EP3080435A1 - Nozzle head and fluid injection valve - Google Patents
Nozzle head and fluid injection valveInfo
- Publication number
- EP3080435A1 EP3080435A1 EP14814794.5A EP14814794A EP3080435A1 EP 3080435 A1 EP3080435 A1 EP 3080435A1 EP 14814794 A EP14814794 A EP 14814794A EP 3080435 A1 EP3080435 A1 EP 3080435A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- nozzle
- fuel
- nozzle hole
- nozzle head
- 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 52
- 239000007924 injection Substances 0.000 title claims abstract description 52
- 239000012530 fluid Substances 0.000 title claims abstract description 29
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 239000000446 fuel Substances 0.000 description 134
- 238000002485 combustion reaction Methods 0.000 description 49
- 239000012080 ambient air Substances 0.000 description 16
- 238000000889 atomisation Methods 0.000 description 12
- 239000003570 air Substances 0.000 description 11
- 239000000203 mixture Substances 0.000 description 11
- 230000008901 benefit Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 6
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000008021 deposition Effects 0.000 description 4
- 239000004071 soot Substances 0.000 description 4
- 238000002156 mixing Methods 0.000 description 3
- 239000002245 particle Substances 0.000 description 3
- 238000002360 preparation method Methods 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000010790 dilution Methods 0.000 description 2
- 239000012895 dilution Substances 0.000 description 2
- 239000008240 homogeneous mixture Substances 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 240000006829 Ficus sundaica Species 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 229940090046 jet injector Drugs 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000009528 severe injury 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
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1853—Orifice plates
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/06—Fuel-injection apparatus having means for preventing coking, e.g. of fuel injector discharge orifices or valve needles
Definitions
- Nozzle head and fluid injection valve The invention relates to a nozzle head and a
- Fluid injection valve in particular a fuel injection valve.
- Fuel injection valves are known with a nozzle head for atomizing a fluid. Usually, such
- Fuel injection valves used for atomizing fuel in a combustion chamber of an internal combustion engine are used for atomizing fuel in a combustion chamber of an internal combustion engine.
- Dir ⁇ injection of the fuel into the combustion chamber at a as Ot tomotor trained internal combustion engine the fuel, among other things, with the aid of the nozzle head, very finely atomize to produce a complete combustion as possible in A gasoline engine requires a fine mixture of air present in the combustion chamber and the injected fuel.
- Another advantage of direct injection is an improvement in the elasticity of the internal combustion engine with regard to its response in dynamic operation, since the fuel passes much faster into the combustion chamber than in the intake manifold, in which the fuel together with the combustion air flowing through a gas inlet valve combustion air into the combustion chamber arrives.
- the problem is that the required homogeneous mixture must be prepared within a short period of time to achieve the stated advantages of direct injection. Because the fuel is quickly introduced into the combustion chamber, evaporation and mixing of the fuel with the combustion air have little time available.
- Fuel injection valve and its jet preparation to a special role The fuel is to be introduced into the cylinder with the help of a particularly fine atomization, i. a droplet size of the fuel should be made as small as possible to allow rapid processing - i. in a very short period of time a homogeneous mixture - can be achieved.
- the fuel should not get to the cylinder walls of the combustion chamber, since there is the possibility of a so-called oil dilution.
- the oil dilution since it causes a change in a lubricant composition, can cause severe damage to the engine due to insufficient
- Viscosity behavior of the diluted lubricating oil A piston ⁇ ground and / or gas inlet valves should not be wetted by the fuel, as it can not adequately evaporate from there, the fuel.
- Another problem is deposition of the fuel at the fuel injection valve. After several hours of operation of the internal combustion engine, the fuel injection valve has a solid and sooty deposit layer. In this deposition layer fuel can accumulate subsequent injection cycles. In later combustion cycles, this fuel may escape as fuel vapor and result in undesirable soot combustion. This leads to an unfavorably large, possibly impermissible number of soot particles in the exhaust gas of the internal combustion engine.
- a nozzle head for a reduced deposit or deposit free power ⁇ injection valve It is an object of the present invention to provide a nozzle head for a reduced deposit or deposit free power ⁇ injection valve. This object is achieved by a nozzle head according to claim 1. Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the subclaims. In one aspect, a nozzle head for a
- the nozzle head is seen before ⁇ to atomize the fluid.
- the fluid is preferably a fuel for an internal combustion ⁇ machine, in particular gasoline.
- the nozzle head has a longitudinal axis.
- a flow-through valve body is specified for a fluid injection valve.
- a supply device for supplying the fluid is formed.
- a remote from the first end second end of the valve body of the nozzle head for atomizing the fluid is arranged.
- the nozzle head and the valve body have a common longitudinal axis.
- the Nozzle head may be formed integrally with a main body of the valve body.
- the nozzle head may be a separate workpiece which is fixed to the main body of the valve body.
- a fluid injection valve - in particular a fuel injection valve - is specified with the nozzle head or with the valve body.
- the fuel injection valve is in particular provided to inject fuel directly into a combustion chamber of the internal combustion engine.
- the nozzle head has a nozzle hole disc.
- the nozzle ⁇ hole disc has an end face and an inner surface opposite the end face.
- the end face facing away from the first end of the valve body ⁇ formed and the inner surface is formed facing the first end of the valve ⁇ body.
- a first axial distance extending in the direction of the longitudinal axis is formed between the inner surface and the end surface.
- the nozzle perforated disk has at least one nozzle hole channel which completely penetrates the nozzle perforated disk in the direction of the longitudinal axis.
- An exit surface is formed on the first channel end assigned to the nozzle-hole channel, and an exit surface is formed on a second channel end of the nozzle-hole channel which is remote from the first channel end.
- the A ⁇ exit surface is arranged on the inner surface of the nozzle orifice plate to ⁇ .
- a nozzle hole projection of the nozzle hole channel which is positioned in particular at the first axial distance from the inlet surface, has a channel wall.
- the duct wall is formed over a circumference of the nozzle hole projection. In other words, the channel wall of the nozzle hole projection defines a portion of the nozzle hole channel.
- the channel wall runs completely around a channel axis of the nozzle hole channel.
- the channel wall has a wall height extending from the end face in the direction of the longitudinal axis, in particular away from the inner face, in such a way that the second channel end corresponds to a channel wall end of the channel wall which is remote from the end face.
- the distance of the exit surface corresponds to a sum of the first axial distance and the wall height. This has the consequence that the exit surface of the nozzle hole channel, which at the second
- Channel end is formed, spaced from the end face is configured on the nozzle hole disc.
- the second channel end is offset in particular in relation to the end face in the direction away from the inner surface.
- the exit surface is not axially spaced from the end face in the direction of the longitudinal axis, an ambient air present there is sucked in over a circumference of the exit face in the region of the end face. That is, the ambient air present in the area of the fuel jet is emitted by the
- Fuel jet entrained This effect, the entrainment or entrainment of the air in the region of a fluid jet, is known and is used in particular in water jet pumps for generating large volume flows.
- a valve needle is arranged in the valve body.
- the valve needle is axially movable relative to the valve body, such that a closing element of the valve needle in a closed position of the valve needle against a valve seat of the valve body to prevent fluid flow through the nozzle hole channels and the valve needle by means of an actuator unit of
- Fluid injection valve is displaced away from the closed position to release fluid flow through the nozzle hole channels.
- the inner surface of the - in particular one-piece - nozzle hole disc on the valve seat is for comparatively large fluid pressures - e.g. from 100 bar or more, preferably from 200 bar or more, in particular in a range between 250 bar and 500 bar, the limits being included - usable.
- the channel wall is formed of a hollow truncated cone.
- the advantage of this embodiment is that the ambient air present in the region of the channel wall has an on-flow direction, which is inclined to the fuel spray emerging from the exit surface.
- the order ⁇ bient improves the fuel spray can be supplied.
- the flow direction of the guided over the hollow cone ⁇ truncated duct wall ambient air crosses the direction of flow of the fuel jet, so that a mixing of the fuel jet and the ambient air is already brought about by the flow directions.
- the improved feedability can be seen in comparison to a hollow-cylinder-like duct wall.
- the ambient air has the same flow direction as the
- the exit surface is smaller than the entry surface.
- the nozzle perforated disc has a plurality of nozzle-hole channels, that is, at least one further nozzle-hole channel is formed penetrating the nozzle perforated disk.
- the nozzle hole channels are usually arranged in a certain, generally uniform, radius of a nozzle hole center, in particular in plan view along the longitudinal axis wherein the nozzle hole center in one embodiment lies on the longitudinal axis.
- Fuel jet is a first range pressure which is less than a second range pressure in a region of the environment further away from the fuel spray.
- An indoor area formed third range pressure is significantly reduced compared to the first range pressure and the second range pressure.
- the wall height can be determined as a function of a free radial distance. This free radial distance is a radially formed between the nozzle hole channel and the other nozzle hole channel distance.
- a particularly advantageous wall height can be described as follows, depending on the radial distance:
- h is the wall height and D is the free radial distance.
- a sufficiently large flow channel is configured over which ambient air in the inner region is feasible, so that the third range pressure in the interior is so large that a return flow of fuel vapor and / or fuel droplets for indoor ⁇ rich is particularly well prevented.
- the wall height is according to
- the nozzle hole projection may have an outer peripheral surface whose contour is configured in a longitudinal section of a continuously differentiable function according to. That's the advantage created that a tearing off of flow threads of the flowing over the channel wall, entrained by the fuel jet ambient air is avoided.
- the outer circumferential surface is ramp-shaped.
- the nozzle hole projection at least in its region adjacent to the end face, preferably has an outer contour which has the shape of a continuously differentiable function in longitudinal section and / which is in the form of a ramp - ie in particular in the form of a ramp function.
- the nozzle hole channel has one of the A ⁇ tread surface adjoining first channel region, the cross-sectional area smaller than the cross-sectional area of the exit surface adjacent second channel region of the due-senlochkanals. Between the first and the second channel region of the nozzle hole channel has a step in a development.
- FIG. 1 is a perspective view schematically a nozzle hole disc of a fuel injection valve according to the prior art
- 2 is a perspective view of the nozzle hole disk according to FIG. 1 with fuel jets during an injection process
- FIG. 3 is a perspective view of the nozzle hole disk with a deposition layer
- Fig. 4 in a side view of the nozzle hole disc gem. 1, with a fuel jet propagation of two juxtaposed nozzle holes, as well as in the area of the fuel jets setting range pressures without backflow,
- Fig. 5 in a side view of the nozzle hole disc gem. 1, with a fuel jet propagation of two juxtaposed nozzle holes, as well as adjusting in the area of the fuel jets range pressures with backflow of fuel vapors,
- FIG. 7 is a perspective view schematically a nozzle head of a fuel injection valve according to the invention.
- FIG. 8 is a detail of a side view of the nozzle ⁇ hole disc of the fuel injection valve according to the invention, with a fuel jet propagation, and adjusting in the range of fuel jet range pressures,
- FIG. 10 in a section of the nozzle hole disc of he ⁇ inventive fuel injection valve in a second variant.
- the nozzle hole disc of a fuel valve of the prior art is formed as shown in FIG. 1, wherein the fuel ⁇ injection valve as a so-called multi-stream injector
- Multi-jet injector is formed, that is, the nozzle orifice plate 10 has a plurality of nozzle hole channels 12, wherein the nozzle hole channel 12, the nozzle hole disc 10 is completely formed by urgent ⁇ .
- the fuel injection valve comprises a valve body (not shown) with a longitudinal axis 14, wherein at a first end of the valve body, a supply device not shown for supplying a fluid, usually fuel for internal combustion engines is formed. At a remote from the first end second end of the valve body of the nozzle head 11 is arranged with the nozzle hole disc 10 for atomizing the fluid.
- the nozzle hole disc 10 has an end face 16 remote from the first end.
- the nozzle-hole channel 12 has an entry surface 22 at a first channel end 18 (see FIGS. 9 and 10) and an exit surface 24 at a second channel end 20 remote from the first channel end 18, wherein the entry surface 22 is formed on an inner surface facing away from the end surface 16 26 of the nozzle hole disc 10 is formed. Between the inner surface 26 and the end face 16 there is a first axial distance Wl extending in the direction of the longitudinal axis 14.
- the nozzle hole disc 10 is received in the nozzle head 11 of the fuel ⁇ fuel injection valve.
- the nozzle head 11 is positioned at the second end of the fuel injection valve, which is arranged in a combustion chamber, not shown, of an internal combustion engine, not shown.
- this type of internal combustion engine works based on a so-called spark ignition, ie, a fuel-air mixture present in the combustion chamber with the aid of mixture formation is ignited with the aid of a spark plug.
- spark ignition ie, a fuel-air mixture present in the combustion chamber with the aid of mixture formation is ignited with the aid of a spark plug.
- This form of ignition requires a homogeneous fuel-air mixture, so that complete combustion of the fuel-air mixture can be brought about. Since this is required in a very short time within an injection cycle, there is a need for a fine atomization by means of the fuel injection valve.
- Air-fuel mixture continues.
- insufficient combustion leads to a so-called soot formation, which can be avoided by means of a fine atomization.
- the fine atomization is achievable with a plurality of nozzle hole channels 12 formed on the nozzle disk 10. Basically, a fineness of the atomization depends on
- Diameter of the nozzle hole channel 12 and the fuel pressure The smaller the diameter of the nozzle hole channel 12 and the
- the nozzle hole channels 12 are introduced into the nozzle perforated disk 10 in a completely penetrating manner through the nozzle perforated disk 10.
- the inlet surfaces 22 of the nozzle hole channels 12 are released by means of a nozzle needle, not shown, so that the fuel located in a valve body of the fuel injection valve flows through the outlet surfaces 24 under a corresponding Einspitztik the valve body.
- Fig. 2 shows schematically from the exit surfaces 24 escaping fuel in the form of fuel jets 28 during an injection process. Laws of fluid mechanics ent ⁇ speaking the fuel from a nozzle hole flows from channel 12 to form a fuel cone.
- FIG. 4 shows a side view of the nozzle perforated disk 10 according to the prior art.
- ⁇ be characterized in the following as the field pressures.
- ambient air is drawn in an exit region of the fuel.
- the ambient air located in the region of the fuel jet 28 is entrained by the fuel jet 28.
- a lower first range pressure pl is established than in a region remote from the exit surface 24 in which there is a second range pressure p2, s. 4 and 5.
- a third range pressure p3 is formed which is greatly reduced from the first range pressure pl and the second range pressure p2, and represents an extreme negative pressure.
- Fuel vapors are caused.
- a return flow direction is indicated by means of the return arrow 36 in the inner region 32 between the fuel jets 28 of FIG.
- the fuel vapors form due to high combustion chamber temperatures during the injection process. In other words, that is Fuel during the injection process in a liquid state of matter and a vapor state.
- the negative pressure p3 which forms in the inner region 32 between the fuel jets 28, there is a return flow of a fuel vapor-fuel droplet mixture. This is deposited on the end face 16.
- the fuel vapors flowing back due to turbulence may be mixed with fuel droplets 34, s. Fig. 6. These fuel droplets 34 are then in the direction of
- End face 16 of the nozzle perforated disk 10 accelerates and deposits in the region of the exit surfaces 24 on the end face 16.
- the fuel particles located in the interior region 32 at least partially have a direction of flow reversal.
- This flow direction reversal is reduced by increasing an exit velocity of the fuel from the exit surfaces 24, which can be realized with the aid of an increase of the Einspitz horres, since ⁇ with increasing exit speed of the third range pressure p3 is no longer sufficient to accelerate the fuel droplets in the direction of the end surface 16 ,
- the nozzle perforated disk 10 of the fuel injection valve according to the invention is designed as shown in FIG.
- the nozzle hole channel 12 has a nozzle hole projection 25 with a channel wall 40, by means of which the exit surface 24 is spaced away from the end face 16 in the direction of the inner surface 26.
- the nozzle hole projection 25 is presently positioned at a first axial distance Wl from the entry surface 22.
- the channel wall 40 is formed over a circumference of the nozzle ⁇ hole channel 12, which is a Having starting from the end face 16 in the direction of the longitudinal axis 14 extending wall height h.
- the second channel end 20 corresponds to one of the
- the channel wall 40 of the nozzle hole 25 extends from a plane common to the end face 16 to the nozzle hole channel 12, such that its axial extent is formed starting from the face 16 in the direction of the fuel jet 28.
- the exemplary embodiment of the fuel injection valve according to the invention has a channel wall 40, which is formed in the manner of a hollow cone.
- the hollow truncated cone-shaped channel wall 40 has a conically tapered and in the region of the nozzle hole projection 25 completely laterally around the nozzle hole channel 12 circumferential inner peripheral surface, so that the outlet surface 24 is smaller than an upstream at a distance h from the exit surface 24 posi ⁇ tioned channel cross-sectional area of the nozzle hole 25, which has the diameter d shown in the figures.
- the channel wall 40 is formed hollow cylinder-shaped.
- the wall height h is determined such that ambient air can be supplied to the inner region 32 in the quantity entrained when the fuel flows out of the outlet surface 24 in accordance with the principle of the water jet pump.
- a free radial distance D is formed between a pair of oppositely disposed nozzle hole channels 12, 13, ie between a nozzle hole channel 12 and a further nozzle hole channel 13, a free radial distance D is formed.
- the free radial distance D is the distance between the nozzle hole channel 12 and the further nozzle hole channel 13, which is determined in a longitudinal axis 14 along the axial distance from the end face 16 and the wall height h corresponds.
- the free radial distance D present is to be determined along a diameter of the nozzle hole disc 10. This can be assumed, since usually the nozzle hole disc 10 has a circular circumference. However, if the nozzle hole disc 10 has no circular circumference and / or an arrangement of the nozzle hole channels are not positioned symmetrically about a center of the nozzle hole disc 10, the free radial distance D between two opposite nozzle hole channels 12 is to be determined.
- the wall height h can be determined as a function of the radial distance D: h> 1/4 ⁇ D.
- a winding-like flow channel 41 is formed between each two adjacent nozzle hole channels 12, a winding-like flow channel 41 is formed. So that this flow channel 41 is designed for a sufficient air supply into the inner region 32, a channel wall thickness 42 of the channel wall 40 in the
- the wall height h is greater than a quarter of the radial distance D to choose. For example, if the radial distance D between the nozzle hole channels 12 6 mm, results in a wall height h of 1.5 mm. So now a sufficiently large
- Flow channel 41 can be created, the wall height h to determine about 2 mm.
- the nozzle hole projection 25 has an outer circumferential surface 44.
- this outer circumferential surface 44 has a contour 45 that is ramp-shaped in a longitudinal section. According to FIG. 10, this contour 45 is rounded ramp-like, ie formed in the shape of a curved, continuously differentiable function.
- the channel diameter dl in a face formed by the entrance surface 22 first passage ⁇ area is smaller than a second channel diameter d2 of the exit surface 24 facing formed second Kanalbe ⁇ realm of nozzle hole channel 12, so that the first channel region has a smaller cross-sectional area than the second Kanalbe ⁇ rich.
- the nozzle hole channel 12 has a step.
- the second channel region extends in the axial direction from the nozzle hole projection 25 beyond the end face 16 in the direction of the inner surface 26.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Nozzles For Spraying Of Liquid Fuel (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013225948.4A DE102013225948A1 (en) | 2013-12-13 | 2013-12-13 | Nozzle head and fluid injection valve |
PCT/EP2014/076912 WO2015086536A1 (en) | 2013-12-13 | 2014-12-08 | Nozzle head and fluid injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3080435A1 true EP3080435A1 (en) | 2016-10-19 |
EP3080435B1 EP3080435B1 (en) | 2019-10-02 |
Family
ID=52117870
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14814794.5A Active EP3080435B1 (en) | 2013-12-13 | 2014-12-08 | Nozzle head and fluid injection valve |
Country Status (6)
Country | Link |
---|---|
US (1) | US10975822B2 (en) |
EP (1) | EP3080435B1 (en) |
KR (1) | KR101908826B1 (en) |
CN (1) | CN206190444U (en) |
DE (1) | DE102013225948A1 (en) |
WO (1) | WO2015086536A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013225948A1 (en) | 2013-12-13 | 2015-06-18 | Continental Automotive Gmbh | Nozzle head and fluid injection valve |
WO2020148821A1 (en) * | 2019-01-16 | 2020-07-23 | 三菱電機株式会社 | Fuel injection device |
US20200224571A1 (en) * | 2019-01-16 | 2020-07-16 | Caterpillar Inc. | Reductant nozzle |
JP7439399B2 (en) * | 2019-06-20 | 2024-02-28 | 株式会社デンソー | fuel injection valve |
DE102019217940A1 (en) * | 2019-11-21 | 2021-05-27 | Continental Reifen Deutschland Gmbh | Commercial vehicle tires |
Family Cites Families (25)
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US1444263A (en) * | 1921-09-15 | 1923-02-06 | Joseph A Mustee | Gas burner |
DE3230671A1 (en) | 1982-08-18 | 1984-02-23 | Robert Bosch Gmbh, 7000 Stuttgart | INJECTION VALVE |
DE3801778A1 (en) * | 1988-01-22 | 1989-07-27 | Vdo Schindling | Orifice plate for an electromagnetically actuated fuel injection valve and a method for its production |
US5054691A (en) | 1989-11-03 | 1991-10-08 | Industrial Technology Research Institute | Fuel oil injector with a floating ball as its valve unit |
AT402164B (en) * | 1992-11-04 | 1997-02-25 | Ideal Standard | SHOWER HEAD |
DE4446241A1 (en) | 1994-12-23 | 1996-06-27 | Bosch Gmbh Robert | Fuel injector |
JPH08232813A (en) * | 1995-02-27 | 1996-09-10 | Aisan Ind Co Ltd | Injector |
DE19530995A1 (en) * | 1995-08-23 | 1997-02-27 | Bosch Gmbh Robert | Fuel injector |
US5699964A (en) * | 1996-08-13 | 1997-12-23 | Ideal-Standard Gmbh | Showerhead and bottom portion thereof |
JP3466480B2 (en) * | 1998-07-06 | 2003-11-10 | 日本碍子株式会社 | Nozzle for liquid ejection device and method for manufacturing the same |
JP2001129438A (en) * | 1999-11-04 | 2001-05-15 | Ebara Hiroyuki | Shower device |
DE10048935A1 (en) | 2000-10-04 | 2002-04-11 | Bosch Gmbh Robert | Fuel injector |
DE10124748A1 (en) | 2001-05-21 | 2003-02-27 | Bosch Gmbh Robert | Fuel injector |
JP4192179B2 (en) * | 2003-01-09 | 2008-12-03 | シーメンス ヴィディーオー オートモティヴ コーポレイション | Control of spray pattern by non-beveled orifice formed on raised fuel injection metering disk with sac volume reduction means |
DE10319694A1 (en) * | 2003-05-02 | 2004-12-02 | Robert Bosch Gmbh | Fuel injector |
US7201329B2 (en) * | 2004-04-30 | 2007-04-10 | Siemens Vdo Automotive Corporation | Fuel injector including a compound angle orifice disc for adjusting spray targeting |
DE102004049280A1 (en) * | 2004-10-09 | 2006-04-13 | Robert Bosch Gmbh | Fuel injector |
DE102004049278A1 (en) * | 2004-10-09 | 2006-04-13 | Robert Bosch Gmbh | Fuel injector |
JP4491474B2 (en) | 2007-05-31 | 2010-06-30 | 日立オートモティブシステムズ株式会社 | Fuel injection valve and its stroke adjusting method |
JP2010185324A (en) | 2009-02-11 | 2010-08-26 | Denso Corp | Fuel injection valve |
US8402979B2 (en) * | 2009-09-18 | 2013-03-26 | David McHugh | Hair wash and rinse brush |
JP5452515B2 (en) * | 2011-01-31 | 2014-03-26 | 日立オートモティブシステムズ株式会社 | Fuel injection valve |
JP2012215135A (en) * | 2011-04-01 | 2012-11-08 | Hitachi Automotive Systems Ltd | Fuel injection valve |
DE102012209326A1 (en) * | 2012-06-01 | 2013-12-05 | Robert Bosch Gmbh | Fuel injector |
DE102013225948A1 (en) | 2013-12-13 | 2015-06-18 | Continental Automotive Gmbh | Nozzle head and fluid injection valve |
-
2013
- 2013-12-13 DE DE102013225948.4A patent/DE102013225948A1/en not_active Ceased
-
2014
- 2014-12-08 EP EP14814794.5A patent/EP3080435B1/en active Active
- 2014-12-08 WO PCT/EP2014/076912 patent/WO2015086536A1/en active Application Filing
- 2014-12-08 KR KR1020167018807A patent/KR101908826B1/en active IP Right Grant
- 2014-12-08 US US15/104,002 patent/US10975822B2/en active Active
- 2014-12-08 CN CN201490001251.5U patent/CN206190444U/en active Active
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Publication number | Publication date |
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DE102013225948A1 (en) | 2015-06-18 |
US10975822B2 (en) | 2021-04-13 |
US20160319793A1 (en) | 2016-11-03 |
EP3080435B1 (en) | 2019-10-02 |
KR101908826B1 (en) | 2018-10-16 |
CN206190444U (en) | 2017-05-24 |
WO2015086536A1 (en) | 2015-06-18 |
KR20160097358A (en) | 2016-08-17 |
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