EP2459866A1 - Kraftstoffeinspritzventil für brennkraftmaschinen - Google Patents
Kraftstoffeinspritzventil für brennkraftmaschinenInfo
- Publication number
- EP2459866A1 EP2459866A1 EP10720789A EP10720789A EP2459866A1 EP 2459866 A1 EP2459866 A1 EP 2459866A1 EP 10720789 A EP10720789 A EP 10720789A EP 10720789 A EP10720789 A EP 10720789A EP 2459866 A1 EP2459866 A1 EP 2459866A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- collar
- valve
- pressure chamber
- fuel injection
- valve needle
- 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
- 238000002347 injection Methods 0.000 title claims abstract description 46
- 239000007924 injection Substances 0.000 title claims abstract description 46
- 239000000446 fuel Substances 0.000 title claims abstract description 45
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 16
- 238000007789 sealing Methods 0.000 claims abstract description 5
- 230000003993 interaction Effects 0.000 claims abstract 2
- 238000004519 manufacturing process Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 4
- 238000000926 separation method Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000000889 atomisation Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
- F02M61/20—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
-
- 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
Definitions
- the invention relates to a fuel injection valve for internal combustion engines, as it is preferably used for the injection of fuel directly into a combustion chamber of a high-speed, self-igniting internal combustion engine.
- Fuel injection valves which are used for injecting fuel under high pressure directly into a combustion chamber of an internal combustion engine, are operated at ever higher pressure. Partial injection pressures of more than 2000 bar are already achieved today.
- the fuel pressure is generated by a high-pressure pump, which conveys the compressed fuel into a high-pressure accumulator, the so-called rail. From this rail usually several injectors are fed, which have a movable valve needle, controlled by the injection openings are opened and controlled by an electric control valve, so that fuel is injected at the desired time and in the desired dosage in the combustion chamber. Due to the high fuel pressure that surrounds the valve needle, acting on the valve needle large hydraulic forces, which are increasingly difficult to control.
- valve needle closes quickly.
- this is achieved by providing a low-pressure stage, so that the hydraulic pressure in a control chamber, which acts on the valve needle and exerts the closing force on the valve needle is greater than the forces acting in the opening direction on the valve needle.
- This excess of hydraulic closing force allows the valve needle to close quickly and thus achieve a clean injection.
- increasing pressure however, the problem arises that it leads to increased leakage to the low-pressure space, which must be compensated by additional pump power and ultimately leads to a fuel consumption of the vehicle.
- valve needle if you simply leave the low-pressure stage, then the valve needle, if it closes the control valve at the end of the injection by the high fuel pressure builds up again in the control room, largely pressure-balanced.
- the closing force could be applied in this case only in other ways, for example by a spring.
- the spring since the injector must open even at low pressures, the spring must not be too strong, so that only a small force is exerted on the valve needle, which makes a fast closing impossible by the spring force.
- a fuel injection valve is known from DE 10 2007 032 741 Al, which has a throttle collar.
- the throttle collar is disposed near the valve seat, from which the injection openings go out, so that between the collar and the wall of the pressure chamber in which the valve needle is arranged, a throttle gap is formed.
- the object of the present invention is thus to provide a fuel injection valve in which the throttle gap is formed by a collar on the valve needle, which is easy to manufacture and is insensitive to tolerance deviations.
- the fuel injection valve according to the invention achieves the stated object by the valve needle has a collar, which has an inlet-side surface and a discharge-side surface, wherein the inlet-side surface is rounded or conical.
- adjoining the inlet-side surface is a cylindrical section, between which and the wall of the pressure chamber, the smallest flow cross-section is formed, which is formed either only over part of the waist circumference or over the entire circumference of the
- the cylindrical portion can be easily grinded by material removal on the outside to an exact diameter or form corresponding passages through polished so that the size of the desired gap choke is easily adjustable.
- the outlet-side surface of the collar is formed by a conical surface or a rounded, which adjoins directly to the cylindrical portion. The edge formed between the cylindrical section and the outlet-side surface ensures that a flow-related tear-off edge is formed, so that the
- a ratio of the gap of the gap throttle to the hydraulic diameter of> 2 and ⁇ 20 is optimal, since so a high temperature independence is achieved and the gap choke is still in an order of magnitude, which is associated with manufacturing technology reasonable effort.
- FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention, wherein only the combustion chamber side part of the injection valve is shown, which otherwise is well known from the prior art,
- FIG. 2 shows an enlarged section of FIG. 1 in the region of the collar of a first exemplary embodiment
- Figure 3 shows the same detail as FIG. 2 of a second embodiment
- the fuel injection valve 1 shows a fuel injection valve according to the invention is shown in longitudinal section, wherein only the part of the injection valve is shown, which faces the combustion chamber in Einbaula- ge in an internal combustion engine.
- the fuel injection valve 1 has a valve body 2, in which a pressure chamber 5 is formed in the form of a bore.
- the pressure chamber 5 is delimited on the combustion chamber side by a substantially conical valve seat 9, from which several injection openings 7 originate.
- a longitudinally displaceable valve needle 3 is arranged, which is rotationally symmetrical with respect to the longitudinal axis of the pressure chamber 5.
- valve needle 3 is guided in a guide section 103 in the pressure chamber 5, wherein the fuel flow past the guide section 103 is ensured by a plurality of bevels 14, which are formed on the outside of the guide section 103.
- the valve needle 3 has at its valve seat facing the end of a valve sealing surface 11, with the valve needle 3 for
- Opening and closing of the injection openings 7 cooperates with the valve seat 9.
- a collar 17 is formed on the valve needle 3, which has an edge 18 on its outer side. Between the edge 18 and the wall of the pressure chamber 5, a gap throttle 15 is formed, which represents the smallest flow cross section with respect to the fuel flow through the pressure chamber 5 to the injection openings 7.
- the gap throttle 15 is designed here as an annular gap throttle having an inner diameter Dj and an outer diameter D a .
- the intended for injection fuel is compressed by a high-pressure pump, not shown in the drawing and fed to a high-pressure accumulator, also not shown in the drawing, with which the injection valve is connected. From the high-pressure accumulator, the compressed fuel in the
- Pressure chamber 5 passed, where it flows through the pressure chamber 5 and, accordingly, through the gap throttle 15 and the bevels 14 in the direction of the valve seat 9.
- the valve needle 3 closes the Einspritzöff- openings 7. If the valve needle 3 is moved away from the valve seat 9, which by means of a also not shown in the drawing - but well-known from the prior art - control valve is performed, the injection ports 7 are connected to the pressure chamber 5, and fuel is injected through the injection ports 7 into a combustion chamber of the internal combustion engine.
- a lower fuel pressure must act on the valve sealing surface 11 than on the opposite end face of the valve needle 3, which is acted upon by the pressure in the control chamber.
- the collar 17 serves as a result of the gap throttle 15 when the valve needle 3 has lifted off the valve seat 9 so that a pressure difference occurs between the areas before and after the collar 17 in the pressure chamber 5. This pressure difference is about 50 to 100 bar at an injection pressure of 1600 to 2000 bar.
- the shape of the collar 17 with the edge 18 causes the throttling at the gap throttle 15 to be largely independent of the Reynolds number. The following conditions must be fulfilled for this.
- the effect of a gap choke is determined by two variables: On the one hand by the hydraulically effective diameter D ⁇ yd and on the other by the length of the gap choke L
- the hydraulically effective diameter DHyd is calculated from the quotient of flow-through cross-section and flow-through boundary length, so that in general:
- the gap throttle 15 is formed by an annular gap, as shown in Figure 1, the flow-through cross section and the boundary length is given by the diameter D a and Dj, ie by the outer diameter of the collar 17 and by the diameter of the pressure chamber 5, as shown in FIG 1. Substituting the corresponding formulas in the above equation, it follows
- the length L of the edge 18 is defined by the length of the gap throttle 15, in which the flow-through cross-section is smaller than 1.2 times the minimum flow cross-section.
- ⁇ 20 the independence of the Reynolds number and thus of the temperature of the fuel is then not completely fulfilled, but sufficient for the purposes of the injection valve. In order to meet the manufacturing tolerances, it is sufficient if the
- Ratio L to D Hyd > 2 is maintained. From a physical point of view, a ratio L to D Hyc
- Such a gap choke is also referred to as hydraulically short.
- Figure 2 shows an enlarged view of the collar 17 and the valve needle 3 of a first embodiment, wherein this area is marked in Fig. 1 with Il.
- the collar 17 can be divided into three sections: an inlet-side surface 20, a cylindrical portion 22 and an outlet-side surface 24.
- the inlet-side surface 20 is rounded and in the area in which it merges into the cylindrical portion 22 with a radius R rounded.
- the radius R is advantageously about 0.2 to 0.3 mm.
- the cylindrical portion 22 is substantially the length L of the throttle gap again, but - as mentioned above - the length L of the gap choke is defined as the length in which the flow-through cross-section is smaller than 1.2 times the minimum flow cross-section , This is indicated in Figure 2, characterized in that the length L is slightly larger than the thickness of the cylindrical
- the outlet-side surface 24 is formed by a first conical surface 124, which adjoins directly to the cylindrical portion 22, and by a second conical surface 224, which forms the end of the collar 17. Due to the shape of the first conical surface 124, an edge 26 is formed at the transition from the cylindrical surface 22, which ensures that the flow of the fuel through the gap throttle 15 always at the same point, namely at the edge 26, detaches. As a result, the throttle effect of the gap choke 15 is robust against influences such as surface condition and fuel properties. In this case, an angle difference between the first conical surface 124 and the cylindrical surface 22 of 20 ° to 30 ° is advantageous.
- FIG. 3 shows a further exemplary embodiment of the collar 17.
- the inlet-side surface 20 ' is formed here as a conical surface, which forms an angle ⁇ with the longitudinal axis of the valve needle 3. This angle ⁇ is preferably in the range of 60 ° to 80 °.
- the outlet-side surface 24 ' is also designed here as a simple conical surface.
- the cone of the inlet-side surface 20 ' causes similar advantages as the rounded inlet-side surface 20 in Fig. 2, in particular, such a surface is easier to produce than an exactly perpendicular to the valve needle-facing inlet-side surface.
- Figure 4 shows a further embodiment of the gap choke 15 and the collar 17 according to the invention in a cross section.
- the gap throttle 15 is formed only over partial regions of the circumference, which are formed by lateral polished sections 28, so that the collar 17 has a substantially triangular shape in cross-section.
- the gap between the collar 28 and the wall of the pressure chamber 5 is so small that practically a seal is achieved.
- the polished sections 28 are exaggeratedly large.
- the length K of these bevels 25 of course to the length L of the collar 17 is directed to obtain the desired hydraulic diameter. It may be provided instead of three bevels 28, as shown in Fig. 4, a larger or smaller number of bevels 28, for example 1, 2, 4, 5 or 6.
- the bevels 28 it is also possible to provide other recesses on the collar 17, which form the gap throttle 15, for example grooves.
- the chosen dimensions achieve a sufficient compromise between achievable manufacturing tolerances and the effect of a gap choke, which is formed by a sharp edge.
- An absolute independence of the Reynolds number could only be achieved if the edge 18 of the collar 17 would be ideally sharp-edged, which, however, manufacturing technology is not represented.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009028122 | 2009-07-30 | ||
DE102009029562A DE102009029562A1 (de) | 2009-07-30 | 2009-09-18 | Kraftstoffeinspritzventil für Brennkraftmaschinen |
PCT/EP2010/057634 WO2011012355A1 (de) | 2009-07-30 | 2010-06-01 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2459866A1 true EP2459866A1 (de) | 2012-06-06 |
EP2459866B1 EP2459866B1 (de) | 2014-12-17 |
Family
ID=43402338
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10720789.6A Active EP2459866B1 (de) | 2009-07-30 | 2010-06-01 | Kraftstoffeinspritzventil für brennkraftmaschinen |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2459866B1 (de) |
CN (1) | CN102472222B (de) |
DE (1) | DE102009029562A1 (de) |
WO (1) | WO2011012355A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2568157A1 (de) | 2011-09-08 | 2013-03-13 | Delphi Technologies Holding S.à.r.l. | Einspritzdüse |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT288784B (de) * | 1966-10-20 | 1971-03-25 | Bosch Gmbh Robert | Elektromagnetisch betätigtes Kraftstoff-Einspritzventil für Brennkraftmaschinen |
JP3136829B2 (ja) * | 1993-05-06 | 2001-02-19 | 株式会社デンソー | 燃料噴射弁 |
DE10055651A1 (de) * | 2000-11-10 | 2002-05-23 | Bosch Gmbh Robert | Druckgesteuerter Injektor mit optimierten Einspritzverlauf über den Hubweg |
DE102007032741A1 (de) | 2007-07-13 | 2009-01-15 | Robert Bosch Gmbh | Kraftstoffeinspritzventil für Brennkraftmaschinen |
US7690588B2 (en) * | 2007-07-31 | 2010-04-06 | Caterpillar Inc. | Fuel injector nozzle with flow restricting device |
DE102009000206A1 (de) * | 2009-01-14 | 2010-07-15 | Robert Bosch Gmbh | Kraftstoffinjektor für Brennkraftmaschinen |
EP2216542A1 (de) * | 2009-02-06 | 2010-08-11 | Continental Automotive GmbH | Ventilanordnung für ein Einspritzventil und Einspritzventil |
-
2009
- 2009-09-18 DE DE102009029562A patent/DE102009029562A1/de not_active Withdrawn
-
2010
- 2010-06-01 WO PCT/EP2010/057634 patent/WO2011012355A1/de active Application Filing
- 2010-06-01 EP EP10720789.6A patent/EP2459866B1/de active Active
- 2010-06-01 CN CN201080033643.6A patent/CN102472222B/zh active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2011012355A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN102472222B (zh) | 2015-07-22 |
WO2011012355A1 (de) | 2011-02-03 |
EP2459866B1 (de) | 2014-12-17 |
DE102009029562A1 (de) | 2011-02-03 |
CN102472222A (zh) | 2012-05-23 |
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