CN102213166B - High-pressure common-rail electronic control oil injector - Google Patents
High-pressure common-rail electronic control oil injector Download PDFInfo
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- CN102213166B CN102213166B CN 201010144322 CN201010144322A CN102213166B CN 102213166 B CN102213166 B CN 102213166B CN 201010144322 CN201010144322 CN 201010144322 CN 201010144322 A CN201010144322 A CN 201010144322A CN 102213166 B CN102213166 B CN 102213166B
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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
- 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
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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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
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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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/008—Arrangement of fuel passages inside of injectors
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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
- 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
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
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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
- 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
- F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
- F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
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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
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/28—Details of throttles in fuel-injection apparatus
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention discloses a high-pressure common-rail electronic control oil injector, which comprises a high-pressure oil inlet end, a control plunger, an oil needle, a needle valve body sealing seat surface and an injection hole, wherein the high-pressure oil inlet end is connected with a common-rail pipe by an oil pipe; an accommodating cavity is formed between the control plunger and the needle valve body sealing seat surface; the lower part of the oil needle is sandwiched between an oil needle spring and the needle valve body sealing seat surface; the accommodating cavity is communicated with a control cavity by a fuel channel and an oil inlet small hole; the control cavity is communicated with a transition cavity of a control valve by an oil outlet small hole; the transition cavity is connected with an oil return pipe of the oil injector; an electromagnetic valve spring pushes a ball valve into the oil outlet small hole in the seat surface by an armature; an electromagnetic valve coil is arranged above the armature; a needle valve body is arranged on the lower part of the high-pressure common-rail electronic control oil injector; the lower part of the oil needle is clamped on the needle valve body; and external contact surfaces of the needle valve body and the oil needle are inclined relative to a vertical direction. The high-pressure common-rail electronic control oil injector can stably control oil injection with small quantity and achieve excellent effects of saving energy, reducing emission and reducing an engine noise.
Description
Technical field
The present invention relates to a kind of high pressure common rail fuel injection system, particularly a kind of high pressure common rail electric control fuel injector.
Background technique
Now, automobile industry is more and more higher to the requirement of emission performance, Economy, reliability, in order to improve diesel engine performance, the fuel-injected high-pressure trend, become more meticulous, inevitable development direction that dexterityization is fuel injection system.High pressure common rail fuel injection system is the main development direction of current diesel fuel injection system, and high pressure common rail electric control fuel injector is the core key part of high pressure common rail fuel injection system, has determined the multinomial key parameter such as speed of response, injection rate, reliability of high pressure common rail fuel injection system.
Existing high pressure common rail electric control fuel injector, structure is as shown in Figure 1 arranged, the high pressure oil inlet end 2 of oil sprayer 1 is connected with common rail pipe by oil pipe, high pressure fuel arrives cavity volume 5 by high pressure oil inlet end 2 by oilhole 4 by clearance filter 3, cavity volume 5 is the cavitys that form between control plunger 17 and needle-valve body sealed seat surface 28, the active force of spindle spring 13 is closed in spindle 18 on the needle-valve body sealed seat surface 28, cut off the fuel gallery of leading to spray orifice 29, cavity volume 5 communicates with control chamber 55 by fuel gallery 40 and oil-feed aperture 48.Control chamber 55 communicates with the adapter cavity 59 of control valve 60 by fuel-displaced aperture 56, and adapter cavity 59 joins with the return tube of oil sprayer, and fuel-displaced aperture 56 is closed by the ball valve 9 that the top is contained on the seat surface 8.Solenoid valve spring 14 is contained in ball valve 9 tops on the seat surface 8 by armature 11.Cavity volume 5 and control chamber 55 communicate with rail pressure, spindle spring 13 is contained in spindle 18 tops on the needle-valve body sealed seat surface 28 by its pretightening force and hydraulic coupling, hydraulic coupling is directly proportional with area and rail pressure that spindle sealing intersection forms, the hydraulic coupling stress balance at control plunger 17 two ends.
During oil spout, electromagnetic valve coil 57 loads the approximately driving current of 20A, current excitation generates an electromagnetic field between the outer magnetic pole 61 of internal magnetic pole 62, armature 11 and the solenoid valve of solenoid valve, gap between armature 11 and outer magnetic pole 61 and the internal magnetic pole 62 is about 0.1mm, electromagnetic field produces electromagnetic force, the spring force that attracts armature 11 to overcome solenoid valve spring 14 moves to pole orientation, when armature 11 moves upward, ball valve 9 leaves seat surface 8 oil circuit that fuel-displaced aperture 56 leads to adapter cavity 59 is opened, fuel oil in the control chamber 55 gushes, and fuel oil enters control chamber 55 by oil-feed aperture 48 simultaneously.If oil-feed aperture 48 is identical with the diameter of fuel-displaced aperture 56, cavity pressure was about 50% of rail pressure after control chamber 55 turnover oil reached steady state, control chamber 55 internal pressures reduce, the pressure at control plunger 17 two ends is balance and produce tensile force f and act on the spindle 18 no longer, after tensile force f is made a concerted effort greater than the hydraulic coupling at spindle spring 13 pretightening forces and needle-valve body sealed seat surface 28 places, tensile force f makes spindle 18 lift from needle-valve body sealed seat surface 28, and the fuel gallery that cavity volume 5 leads to spray orifice 29 places is opened and commencement of fuel injection.When stopping oil spout, cut off the electric current of solenoid valve 12 by tenminal block 58, electromagnetic force descends rapidly, solenoid valve spring 14 forces armature 11 to move downward, ball valve 9 is closed fuel-displaced aperture 56, and the fuel oil that is entered by oil-feed aperture 48 rises the oil pressure in the control chamber 55, and control plunger 17 two ends reach hydraulic resistance balance again, the active force of spindle spring 13 is contained in spindle 18 tops needle-valve body sealed seat surface 28 and cuts off and leads to the fuel gallery of spray orifice 29, end of injection.
The spindle that high pressure common rail electric control fuel injector among Fig. 1 has-control plunger unit only relies on spindle spring force and very little hydraulic coupling to close spindle and finishes oil spout, and hydraulic coupling is relevant with the low-pressure section of needle-valve body sealed seat surface lower end.In order to realize little fuel injection quantity, need spindle to open slowly, close rapidly, and high pressure common rail electric control fuel injector shown in Figure 1 does not have and open slowly, closes rapidly characteristics.
The patent No. is US 7,188,788B2, notice of authorization day are the common-rail injector that the U. S. Patent on March 13rd, 2007 discloses a kind of subsidiary spindle shutoff device, this shutoff device adopts sleeve and control edge to realize the variation of pressure, open the initial stage at spindle, the fuel oil circulation area is invariable to be to be formed by two cylindrical gap, along with the increase of lift, the fuel gallery is opened after crossing the control edge, and circulation area sharply increases.
In order to reach better energy-saving and emission-reduction and to reduce noise, need oil-fired system to have the characteristics of multi-injection, its medium and small oil mass pre-spray is very important to reducing discharging, spray is also very important to reducing particulate emission after the little oil mass, and oil sprayer opens slowly and cut out rapidly guaranteeing that little oil mass sprays most important.
Summary of the invention
The objective of the invention is to disclose a kind of high pressure common rail electric control fuel injector, to solve the technical problem that promotes little oil mass jetting stability.
In order to realize above purpose, the invention discloses a kind of high pressure common rail electric control fuel injector, comprise the high pressure oil inlet end, the control plunger, spindle, needle-valve body sealed seat surface and spray orifice, the high pressure oil inlet end is connected with common rail pipe by oil pipe, be formed with cavity volume between control plunger and the needle-valve body sealed seat surface, the bottom of spindle is clipped between spindle spring and the needle-valve body sealed seat surface, cavity volume passes through the fuel gallery, the oil-feed aperture is connected with control chamber, control chamber is connected with the adapter cavity of control valve by fuel-displaced aperture, adapter cavity links to each other with the return tube of oil sprayer, the solenoid valve spring pushes up ball valve the fuel-displaced aperture that is contained on the seat surface by armature, above armature, be provided with electromagnetic valve coil, bottom at high pressure common rail electric control fuel injector is provided with needle-valve body, the bottom of spindle is connected on the needle-valve body, and the outer contacting face of needle-valve body and spindle is all in vertical direction with being obliquely installed.
Wherein, the outer contacting face of needle-valve body and spindle is identical with the angle of inclination of vertical direction.
Wherein, the outer contacting face of needle-valve body and the angle of inclination of vertical direction are α, and the outer contacting face of spindle and the angle of inclination of vertical direction are β, and the angular range of α and β is 5 to 40 degree.
Wherein, the angle value of α and β is 5,5.5,6,7.5,8,10 or 12 degree.
Wherein, the needle-valve body next-door neighbour is arranged at the lower end of spindle spring.
Wherein, needle-valve body is arranged at the lower end of high pressure common rail electric control fuel injector, and next-door neighbour's needle-valve body sealed seat surface top arranges.
High pressure common rail electric control fuel injector of the present invention can be stablized the little oil mass of control and spray, and reaches good energy-saving and emission-reduction and the effect of reduction engine noise.
Description of drawings
Fig. 1 is the structural representation of existing high pressure common rail electric control fuel injector;
Fig. 2 is high pressure common rail electric control fuel injector embodiment's one of the present invention structural representation;
Fig. 3 is the enlarged diagram of circle part among Fig. 2;
Fig. 4 is the enlarged diagram that is provided with gasket construction with Fig. 3 same principle;
Fig. 5 is high pressure common rail electric control fuel injector embodiment's two of the present invention structural representation;
Fig. 6 is the schematic diagram of the function curve of high pressure common rail electric control fuel injector needle lift of the present invention and conical surface gap circulation area;
Fig. 7 is the schematic diagram of the function curve of high pressure common rail electric control fuel injector needle lift of the present invention and needle-valve body sealed seat surface circulation area;
Fig. 8 is the schematic diagram of the function curve of the fuel pressure in high pressure common rail electric control fuel injector needle lift of the present invention and the cavity volume;
Fig. 9 is the schematic diagram that high pressure common rail electric control fuel injector needle lift of the present invention and spindle are closed the function curve of power.
Mark the following drawings mark thereon by reference to the accompanying drawings:
The 1-oil sprayer, 2-high pressure oil inlet end, 3-clearance filter, 4-oilhole, the 5-cavity volume, 6-needle-valve body, 8-seat surface, 9-ball valve, 11-armature, 12-solenoid valve, 13-spindle spring, 14-solenoid valve spring, 16-controls valve pocket, and 17-controls plunger, 18-spindle, the 20-supplementary structure, 21-first conical surface, 22-second conical surface, 26-downstream cavity volume, 27-upstream volume chamber, 28-needle-valve body sealed seat surface, the 29-spray orifice, 30-pad, 40-fuel gallery, 48-oil-feed aperture, 55-control chamber, the fuel-displaced aperture of 56-, the 57-electromagnetic valve coil, 58-tenminal block, 59-adapter cavity, the 60-control valve, 61-outer magnetic pole, 62-internal magnetic pole.
Embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
Shown in Fig. 1-9, a kind of high pressure common rail electric control fuel injector is disclosed, this high pressure common rail electric control fuel injector is driven by solenoid valve 12, spindle 18 is connected with control plunger 17, be set with control valve pocket 16 on the control plunger 17, the active force of spindle spring 13 is contained on the needle-valve body sealed seat surface 28 spindle 18 tops, the bottom of spindle 18 is connected in the needle-valve body 6, the cooperation conical surface of needle-valve body 6 and spindle 18 all forms certain angle of inclination with vertical direction, for convenience of description, the outer contacting face with spindle 18 and needle-valve body 6 is named as respectively first conical surface 21, second conical surface 22.
The lift difference of the spindle 18 then gap between two conical surfaces 21 and 22 changes thereupon, and when spindle 18 top was contained on the needle-valve body sealed seat surface 28, this gap was minimum value, and when spindle 18 during in maximum lift, this gap is maximum value.
Shown in Fig. 2,3, there is pressure difference between the upstream volume chamber 27 of fuel-injected fuel flow path, the downstream cavity volume 26, upstream volume chamber 27 higher pressure produce the power of closing to spindle 18, cavity volume 26 less pressure in downstream then produce opening force to spindle 18, and the size of this power is simultaneously relevant with the spindle intersection.The difference of more than closing power, two power of opening force reduces and the closing velocity increase spindle 18 opening speeds.The speed that spindle opens and closes is relevant with oil-feed hole diameter, fuel-displaced hole diameter, control plunger diameter, spindle spring force simultaneously.
Fig. 2-4 discloses the detailed structure of the supplementary structure 20 that spindle closes, needle-valve body 6 has second conical surface 22 that an expanded angle is 2 α, spindle 18 has first conical surface 21 that an expanded angle is 2 β, angle [alpha] and β generally can be the same or different, when spindle 18 tops are contained on the needle-valve body sealed seat surface 28, between the conical surface 22 and 21, there is the gap.When spindle 18 is opened and is moved upward, gap between the conical surface 22 and 21 increases, in case spindle 18 breaks away from needle-valve body sealed seat surface 28, fuel oil enters spray orifice 29 by the cavity volume 5 needle-valve body sealed seat surface 28 of flowing through, gap between the conical surface 22 and 21 is the minimum actual internal area Fmin of fuel flow path and has formed the link of damming, caused the cavity volume 5 of upstream different from needle-valve body sealed seat surface 28 circumferential pressures, this pressure difference has produced the additional hydraulic coupling that spindle 18 is closed, this hydraulic coupling reduces the opening speed of spindle 18, in case spindle 18 arrives maximum lift position, it is large that gap between the conical surface 22 and 21 becomes, minimum actual internal area Fmin sharply increases, and the cavity volume 5 that has reduced the upstream is poor with needle-valve body sealed seat surface 28 circumferential pressures.Spray when finishing, spindle 18 pushes up dress needle-valve body sealed seat surface 28 again, and the gap smaller between the conical surface 22 and 21 has also produced larger pressure difference, and then has produced the additional hydraulic coupling that auxiliary spindle 18 is closed, and accelerates the closing velocity of spindle 18.The supplementary structure 20 that spindle is closed has reduced the opening speed of spindle 18, has increased the closing velocity of spindle 18.
In Fig. 4, the supplementary structure 20 that spindle is closed is Split type structure with spindle 18, the spring seat of spindle spring 13 simultaneously, supplementary structure 20 is adjusted by pad 30 with the relative position of spindle 18, adopt pad 30 can control flexibly the conical surface 21,22 primary clearance, and then realize the optimization of oil sprayer spray characteristic.In order to adjust gap suitable between the conical surface 22 and 21, at first in the situation that there is not spindle 18 to measure the relative position " x " of supplementary structure 20 and needle-valve body, this moment, supplementary structure 20 contacted with needle-valve body, gap between the two is 0, and the thickness of pad 30 is chosen according to " measured value x+ supplementary structure 20 initial lifts ".
Fig. 5 discloses another high pressure common rail electric control fuel injector, in this embodiment, supplementary structure 20 is integrated with spindle 18, first conical surface 21, second conical surface 22 place between spindle 18 and the needle-valve body, during spindle 18 opening and closing, this supplementary structure 20 makes between upstream volume chamber 27 and the downstream cavity volume 26 and has pressure difference, and auxiliary spindle 18 opening speeds of this pressure difference descend, and closing velocity increases.
Fig. 6 has shown the function curve of high pressure common rail electric control fuel injector needle lift of the present invention and conical surface gap circulation area, when the spindle top was contained in the needle-valve body sealed seat surface, needle lift was 0, and the fuel oil circulation area is very little, when spindle lifted, fuel oil circulation area and conical surface gap were linear.
Fig. 7 has shown the function curve of high pressure common rail electric control fuel injector needle lift and needle-valve body sealed seat surface circulation area, and this curve is relevant with circulation area and needle-valve body sealed seat surface circulation area that spray orifice is fixed.
Fig. 8 has shown the function curve of fuel pressure in high pressure common rail electric control fuel injector needle lift and the cavity volume, when spindle is closed, although circulation area is little because without fuel flow, so there is not pressure difference, when spindle arrives maximum lift position, circulation area maximum and fuel flow rate are maximum, and in the process of spindle opening and closing, it is maximum that the poor decline of fuel pressure reaches.
Fig. 9 has shown that high pressure common rail electric control fuel injector needle lift and spindle close the function curve of power.
Above disclosed only be several specific embodiment of the present invention, still, the present invention is not limited thereto, the changes that any person skilled in the art can think of all should fall into protection scope of the present invention.
Claims (6)
1. high pressure common rail electric control fuel injector, it is characterized in that, comprise the high pressure oil inlet end, the control plunger, spindle, needle-valve body sealed seat surface and spray orifice, described high pressure oil inlet end is connected with common rail pipe by oil pipe, be formed with cavity volume between described control plunger and the needle-valve body sealed seat surface, the bottom of described spindle is clipped between spindle spring and the needle-valve body sealed seat surface, described cavity volume passes through the fuel gallery, the oil-feed aperture is connected with control chamber, described control chamber is connected with the adapter cavity of control valve by fuel-displaced aperture, adapter cavity links to each other with the return tube of oil sprayer, the solenoid valve spring pushes up ball valve the fuel-displaced aperture that is contained on the seat surface by armature, above described armature, be provided with electromagnetic valve coil, bottom at described high pressure common rail electric control fuel injector is provided with needle-valve body, the bottom of described spindle is connected on the described needle-valve body, the outer contacting face of described needle-valve body and spindle is all in vertical direction with being obliquely installed, the lift difference of the described spindle then gap between the outer contacting face of described needle-valve body and spindle changes thereupon, form upstream volume chamber and the downstream cavity volume that has pressure difference in the fuel-injected fuel flow path, with generation described spindle opening speed is reduced and the additional hydraulic power of closing velocity increase.
2. high pressure common rail electric control fuel injector according to claim 1 is characterized in that, the outer contacting face of described needle-valve body and spindle is identical with the angle of inclination of vertical direction.
3. high pressure common rail electric control fuel injector according to claim 1 and 2, it is characterized in that, the outer contacting face of described needle-valve body and the angle of inclination of vertical direction are α, and the outer contacting face of described spindle and the angle of inclination of vertical direction are β, and the angular range of described α and β is 5 to 40 degree.
4. high pressure common rail electric control fuel injector according to claim 3 is characterized in that, the angle value of described α and β is 5,5.5,6,7.5,8,10 or 12 degree.
5. high pressure common rail electric control fuel injector according to claim 1 and 2 is characterized in that, described needle-valve body next-door neighbour is arranged at the lower end of described spindle spring.
6. high pressure common rail electric control fuel injector according to claim 1 and 2 is characterized in that, described needle-valve body is arranged at the lower end of high pressure common rail electric control fuel injector, is close to described needle-valve body sealed seat surface top and arranges.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010144322 CN102213166B (en) | 2010-04-08 | 2010-04-08 | High-pressure common-rail electronic control oil injector |
| PCT/CN2010/075148 WO2011124045A1 (en) | 2010-04-08 | 2010-07-14 | High-pressure common rail electric control fuel injector |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010144322 CN102213166B (en) | 2010-04-08 | 2010-04-08 | High-pressure common-rail electronic control oil injector |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102213166A CN102213166A (en) | 2011-10-12 |
| CN102213166B true CN102213166B (en) | 2013-01-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010144322 Active CN102213166B (en) | 2010-04-08 | 2010-04-08 | High-pressure common-rail electronic control oil injector |
Country Status (2)
| Country | Link |
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| CN (1) | CN102213166B (en) |
| WO (1) | WO2011124045A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102330627A (en) * | 2011-10-16 | 2012-01-25 | 中国兵器工业集团第七0研究所 | Oil nozzle for common rail injector of flat dual-opposed diesel engine |
| CN102705120B (en) * | 2012-06-19 | 2015-03-11 | 哈尔滨工程大学 | Dual-fuel electric control monomer ejector |
| EP2722518A1 (en) * | 2012-10-22 | 2014-04-23 | Delphi International Operations Luxembourg S.à r.l. | Fuel Injection nozzle having a flow restricting element |
| CN103498743B (en) * | 2013-10-23 | 2015-08-05 | 重庆红江机械有限责任公司 | A kind of control valve of high pressure common rail electric control fuel injector |
| CN104747337A (en) * | 2015-03-26 | 2015-07-01 | 常州博瑞油泵油嘴有限公司 | Hydraulic coupler of instant response type common-rail oil injector |
| CN107605633B (en) * | 2017-07-12 | 2020-01-07 | 北京航空航天大学 | Multi-fuel pump oil outlet valve with viscosity compensation function for aviation heavy oil piston engine |
| CN107609260B (en) * | 2017-09-08 | 2020-08-28 | 哈尔滨电气动力装备有限公司 | High-parameter vertical pump impeller axial and radial water thrust load similar conversion method |
| CN113250878B (en) * | 2021-06-18 | 2022-08-16 | 中国北方发动机研究所(天津) | Control plunger part of common rail fuel injector |
| CN116292001B (en) * | 2023-03-31 | 2024-07-09 | 北京理工大学 | Control plunger sleeve of high-pressure oil supply system |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5020500A (en) * | 1990-03-28 | 1991-06-04 | Stanadyne Automotive Corp. | Hole type fuel injector and injection method |
| RU2175078C2 (en) * | 2000-01-31 | 2001-10-20 | Гундоров Валентин Михайлович | Spray tip internal combustion engine nozzle |
| DE102008001907A1 (en) * | 2008-05-21 | 2009-11-26 | Robert Bosch Gmbh | Fuel injector |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0752060B1 (en) * | 1994-03-24 | 1999-01-27 | Siemens Aktiengesellschaft | Injection valve |
| JPH08189437A (en) * | 1995-01-09 | 1996-07-23 | Zexel Corp | Electromagnetic fuel injection valve |
| JP2007107460A (en) * | 2005-10-13 | 2007-04-26 | Toyota Motor Corp | Fuel injection device |
| DE102005059169A1 (en) * | 2005-12-12 | 2007-06-14 | Robert Bosch Gmbh | Fuel injector with directly actuatable injection valve member |
| US9163597B2 (en) * | 2008-10-01 | 2015-10-20 | Caterpillar Inc. | High-pressure containment sleeve for nozzle assembly and fuel injector using same |
-
2010
- 2010-04-08 CN CN 201010144322 patent/CN102213166B/en active Active
- 2010-07-14 WO PCT/CN2010/075148 patent/WO2011124045A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5020500A (en) * | 1990-03-28 | 1991-06-04 | Stanadyne Automotive Corp. | Hole type fuel injector and injection method |
| RU2175078C2 (en) * | 2000-01-31 | 2001-10-20 | Гундоров Валентин Михайлович | Spray tip internal combustion engine nozzle |
| DE102008001907A1 (en) * | 2008-05-21 | 2009-11-26 | Robert Bosch Gmbh | Fuel injector |
Non-Patent Citations (1)
| Title |
|---|
| JP特开2007-107460A 2007.04.26 |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011124045A1 (en) | 2011-10-13 |
| CN102213166A (en) | 2011-10-12 |
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Inventor after: Li Jun Inventor after: You Li Inventor after: Li Chunyan Inventor before: You Li Inventor before: Li Chunyan |
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Effective date of registration: 20180719 Address after: 300000 2 Yulong Road, automobile industrial park, Wuqing District, Tianjin Patentee after: North oil electronic control fuel injection system (Tianjin) Co., Ltd. Address before: No. 3 City Zhuang Road, Fengtai District, Beijing Patentee before: Beijing Yaxin Ketianwei Oil Pume Nozzle Tip Co., Ltd. |