WO2019109825A1 - 柴油机共轨喷油器 - Google Patents

柴油机共轨喷油器 Download PDF

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Publication number
WO2019109825A1
WO2019109825A1 PCT/CN2018/117368 CN2018117368W WO2019109825A1 WO 2019109825 A1 WO2019109825 A1 WO 2019109825A1 CN 2018117368 W CN2018117368 W CN 2018117368W WO 2019109825 A1 WO2019109825 A1 WO 2019109825A1
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WO
WIPO (PCT)
Prior art keywords
valve
seat
needle
control valve
pressure
Prior art date
Application number
PCT/CN2018/117368
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English (en)
French (fr)
Inventor
唐明龙
Original Assignee
天津盛欧美发动机技术有限公司
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 claimed from CN201811077686.9A external-priority patent/CN109098907A/zh
Application filed by 天津盛欧美发动机技术有限公司 filed Critical 天津盛欧美发动机技术有限公司
Priority to EP18886919.2A priority Critical patent/EP3722590A4/en
Priority to US16/968,189 priority patent/US20210079876A1/en
Publication of WO2019109825A1 publication Critical patent/WO2019109825A1/zh

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    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-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
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention is in the field of diesel fuel injection, especially in the field of high pressure common rail electric control injection.
  • the well-known high-pressure common rail electronically controlled fuel injector has a whole structure of a pilot-operated hydraulic valve.
  • the main structure can be divided into three parts, a needle valve part, a pilot valve part and an electromagnet part.
  • Needle valve part also called injector part, including needle valve body and needle valve with multiple nozzles, the needle valve body is connected with high pressure diesel oil, which is the direct control unit of the injector, due to the needle valve
  • the bearing area is large, the diesel pressure is high, and it is limited by the installation space. It cannot be directly driven by the electromagnet.
  • the pilot valve the pilot valve is also called the control valve. It is a high-speed electronically controlled hydraulic valve.
  • the electromagnet is electromagnetically driven by a high-speed hydraulic valve.
  • the main pilot valve and control mechanism have two types of structures: (1) a structure with a control plunger represented by Bosch (BOSCH), the valve body of the pilot valve is a sphere, the valve seat of the pilot valve is tapered, and the pilot valve The installation position is relatively high, and is far from the needle valve body.
  • a structure with a control plunger represented by Bosch (BOSCH) the valve body of the pilot valve is a sphere, the valve seat of the pilot valve is tapered, and the pilot valve The installation position is relatively high, and is far from the needle valve body.
  • the cone bottom of the pilot valve seat has an oil discharge hole communicating with the control hydraulic cylinder, and the control valve body is provided with an oil inlet hole to control the control plunger of the hydraulic cylinder and
  • the control valve body is composed, and the needle valve of the even piece is assembled with the control plunger string, the diameter of the control plunger is larger than the diameter of the needle valve of the even part, and the oil return hole is provided between the needle valve of the even piece and the control plunger, and the even piece
  • the pre-pressure spring is installed on the needle valve, and the pressure of the hydraulic cylinder is controlled by the electromagnetic valve to realize the change of the overall force of the needle valve and the control plunger.
  • the pilot valve When the pilot valve is opened, the pressure in the hydraulic cylinder is controlled to decrease, the needle valve and the control The plunger force causes the needle valve to lift.
  • the solenoid valve When the solenoid valve is closed, the pressure of the control hydraulic cylinder is raised, and the needle valve and the control plunger cooperate to close the needle valve.
  • the uncontrolled plunger type represented by Delphi the pilot valve is installed next to the needle valve, and the pilot valve directly controls the liquid pressure at the tail of the needle valve to realize the lifting and lowering of the needle valve. 3.
  • the driving part the driving part generates the driving force of the pilot valve.
  • the existing structure has electromagnet type, piezoelectric type, and magnetostrictive type, and the spring presses the valve body of the pilot valve on the valve seat to make the pilot valve When closed, the electromagnetic driving force overcomes the spring force to open the pilot valve.
  • a needle valve spring is mounted on the needle valve, one end of the needle valve spring is placed on the spring seat of the needle valve, and one end is placed on the spring seat of the injector body. on.
  • the pilot valve controls the pressure at the tail of the needle valve to control the lift of the needle valve.
  • the clearance space at the position where the needle spring is installed is connected with the hydraulic cylinder at the tail of the needle valve.
  • the volume of the hydraulic cylinder due to the large change in the pressure of the control hydraulic cylinder, the elasticity of the liquid reduces the response speed of the needle valve.
  • valve ball ejector of the pilot valve passes through the center hole of the electromagnet, and the valve ball ejector and the armature are mounted in a concentric sliding fit.
  • the upper part of the ejector pin (near the coil direction) has a larger diameter than the electromagnetic
  • the armature of the iron has a central hole diameter and a spring is mounted on the tail of the ejector.
  • the downward movement of the top pillar relative to the armature can be transmitted to the armature.
  • the upward movement of the top pillar relative to the armature is not transmitted to the armature, and the armature moves upward relative to the top pillar and can be transmitted to the top.
  • the downward movement of the armature relative to the top column cannot be transmitted to the top column, and the top column moves downward.
  • the speed of the top column decreases rapidly, the top column moves upward relative to the armature, and the armature continues to move downward, the valve seat The ball seat is not affected by the armature.
  • the armature moves upward and comes into contact with the upper part of the electromagnet, the armature does not accept the impact of the top column.
  • the armature and the top post are gap-fitted, and in order to ensure effective guiding, the top column must have a large diameter and height, so that the quality of the top column is large, which in turn increases the armature.
  • the diameter, and ultimately the reduced impact force of the structure is largely offset, while the presence of the armature buffer lift also reduces the response speed.
  • the technical problem to be solved is to solve the problem that affects the response speed of the existing electronically controlled injector, and the large impact force of the needle valve and the control valve.
  • the valve seat of the injector control valve adopts a long hole T-column structure.
  • the liquid passes through the long hole of the pilot valve seat to control the tail hydraulic pressure of the needle valve, and controls the lifting and lowering of the needle valve, and cancels the Bosch (BOSCH) Represents the control plunger of the injector;
  • the T-type pilot valve seat adopts the floating installation structure: the big end of the T-type control valve seat is downward, and the T-shaped pilot valve seat is slidably assembled in the center hole of the injector body.
  • the large end of the T-type control valve seat and the center hole of the injector body are provided with a matching sealing seat surface, and the liquid pressure at the lower end of the T-type control valve seat causes the sealing surface of the T-type control valve seat to be pressed against the injection
  • the sealing surface on the body; the needle valve spring is not installed at the tail of the needle valve.
  • the control valve spring force drives the T-type control valve seat, so that the T-type control valve seat is pressed at the tail of the needle valve to close the needle valve, and the control valve spring also functions as a needle valve pre-compression spring.
  • the pressure regulating mechanism When the pressure regulating mechanism is set on the main oil inlet, when the needle valve is opened, the diesel pressure entering the lower part of the needle valve is lowered. When the control valve is closed, the pressure at the tail end of the needle valve is higher than the pressure at the front end of the needle valve, and the needle valve is closed by the pressure difference.
  • the optimized main oil circuit hydraulic pressure regulating mechanism is a structure in which a spring pressure regulating valve is connected in series with a throttle hole pad. From top to bottom, it is a pressure regulating valve seat, a pressure regulating valve core, a pressure regulating spring, and a throttle hole pad.
  • the simplified main oil line hydraulic pressure regulating mechanism is a simple orifice structure, and there is no spring pressure regulating valve.
  • the optimized main oil passage hydraulic adjustment mechanism is disposed on the injector body, and the tapered throttle orifice core is installed in the cone hole of the fuel injector body inlet passage.
  • the optimized control oil inlet is provided with an oil inlet hole between the main oil gallery of the injector body and the center hole of the injector body.
  • the optimized control valve is a cone-shaped ball valve structure
  • the driving mechanism is an EI-type electromagnet structure
  • the electromagnet armature is fixed with the armature guiding column
  • the armature guiding column is installed downward in the guiding sleeve
  • the guiding column top is on the ball seat
  • the armature The upper end surface is placed on the control valve spring
  • the armature buffer structure represented by Bosch (BOSCH) is eliminated to reduce the quality of the motion system.
  • the optimized electromagnet armature is a trough-shaped discharge electromagnet armature, and a longitudinal groove is arranged on the outer circumference of the guide post as an oil discharge passage, thereby reducing the motion quality and reducing the magnetic flux leakage.
  • the optimized electromagnet is the inner hole draining armature, and the guiding column is provided with a central through hole as an oil discharging passage.
  • the guiding column end is provided with a liquid guiding groove, and at the same time, the movement quality is reduced, the magnetic circuit leakage is reduced, and the control valve is discharged. Diesel cools the electromagnet.
  • the guide sleeve of the electromagnet armature guide post is concentric with the center hole of the injector, and the guide sleeve is convex upward for a length (2 to 5 mm) to increase the air gap between the lower surface of the armature and the injector body, thereby reducing magnetic flux leakage.
  • the simplified electromagnet guide sleeve has no upward convexity, and the length of the elongated guide post is used to increase the distance between the electromagnet armature disc and the guide sleeve end face to 2 to 5 mm, thereby increasing the air gap between the lower surface of the armature and the injector body, and reducing Magnetic circuit leakage.
  • the optimized electromagnet core is a multi-layer (2 to 4 layers) double ring structure with a central hole.
  • the invention has the beneficial effects that the T-type control valve with a long hole is used to control the hydraulic pressure of the tail of the needle valve to control the lifting and lowering of the needle valve, the control valve column is eliminated, the total mass of the moving body of the needle valve is reduced, and the response speed can be improved. Reduce the impact of the needle valve.
  • the T-type control valve seat adopts a floating installation structure, and the liquid pressure at the lower end surface of the T-type control valve causes the sealing surface of the T-type control valve seat to be pressed against the sealing surface of the injector body, thereby reducing the installation process and the T-type pilot valve seat.
  • the T-pillar of the T-type pilot seat is shortened to absorb the impact of some of the control ball.
  • the spring of the control valve also acts as a pre-pressure spring for the needle valve, and the tail of the needle valve controls the volume of the hydraulic fluid to improve the response speed.
  • the guide sleeve of the electromagnet armature guide post is upwardly extended for a length (2 to 5 mm) to increase the air gap between the lower surface of the armature and the injector body, thereby reducing magnetic flux leakage and reducing the diameter of the armature.
  • Figure 1 shows the schematic diagram of the structure of the control plunger injector.
  • FIG. 1 Schematic diagram of the structure of the uncontrolled plunger injector
  • Figure 3 is a structural diagram of the needleless valve preload spring injector
  • Figure 4 is a partial view of the needleless valve preload spring injector control valve
  • Figure 5 is a partial view of the pressure regulating part of the needleless valve preloading spring injector
  • Figure 6 is a structural diagram of the electromagnet core scheme
  • Figure 3 is a three-dimensional diagram of the trough-shaped drainage armature
  • Figure 8 is a three-dimensional view of the inner hole draining armature
  • Figure 9 is a structural diagram of the main oil line pressure adjustment scheme.
  • FIG. 1 is a structural view of a known controllable plunger injector, in which a coupler seat (1001a) with a middle hole and a tapered base is mounted in a concentric sliding relationship with a valve needle (1004a) having a tapered tip, and a coupler seat (
  • the tapered base of 1001a) is distributed with several oil injection holes, and the oil passage (1002a) on the even seat (1001a) is connected to the high pressure oil through the oil passage (4001a) on the injector body (4000a), and the even seat (
  • the oil passage (1002a) on 1001a) enters the annular oil passage in the lower part of the valve needle (1004a) and the even part seat (1001a) through the annular groove (1003a), the valve needle (1004a) is lowered, and the even seat cone base and the valve
  • the injector is closed, the valve needle (1004a) is raised, and the injector seat is separated from the valve needle (1004a) cone tip, and the injector opens
  • the needle valve is fitted with a spring seat (1005a), and the needle spring (1006a) is mounted on the spring seat (1005a) and the spring seat of the injector body (4000a).
  • the needle spring (1006a) causes the valve needle (1004a) to be directed.
  • the lower force ensures that the needle valve is closed when the diesel pressure is low in the high pressure oil passage.
  • the control plunger (2005a) is slidably mounted in the hole of the control valve of the control valve seat (2001a), and the control cylinder (2005a-1) is between the tail of the control plunger (2005a) and the hole in the control valve seat (2001a).
  • the control oil inlet hole (2004a) communicates with the control cylinder and the high pressure oil passage (4001a), and the oil discharge hole (2003a) on the control valve seat (2001a) connects the control cylinder to the conical seat of the control valve seat (2001a)
  • the valve ball (2002a) is installed between the control valve conical seat (2006a) and the ball seat (2007a), the injector body (4000a) is provided with the oil return hole (4002a), the oil return hole and the control plunger (2005a)
  • the lower section, the top of the needle valve, and the outlet of the control valve are connected.
  • the upper part of the solenoid valve guide top column (2008a) is slidably mounted in the electromagnet guide hole (3005a), and the solenoid valve is guided to the lower section of the top column for sliding installation.
  • the central valve of the solenoid valve guiding top column (2008a) is pressed against the upper end surface of the armature (3004a), and the solenoid valve is guided to the top of the top column to install the solenoid spring (2011a), and the lower part of the armature (3004a) Install the armature spring (2010a) and press the seat retainer (2009a) against the control seat (2001a).
  • the electromagnet is an EI type electromagnet, and the electromagnet is composed of a core of a double ring structure (3001a, 3002a) and a coil (3003a).
  • the armature (3004a) moves upward, causing the solenoid valve to guide the top post (2008a) to move upward, the valve ball (2002a) opens upward, and the control oil is discharged from the oil discharge hole (2003a).
  • the top pressure of the control plunger (2005a) is lowered, the needle valve (1004a) is subjected to an upward force greater than the sum of the top pressure of the spring (1006a) and the control plunger (2005a), and the needle valve (1004a) and the control plunger (2005a) are moved upward.
  • the needle valve (1004a) is opened and the injector starts to inject oil.
  • the valve ball (2002a) Moving to the control valve seat (2001a), the valve ball (2002a) is closed, the oil discharge hole (2003a) stops draining, the pressure at the top of the control plunger (2005a) rises, and the needle valve (1004a) receives an upward force smaller than the spring (1006a) And the sum of the top pressures of the control plunger (2005a), the needle valve (1004a) and the control plunger (2005a) move downward, the needle valve (1004a) closes, and the injector stops the injection.
  • the solenoid valve guide top column moves downward under the action of the solenoid valve spring (2011a), pushing the armature (3004a), the ball seat (2007a), the valve ball (2002a) to the control valve seat (2001a), and the valve
  • the solenoid valve guides the top post (2008a), the ball seat (2007a), the valve ball (2002a) stops quickly, the armature (3004a) continues to move forward, and the armature (3004a) )
  • the contact with the guide post (2008a) is reduced, and the impact force of the armature (3004a) acting on the valve ball (2002a) is reduced.
  • the solenoid valve guiding top column moves upward under the action of the armature (3004a).
  • the armature (3004a) stops rapidly, and the guiding top column continues in the armature (3004a). Moving forward, the armature (3004a) is out of contact with the guiding top post (2008a), and the impact force on the armature (3004a) acting core (3001a, 3002a) is reduced.
  • the solenoid valve guide top column is slidingly matched with the armature (3004a), and is divided into a larger diameter guide section and a smaller diameter ejector section.
  • the solenoid valve guides the top pillar as a whole mass, although the valve ball (2002a) is closed.
  • the armature (3004a) is loaded onto the valve ball (2002a)
  • the force is reduced, and the impact between the ball (2002a) and the control valve cone (2006a) is still large.
  • FIG. 2 is a schematic structural view of a known uncontrolled plunger injector, in which a coupler seat (1001b) with a middle hole and a tapered base is mounted in a concentric sliding relationship with a valve needle (1004b) having a tapered tip, and a coupler seat is mounted.
  • the tapered base of (1001b) is distributed with several injection holes, and the oil passage (1002b) on the even seat (1001b) is connected to the high pressure oil through the main oil passage (4001b) on the injector body (4000b), the main oil An orifice (4001b-1) is arranged on the road, and the oil passage (1002b) on the even seat (1001b) enters the annular oil passage in the lower part of the valve needle (1004b) and the even seat (1001b) through the annular groove (1003b).
  • the valve needle (1004b) is lowered.
  • the injector When the conical base of the even seat is in contact with the cone tip of the valve needle (1004b), the injector is closed, the valve needle (1004b) is raised, and the conical base and the valve needle (1004b) are tapered. When the tip is separated, the injector opens the fuel injection.
  • the needle valve spring (1006b) is installed at the tail of the needle valve.
  • the top of the needle valve spring (1004b) and the spring (1006b) are installed in the control hydraulic cylinder (1006b-1), the needle valve spring ( 1006b) causes the valve needle (1004b) to generate a downward force to ensure that the needle valve is closed when the diesel pressure is low in the high pressure oil passage, while providing the needle closing force.
  • the controllable plunger injector control valve adopts a structure with a balance mechanism
  • the valve core (2002b) is combined with the armature (3004b)
  • the control arm spring (2011b) is mounted on the upper surface of the armature (3004b).
  • a tapered sealing surface (2002b-1) and a sliding sealing section (2002b-2) are provided, and the sliding sealing section (2002b-2) simultaneously serves as a guide, and the sliding sealing section (2002b-2) is mounted on the valve seat (2001b).
  • Control valve pilot hole (2001b-2), conical sealing surface (2002b-1) and sealing seat (2001b-1) of valve seat (2001b), valve seat guide hole (2001b-2) and pressure relief hole (2001b-3) is the same, the liquid pressure of the valve core (2002b) is nearly balanced, so the spring force of the control valve spring (2010b) mounted on the armature (3004b) is small.
  • the electromagnet of the uncontrolled plunger injector is an EI type electromagnet, and the electromagnet is composed of a core of a double ring structure (3001b, 3002b) and a coil (3003b).
  • the needleless valve preload spring injector structure of the present invention is illustrated in Figures 3 to 5, in which the coupler seat (1001c) with the center hole and the tapered base is concentrically slid with the valve needle (1004c) with a tapered tip.
  • the conical base of the even seat (1001c) is distributed with several injection holes, and the oil passage (1002c) on the even seat (1001c) passes through the throttle hole pad (1007c) on the injector body (4000c),
  • the pressure regulating spring (1008c), the gap between the pressure regulating valve core (1009c) and the pressure regulating valve seat, the oil passage (4001c) are connected with the high pressure oil, and the oil passage (1002c) on the even seat (1001c) passes through the annular groove.
  • the seat of the injector control valve (2001c) adopts a long hole T-pillar structure.
  • the seat of the control valve includes a conical seat (2006c) and a medium-length long cylinder.
  • the lower large diameter sealing head (2001c-1), the conical valve seat has the oil volume hole (2003c) and the central long hole (2005c), the center long hole (2005c) and the needle valve (1004c) the tail hydraulic cylinder ( 1004c-1) is connected, the valve seat of the T-type control valve adopts a floating installation structure, and the valve seat long column of the T-type control valve is slidably assembled in the center hole of the injector body (4000c), and the T-shaped control valve seat is sealed with a large diameter.
  • the liquid pressure of the end face (2001c-1) causes the sealing seat of the T-shaped control seat to be pressed against the sealing seat (4003c) of the injector body, and the control oil passes through the main oil passage (4001c) and the oil inlet hole (2004c) in sequence.
  • Control the valve seat and the middle hole clearance enter the control hydraulic cylinder (1004c-1); control oil from the hydraulic cylinder (1004c-1) through the center long hole (2005c) oil output hole oil output hole (2003c), valve seat (2006c)
  • the control valve and oil return hole (4002c) composed of the valve ball (2002c) are discharged.
  • the ball (2002c) is mounted on the conical seat (2006c), the ball seat (2007c) is mounted on the ball (2002c), and the guide post (2008c) is placed on the tee (2007c).
  • the guide post (2008c) is fixed with the armature (3004c), the guide sleeve (3005c) is upwardly convex, the guide post (2008c) is mounted on the guide sleeve (3005c), and the control valve spring (2010c) is mounted on the upper part of the armature (3004c).
  • the outer core of the iron is formed by a double-layer L-shaped ring (3002c, 3002c-1), and the inner iron core is composed of a fixed column (3001c) with a positioning step and an L-shaped pressure ring (3001c-1), and the inner iron core is fixed.
  • (3001c) is fixed on the iron core mounting body, the step of the inner iron core fixing column (3001c) is pressed on the pressure ring (3001c-1), and the pressure ring (3001c-1) is pressed against the outer iron core by the double-layer L-shaped ring ( On the 3002c, 3002c-1), the coil (3003c) is installed in the annular space of the outer and inner cores.
  • Figure 6 depicts a second electromagnet core implementation in which the inner and outer cores (3001d-1, 3001d-2, 3002d, 3002d-1) are stacked from two U-shaped rings, and the U-shaped ring is stepped.
  • the iron core fixing column (3001d) is fixed.
  • Figure 7 shows the shape of the trough-shaped drainage armature.
  • the large-disc armature is fixed with the guide post.
  • the outer circumference of the guide post is distributed with the drainage trough.
  • the armature is suitable for the external oil return port of the electromagnet. Oiler.
  • Figure 8 shows the shape of the inner hole draining armature.
  • the large disc-shaped armature is fixed with the guide post (2008c-1).
  • the through-hole is set in the center of the guide post.
  • the liquid guide groove is arranged at the end of the guide post.
  • the high pressure is removed from the control valve.
  • the liquid flows directly to the electromagnet to cool the electromagnet.
  • the armature is particularly suitable for the internal oil return port injector with a lower return port position than the electromagnet, and is also suitable for the external return of the oil return port position higher than the electromagnet. Oil interface injector.
  • Figure 9 shows the simplified main oil pressure adjustment mechanism structure.
  • the upper part of the inclined oil passage (1002d) is provided with a tapered oil hole (1007d-1), and the tapered throttle hole core (1007d) is installed on the tapered surface.
  • the valve needle (1004d) is reduced in length
  • the stroke adjustment pad (1004d-1) is installed in the nozzle hole of the injector
  • the oil inlet hole (2004d) is set in the injector.
  • the fuel injector body inlet port and the oil return port are built-in type, and it is obvious that the solution of the present invention is also applicable to the injector type in which the inlet port and the oil return port are external, and will not be described in detail.

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Abstract

一种柴油机共轨喷油器，喷油器控制阀的阀座采用长孔T型柱结构(2001c)，液体通过控制阀的阀座的长孔来控制针阀的尾部液压；T型先导阀座采用浮动安装结构：T型控制阀阀座的大端向下，T型先导阀座长柱滑动装配在喷油器体的中心孔中，T型控制阀阀座的大端和喷油器体的中心孔设有相互配合的密封座面，T型控制阀阀座下端液压力使T型控制阀阀座的密封面压在喷油器体上的密封面上，针阀尾部不安装针阀弹簧，当发动机停机或刚启动，控制阀弹簧也起到了针阀预压弹簧的作用，使针阀关闭；控制阀关闭时，针阀尾部压力高于针阀前端压力，依靠压力差使针阀关闭。

Description

柴油机共轨喷油器 技术领域
本发明于柴油机喷油领域，尤其是高压共轨电控喷油领域。
背景技术
公知的高压共轨电控喷油器，整体结构为先导式液压阀，主要结构可分为三个部份，针阀部份、先导阀部份和电磁铁部份。1、针阀部份：也叫喷油器偶件，包含带多个喷嘴的针阀体和针阀，针阀体与高压柴油相通，这是直接控制喷油器的执行部件，由于针阀受力面积大，柴油压力高，同时受安装空间限制，不能用电磁铁直接驱动；2、先导阀：先导阀也叫控制阀，是高速电控液压阀，通过高速液压阀将电磁铁的电磁力通过液压放大后，控制针阀的升降，来实现控制喷油。目前主要的先导阀和控制机构有二类结构：(1)以博世(BOSCH)为代表的带控制柱塞的结构，先导阀的阀体为球体，先导阀的阀座为锥形，先导阀安装位置较高，距离针阀体较远，先导阀阀座的锥底有排油量孔与控制液压缸相通，控制阀体上设置有进油量孔，控制液压缸由的控制柱塞和控制阀体组成，偶件的针阀与控制柱塞串装在一起，控制柱塞的直径大于偶件针阀直径，偶件的针阀和控制柱塞之间设有回油孔，偶件的针阀上安装预压弹簧，通过电磁阀控制液压缸体的压力，实现针阀和控制柱塞总体受力情况改变，先导阀开启时，控制液压缸体内的压力降低，针阀和控制柱塞合力使针阀抬起，电磁阀关闭时，控制液压缸体的压力升高，针阀和控制柱塞合力使针阀关闭。(2)以德尔福(Delphi)为代表的无控制柱塞式，先导阀紧邻针阀安装，先导阀直接控制针阀尾部液体压力来实现针阀的升降。3、驱动部份，驱动部份产生先导阀的驱动力，现有结构有电磁铁式、压电式、和磁致伸缩式，弹簧将先导阀的阀体压在阀座上，使先导阀关闭，电磁驱动力克服弹簧力使先导阀打开。
公知的高压共轨电控喷油器为了保证针阀的初始密封，针阀上安装上针阀弹簧，针阀弹簧一端顶在针阀的弹簧座上，一端顶在喷油器体的弹簧座上。对于以德尔福(Delphi)为代表的无控制柱塞的结构，先导阀控制针阀尾部压力来控制针阀升降，安装针阀弹簧的位置的空隙空间与针阀尾部的液压缸连在一起，增加了 液压缸的体积，由于控制液压缸压力变化大，液体的弹性使针阀的响应速度降低。
对于以博世(BOSCH)为代表的带控制柱塞的结构，由于针阀尾部与回油口相通，针阀弹簧本身不会引起响应速度降低，但控制柱塞质量大，控制柱塞和针阀的总质量为阀体的运动质量，在相同的响应速度下，要求更高的驱动力，同时针阀关闭时，针阀与针阀座的冲击力较大。
以博世(BOSCH)为代表的喷油器，先导阀的阀球顶杆穿过电磁铁的中心孔，阀球顶杆与衔铁为同心滑动配合安装，顶杆上部(靠近线圈方向)直径大于电磁铁的衔铁中心孔直径，顶杆尾部安装弹簧，该结构顶柱相对衔铁向下的运动可传递给衔铁，顶柱相对衔铁向上的运动不传递给衔铁，衔铁相对顶柱向上运动可传递给顶柱，衔铁相对顶柱向下运动不能传递给顶柱，顶柱向下运动，阀球与球座接触时，顶柱速度快速降低，顶柱相对衔铁向上运动，衔铁继续向下运动，阀座与球座不会受衔铁的冲击力，同样，当衔铁向上运动，与电磁铁的上半部份接触时，衔铁也不接受顶柱的冲击力。但是为了实现该功能，衔铁与顶柱之间为间隙滑动配合，同时为了保证有效的导向，顶柱必须有较大的直径和高度，这样顶柱的质量较大，反过来又增加了衔铁的直径，最终该结构减少的冲击力大量抵消，同时衔铁缓冲升程的存在，也降低了响应速度。
发明内容
解决的技术问题是：解决影响现有电控喷油器响应速度的问题，以及针阀、控制阀冲击力大问题。
具体技术方案：喷油器控制阀的阀座采用长孔T型柱结构，液体通过先导阀座的长孔来控制针阀的尾部液压，控制针阀的升降，取消了以博世(BOSCH)为代表的喷油器的控制柱塞；T型先导阀座采用浮动安装结构：T型控制阀阀座的大端向下，T型先导阀座长柱滑动装配在喷油器体的中心孔中，T型控制阀阀座的大端和喷油器体的中心孔设有相互配合的密封座面，T型控制阀阀座下端液压力使T型控制阀阀座的密封面压在喷油器体上的密封面上；针阀尾部不安装针阀弹簧，当发动机停机或刚启动，T型控制阀系统压力较低时，T型控制阀阀座下端面压力小于控制阀弹簧力时，控制阀弹簧力驱动T型控制阀座，使T型控制阀座压在针阀尾部，使针阀关闭，控制阀弹簧也起到了针阀预压弹簧的作用。
在主进油路上设置压力调节机构，使针阀打开时，进入针阀下部的柴油压力降低，控制阀关闭时，针阀尾部压力高于针阀前端压力，依靠压力差使针阀关闭。
优化的主油路液压调压机构为弹簧调压阀串接节流量孔垫的结构。从上至下依次为调压阀座、调压阀芯、调压弹簧，节流量孔垫。
简化的主油路液压调压机构为单纯的节流孔结构，无弹簧调压阀。
优化的主油路液压调整机构设置在喷油器偶件体上，锥形节流量孔芯安装在喷油器偶件体进油道上锥孔内。
优化的控制油入口通过在喷油器体主油道和喷油器体中心孔之间设置进油量孔。
优化的控制阀为锥座球阀结构，驱动机构为EI式电磁铁结构，电磁铁衔铁与衔铁导向柱固定在一起，衔铁导向柱向下安装在导向套内，导向柱顶在球座上，衔铁上端面顶在控制阀弹簧上，取消以博世公司(BOSCH)为代表的衔铁缓冲结构，减小运动体系的质量。
优化的电磁铁衔铁为槽状排液电磁铁衔铁，导向柱外周设置纵向槽，作为排油通道，同时减小运动质量，减小磁路漏磁。
优化的电磁铁衔为内孔排液衔铁，导向柱设置中心通孔，作为排油通道，导向柱端部设导液槽，同时减小运动质量，减小磁路漏磁，控制阀排出的柴油对电磁铁起到冷却作用。
电磁铁衔铁导向柱的导向套与喷油器中心孔同心，导向套向上凸起一段长度(2～5mm)增加衔铁下表面与喷油器体之间的气隙，减小磁路漏磁。
简化的电磁铁导向套无向上凸起，采用加长导向柱长度，将电磁铁衔铁大盘与导向套端面距离增加到2～5mm，增加衔铁下表面与喷油器体之间的气隙，减小磁路漏磁。
优化电磁铁铁心为带中心孔的多层(2～4层)双环结构。
本发明的有益效果为：通过带长孔的T型控制阀来控制针阀尾部液压来控制针阀升降，取消了控制阀柱，减小了针阀运动体的总质量，可提高响应速度，降低针阀的冲击力。
T型控制阀阀座采用浮动安装结构，T型控制阀下端面液体压力使T型控制阀座密封面压在喷油器体的密封面上，减小了安装工序，同时T型先导阀座与 阀球接触时，T型先导阀座的T型柱长度缩短，可吸收部份控制阀球的冲击力。
通过T型控制阀座的浮动安装，控制阀的弹簧同时起到了针阀预压弹簧的作用，针阀尾部控制液压液体的体积，提高响应速度。
衔铁和导向柱一体化结构，导向柱向下同时起球阀顶柱的作用，降低运动体系的质量，减小衔铁的直径。
通过电磁铁衔铁导向柱的导向套向上凸起一段长度(2～5mm)增加衔铁下表面与喷油器体之间的气隙，减小磁路漏磁，减小衔铁直径。
附图说明
下面结合附图对本发明进一步说明，
图1带控制柱塞喷油器结构原理图，
图2无控制柱塞喷油器结构原理图，
图3无针阀预压弹簧喷油器结构图，
图4无针阀预压弹簧喷油器控制阀局部图，
图5无针阀预压弹簧喷油器调压部份局部图，
图6电磁铁铁心方案二结构图，
图7槽状排液衔铁三维图，
图8内孔排液衔铁三维图，
图9主油路压力调整方案二结构图。
具体实施方式
图1是公知的带控制柱塞喷油器结构图，图中带中孔和锥形底座的偶件座(1001a)与带锥尖的阀针(1004a)同心滑动配合安装，偶件座(1001a)的锥形底座分布数个喷油孔，偶件座(1001a)上的油道(1002a)通过喷油器体(4000a)上的油道(4001a)与高压油相连，偶件座(1001a)上的油道(1002a)通过环状槽(1003a)进入阀针(1004a)与偶件座(1001a)下部的环形油道，阀针(1004a)下降，偶件座锥形底座与阀针(1004a)锥尖接触时，喷油器关闭，阀针(1004a)上升，偶件座锥形底座与阀针(1004a)锥尖分开时，喷油器打开喷油。
针阀尾部安装弹簧座(1005a)，针阀弹簧(1006a)安装在弹簧座(1005a)和喷油器体(4000a)的弹簧座上，针阀弹簧(1006a)使阀针(1004a)产生向下的力，保证系统在高压油道中柴油压力较低时针阀关闭。
控制柱塞(2005a)滑动安装在控制阀座(2001a)的控制阀中孔中，控制柱塞(2005a)的尾部与控制阀座(2001a)中孔之间为控制油缸(2005a-1)，控制进油量孔(2004a)与控制油缸和高压油道(4001a)相通，控制阀座(2001a)上的排油量孔(2003a)使控制油缸和控制阀座(2001a)的锥形座相通，阀球(2002a)安装在控制阀锥形座(2006a)和阀球座(2007a)之间，喷油器体(4000a)设置回油孔(4002a)，回油孔与控制柱塞(2005a)下段、针阀顶部，以及控制阀出油口相通，电磁阀导向顶柱(2008a)上部大直径段滑动安装在电磁铁导向孔(3005a)中，电磁阀导向顶柱下段小直径段滑动安装在衔铁(3004a)的中心孔中，电磁阀导向顶柱(2008a)中部台阶压在衔铁(3004a)的上端面上，电磁阀导向顶柱顶部安装电磁阀弹簧(2011a)，衔铁(3004a)下部安装衔铁弹簧(2010a)，控制阀座固定螺丝(2009a)压在控制阀座(2001a)上。
电磁铁为EI式电磁铁，电磁铁由双环结构(3001a、3002a)的铁芯和线圈(3003a)构成。
图1中电磁铁线圈(3003a)通电后，衔铁(3004a)向上运动，带动电磁阀导向顶柱(2008a)向上运动，阀球(2002a)向上打开，控制油从排油量孔(2003a)排出，控制柱塞(2005a)顶部压力降低，针阀(1004a)受到向上力大于弹簧(1006a)和控制柱塞(2005a)顶部压力之和，针阀(1004a)和控制柱塞(2005a)向上运动，针阀(1004a)打开，喷油器开始喷油。
当图1中电磁铁线圈(3003a)断电后，电磁阀导向顶柱在电磁阀弹簧(2011a)作用下向下运动，推动衔铁(3004a)、阀球座(2007a)、阀球(2002a)向控制阀座(2001a)运动，阀球(2002a)关闭，排油量孔(2003a)停止排油，控制柱塞(2005a)顶部压力升高，针阀(1004a)受到向上力小于弹簧(1006a)和控制柱塞(2005a)顶部压力之和，针阀(1004a)和控制柱塞(2005a)向下运动，针阀(1004a)关闭，喷油器停止喷油。
图1中控制柱塞(2005a)和针阀(1004a)同步运动，针阀(1004a)关闭时冲击力较大。
图1中电磁阀导向顶柱在电磁阀弹簧(2011a)作用下向下运动，推动衔铁(3004a)、阀球座(2007a)、阀球(2002a)向控制阀座(2001a)运动，当阀球(2002a)接触控制阀锥形座(2006a)时电磁阀导向顶柱(2008a)、阀球座 (2007a)、阀球(2002a)快速停止，衔铁(3004a)继续向前运动，衔铁(3004a)与导向顶柱(2008a)脱离接触，衔铁(3004a)作用在阀球(2002a)上的冲击力减少。
图1中电磁阀导向顶柱在衔铁(3004a)作用下向上运动，当衔铁(3004a)与铁芯(3001a、3002a)接触时，衔铁(3004a)快速停止，导向顶柱在衔铁(3004a)继续向前运动，衔铁(3004a)与导向顶柱(2008a)脱离接触，衔铁(3004a)作用铁芯(3001a、3002a)上的冲击力减小。
图1电磁阀导向顶柱与衔铁(3004a)滑动配合，分为直径较大的导向段和直径较小的顶杆段，电磁阀导向顶柱整体质量较大，尽管在阀球(2002a)关闭时衔铁(3004a)加载到阀球(2002a)上的力减少，阀球(2002a)与控制阀锥形座(2006a)之间的冲击力仍较大。
图2是公知的无控制柱塞喷油器结构原理图，图中带中孔和锥形底座的偶件座(1001b)与带锥尖的阀针(1004b)同心滑动配合安装，偶件座(1001b)的锥形底座分布数个喷油孔，偶件座(1001b)上的油道(1002b)通过喷油器体(4000b)上的主油道(4001b)与高压油相连，主油道上设置有节流孔(4001b-1)，偶件座(1001b)上的油道(1002b)通过环状槽(1003b)进入阀针(1004b)与偶件座(1001b)下部的环形油道，阀针(1004b)下降，偶件座锥形底座与阀针(1004b)锥尖接触时，喷油器关闭，阀针(1004b)上升，偶件座锥形底座与阀针(1004b)锥尖分开时，喷油器打开喷油。
图2中无控制柱塞喷油器，针阀尾部安装针阀弹簧(1006b)，针阀弹簧(1004b)顶部与弹簧(1006b)安装空间为控制液压缸(1006b-1)，针阀弹簧(1006b)使阀针(1004b)产生向下的力，保证系统在高压油道中柴油压力较低时针阀关闭，同时提供针阀关闭力。
图2中无控制柱塞喷油器控制阀采用了带平衡机构的结构，阀芯(2002b)与衔铁(3004b)结合在一起，衔铁(3004b)上表面安装控制阀弹簧(2011b)，阀芯上设锥形密封面(2002b-1)和滑动密封段(2002b-2)，滑动密封段(2002b-2)同时起导向作用，滑动密封段(2002b-2)安装在阀座(2001b)的控制阀导向孔(2001b-2)，锥形密封面(2002b-1)与阀座(2001b)的锥形面(2001b-1)密封配合，阀座导向孔(2001b-2)与泄压孔(2001b-3)相通，阀芯(2002b)受到的 液体压力是近平衡的，因此安装在衔铁(3004b)的控制阀弹簧(2010b)的弹簧力较小。
图2中无控制柱塞喷油器的电磁铁为EI式电磁铁，电磁铁由双环结构(3001b、3002b)的铁芯和线圈(3003b)构成。
图3～图5中描述了本发明的无针阀预压弹簧喷油器结构，图中带中孔和锥形底座的偶件座(1001c)与带锥尖的阀针(1004c)同心滑动配合安装，偶件座(1001c)的锥形底座分布数个喷油孔，偶件座(1001c)上的油道(1002c)通过喷油器体(4000c)上节流量孔垫(1007c)、调压弹簧(1008c)、调压阀芯(1009c)与调压阀座之间间隙、油道(4001c)与高压油相连，偶件座(1001c)上的油道(1002c)通过环状槽(1003c)进入阀针(1004c)与偶件座(1001c)下部的环形油道，当阀针(1004c)下降，偶件座锥形底座与阀针(1004c)锥头接触时，喷油器关闭，阀针(1004c)上升，偶件座锥形底座与阀针(1004c)锥尖分开时，喷油器打开喷油。
图3～图5中无针阀弹簧喷油器，喷油器控制阀的阀座(2001c)采用长孔T型柱结构，控制阀的阀座包括锥形阀座(2006c)、中孔长柱体，下部大直径密封头(2001c-1)，锥形阀座有出油量孔(2003c)与中心长孔(2005c)相通，中心长孔(2005c)与针阀(1004c)的尾部液压缸(1004c-1)相通，T型控制阀的阀座采用浮动安装结构，T型控制阀的阀座长柱滑动装配在喷油器体(4000c)的中心孔中，T型控制阀座大直径密封头(2001c-1)端面液体压力使T型控制阀座的密封座压在喷油器体的密封座(4003c)，控制油依次通过主油道(4001c)、进油量孔(2004c)，控制阀座与中孔间隙、进入控制液压缸(1004c-1)；控制油从液压缸(1004c-1)依次通过中心长孔(2005c)出油量孔出油量孔(2003c)，阀座(2006c)阀球(2002c)组成的控制阀及回油孔(4002c)排出。
图3～图5中，阀球(2002c)安装在锥形阀座(2006c)上，球座(2007c)安装在阀球(2002c)，导向柱(2008c)顶在球座(2007c)上，导向柱(2008c)与衔铁(3004c)固定在一起，导向套(3005c)向上凸起，导向柱(2008c)安装在导向套(3005c)，衔铁(3004c)上部安装控制阀弹簧(2010c)，电磁铁外铁芯由双层L型环(3002c、3002c-1)叠成，内铁芯由带定位台阶的固定柱(3001c)和L型压环(3001c-1)组成，内铁芯固定柱(3001c)固定在铁芯安装体上，内 铁芯固定柱(3001c)的台阶压在压环(3001c-1)上，压环(3001c-1)压在外铁芯由双层L型环(3002c、3002c-1)上，线圈(3003c)安装在外、内铁芯的环形空间内。
图6描述了第二种电磁铁铁芯实施方案，内外、铁芯(3001d-1、3001d-2、3002d、3002d-1)由两层U型环叠而成，U型环由带台阶的铁芯固定柱(3001d)固定。
图7展示了槽状排液衔铁形状，图中大盘状衔铁与导向柱固定在一起，导向柱的外周分布排液槽，本衔铁适合回油口位置高于电磁铁的外置式回油接口喷油器。
图8展示了内孔排液衔铁形状，图中大盘状衔铁与导向柱固定在一起(2008c-1)，导向柱中心设置通孔，导向柱端部设导液槽，从控制阀排除的高压液直接流向电磁铁，对电磁铁起冷却作用，本衔铁特别适合回油口位置低于电磁铁的内置式回油接口喷油器，同时也适合回油口位置高于电磁铁的外置式回油接口喷油器。
图9展示了简化的主油路压力调整机构结构，图中偶件体斜油道(1002d)上段设置锥面油孔(1007d-1)，锥形节流量孔芯(1007d)安装在锥面油孔(1007d-1)中，图中阀针(1004d)减小长度，在喷油器偶件孔中安装行程调整垫(1004d-1)，进油量孔(2004d)设置在喷油器体中孔口部向外张开的斜面上，
本发明的实施例喷油器体进油口和回油口为内置式，很显然本发明的方案同样适用于进油口和回油口为外置式的喷油器，不再详述。

Claims (8)

  1. 柴油机共轨喷油器，其特征是，喷油器控制阀的阀座采用长孔T型柱结构(2001c)，液体通过控制阀的阀座的长孔来控制针阀的尾部液压；T型先导阀座采用浮动安装结构：T型控制阀阀座的大端向下，T型先导阀座长柱滑动装配在喷油器体的中心孔中，T型控制阀阀座的大端和喷油器体的中心孔设有相互配合的密封座面，T型控制阀阀座下端液压力使T型控制阀阀座的密封面压在喷油器体上的密封面上；针阀尾部不安装针阀弹簧，当发动机停机或刚启动，T型控制阀系统压力较低时，T型控制阀阀座下端面压力小于控制阀弹簧力时，控制阀弹簧力驱动T型控制阀座，使T型控制阀座压在针阀尾部，使针阀关闭，控制阀弹簧也起到了针阀预压弹簧的作用；在主进油路上设置压力调节机构，使针阀打开时，进入针阀下部的柴油压力降低，控制阀关闭时，针阀尾部压力高于针阀前端压力，依靠压力差使针阀关闭。
  2. 权利要求1所述柴油机共轨喷油器，其特征是：主油路液压调压机构为弹簧调压阀串接节流量孔垫的结构，从上至下依次为调压阀座、调压阀芯(1009c)、调压弹簧(1008c)，节流量孔垫(1007c)。
  3. 权利要求1所述柴油机共轨喷油器，其特征是：主油路液压调压机构为锥形节流量孔芯(1007d)，结构为在偶件体斜油道(1002d)上段设置锥面油孔(1007d-1)，锥形节流量孔芯(1007d)安装在锥面油孔(1007d-1)中。
  4. 权利要求1所述柴油机共轨喷油器，其特征是：主油路液压调整机构中阀座设置在喷油器体上，调压阀芯(1009c)安装在喷油器体的调压阀座上；调压弹簧(1008c)和节流量孔垫(1007c)安装在偶件的主油道上。
  5. 权利要求1所述柴油机共轨喷油器，其特征是：电磁铁衔铁(3004c)与衔铁导向柱(2008c)固定在一起，衔铁导向柱向下安装在导向套内(3005c)，导向柱顶在球阀座(2007c)。
  6. 权利要求1所述柴油机共轨喷油器，其特征是：优化的电磁铁衔铁为槽状排液电磁铁衔铁，导向柱外周(2008c)设置纵向槽，作为排油通道。
  7. 权利要求1所述柴油机共轨喷油器，其特征是：优化的电磁铁衔铁为内孔排液衔铁，衔铁与导向柱固定在一起(2008c-1)，导向柱中心设置通孔，导向柱端部设导液槽。
  8. 权利要求1所述柴油机共轨喷油器，其特征是：导向柱的导向套向上凸起一 段2～5mm高度，增加衔铁下表面与喷油器体之间的气隙。
PCT/CN2018/117368 2017-12-07 2018-11-26 柴油机共轨喷油器 WO2019109825A1 (zh)

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