CN105408616A - Switch valve for a fuel injector - Google Patents

Switch valve for a fuel injector Download PDF

Info

Publication number
CN105408616A
CN105408616A CN201480041908.5A CN201480041908A CN105408616A CN 105408616 A CN105408616 A CN 105408616A CN 201480041908 A CN201480041908 A CN 201480041908A CN 105408616 A CN105408616 A CN 105408616A
Authority
CN
China
Prior art keywords
valve
diameter
diffusion part
switching valve
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
Application number
CN201480041908.5A
Other languages
Chinese (zh)
Other versions
CN105408616B (en
Inventor
M·克劳泽
L·奥勒姆斯
T·尼埃里克罗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of CN105408616A publication Critical patent/CN105408616A/en
Application granted granted Critical
Publication of CN105408616B publication Critical patent/CN105408616B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
    • 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
    • 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
    • F02M2547/001—Control chambers formed by movable sleeves

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a switch valve (10) for a fuel injector (100) for internal combustion engines. The switch valve comprises a valve piece (11), which has a valve seat (12) and a valve closing armature (20), which interacts with the valve seat (12) and can be moved in a reciprocating manner. A discharge bore (30) having a circular cross-section is formed in the valve piece (11). The discharge bore comprises a first region having a diameter d1, which first region serves as a throttle (31), a second region, which serves as a diffuser (32), and a third region having a diameter d3, which third region serves as a following flow geometry (33). The second region has at least one segment having a diameter d2, and the following applies: d1<d2<d3. The third region B3 serving as a following flow geometry (33) has a length l3, wherein the following applies to the ratio l3/d3: 2<l3/d3<4, l3/d3 preferably being approximately equal to 2.5.

Description

For the switching valve of fuel injector
Background technique
By prior art, as such as DE19859537 known fuel sparger, as described in fuel injector be preferred for injecting fuel directly in the firing chamber of internal-combustion engine.According in the ejecting system of so-called common rail principle work, compressed fuel to provide in-orbit for use by means of high-pressure service pump and is ejected in the respective combustion chamber of internal-combustion engine by means of fuel injector.Control to spray by means of the valve needle arranged within the fuel injector, described valve needle is implemented longitudinal movement and is is therefore opened and closed one or more injection opening.By hydraulic coupling, valve needle is moved, described hydraulic coupling is applied on valve needle due to the pressure in control room.By pressure in control room change and therefore can the longitudinal movement of Control Nozzle pin targetedly to the closing forces change on valve needle.Open motion for valve needle, reduce the pressure in control room by means of switching valve, its mode is, opens the hydraulic connecting between control room and low pressure chamber, and wherein, this hydraulic connecting is configured to restriction.
Also known by DE19859537, particularly advantageous course of injection form (Einspritzverlaufsformung) can be realized by the combination of restriction and diffusion part as hydraulic connecting.Due to the requirement more and more improved in the high pressure of the fuel that will spray, the high pressure in control room and the high pressure that therefore will be exported by restriction are also risen.Therefore, because bubble increasing in the fuel exported is formed, with follow-up flow geometry portion in restriction in hole infringement risk improve.
Summary of the invention
The present invention is based on following object: propose a kind of switching valve, it has the hydraulic connecting for being outputted to from control room by fuel low pressure chamber, wherein, occurs the least possible hole infringement in described hydraulic connecting.
Have according to the present invention the feature of claim 1 switching valve this realize particularly advantageous course of injection form and the appearance on the other hand hole being damaged minimizes in the situation further aspect that pressure is very high.
For this reason, the switching valve for the fuel injector of internal-combustion engine comprises: the valve block with valve seat; And interactional with valve seat, the valve of stroke motion can close armature, wherein, in valve block, there is the discharge boring of circular cross section.Discharge boring comprises: have diameter d 1, as the first area of restriction; As the second area of diffusion part; With there is diameter d 3, as the 3rd region in follow-up flow geometry portion.Second area has at least one with diameter d 2section and meet d 1<d 2<d 3.As the 3rd region B in follow-up flow geometry portion 3there is length l 3, wherein, ratio l 3/ d 3meet: 2<l 3/ d 3<4, preferably l 3/ d 3approximate 2.5 greatly.
Advantageously, follow-up flow geometry portion has the diameter d of 1.0mm to 1.5mm 3, be preferably about 1.3mm.Diameter d 3only implement slightly minutely than the diameter of valve seat, thus the region near wall is in flow axes distance far away as far as possible and the implosion of cavitation bubbles does not cause only causing minimized hole to be damaged in other words.
Advantageously, restriction has the length l of about 0.8mm 1with the diameter d of about 0.25mm 1.The restriction diameter d of about 0.25mm 1cause particularly advantageous course of injection form, especially valve needle open stroke motion during.Preferably, the length-to-diameter ratio value l of restriction 1/ d 1be greater than 3, to avoid reducing the eddy current of flow in fuel in subsequent sections in other words.Therefore the restriction length l of the optimization of about 0.80mm is produced 1.
In a favourable embodiment, diffusion part has with diameter d 2bthe second section.Therefore, diffusion part is configured to double diffusion portion, and it has: be connected and restriction has diameter d 2d in other words 2athe first diffusion part; With there is diameter d 2bthe second diffusion part, wherein, d 2b>d 2a.Whole flowing of discharging in boring is advantageously formed in: reduce eddy current and avoid " dead water region " near wall the bubble implosion of---namely there is the region of very little flowing velocity, in most of the cases on inside edge---as much as possible by using double diffusion portion.
Advantageously, the twice of through flow cross section approximately as the through flow cross section of the first diffusion part of the second diffusion part is large.Therefore, the disadvantageous high μ value (water vapor diffusion impedance) because throttling causes is reduced again.
In a favourable configuration, the first diffusion part has length l 2aand there is the length-to-diameter ratio value l being approximately 1 2a/ d 2a.This ratio realizes the compromise of the best of flow graph, through-current capacity, reduction μ value and generation air pocket.
Similarly, also advantageously, the second diffusion part has length l 2band there is the length-to-diameter ratio value l being approximately 1 2b/ d 2b.
In a preferred manner, the first diffusion part has the diameter d of about 0.35mm 2a.In the region in double diffusion portion, the through flow cross section of each ladder approximately doubles for diameter is widened to be particularly advantageous.Therefore, the flow in fuel with as far as possible only little eddy current is guided when the pressure recover optimized at the same time.Therefore, by the restriction diameter d of about 0.25mm 1, for the diameter d of the first diffusion part 2adraw about 0.35mm.
Similarly, the second diffusion part d 2bdiameter be about 0.5mm.
Preferably, switching valve is configured to pressure balanced valve substantially.Therefore, high switch speed can be realized, and therefore switching valve is very well applicable to multi-injection.
Advantageously, switching valve is configured to solenoid valve.According to structure, the special electromagnetic excitation being conducive to valve closedown armature in the structure near the discharge restriction of valve seat of switching valve of the present invention.Therefore pressure conversion (Druck ü bersetzung) by means of additional throttle position can be saved.
Accompanying drawing explanation
Fig. 1 illustrates according to switching valve of the present invention with longitudinal section, wherein only main region is shown.
Fig. 2 illustrates the amplification Local map of the valve block of the switching valve of Fig. 1, wherein, the discharge boring be configured in valve block is shown more accurately.
Embodiment
Fig. 1 illustrates that this switching valve is used in fuel injector 100 according to switching valve 10 of the present invention here.Fuel injector 100 has housing, and this housing comprises nozzle body 2 and valve chest 40 together with being screwed in nozzle body 2.In nozzle body 2, structure is in the pressure chamber 3 under high pressure, and this pressure chamber is operationally connected with the unshowned fuel source (being generally common rail) be under high pressure.In pressure chamber 3, be furnished with the valve needle 4 be directed in sleeve 6 with longitudinal movement, this valve needle is for opening and closing unshowned injection opening, and described injection opening leads in the unshowned firing chamber of internal-combustion engine.
In valve chest 40, be furnished with valve block 11, this valve block to abut on the shoulder in valve chest 40 and until puts in pressure chamber 3.
The pressure that the opening and closing of valve needle 4 move through in control room 5 controls.Control room 5 is by valve needle 4, sleeve 6 and valve block 11 gauge.Be configured with in sleeve 6 and flow into boring 7, pressure chamber 3 is connected with control room 5 by this inflow boring.In valve block 11, structure discharges boring 30, and control room 5 is switchably connected with low pressure chamber 50 by this discharge boring, and this low pressure chamber is configured in valve chest 40.In other embodiments, valve block 11 and sleeve 6 also can be embodied as large valve block 6,11 single type, thus valve needle 4 is directed in valve block 6, and not only inflow boring 7 but also discharge boring 30 are all configured in valve block 6, in 11.
In valve chest 40, be furnished with switching valve 10, except valve block 11, this switching valve comprises electromagnet 42, valve cuts out armature 20 and bibcock 44.In valve chest 40, valve block 11 and electromagnet 42 when between be equipped with valve cage 41 clamped securely by clamping screw 43.Bibcock 44 and clamping screw 43 are permanently connected, and valve cuts out armature 20 and fixes can axially movably be directed to being configured in the armature boring 21 that this valve cuts out in armature at this valve.Therefore, the bibcock 44 by arranging rigidly realizes pressure balanced switching valve 10 to a certain extent.
Valve cuts out the valve seat 12 of defeating to be configured in valve block 11 on of armature 20 by the spring 45 be arranged between bibcock 44 and valve cut out armature 20.The diameter of valve seat 12 and the diameter of bibcock 44 are almost same large.Therefore, the hydraulic coupling of closing on armature 20 at valve is almost nil in the axial direction, switching valve 10 pressure balance to a certain extent.Structurally, this such as realizes by stepped armature boring 21.
Low pressure chamber 50 is hydraulically connected with the return-flow system be under low pressure of fuel injector 100.
Discharge boring 30 and be divided into three regions from control room 5 to low pressure chamber 50: as the first area of restriction 31 use, as the second area of diffusion part 32 use and the 3rd region as the use of follow-up flow geometry portion 33.At this, the through flow cross section of restriction 31 is less than the through flow cross section of diffusion part 32, and the through flow cross section of this diffusion part is less than again the through flow cross section in follow-up flow geometry portion 33.
Fig. 2 illustrates the detailed view of the discharge boring 30 in valve block 11.Restriction 31 is arranged in the first region and is had length l near control room 1with there is diameter d 1circular through flow cross section.Advantageously, its length-to-diameter ratio value l 1/ d 1be about 3.In the second area there is length l 2diffusion part 32 be connected in restriction 31, this diffusion part is configured to double diffusion portion 32 in the illustrated embodiment, and has the through flow cross section larger than restriction 31: double diffusion portion 32 is by having length l near restriction 2athe first diffusion part 32a and there is length l 2bthe second diffusion part 32b form, wherein, there is diameter d 2bthe second diffusion part 32b ratio there is diameter d 2athe first diffusion part 32a there is larger through flow cross section.The follow-up flow geometry portion 33 in the 3rd region is connected in double diffusion portion 32 near low pressure chamber; It has length l 3and diameter d 3.
Whole three regions of discharging boring 30 are characterized by the through flow cross section of circle.At this, the through flow cross section from side, control room to low pressure chamber side is always widened:
For discharge boring 30, the d with single diffusion part 32 1<d 2<d 3
For discharge boring 30, the d with double diffusion portion 32a and 32b 1<d 2a<d 2b<d 3
Transition part between different through flow cross sections---namely from restriction 31 to the first diffusion part 32a, from the first diffusion part 32a to the second diffusion part 32b with from the second diffusion part 32b to the transition part in follow-up flow geometry portion 33---is by chamfered edge configuration, but described chamfered edge rounding.Preferably, from the transition part of restriction 31 to the first diffusion part 32a with from the first diffusion part 32a to the transition part of the second diffusion part 32b, respectively there are 45 ° of chamfered edges, and from the second diffusion part 32a to the transition part in follow-up flow geometry portion 33, there are 30 ° of chamfered edges.
The working principle of switching valve 10 is as follows: shut-off nozzle pin 4 and switching valve 10 before the injection event is initiated, does not have fuel to flow in the firing chamber of internal-combustion engine.Close switching valve 10 to mean, valve cuts out armature 20 and is pressed towards valve seat 12 and makes it seal.Under control room 5 is in high pressure, this high pressure is roughly equivalent to the high pressure of common rail.
When course of injection starts, electromagnet 42 is driven control by electricity and therefore applies attraction force and closes on armature 20 to valve.Therefore, valve cuts out the power that armature 20 resists spring 45 and implements stroke motion towards the direction of electromagnet 42 and therefore rise from valve seat 12.Now, control room 5 is connected with low pressure chamber 50 by discharging boring 30.Fuel flows to low pressure chamber 50 from control room 5, and this is also referred to as the output of fuel.Pressure drop in control room 5 because with by flowing into compared with boring 7 flows into, more fuel passes through discharge boring 30 and exports.Identically with the pressure in control room 5, what produce to valve needle 4 also declines towards the hydraulic coupling of spraying opening direction.Therefore, valve needle 4 rises from nozzle needle stand and opens and sprays opening; Fuel flows in the firing chamber of internal-combustion engine.
In order to end injection process, make the electricity of electromagnet 42 drive control and terminate.Electromagnet 42 no longer applies attraction force and closes on armature 20 to valve, and valve closedown armature 20 is pressed to again valve seat 12 by the spring force of spring 45.By flowing into boring 7 to be in the filling fuels control room 5 under high pressure, until it is identical in common rail in other words with in pressure chamber 3 to account for leading pressure in control room 5.Along with the pressure increase in control room 5, valve needle 4 also rises towards the hydraulic coupling of spraying opening direction, and valve needle 4 is pressed towards again its nozzle needle stand.No longer include fuel to flow in the firing chamber of internal-combustion engine.
Due to high pressure and for burner oil to the course of injection form in combustion chambers of internal combustion engines, the fuel that will export, proposes high requirement to switching valve 10: during switching cycle, occur large pressure difference within control room 5 and in discharge boring 30 on the one hand.On the other hand, when exporting, fuel especially reaches high through flow velocity in discharge boring 30.Along with through flow velocity improves, static pressure declines.If this static pressure drops to below the vapor pressure of fuel, then form bubble.Bubble is transported in the region of higher static pressure power (through flow cross section that namely less through flow velocity is larger in other words) along with stream.Along with static pressure is increased beyond vapour tension there, bubble liquefies suddenly, and bubble implosion.This process is called as cavitation.For around flow geometry portion, if through reflection, may have until 40kbar pressure peak implosion bubble occur near wall, then they are harmful; Generating material corrodes, and at this, that is, cavitation erosion or hole infringement occurs.Therefore, the end regions that the region that switching valve 10 is endangered especially in the infringement of hole is restriction 31, diffusion part 32, follow-up flow geometry portion 33, valve seat 12, valve close armature 20 and bibcock 44, i.e. the high pressure loading area in restriction 31 downstream of switching valve 10.
In order to avoid reducing hole infringement in other words, two measures are taked: on the one hand reduce the appearance of bubble near wall and guiding by the special configuration of restriction 31 and diffusion part 32 in the configuration of discharging boring 30, on the other hand, by use the follow-up flow geometry portion 33 with large volume make the implosion of bubble be distributed in large, as far as possible away from the region of wall.
The task of restriction 31 makes fuel throttling when exporting from control room 5, and then the motion of such Control Nozzle pin 4, makes to realize the course of injection form for the optimization of fuel injector 100.Throttling function is mainly through the diameter d of the circular through flow cross section of restriction 31 1determine.The hydraulic pressure layout of course of injection form shows, by 0.2 ... the throttling diameter d of 0.3mm, especially approximately 0.25mm 1realize best course of injection form.
Ideally, the length-to-diameter ratio value of restriction 31 is approximately greater than 3, thus the length l of restriction 31 1be 0.7 ... 1.0mm, especially approximately 0.8mm.Avoid thus because for lesion area propagates into from diffusion part 32 the through-flow change that restriction 31 causes.In addition, compared with the situation that restriction is shorter, in subsequent sections, namely, in diffusion part 32, the not stronger eddy current of fuel generation is flow through.Eddy current may to carry in bubble to wall near zone and therefore to cause hole to damage.The output stream being loaded with steam entered in diffusion part 32 concentrates in flow axes, namely discharges on the axis of symmetry of boring 30 by long restriction 31 more.Naturally, the length-to-diameter ratio value of restriction 31 also can be selected larger, but this then can need more installing space, and does not additionally improve flow in fuel.
The unavoidable shortcoming of relatively long restriction 31 is deteriorations of μ value (water vapor diffusion impedance): μ value improves along with the increase of restriction length, and the μ value of raising causes again the consequence of high backflow back pressure.Therefore, the flowing of bubble in follow-up flow geometry portion 33 in other words " diffusion " has higher impedance, and correspondingly, this causes undesired eddy current.The task of diffusion part 32 by the pressure recover of optimization, μ value is reduced again.Advantageously, this task has been come by using double diffusion portion 32.
Diameter in double diffusion portion 32 is widened the flow in fuel in whole discharge boring 30 and then is also had conclusive impact to μ value.Advantageously, in the region in double diffusion portion 32, such configuration diameter is widened, and the through flow cross section of each ladder is approximately doubled.That is, the through flow cross section A of the first diffusion part 32a 2aapproximately as the through flow cross section A of restriction 31 1twice is large, and the through flow cross section A of the second diffusion part 32b 2bapproximately as A 2atwice is large.Therefore, for the diameter d of the circular through flow cross section of the first diffusion part 32a 2a, draw: d 2a=0.28 ... 0.42mm, especially 0.35mm.Further, for the diameter d of the circular through flow cross section of the second diffusion part 32b 2b, draw: d 2b=0.40 ... 0.60mm, especially approximately 0.50mm.
Diffusion part 32 is had in other words to the length-to-diameter ratio value in the double diffusion portion 32 of the first diffusion part 32a and the second diffusion part 32b, the ratio that approximately every diameter widens 1 is proved in flow technique advantageous particularly.This ratio realizes flow graph, through-current capacity, reduction μ value and the optimal compromise in hole occurs.
Therefore, for the first diffusion part 32a, length l is drawn 2a=0.28 ... 0.42mm, especially approximately 0.35mm, and, for the second diffusion part 32b, draw length l 2b=0.40 ... 0.60mm, especially 0.5mm.
In flow technique particularly advantageously, widen from the diameter of restriction 31 to the first diffusion part 32a and widen from the first diffusion part 32a to the diameter of the second diffusion part 32b and conically widen with 45 °, namely there are 45 ° of chamfered edges, this chamfered edge can on its edge rounding.In cusped edge situation, namely 90 ° of transition parts when, in the region, inside edge in double diffusion portion 32, occur so-called dead water region, described dead water region may cause again being formed the cavitation bubbles near wall that low pressure area and then cause adds.
Be connected, to the follow-up flow geometry portion 33 in double diffusion portion 32, there is such task: improve the static pressure level in follow-up flow geometry portion 33 when valve seat 12 and the valve discharge of closing between armature 20 remain unchanged, so that the steam realizing reducing is formed.This is realized by relatively large volume.And, remaining bubble formed and particularly also alveolate implosion to be distributed on larger volume and away from valve seat 12 and valve closedown armature 20.Therefore, make the hole in the region in diffusion part 32 downstream damage to minimize.Meanwhile, long follow-up flow geometry portion 33 reduces μ value by the uniform flow graph of structure, improves the functional of fuel injector 100 thus.
Owing to using double diffusion portion 32 before, the diameter for follow-up flow geometry portion 33 is being widened and need not be restricted to the through flow cross section doubled again.Advantageously, the diameter d in follow-up flow geometry portion 33 3only slightly be less than the diameter of valve seat 12, and be in 1.0 ... in the scope of 1.5mm, be preferably 1.3mm.The relatively large diameter of valve seat 12 has advantage: the output quantity needed for can having derived between valve seat 12 and valve closedown armature 20 when the stroke that valve cuts out armature 20 is little.
The length-to-diameter ratio value l in follow-up flow geometry portion 33 3/ d 33 ground need not be greater than again select, because restriction 31 and double diffusion portion 32 have reduced the major part of control room 5 mesohigh; In follow-up flow geometry portion 33, there is significantly less bubble and formed.But, length l 3must select like this, make the sufficient decent that μ value occurs.Typically, l is selected 3/ d 3=2 ... 4, l ideally 3/ d 3=about 2.5.And then, for follow-up flow geometry portion 33, draw length l 3=2.0 ... 6.0mm, especially approximately 3.25mm.
In addition, long follow-up flow geometry portion 33 has such advantage: discharge the region of the counter stress key of boring 30, namely can locate like this from restriction 31 to the diameter transition of diffusion part 32 with from diffusion part 32 to the diameter transition in follow-up flow geometry portion 33, the static stress existed due to screwing of valve block 11 is advantageously superposed with the dynamic stress caused due to high voltage load.

Claims (11)

1. for the switching valve (10) of the fuel injector (100) of internal-combustion engine, comprise the valve block (11) with valve seat (12) and coefficient with this valve seat (12), the valve of stroke motion can close armature (20), wherein, in this valve block (11), there is discharge boring (30) of circular cross section, described discharge boring comprises: have diameter d 1, as the first area of restriction (31); As the second area of diffusion part (32); With there is diameter d 3, as the 3rd region in follow-up flow geometry portion (33), wherein, described second area has at least one and has diameter d 2section and meet d 1<d 2<d 3,
It is characterized in that, as the 3rd region B in follow-up flow geometry portion (33) 3there is length l 3, wherein, ratio l 3/ d 3meet: 2<l 3/ d 3<4, preferably l 3/ d 3approximate 2.5 greatly.
2. switching valve according to claim 1 (10),
It is characterized in that, the diameter d in described follow-up flow geometry portion (33) 3for 1.0mm to 1.5mm, be preferably about 1.3mm.
3. switching valve according to claim 1 and 2 (10),
It is characterized in that, described restriction (31) has the length l of about 0.80mm 1, and, the diameter d of described restriction (31) 1for about 0.25mm.
4. the switching valve (10) according to any one of the preceding claims,
It is characterized in that, the second area as diffusion part (32) is configured to double diffusion portion and has two cylindrical sectors, and it has: be connected in described restriction (31), there is diameter d 2athe first diffusion part (32a); With there is diameter d 2bthe second diffusion part (32b), wherein, d 2b>d 2a.
5. switching valve according to claim 4 (10),
It is characterized in that, the through flow cross section of described second diffusion part (32b) approximately as described in the twice of through flow cross section of the first diffusion part (32a) large.
6. the switching valve (10) according to claim 4 or 5,
It is characterized in that, described first diffusion part (32a) has length l 2aand there is the length-to-diameter ratio value l being approximately 1 2a/ d 2a.
7. the switching valve (10) according to any one of claim 4 to 6,
It is characterized in that, described second diffusion part (32b) has length l 2band there is the length-to-diameter ratio value l being approximately 1 2b/ d 2b.
8. the switching valve (10) according to any one of claim 4 to 7,
It is characterized in that, the diameter d of described first diffusion part (32a) 2afor about 0.35mm.
9. the switching valve (10) according to any one of claim 4 to 8,
It is characterized in that, the diameter d of described second diffusion part (32b) 2bfor about 0.5mm.
10. the switching valve (10) according to any one of the preceding claims,
It is characterized in that, described switching valve (10) is configured to pressure balanced valve substantially.
11. fuel injectors (100), it has the switching valve (10) according to any one of the preceding claims, and wherein, described switching valve (10) is configured to solenoid valve.
CN201480041908.5A 2013-07-25 2014-05-20 Switching valve for fuel injector Active CN105408616B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013214589.6 2013-07-25
DE102013214589.6A DE102013214589A1 (en) 2013-07-25 2013-07-25 Switching valve for a fuel injector
PCT/EP2014/060288 WO2015010805A1 (en) 2013-07-25 2014-05-20 Control valve for a fuel injector

Publications (2)

Publication Number Publication Date
CN105408616A true CN105408616A (en) 2016-03-16
CN105408616B CN105408616B (en) 2019-07-16

Family

ID=50733090

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201480041908.5A Active CN105408616B (en) 2013-07-25 2014-05-20 Switching valve for fuel injector

Country Status (5)

Country Link
EP (1) EP3025048B1 (en)
KR (1) KR102166315B1 (en)
CN (1) CN105408616B (en)
DE (1) DE102013214589A1 (en)
WO (1) WO2015010805A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015210800A1 (en) * 2015-06-12 2016-12-15 Continental Automotive Gmbh Valve device for a fuel injection system and fuel injection system
TR201820749A2 (en) * 2018-12-27 2020-07-21 Bosch Sanayi Ve Tic A S A FUEL FLOW PATH FOR A FUEL INJECTOR'S VALVE GROUP
DE102021201908A1 (en) 2021-03-01 2022-09-01 Robert Bosch Gesellschaft mit beschränkter Haftung Method for determining a state of a switching valve of a fuel injector

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19859537A1 (en) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Fuel injector
US20030087487A1 (en) * 2001-10-23 2003-05-08 Uwe Finke Solenoid valve for controlling a fuel injector
CN101490403A (en) * 2006-05-10 2009-07-22 罗伯特·博世有限公司 Fuel injector comprising a pressure-compensated control valve
CN101595297A (en) * 2007-01-30 2009-12-02 罗伯特·博世有限公司 Valve with ball seat with etching characteristic of reduction
CN101680413A (en) * 2007-06-21 2010-03-24 罗伯特·博世有限公司 Control valve for a fuel injection valve
CN102227554A (en) * 2008-11-27 2011-10-26 罗伯特·博世有限公司 Method for producing throttle holes having low cavitation transition point
DE102010028844A1 (en) * 2010-05-11 2011-11-17 Robert Bosch Gmbh switching valve
CN103180588A (en) * 2010-11-03 2013-06-26 罗伯特·博世有限公司 Method for operating a magnetic switching element

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19963389A1 (en) * 1999-12-28 2001-07-05 Bosch Gmbh Robert Method of manufacturing a valve piece for a fuel injector
DE102006034111A1 (en) * 2006-07-24 2008-01-31 Robert Bosch Gmbh Servo-valve-controlled injector for injecting fuel into cylinder combustion chambers of internal combustion engines; in particular common rail injector

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19859537A1 (en) * 1998-12-22 2000-07-06 Bosch Gmbh Robert Fuel injector
US20030087487A1 (en) * 2001-10-23 2003-05-08 Uwe Finke Solenoid valve for controlling a fuel injector
CN101490403A (en) * 2006-05-10 2009-07-22 罗伯特·博世有限公司 Fuel injector comprising a pressure-compensated control valve
CN101595297A (en) * 2007-01-30 2009-12-02 罗伯特·博世有限公司 Valve with ball seat with etching characteristic of reduction
CN101680413A (en) * 2007-06-21 2010-03-24 罗伯特·博世有限公司 Control valve for a fuel injection valve
CN102227554A (en) * 2008-11-27 2011-10-26 罗伯特·博世有限公司 Method for producing throttle holes having low cavitation transition point
DE102010028844A1 (en) * 2010-05-11 2011-11-17 Robert Bosch Gmbh switching valve
CN103180588A (en) * 2010-11-03 2013-06-26 罗伯特·博世有限公司 Method for operating a magnetic switching element

Also Published As

Publication number Publication date
EP3025048B1 (en) 2018-08-01
KR20160034407A (en) 2016-03-29
EP3025048A1 (en) 2016-06-01
WO2015010805A1 (en) 2015-01-29
KR102166315B1 (en) 2020-10-16
DE102013214589A1 (en) 2015-01-29
CN105408616B (en) 2019-07-16

Similar Documents

Publication Publication Date Title
CN101382108B (en) Low back-flow pulsation fuel injection pump
RU2559096C2 (en) Device for fuel injection to combustion chamber of internal combustion engine
CN101743394B (en) Throttle on a valve needle of a fuel injection valve for internal combustion engines
US8069840B2 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
CN102812232B (en) High-pressure fuel injection valve for an internal combustion engine
CN102691605B (en) Electrically-controlled fuel injector for large diesel engines
US6745750B2 (en) Fuel injection system for internal combustion engines
CN105408616A (en) Switch valve for a fuel injector
EP1612401B1 (en) An injection system for an internal combustion engine
US8136741B2 (en) Fuel injection device for an internal combustion engine using direct fuel injection
DK2423498T3 (en) Passive flow control valve
FI20030054A0 (en) Arrangement in the fuel supply system
EP2378109B1 (en) A fuel valve for large stroke diesel engines
CZ295572B6 (en) Pressure translator for a fuel injection system of internal combustion engine
US20160108781A1 (en) Variable-flow rate oil pump
KR102067395B1 (en) Valve device
KR20180100675A (en) Fuel injection system
CN102822496A (en) Common-rail injector having a pressure-balanced control valve and additional reservoir volume
JP2013011274A (en) Fuel valve for turbocharger type large two-cycle diesel engine
US20170218901A1 (en) Injector for Injecting Fluid
KR20060028699A (en) Fuel-injection system with reduced pressure pulsations in the return rail
CN103261660B (en) For the Fuelinjection nozzle of internal-combustion engine
RU2638240C2 (en) Fuel valve for two-stroke engine of internal combustion engine with self-ignition
WO2018003415A1 (en) High-pressure fuel supply pump
KR20190047049A (en) In particular, overflow valves, high-pressure pumps, and fuel injection systems for use in fuel injection systems

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant