EP2185807A1 - Steuerventil für einen kraftstoffinjektor - Google Patents
Steuerventil für einen kraftstoffinjektorInfo
- Publication number
- EP2185807A1 EP2185807A1 EP08787092A EP08787092A EP2185807A1 EP 2185807 A1 EP2185807 A1 EP 2185807A1 EP 08787092 A EP08787092 A EP 08787092A EP 08787092 A EP08787092 A EP 08787092A EP 2185807 A1 EP2185807 A1 EP 2185807A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- guide
- control
- valve sleeve
- region
- 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
- 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
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
-
- 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
- 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
-
- 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
- F02M63/008—Hollow valve members, e.g. members internally guided
-
- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
Definitions
- the invention relates to a control valve for a fuel injector with the features of the preamble of claim 1.
- a force-balanced control valve in which a valve sleeve is guided axially movably on a valve body.
- the valve sleeve defines an annular space to the outside, which is connected to a control chamber of a nozzle needle of the fuel injector via an outlet throttle.
- a closing spring By a closing spring, the valve sleeve is pressed against a valve seat formed on the valve body and thereby closes the annular space to the outside.
- the valve sleeve is moved by an electromagnetic actuator and thereby operated force-free, ie, that no force is exerted in the direction of movement of the valve sleeve by the fuel pressure in the annulus.
- valve sleeve is pulled away via an electromagnet of the electromagnetic actuator from the valve seat, which can be done very quickly by the lack of hydraulic force component and overcoming the relatively small closing force of the closing spring.
- the control chamber of the nozzle needle is connected to a low-pressure / return system and as a result depressurized.
- a disadvantage of such a technical solution is that over the system pressure, the dynamics of the fuel injector on the control valve remains constant and the control valve does not open automatically at massive excess of the maximum pressure in order to have a safety function.
- the problem may arise that there is an overpressure within the fuel injection valve or the high-pressure accumulator.
- the control valve according to the invention with the characterizing features of claim 1 has the advantage that the control valve opens faster. This is achieved by the formation of a dynamic pressure stage in the guide gap between the valve sleeve and guide pin.
- the dynamic pressure level is created by a targeted widening of the guide clearance on the valve sleeve by the valve sleeve in the region of the valve seat portion is stiff and relatively soft in the remaining area of the guide portion.
- the valve sleeve in the region of the valve seat portion has a higher rigidity than in the region of the guide portion, so that the guide clearance of the guide diameter of the valve sleeve widens relative to the valve seat diameter with increasing pressure in the annular space.
- the minimum, automatically forming dynamic pressure stage generates, for example, at an increase in pressure from 200 to 1800 bar, an opening force of, for example 8 - ION.
- this dynamic pressure stage causes the control valve to open automatically when the closing force of the closing spring is exceeded, thereby reducing the pressure in the uncritical low-pressure / return region.
- the force balanced function of the control valve is thereby maintained, in which the valve seat has the same diameter as the guide portion of the valve sleeve.
- the dynamic pressure level which forms relative to the diameter of the valve seat, arises because within the valve sleeve of the annulus is pressurized with system pressure of the common rail and the valve sleeve from the outside surrounded by the leak oil pressure, which corresponds to the pressure of the low pressure / return system, for example, 10 bar.
- valve sleeve in the form that in the region of the guide portion, the valve sleeve is made relatively soft compared to the region of the valve seat portion is suitably formed by the outer diameter Dl in the region of the guide portion is smaller than the outer diameter D2 in the region of the valve seat portion.
- FIG. 1 shows a partial section of a fuel injector with a first
- Figure 2 shows a partial section of a fuel injector with a second
- Figure 4 shows an enlarged partial section through the control valve of Figure 1 with a representation of the dynamic expansion of the valve sleeve and
- Figure 5 is an enlarged partial section through the control valve of the second
- a fuel injector for a common rail system of a diesel injection device is shown in partial section, with an injector housing 10, a base body 11, a nozzle needle 12, a control valve 13 and an actuating element 14.
- a high-pressure chamber 17 of a low-pressure chamber 37 In the formed between the injector housing 10 and body 11 annular high-pressure chamber 17 opens a high-pressure bore 18 which is connected to the unillustrated Commom Rail system.
- a control chamber 20 In the guide part 15 of the main body 11, a control chamber 20 is formed, to which the nozzle needle 12 is exposed to a control surface 21. From the high-pressure chamber 17, an inlet bore 22 with an inlet throttle 23 leads into the control chamber 20.
- the valve piece 16 has a guide pin 31 on which a valve sleeve 32 is arranged axially displaceable.
- the valve sleeve 32 is connected to a
- the valve sleeve 32 is guided axially displaceably with the guide cylinder 34 with a guide diameter d on the guide pin 31, wherein a guide gap 39 is present in the region of the guide diameter d between the guide pin 31 and the valve sleeve 32.
- the valve sleeve 32 has a control chamber remote end portion 45 and a control near the end portion 47.
- a sealing surface 43 is further formed, with which the valve sleeve 32 rests with a valve seat diameter on a valve seat 33 formed on the valve seat 33.
- the sealing surface 43 and the valve seat 33 can, as the embodiments in Figure 1, 3 and 4 or Figure 2 and
- valve member 16 and the valve sleeve 32 show, be formed at different locations on the valve member 16 and the valve sleeve 32.
- valve sleeve 32 Between guide pin 31 and valve sleeve 32, an annular space 36 is further formed.
- the valve sleeve 32 is further surrounded by the low pressure chamber 37, which is connected to a pressurized with leak oil pressure, not shown, low pressure / return system.
- a closing spring 38 acts on the valve sleeve 32, so that the valve sleeve 32 is held with the sealing surface 43 against the valve seat 33 in the closed position.
- a riser 25 with an outlet throttle 26 and, for example, two oblique holes 27 are arranged, which lead from the riser bore 25 into the annular space 36.
- the adjusting element 14, which is for example a magnetic actuator, comprises a magnetic coil 41, which is fixed in a magnetic core 42 and acts on the armature 35 of the valve sleeve 32.
- the electromagnetic actuator 14 forms together with the control valve 13, a servo-valve for controlling the
- the valve sleeve 32 has a guide portion 48 and a valve seat portion 49.
- the guide portion 48 is provided with an outer diameter Dl and the
- Valve seat portion 49 executed with an outer diameter D2, wherein Dl ⁇ D2.
- the annular space 36 is incorporated in the valve sleeve 32.
- the valve seat 33 is formed there on an actuating element-side section of the guide pin 31.
- the valve seat portion 49 with the outer diameter D2 and with the sealing surface 43 is located at the control chamber remote end portion 45 of the valve sleeve 32.
- the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the valve sleeve 32 at the control room remote end portion 45 through the plate-shaped armature 35 is stronger than in the underlying guide section 48.
- the annular space 36 is incorporated in the guide pin 31.
- the valve seat portion 33 is located at a control-room-side end portion of the guide pin 31.
- the valve seat portion 49 with the outer diameter D2 and with the sealing surface 43 is located at the control chamber near end portion 47 of the valve sleeve 32.
- the larger outer diameter D2 of the valve seat portion 49 is realized by the wall of the Valve sleeve 32 is thickened at the control chamber near end portion 47.
- the valve sleeve 32 on the valve seat portion 49 is relatively stiff and the rest of the guide portion 48 relative soft.
- This measure has the effect that the guide diameter d of the valve sleeve 32 in the region of the guide section 48 can widen relative to the valve seat diameter of the valve seat 33.
- the valve sleeve 32 remains rigid, so that there the guide diameter d does not widen or significantly less expands than in the region of the guide portion 48, so that there the guide diameter d corresponds substantially to the valve seat diameter.
- Compression 51 forms the guide diameter d of the valve sleeve 32.
- the rigidity of the valve sleeve 32 should be designed so that the pressure stage 51 acts in the opening direction of the valve seat 33 of the valve sleeve 32.
- the widening 50 arises due to the high pressure of, for example, 1800 bar of the common rail pressure, which acts via the riser bore 25, the oblique bore 27 and via the annular space 36 in the guide gap 39 from the inside to the valve sleeve 32. Because only the pressure in the low-pressure chamber 37 leak oil pressure of less than 10 bar acts on the outside of the valve sleeve 32, said expansion 50 is formed with the dynamically acting compression stage 51st
- valve sleeve 32 opens when actuated by the actuator 14 quickly and / or that at a rail pressure exceeding the valve sleeve 32 lifts off the valve seat 33 without activation by the actuator 14.
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 (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200710040248 DE102007040248A1 (de) | 2007-08-27 | 2007-08-27 | Steuerventil für einen Kraftstoffinjektor |
PCT/EP2008/060518 WO2009027215A1 (de) | 2007-08-27 | 2008-08-11 | Steuerventil für einen kraftstoffinjektor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2185807A1 true EP2185807A1 (de) | 2010-05-19 |
EP2185807B1 EP2185807B1 (de) | 2012-10-31 |
Family
ID=39951479
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08787092A Not-in-force EP2185807B1 (de) | 2007-08-27 | 2008-08-11 | Steuerventil für einen kraftstoffinjektor |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2185807B1 (de) |
DE (1) | DE102007040248A1 (de) |
WO (1) | WO2009027215A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009046563A1 (de) * | 2009-11-10 | 2011-05-12 | Robert Bosch Gmbh | Kraftstoffinjektor |
DE102013211855A1 (de) * | 2013-06-21 | 2014-12-24 | Robert Bosch Gmbh | Steuerventil für einen Kraftstoffinjektor |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES2277229T3 (es) | 2004-06-30 | 2007-07-01 | C.R.F. Societa Consortile Per Azioni | Servovalvula para controlar el inyector de combustible de un motor de combustion interna. |
EP1707797B1 (de) * | 2005-03-14 | 2007-08-22 | C.R.F. Società Consortile per Azioni | Verstellbares Dosierservoventil eines Einspritzventils |
DE102006027485A1 (de) | 2006-06-14 | 2007-12-20 | Robert Bosch Gmbh | Kraftstoffeinspritzventil mit Sicherheitssteuerventil |
-
2007
- 2007-08-27 DE DE200710040248 patent/DE102007040248A1/de not_active Withdrawn
-
2008
- 2008-08-11 WO PCT/EP2008/060518 patent/WO2009027215A1/de active Application Filing
- 2008-08-11 EP EP08787092A patent/EP2185807B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2009027215A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP2185807B1 (de) | 2012-10-31 |
DE102007040248A1 (de) | 2009-03-05 |
WO2009027215A1 (de) | 2009-03-05 |
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