EP1387939A1 - Kraftstoffeinspritzventil für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzventil für brennkraftmaschinenInfo
- Publication number
- EP1387939A1 EP1387939A1 EP02726069A EP02726069A EP1387939A1 EP 1387939 A1 EP1387939 A1 EP 1387939A1 EP 02726069 A EP02726069 A EP 02726069A EP 02726069 A EP02726069 A EP 02726069A EP 1387939 A1 EP1387939 A1 EP 1387939A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve needle
- pressure
- valve
- piston rod
- control chamber
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
- F02M45/086—Having more than one injection-valve controlling discharge orifices
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
Definitions
- the injection pressure at which the fuel is injected through the fuel injection valve is increased.
- the number of injection holes in the fuel injection valve is increased, so that the diameter of the individual injection holes can be reduced.
- the aim of this measure is to increase the jet energy in the case of injection jets while at the same time reducing the drop diameter. If very small quantities are to be delivered, the injection times are very short at high pressures on the fuel injection valve. This results in a violent course of combustion with a correspondingly large noise development.
- a fuel injection valve with a variable injection cross section in which two rows of injection openings are formed. These injection openings are defined by an inner valve needle and a valve del surrounding sleeve controlled, both the sleeve and the inner needle are acted upon by closing springs which press them into abutment against a valve seat, whereby the injection openings are closed. If fuel is introduced into corresponding pressure chambers under high pressure, the sleeve and the inner needle are acted upon by the fuel pressure in these pressure chambers.
- stroke-controlled fuel injection systems are known from the prior art, in which a valve needle has a pressure surface which is constantly acted upon by fuel under high pressure in the opening direction.
- the counterforce is not generated by a closing spring, but hydraulically by a valve piston which acts on the valve needle and which in turn exerts a closing force on the valve needle due to the fuel pressure in a control chamber.
- the document DE 198 27 267 AI may be mentioned here.
- the closing force on the valve needle changes so that it is moved by the hydraulic force on the pressure surface.
- Such stroke-controlled fuel injection systems are used in many modern internal combustion engines, especially for self-igniting internal combustion engines in passenger cars.
- variable injection cross section and the stroke-controlled injection system
- stroke-controlled injection system would be particularly advantageous for a further optimization of the combustion process. So far, however, this has not been possible without great effort to easily transfer the variable injection cross-section to the stroke-controlled systems. This requires complicated sealing edges or additional control valves, which are complex to manufacture and costly.
- the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that two rows of injection openings can be opened successively with a stroke-controlled injection system and thus an injection curve can be formed without additional control edges or control valves being necessary.
- An inner valve needle is guided in the outer valve needle, both the outer valve needle and the inner valve needle controlling at least one injection opening.
- a fuel-filled control chamber is formed in the fuel injection valve, the pressure of which acts on the valve needles at least indirectly in the direction of the valve seat. If the pressure in the control chamber is changed, the closing force also changes due to the valve needles, so that the injection openings can be actuated.
- a throttle connection is formed by the opening stroke movement of the outer valve needle, so that the pressure in the control chamber is no longer applied to the inner valve needle. This causes the closing force on the inner valve needle reduced in a simple manner without the need for a control edge or a further valve.
- the outer valve needle is connected to an outer piston rod, the end face of which is acted upon by the pressure in the control chamber and thereby generates the closing force on the valve member.
- the throttle connection is formed between the end face of the piston rod and a fixed base, so that the throttle connection can be formed in a simple and thus easy to manufacture manner.
- the inner valve needle is also connected to an inner piston rod, the end face of which is also acted upon by the pressure in the pressure chamber and thus generates the closing force on the inner valve needle.
- the function of the valve needle and piston rod can also be separated here.
- the inner piston rod is guided in the outer piston rod, so that both piston rods are arranged coaxially with one another. In this way, the connection of the outer piston rod to the outer valve needle and the inner valve needle to the inner piston rod can advantageously be easily realized.
- the inner piston rod comes with the opening stroke movement of the inner valve needle at one on the inside of the outer piston rod-shaped stop surface to the system.
- the outer piston rod has an inwardly projecting region at its end facing away from the combustion chamber.
- an inner control chamber is delimited by the outer valve needle, the inwardly projecting region and the inner valve needle, which is connected to the control chamber, the connection being designed in the form of a connecting bore.
- the inner valve needle has a pressure surface which is only acted upon by the pressure in the pressure chamber after the outer valve needle has lifted off the valve seat. This results in an opening force on the inner valve needle only when an injection is to take place. As a result, no opening force acts on the inner valve needle between the injections and the latter always closes the injection openings assigned to it.
- the pressure in the control chamber is set by a connection to a leakage oil chamber that can be controlled by a valve. Only this one 2/2-way valve is necessary for pressure control, since the inlet throttle remains unchanged.
- the outer piston rod at least partially closes the inlet throttle during the opening stroke movement of the outer valve needle. This leads to a further reduction in the pressure in the control chamber, so that the closing force on the inner valve needle decreases further.
- FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention
- FIG. 2 shows an enlargement of FIG. 1 in the area designated II
- FIG. 3 shows an enlargement of FIG. 1 in the area designated III
- Figure 4 shows the same section as Figure 3, with the outer piston rod in a different switching position. Description of the embodiment
- FIG. 1 an embodiment of the fuel injection valve according to the invention is shown in longitudinal section.
- the fuel injection valve comprises a housing 1, which can be constructed in several parts.
- the housing 1 has a bore 3 in its end region on the combustion chamber, in which a piston-shaped outer valve needle 10 is arranged.
- the outer valve needle 10 is sealingly guided in a section facing away from the combustion chamber in the bore 3 and tapers towards the combustion chamber, forming a pressure shoulder 9.
- the outer valve needle 10 merges into a conical pressure surface 101 and finally into a likewise conical valve sealing surface 11, the sealing surface 11 coming into contact with a valve seat 13 formed at the end of the bore 3 on the combustion chamber side.
- FIG. 2 shows an enlarged illustration of the section from FIG.
- a pressure chamber 5 is formed in the housing 1 at the level of the pressure shoulder 9 and continues as an annular channel surrounding the outer valve needle 10 up to the valve seat 13.
- a plurality of injection openings 7 are formed in the valve seat 13 and are arranged in a first injection opening row 107 and in a second injection opening row 207 arranged axially offset therewith.
- An inner valve needle 12 is arranged in the outer valve needle 10, which is piston-shaped and has a conical pressure surface 112 and a valve sealing surface 14 at its combustion chamber end. Comes the inner valve needle 12 on the valve seat 13, the valve sealing surface 14 touches the valve seat 13 between the first injection opening row 107 and the second injection opening row 207. The interaction of the outer valve needle 10 and the inner valve needle 12 enables the injection opening rows 107, 207 with the pressure chamber 5 connect. If the outer valve needle 10 lies with the valve sealing surface 11 on the valve seat 13, both rows of injection openings 107, 207 are closed against the pressure chamber 5.
- the pressure chamber 5 is connected to a high-pressure connection 17, which is connected to a high-pressure fuel source, not shown in the drawing.
- the high-pressure fuel source supplies a predetermined high-pressure fuel during operation of the internal combustion engine, so that this fuel pressure always prevails in the inlet channel 15 and thus also in the pressure chamber 5 and forms a high-pressure fuel region.
- an outer piston rod 20 is arranged so as to be longitudinally displaceable, the end face of which faces the combustion chamber against the outer valve needle 10 and the end face 21 facing away from the combustion chamber delimits a control chamber 24 formed at the end of the piston bore 18.
- the spring 42 is supported on the end facing away from the combustion chamber and is located at its end facing the combustion chamber on a spring plate 44 which is connected to the outer piston rod 20, so that the spring 42 applies a force in the direction of the valve seat 13 to the outer piston rod 20 and thus also exerts on the outer valve needle 10.
- FIG. 3 shows an enlargement of FIG. 1 in the area of the control chamber 24.
- the control chamber 24 is delimited by the base area 19, the wall of the piston bore 18 and the end face 21 of the outer piston rod 20.
- the outer piston rod 20 has an inwardly projecting region 27 at its end facing away from the combustion chamber, so that an inner control chamber 29 is delimited by the outer piston rod 20 and the end side 31 of the inner piston rod 22 facing away from the combustion chamber, said control chamber 29 being connected via a connecting bore 28 in the outer Piston rod 20 is connected to the control chamber 24.
- a stop surface 23 is formed in the interior of the outer piston rod 20 and limits the longitudinal movement of the inner piston rod 22.
- the control chamber 24 is connected to the inlet duct 15 via an inlet throttle 25.
- the control chamber 24 is connected via an outlet throttle 25 to a leak oil chamber 30 formed in the housing 1.
- a longitudinally movable magnet armature 34 is arranged in the leakage oil chamber 30 and has a sealing ball 32 at its end facing the control chamber 24.
- the magnet armature 34 is acted upon by a closing spring 38 which presses the magnet armature 34 in the direction of the control chamber 24.
- an electromagnet 36 is arranged in the leak oil chamber 30, which, when suitably energized, exerts an attractive force on the magnet armature 34 and moves it away from the control chamber 24 against the force of the closing spring 38.
- the magnet armature 34 is pressed by the closing spring 38 in the direction of the control chamber 24, and the sealing ball 32 closes the flow restrictor 26.
- the electromagnet 36 is energized, the magnet armature 34 is moved away from the control chamber 24 and the sealing ball 32 is released the outlet throttle 26 free. In this position, fuel can flow out of the control chamber 24 into the leakage oil chamber 30 via the outlet throttle 26.
- the magnetic tank 34, the sealing ball 32 and the electromagnet 36 thus form a valve 33.
- the fuel injector works as follows: When the fuel injector is closed, ie when no fuel is injected through the injection openings 7 into the combustion chamber of the internal combustion engine, the sealing ball 32 closes the outlet throttle 26.
- the inlet throttle 25 in control chamber 24 has the same effect Fuel pressure as in the inlet duct 15. This results in a hydraulic force on the end face 21 of the outer piston rod 20 and on the end face 31 of the inner piston rod 22, which transmit these to the outer valve needle 10 or the inner valve needle 12, so that the valve needles 10 , 12 are pressed against the valve seat 13 and close the injection openings 7.
- the size ratio of the end face 21 to the pressure shoulder 9 or the pressure surface 101 of the outer valve needle 10 is designed such that in this state of the fuel injection valve the hydraulic force on the end face 21 of the outer piston rod 20 predominates. If fuel is to be injected into the combustion chamber, the electromagnet 36 is energized, as a result of which the magnet armature 34 and thus also the sealing ball 32 move away from the outlet throttle 26 and connect the control chamber 24 to the leak oil chamber 30 via the outlet throttle 26.
- inlet throttle 25 and outlet throttle 26 are designed so that the fuel pressure thereby drops in the control chamber 24, to the extent that the outer valve needle 10 experiences a greater hydraulic force through the pressure surface 101 and the pressure shoulder 9 than that now End face 21 of the outer piston rod 20 hydraulic force acting in the control chamber 24.
- the inner piston rod 22 moves in the axial direction until it comes into contact with the stop surface 23 of the outer piston rod 20.
- the successive opening of the two rows of injection openings 107 and 207 results in an injection profile formation in which fuel is injected into the combustion chamber of the internal combustion engine at full pressure at the beginning of injection, but only through part of the injection openings 7, while in the main injection through all Injection openings 7 of both rows of injection openings 107 and 207 is injected and thus also with a higher injection rate.
- the valve 33 which is formed by the electromagnet 34, the magnet armature 34 and the sealing ball 32, becomes again closed before the fuel pressure in the control chamber 24 has dropped so far that the inner valve needle 12 opens.
- the outlet throttle 26 is then already closed again before the outer piston rod 20 comes to rest with the end face 21 on the base 19 of the piston bore 18. This results in a hydraulic cushion between the end face 21 and the base surface 19, which dampens the opening movement of the outer piston rod 20 and prevents a pressure drop in the control chamber 24, so that the inner piston rod 22 always exerts a sufficient closing force on the inner valve needle 12.
- the outer piston rod 20 partially covers the inlet throttle 25 during the opening stroke movement of the outer valve needle 10, so that the cross section of the inlet throttle 25 is reduced, but this is not completely closed. This can be achieved, for example, by a remaining annular gap between the outer piston rod 20 and the wall of the piston bore 18.
- the connection of the control chamber 24 to the discharge throttle 26 is ensured, for example, by grooves in the radial direction on the end face 21 of the outer piston rod 20.
- the fuel flow through the inlet throttle 25 into the control chamber 24 is significantly reduced, so that the fuel pressure in the control chamber 24 and, via the connecting bore 28, also in the inner control chamber 29 continues to drop and the inner piston rod 22 and thus the inner valve needle 12 opens in the manner described above.
Landscapes
- 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
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10122241A DE10122241A1 (de) | 2001-05-08 | 2001-05-08 | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10122241 | 2001-05-08 | ||
PCT/DE2002/001036 WO2002090754A1 (de) | 2001-05-08 | 2002-03-22 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1387939A1 true EP1387939A1 (de) | 2004-02-11 |
EP1387939B1 EP1387939B1 (de) | 2008-01-16 |
Family
ID=7683966
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02726069A Expired - Lifetime EP1387939B1 (de) | 2001-05-08 | 2002-03-22 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US7117842B2 (de) |
EP (1) | EP1387939B1 (de) |
JP (1) | JP4116448B2 (de) |
DE (2) | DE10122241A1 (de) |
WO (1) | WO2002090754A1 (de) |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10205970A1 (de) * | 2002-02-14 | 2003-09-04 | Bosch Gmbh Robert | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10227277A1 (de) * | 2002-06-19 | 2004-01-08 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10246974A1 (de) * | 2002-10-09 | 2004-04-22 | Robert Bosch Gmbh | Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine |
DE10312738B4 (de) * | 2003-03-21 | 2005-02-24 | Siemens Ag | Einspritzventil mit hydraulisch betätigter Nadel und Hohlnadel und Verfahren zum Steuern einer Einspritzung |
DE10312586A1 (de) * | 2003-03-21 | 2004-09-30 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10326043A1 (de) * | 2003-06-10 | 2004-12-30 | Robert Bosch Gmbh | Einspritzdüse für Brennkraftmaschinen |
DE10330705B4 (de) * | 2003-07-08 | 2014-09-04 | Robert Bosch Gmbh | Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine |
DE10334209A1 (de) * | 2003-07-26 | 2005-02-10 | Robert Bosch Gmbh | Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine |
DE10338228A1 (de) * | 2003-08-20 | 2005-03-10 | Bosch Gmbh Robert | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE10354878A1 (de) * | 2003-11-24 | 2005-06-09 | Robert Bosch Gmbh | Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Kraftstoff-Direkteinspritzung, sowie Verfahren zu ihrer Herstellung |
DE10357769B4 (de) * | 2003-12-10 | 2007-06-21 | Siemens Ag | Kraftstoffeinspritzventil |
DE102004010760A1 (de) * | 2004-03-05 | 2005-09-22 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen mit Nadelhubdämpfung |
DE102004015360A1 (de) * | 2004-03-30 | 2005-10-20 | Bosch Gmbh Robert | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE102004030448A1 (de) * | 2004-06-24 | 2006-01-12 | Robert Bosch Gmbh | Kraftstoffeinspritzvorrichtung |
EP1626173B1 (de) * | 2004-08-13 | 2008-03-05 | Delphi Technologies, Inc. | Einspritzdüse |
ATE371809T1 (de) * | 2004-10-01 | 2007-09-15 | Delphi Tech Inc | Einspritzdüse |
DE102004051756A1 (de) * | 2004-10-23 | 2006-04-27 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
US7507210B2 (en) * | 2006-05-01 | 2009-03-24 | Ethicon Endo-Surgery, Inc. | Biopsy cannula adjustable depth stop |
JP5258303B2 (ja) * | 2006-05-09 | 2013-08-07 | オカムラ有限会社 | 回転ピストン型内燃機関 |
DE102007004553A1 (de) * | 2007-01-30 | 2008-07-31 | Robert Bosch Gmbh | Kugelsitzventil mit verringertem Erosionsverhalten |
DE102007011047A1 (de) * | 2007-03-07 | 2008-09-11 | Robert Bosch Gmbh | Magnetventilinjektor |
HUE027556T2 (en) * | 2012-06-13 | 2016-10-28 | Delphi Int Operations Luxembourg Sarl | atomizer |
DE102015211918A1 (de) * | 2015-06-26 | 2016-12-29 | Robert Bosch Gmbh | Kraftstoffinjektor |
CN111648893A (zh) * | 2020-05-27 | 2020-09-11 | 天津职业技术师范大学(中国职业培训指导教师进修中心) | 一种电控喷油器控制阀用柱塞、快速响应电控喷油器控制阀及其控制方法 |
CN114165373A (zh) * | 2021-12-17 | 2022-03-11 | 中国船舶重工集团公司第七一一研究所 | 喷油器和共轨系统 |
US11815055B1 (en) * | 2022-12-01 | 2023-11-14 | Caterpillar Inc. | Multi-fuel injector and method |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4023223A1 (de) | 1990-07-21 | 1992-01-23 | Bosch Gmbh Robert | Kraftstoff-einspritzduese fuer brennkraftmaschinen |
GB9709678D0 (en) * | 1997-05-14 | 1997-07-02 | Lucas Ind Plc | Fuel injector |
DE19756986C1 (de) * | 1997-12-20 | 1999-06-02 | Daimler Chrysler Ag | Speichereinspritzsystem |
DE19827267A1 (de) | 1998-06-18 | 1999-12-23 | Bosch Gmbh Robert | Kraftstoff-Einspritzventil für Hochdruck-Einspritzung mit verbesserter Steuerung der Kraftstoffzufuhr |
DE59909449D1 (de) * | 1998-08-06 | 2004-06-17 | Siemens Ag | Kraftstoffeinspritzdüse |
GB9916464D0 (en) * | 1999-07-14 | 1999-09-15 | Lucas Ind Plc | Fuel injector |
AT3763U3 (de) * | 1999-08-05 | 2000-12-27 | Avl List Gmbh | Nockenbetätigte einspritzeinrichtung für eine brennkraftmaschine |
DE10221384A1 (de) * | 2002-05-14 | 2003-11-27 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
DE10229417A1 (de) * | 2002-06-29 | 2004-01-15 | Robert Bosch Gmbh | Speichereinspritzsystem mit Variodüse und Druckübersetzungseinrichtung |
DE102004028521A1 (de) * | 2004-06-11 | 2005-12-29 | Robert Bosch Gmbh | Kraftstoffinjektor mit mehrteiligem Einspritzventilglied und mit Druckverstärker |
-
2001
- 2001-05-08 DE DE10122241A patent/DE10122241A1/de not_active Withdrawn
-
2002
- 2002-03-22 JP JP2002587791A patent/JP4116448B2/ja not_active Expired - Fee Related
- 2002-03-22 US US10/332,375 patent/US7117842B2/en not_active Expired - Fee Related
- 2002-03-22 EP EP02726069A patent/EP1387939B1/de not_active Expired - Lifetime
- 2002-03-22 DE DE50211554T patent/DE50211554D1/de not_active Expired - Lifetime
- 2002-03-22 WO PCT/DE2002/001036 patent/WO2002090754A1/de active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO02090754A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP1387939B1 (de) | 2008-01-16 |
US7117842B2 (en) | 2006-10-10 |
DE10122241A1 (de) | 2002-12-05 |
DE50211554D1 (de) | 2008-03-06 |
US20050199753A1 (en) | 2005-09-15 |
JP4116448B2 (ja) | 2008-07-09 |
WO2002090754A1 (de) | 2002-11-14 |
JP2004519597A (ja) | 2004-07-02 |
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