reserve a certain lifting height when the tapered surface of the lower valve seat 34 . 32 with the lower valve 64 is in contact. When the upper valve head 33 the upper valve 63 closes, pushes the upper valve 31 thus the lower valve 32 down to cause the lower valve head 33 the lower valve 64 opens. When the lower valve head 33 the lower valve 64 closes, pushes the lower valve 32 the upper valve 31 upwards to cause the upper valve head 33 the upper valve 63 opens. In this regard, the lower valve 32 slightly out of the upper valve 31 pulled out, after a valve opening of the upper or lower valve 63 . 64 to distribute a valve seat energy to a shock of the upper and lower valve 32 . 34 to prevent.
  • Other Embodiments
  • 3B to 3D each show a hydraulic servo valve 3 according to a second to fourth embodiment of the invention. 3B shows the second embodiment of the present invention. In the second embodiment, the seating surface of the upper valve seat 63 at the top of the valve head 33 of the upper valve 31 sits, a tapered surface that has a diameter that gradually decreases downwards, as well as the upper valve head 33 , the upper valve seat 63 opposite. In the same way has the seat of the lower valve seat 64 at the bottom of the valve head 34 of the lower valve 32 sits, a tapered surface with a diameter that gradually increases downwards, as well as the lower valve head 34 , the upper valve seat 64 opposite. Due to the tapered shapes of the seats of the valve heads 33 . 34 and the valve seats 63 . 64 , is a reliability of the hydraulic servo valve 3 increased with a simple editing process.
  • 3C shows the third embodiment of the present invention, the upper and the lower valve seat 63 . 64 that has the tapered surfaces like those in the second embodiment. A feature of the third embodiment is that the lower valve head 33 of the lower valve 32 has a spherical surface. According to this structure, the lower valve head can 33 on the lower valve 64 put, even if an axis of the lower valve 32 to an axis of the cylinder 65 inclined to reliability of the hydraulic servo valve 3 to improve.
  • 3D shows the fourth embodiment of the present invention, in which the lower valve head 33 of the lower valve 32 has a flat shape. According to this structure, when the upper valve 31 and the lower valve 32 not aligned with each other exactly, the lower valve head 34 of the lower valve 32 the lower valve seat 64 seal securely, even if a distance between an inner circumferential surface of the central hole of the upper valve 31 and the outer peripheral surface of the lower valve 32 consists. Furthermore, a surface pressure (surface pressure) becomes small when the lower valve head 34 on the lower valve seat 64 sits around a reliability of the hydraulic servo valve 6 Ensure even when it's in a high pressure system is applied. Furthermore, the present embodiment has a through hole 35 passing through the upper valve 31 and the lower valve 32 passes through, and a Einlassöffnung or -öffnung 25 at an upper end portion of the through-hole 25 , Thus, the Sevoventil control chamber 13 over the high pressure connection 22 with the common rail 2 connected to simplify a construction of the passages.
  • 4A to 4C show a fifth to seventh embodiment of the hydraulic servo valve 3 according to the present invention. In the embodiments described above, the lower valve 32 in the central hole of the upper valve 31 used and held by this. In the fifth to seventh embodiments, as in 4A to 4C is shown, is the upper valve 31 provided with a shank to the lower valve 32 to lead, and a spring (urging element) 37 pushes the lower valve 32 so to the upper valve 31 that is the upper and lower valve 31 . 32 moving in one piece with each other.
  • 4A shows the hydraulic servo valve 3 according to the fifth embodiment of the present invention. In the fifth embodiment, the upper valve has 31 a leadership 36 that extends from the upper valve head 33 extends downwards. A lower end of the leadership 36 is in the lower, large diameter section of the cylinder 65 positioned. The lower valve 32 has a hemispherical shape. The lower valve head 34 of the lower valve 32 has a hemispherical surface with a recessed section 38 provided at its central section, in the leadership shaft 36 fitted or press fitted. The feather 37 that is below the lower valve 32 is arranged, presses the lower valve 32 so that the lower valve 32 not from the upper valve 31 is disconnected.
  • 4B shows the hydraulic servo valve 3 according to the sixth embodiment of the present invention. In the sixth embodiment, the lower valve head 34 of the lower valve 32 a tapered surface instead of the spherical, lower valve head 34 of the lower valve 32 in the fifth embodiment. 4C shows the hydraulic servo valve 3 according to the seventh embodiment of the present invention. In the seventh embodiment, the lower valve has 32 a T-shaped cross-section. The lower valve head 34 of the lower valve 32 has a flat shape instead of the spherical lower valve head 34 of the lower valve 32 in the fifth embodiment. The feather 37 is arranged to a small diameter portion of the lower valve 32 surrounded by a lower section of this. In this construction, the lower valve is 32 not with the recessed section 38 provided so that the lower valve head 34 of the lower valve 32 safely on the lower valve seat 64 can sit, even if the upper valve 31 and the lower valve 32 are not aligned properly.
  • According to the present Invention it is possible to obtain a control valve, which provides a high-precision pressure increase control and fuel injection control with a simple construction. The present invention can also be applied to a control valve by a small solenoid is driven in a conventional pressurized fuel injection member, the two actuators has, and for a fluid control valve other than the fuel injection valve may be used.

Claims (16)

  1. Control valve ( 3 ) with: a valve housing ( 61 . 62 ), which has a first cylinder ( 30a ), a second cylinder ( 30b ) coaxial with the first cylinder ( 30a ), a connection passage ( 30c ), the first cylinder ( 30a ) and the second cylinder ( 30b ) connects a first port ( 28 ) leading to the first cylinder ( 30a ) opens a second port ( 22 ) leading to the second cylinder ( 30b ), and a control port ( 14a . 15a ) leading to the connection passage ( 30c ) opens, a first valve seat ( 63 ) for allowing and preventing a connection between the first cylinder ( 30a ) and the control terminal ( 14a . 15a ) and a second valve seat ( 64 ) for allowing and preventing a connection between the second cylinder ( 30b ) and the control terminal ( 14a . 15a ) Has; a first valve body ( 31 ) slidable in the first cylinder ( 30a ) is installed to the first valve seat ( 63 ) to open and close; a second valve body ( 32 ) slidable in the second cylinder ( 30b ) is installed to the second valve seat ( 64 ) to open and close, wherein the second valve body ( 32 ) with the first valve body ( 31 ) is connected so that the first valve body ( 31 ) and the second valve body ( 32 ) optionally one of a connection between the control terminal ( 14a . 15a ) and the first connection ( 28 ) and a connection between the control terminal ( 14a . 15a ) and the second connection ( 22 ), characterized in that one of the first valve body ( 31 ) and the second valve body ( 32 ) partially in the other of the first valve body ( 31 ) and the second valve body ( 32 ) is inserted so that the first valve body ( 31 ) and the second valve body ( 32 ) are loosely fitted together and the first valve body ( 31 ) relative to the second valve body ( 32 ) in the longitudinal direction of the first cylinder ( 30a ) and the second cylinder ( 30b ) is slidable.
  2. Control valve ( 3 ) according to claim 1, wherein the first valve body ( 31 ) and the second valve body ( 32 ) in longitudinal directions of the first cylinder ( 30a ) and the second cylinder ( 30b ) press each other when the first valve body ( 31 ) the first valve seat ( 63 ), or when the second valve body ( 32 ) the second valve seat ( 64 ) closes.
  3. Control valve ( 3 ) according to claim 1 or 2, wherein the connection passage ( 30c ) has a smaller diameter than the first cylinder ( 30a ) and the second cylinder ( 30b ); the first valve seat ( 63 ) at one end of the valve housing ( 61 ) between the connection passage ( 30c ) and the first cylinder ( 30a ) is trained; the second valve seat ( 64 ) at one end of the valve housing ( 61 ) between the connection passage ( 30c ) and the second cylinder ( 30b ) is trained; and the first valve body ( 31 ) and the second valve body ( 32 ) by inserting the first valve body ( 31 ) and the second valve body ( 32 ) from the first cylinder ( 30a ) or the second cylinder ( 30b ) are loosely matched.
  4. Control valve ( 3 ) according to one of claims 1 to 3, further comprising a squeezing device ( 37 ) to the first valve body ( 31 ) and the second valve body ( 32 ) to get in contact with each other.
  5. Control valve ( 3 ) according to one of claims 1 to 4, wherein a diameter of the first valve seat ( 63 ) and a diameter of the second valve seat ( 64 ) is smaller than a diameter of the first cylinder ( 30a ).
  6. Control valve ( 3 ) according to one of claims 1 to 5, wherein the second valve body ( 32 ) is not in contact with an inner peripheral surface of the second cylinder ( 30b ).
  7. Control valve ( 3 ) according to one of claims 1 to 6, wherein: the first cylinder ( 30a ) with a low pressure fluid passage ( 27 ) connected is; the second connection ( 22 ) with a high pressure fluid passage ( 21 ) connected is; and a diameter of the first valve seat ( 63 ) approximately equal to a diameter of the second valve seat ( 64 ).
  8. Control valve ( 3 ) according to one of claims 1 to 6, wherein: the first connection ( 28 ) with a low pressure fluid passage ( 27 ) connected is; the second connection ( 22 ) with a high pressure fluid passage ( 21 ) connected is; and a diameter of the first valve seat ( 63 ) is smaller than a diameter of the second valve seat ( 64 ).
  9. Control valve ( 3 ) according to one of claims 1 to 8, wherein: the first cylinder ( 30a ) a hydraulic pressure chamber ( 13 ) formed by an end face of the first valve body ( 31 ) and an inner surface of the first cylinder ( 30a ) is defined; and the first valve body ( 31 ) by a fluid pressure in the hydraulic pressure chamber ( 13 ) which is controlled by an electric actuator.
  10. Control valve ( 3 ) according to claim 9, further comprising: a passage, the hydraulic pressure chamber ( 13 ) over a first mouth ( 25 ) with a high pressure fluid passage ( 21 ) connects; and a passage containing the hydraulic pressure chamber ( 13 ) over a second mouth ( 26 ) and an electric valve ( 5 ) with a low pressure fluid passage ( 27 ) connects.
  11. Control valve ( 3 ) according to claim 10, wherein: the first valve body ( 31 ) a valve pressure at the control port ( 14a . 15a ) as it exits the first valve seat ( 63 ) is raised to a pressure difference between a fluid pressure at the control port ( 14a . 15a ) and a fluid pressure in the high-pressure fluid passage ( 21 ) to the second valve body ( 32 ) on the second valve seat ( 64 ).
  12. Control valve ( 3 ) according to one of claims 1 to 11, wherein: a valve head ( 33 ) of the first valve body ( 31 ), which is on the first valve seat ( 63 ), has an approximately conical surface; and a valve head ( 34 ) of the second valve body ( 32 ), which is on the second valve seat ( 64 ), has an approximately conical surface.
  13. Control valve ( 3 ) according to one of claims 1 to 11, wherein: a valve head ( 33 ) of the first valve body ( 31 ), which is on the first valve seat ( 63 ), has an approximately conical surface; and a valve head ( 34 ) of the second valve body ( 32 ), which is on the second valve seat ( 64 ), has an approximately spherical surface.
  14. Control valve ( 3 ) according to one of claims 1 to 11, wherein: a valve head ( 33 ) of the first valve body ( 31 ), which is on the first valve seat ( 63 ), has an approximately conical surface; and a valve head ( 34 ) of the second valve body ( 32 ), which is on the second valve seat ( 64 ), has an approximately flat surface.
  15. Fuel Injector ( 1 ) with: the control valve ( 3 ) according to any one of claims 9 to 13; a pressure booster piston ( 44 ) for pressurizing a fuel to be injected; a nozzle needle ( 71 ) to allow or prevent fuel injection; and a control passage ( 14 . 15 ) connecting the control terminal ( 14a . 15a ) of the control valve ( 3 ) with a control chamber ( 42 ) of the pressure increasing piston ( 44 ) and a control chamber ( 12 ) of the nozzle needle ( 71 ) connects; where: the pressure booster piston ( 44 ) pressurizes the fuel and the nozzle needle ( 71 ) allows the injection of the fuel when the electric valve is energized to the first valve seat ( 63 ) and the second valve seat ( 64 ) to close fluid pressures in the control chamber ( 42 ) of the pressure increasing piston ( 44 ) and the control chamber ( 12 ) of the nozzle needle ( 71 ) to the pressure increase piston ( 44 ) to pressurize the fuel and the nozzle needle ( 71 ) to open; and the pressure booster piston ( 44 ) stops pressurizing the fuel and the nozzle needle ( 71 ) prevents the injection of the fuel when the electric valve is not energized to the first valve seat ( 63 ) and the second valve seat ( 64 ) to open the fuel pressures in the control chamber ( 42 ) of the pressure increasing piston ( 44 ) and the control chamber ( 12 ) of the nozzle needle ( 71 ) to increase operation of the booster piston ( 44 ) to stop the nozzle needle ( 71 ) close.
  16. Fuel Injector ( 1 ) according to claim 15, wherein: the control passage ( 14 . 15 ) with a mouth ( 141 . 151 ) to adjust a flow of fluid therethrough to adjust injection timing of the fuel injection and timing to pressurize the fuel.
DE200510057526 2004-12-02 2005-12-01 Control valve and fuel injector with this Expired - Fee Related DE102005057526B4 (en)

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JP2004349966A JP4286770B2 (en) 2004-12-02 2004-12-02 Control valve and fuel injection valve having the same

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JP2006161568A (en) 2006-06-22
JP4286770B2 (en) 2009-07-01

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