CN1745243B - High-pressure line for a fuel injection system - Google Patents
High-pressure line for a fuel injection system Download PDFInfo
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- CN1745243B CN1745243B CN03826031.XA CN03826031A CN1745243B CN 1745243 B CN1745243 B CN 1745243B CN 03826031 A CN03826031 A CN 03826031A CN 1745243 B CN1745243 B CN 1745243B
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- high pressure
- pressure pipe
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- 239000000446 fuel Substances 0.000 title claims description 39
- 238000002347 injection Methods 0.000 title claims description 27
- 239000007924 injection Substances 0.000 title claims description 27
- 238000002485 combustion reaction Methods 0.000 claims description 15
- 238000007789 sealing Methods 0.000 claims description 5
- 230000003247 decreasing effect Effects 0.000 description 10
- 239000007921 spray Substances 0.000 description 8
- 238000005507 spraying Methods 0.000 description 7
- 230000011514 reflex Effects 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000010304 firing Methods 0.000 description 5
- 230000003068 static effect Effects 0.000 description 4
- 230000002349 favourable effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000000644 propagated effect Effects 0.000 description 3
- 230000002238 attenuated effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000012885 constant function Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 238000009499 grossing Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
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- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
-
- 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
- F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
- F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a high-pressure line between an injector (1) and a common rail (114), which fully or partially decomposes the pressure waves created when the injector (1) is actuated.
Description
Technical field
The present invention relates to a kind of high pressure pipe line for fuel injection system for IC engine.
Background technique
The below explains a kind of fuel injection system 102 according to prior art of internal-combustion engine by Fig. 8.Reference number also utilizes when explanation high pressure pipe line of the present invention as used herein.
The fuel injection system 102 of describing in Fig. 8 comprises a fuel container 104, transfers out fuel 106 by petrolift 108 electricity or machinery from this fuel container.Fuel 106 flows to a high pressure fuel pump 111 by a low-pressure fuel pipeline 110.Fuel 106 arrives altogether rail 114 from high pressure fuel pump 111 through a fuel under high pressure pipeline 112.Connected a plurality of spargers 1 at common rail 114, they are directly injected to fuel 106 in the firing chamber 118 of unshowned internal-combustion engine.Hydraulic connecting between rail 114 and these spargers 1 is respectively realized by a high pressure pipe line 3 altogether.
During to firing chamber 118 an interior injection beginning, the sparger 1 that belongs to this firing chamber 118 is opened at fuel.Thus, be in fuel 106 under the high pressure from sparger 1 flowing in combustion chamber 118.The fuel quantity that overflows since altogether rail 114 and subsequent flows to sparger 1.
Because the sparger of modern sparger 1, particularly piezoelectricity control opens and closes soon, when sparger 1 operation in high pressure pipe line 3 pressure wave appears, and this pressure wave imports common rail 114 into from the sparger 1.There, this pressure wave is reflected, and arrives again sparger 1.Sparger 1 is opened faster, and the edge of pressure wave is steeper.The steepness at pressure wave edge is also referred to as gradient dp/dt below.
Like this, in high pressure pipe line 3 and in sparger 1, directly behind injection beginning, the pressure wave amplitude that common rail static pressure has been superposeed and illustrated previously.Therefore, the pressure in the sparger 1 is not constant, but bears obvious timeliness fluctuation.Not only especially itself be this situation between injection period, and on the time period of and then spraying, also be like this.Because the fuel quantity that spray in the firing chamber 118 this moment also depends on the pressure that is acting between injection period in sparger 1, above-mentioned pressure wave has undesirable impact to emitted dose.When injection duration specific pressure Reeb is long by the propagation time of high pressure pipe line, be so on the one hand, but particularly when when in sparger 1, working during the main injection subsequently, being like this by the pressure wave that sprays in advance triggering and reflect at common rail 114.Also show thus, the amount that sprays into during the main injection depend on to a great extent it with before the interval of spraying in advance that occurs.
Some configurations for reducing the pressure wave in the fuel injection system 102 that the following describes are disclosed in the prior art:
The throttle valve (not shown) of in high pressure pipe line 3, packing into.Thus, although pressure wave is attenuated, throttle valve has also reduced the operational jet pressure on the sparger 1, and this is undesirable.
Can be arranged in parallel a safety check (not shown) with the throttle valve (not shown) in addition, it is opened towards sparger 1 direction.Thus, although avoided restriction loss, throttle valve is inoperative during fuel flows to sparger 1 from common rail 114, in other words, should configure inoperative between injection period.In addition, to have safety check cost of each sparger very high in such configuration.
Disclose a kind of configuration among DE 100 60 811 A1, in this configuration, be provided with a buffer cell in sparger 1, it is by a throttle valve and high pressure pipe line 3 hydraulic connectings.
Disclosed these effects for the measure of the pressure surge that reduces high pressure pipe line also need to improve in the prior art, and particularly because of improving along with jet pressure and more and more requiring sparger faster, the problems referred to above are more obvious.
Summary of the invention
According to the present invention, high pressure pipe line a kind of fuel injection system for internal-combustion engine, that fuel is provided to sparger has been proposed, wherein, this high pressure pipe line is comprised of a first paragraph and a second segment, and, first paragraph and second segment are connected in parallel, wherein, first paragraph has a unlimited end, and second segment has the end of a sealing, and, merge in this first paragraph and the zone of this second segment on being connected to sparger.
According to the present invention, a kind of fuel injection system for internal-combustion engine has also been proposed, having one is total to each sparger of each cylinder of rail and internal-combustion engine and has a high pressure pipe line that will be total to rail and sparger hydraulic connecting, wherein, this high pressure pipe line is according to the described high pressure pipe line of one of aforementioned claim.
Stipulate in the first mode of execution of high pressure pipe line of the present invention, high pressure pipe line is comprised of a first paragraph and a second segment, and first paragraph and second segment are connected in parallel.
The characteristics of a particularly advantageous scheme of the present invention are, first paragraph has a unlimited end, and second segment has the end of a sealing.According to the present invention, the open end of first paragraph is connected on the common rail, and the first paragraph of high pressure pipe line and second segment merge in the zone on being connected to sparger.Can utilize following effect in this case:
When pressure wave reflex time on an open end (on this first paragraph at high pressure pipe line), the pressure wave reflection not only occurs in the place that passes into common rail at high pressure pipe line, and the conversion of amplitude symbol occurs simultaneously.In other words, after reflection, become the increased pressure of equivalent from pressure drop.
When pressure wave reflex time on a closed end, only have the pressure-wave propagation direction to change, but the symbol of amplitude is constant.If this moment is substantially the same long with the second segment with closed end with the first paragraph of open end, then in the there of first paragraph and second segment merging, two pressure waves meet each other, they have identical amplitude, wherein, the symbol of a pressure wave amplitude is positive, and another is born.Thus, these pressure waves are cancelled out each other, so that no longer have pressure wave at flow direction in the back of first paragraph and second segment merging place.But in sparger, act on a constant pressure, thereby for example to following the constant initial conditions of main injection effect after spraying in advance, exactly do not rely on the space between them.
In another program of fuel high pressure pipeline of the present invention, first paragraph and second segment are by a throttle valve hydraulic connecting.Reach thus, arrive merging place, be by before the there of a throttle valve hydraulic connecting between first paragraph and the second segment, the major part of reflected pressure wave amplitude just is cancelled so that merge bit be set up just only also have very little, arrive from the residual pressure ripple of two pipe sections.
In another program of fuel high pressure pipeline of the present invention, a throttle valve is set in the second segment of pipeline.Thus, the part of pressure wave is subdued, and however, the first paragraph by high pressure pipe line can be in the situation that there be the noticeable pressure loss to flow to enough fuel quantity of sparger from common rail.
The effect of high pressure pipe line of the present invention can further improve, and its mode is that a safety check that is connected in series with throttle valve is set in second segment.Reach thus, be reflected as so far on closed end by the low-pressure wave that spray to trigger, but may come then valve to open and these ripples are subdued in common rail by throttle valve in low-pressure wave so that do not have or almost reflection occur.
Perhaps also can stipulate, high pressure pipe line has one the 3rd section, and not only first paragraph but also second segment all pass in the 3rd section, and this section is extended between merging position and sparger.Guaranteed that by this mode of execution high pressure pipe line of the present invention can be in the situation that do not make structure and change to be connected to and be on the common rail and sparger of having produced in batches.In the numerous embodiments of high pressure pipe line of the present invention and in using advantageously, the length L of first paragraph
1Length L with second segment
2Substantially equal.
Equally under many applicable cases advantageously, the hydraulic diameter D of first paragraph
1Hydraulic diameter D with second segment
2Substantially equal.At last, also advantageously, the hydraulic diameter D of first paragraph
1Hydraulic diameter D with second segment
2Quadratic sum and the 3rd section hydraulic diameter D
3Square equally large.
But these relations are not the pressure prerequisites of high pressure pipe line of the present invention.Multiple use field is also arranged, meaningfully different from these relations therein.For example can wish have autotelic, the temporal partially wrong merge bit that arrives to be set up from the reflected pressure wavestrip of first paragraph and second segment.This can pass through different duct length L
1And L
2Reach.For example can also not wish the diameter D of these pipe sections in just the same ground
1, D
2And D
3Equate.
The shortcoming of prior art also can be improved by the high pressure pipe line of a single type, and wherein, an end of high pressure pipe line has a diameter and widens.By this measure, altogether the pressure on the rail is not to reflex to fully on the position, but pressure wave partly interrupts and reflects in the zone that the diameter in high pressure pipe line increases gradually.Therefore, the edge of reflected pressure ripple becomes milder, and in other words, gradient dp/dt descends strongly.Thus, the pressure surge in the zone of the nozzle needle stand in the sparger also reduces, and this has obviously reduced the impact of interval on spraying for the second time between twice injection on the one hand, on the other hand so that the wearing and tearing of nozzle carrier obviously reduce.
The diameter of high pressure pipe line is widened and can or be truncated cone shape or stepwise enforcement.According to the present invention, from this scheme, also can draw some high pressure pipe lines, wherein, an attachment portion special, that widen, particularly widen with truncated cone shape or tapered diameter with diameter is fixed on the common rail.Replace the taper form, diameter also can increase with nonlinear way on length, and this causes crooked cone-shaped internal part shape.
As already mentioned, the high pressure pipe line structure characteristic of the present invention that had before illustrated can be made up mutually, so that the runnability by suitable selection and definite size of high pressure pipe line of the present invention are optimized the special fuel ejecting system.
Draw in the accompanying drawing, the description of the drawings that other advantage of the present invention and favourable scheme can be from behind.
Description of drawings
Accompanying drawing represents:
Fig. 1 is according to a high pressure pipe line of prior art,
Some embodiments of Fig. 2-7 high pressure pipe line of the present invention, and
The schematic diagram of a fuel injection system of Fig. 8.
Embodiment
Fig. 1 represents one from high pressure pipe line 3 well known in the prior art, and it is altogether rail 114 and sparger 1 hydraulic connecting, by Fig. 1 to explain in detail the pressure wave repeatedly mentioned and in high pressure pipe line 3 in time with the change curve of position.
For this reason, an x-p plotted curve is shown on the left side of high pressure pipe line 3.At this, x represents the length coordinate of high pressure pipe line 3, its zero point the joint between sparger 1 and high pressure pipe line 3.The Y-axis of the usefulness of plotted curve " p " mark represents the pressure p (x) in the high pressure pipe line 3.High pressure pipe line 3 has length L, in other words when position coordinate x=L, from altogether rail 114 and the there reflection of pressure wave arrival of sparger 1.
On high pressure pipe line 3 left sides x-p plotted curve is shown, the pressure history when its representative is moved from sparger 1 to common rail 114 directions when pressure wave the high pressure pipe line 3.This curve on high pressure pipe line 3 left sides is shown in the maximum value 5 of pressure wave in sparger 1 and the altogether instantaneous record of the time point between the rail 114.The pressure-wave propagation direction is by 7 expressions of an arrow.Attractive when observing at the p-x plotted curve shown in high pressure pipe line 3 left sides is that this pressure wave has the form that is pressure decreased with respect to the static pressure in the high pressure pipe line 3.This explains because sparger 1 is opened, particularly impact type is opened, and fuel sprays into firing chamber 118 (seeing Fig. 8) from sparger 1 people, so that be directly apparent when in the sparger 1 release occuring.Therefore produce a pressure wave with negative amplitude (pressure decreased), it is propagated to common rail 114 directions from the sparger 1 by high pressure pipe line 3.This pressure wave amplitude is used " A " mark in Fig. 1.
When pressure wave arrived on the common rail 114 at this moment, altogether rail 114 played effect such as same open end with static pressure for pressure wave.Pressure wave reflects at this open end, and in other words, it changes the direction of propagation and propagate from common rail 114 to sparger 1 direction this moment.The sign modification of amplitude is so that become increased pressure from pressure decreased but simultaneously.This p-x graphical representation by high pressure pipe line 3 the right out.The direction of arrow 7 is with respect to opposite in the description in high pressure pipe line 3 left sides.More illustrated as the pressure wave in the p-x plotted curve on high pressure pipe line 3 left sides and the right also becomes increased pressure from pressure decreased.
If this moment, the reflected pressure ripple arrived sparger 1, then the pressure bearing in the sparger 1 fluctuates significantly.From a static pressure p who is painted on the px plotted curve
StatSet out amplitude A of the increased pressure in the sparger.
Just in time occur once to spray if thereby arrive that time period that the pressure in the sparger on the sparger 1 bears surging in time at pressure wave this moment, then this has a direct impact the fuel quantity that sprays into.The measuring accuracy of sparger 1 so variation, the emission performance of internal-combustion engine be therefore variation also.The runnability of internal-combustion engine (Laufkultur) also can suffer damage.
If opposite sparger 1 cuts out at that time point that the reflected pressure ripple arrives it, then it becomes a closed end for pressure wave and makes this ripple-current in the situation that keep its amplitude-again to common rail direction reflection.Finally in pipeline, consist of this moment one only very underdamp, keep motionless ripple, the pressure in the sparger 1 is long-time transition fluctuation after once spraying, the interval between twice injection produces obviously impact to spraying for the second time.
In the p-x plotted curve on high pressure pipe line 3 left sides, express qualitatively a gradient dp/dt.This figure is not exclusively accurate, because in a p-x plotted curve, can not express the time changing curve of pressure " p ", but because pressure wave constant velocity of propagation in high pressure pipe line 3, at the edge steepness of the pressure wave as in the p-x plotted curve of Fig. 1 and the pressure wave as definition related to the present invention, namely have a kind of direct relation between (being also referred to as gradient dp/dt here) over time as the fuel pressure in the high pressure pipe line 3.
In Fig. 2, express first embodiment of high pressure pipe line 3 of the present invention.At this, high pressure pipe line 3 two-piece type ground are realized.It has a first paragraph 3.1 and a second segment 3.2.First paragraph 3.1 will be total to rail 114 and be connected with sparger 1 and have a length L
1With hydraulic diameter D
1
Second segment 3.2 has length L
2With hydraulic diameter D
2First paragraph 3.1 and second segment 3.2 meet and communicate with each other in the there that they are connected on the sparger 1.
Opposite with first paragraph 3.1, second segment 3.2 has the end 9 of a sealing.Hydraulic diameter D
1And D
2Can be substantially equal.If length L
1And L
2Substantially equal, the same is favourable under many applicable cases.But the present invention is not limited to and determines like this size.
If this moment, sparger 1 was opened, then as explaining in detail by Fig. 1, produce a pressure wave that is the pressure decreased form, it was both propagated by the first paragraph 3.1 of high pressure pipe line 3, also propagated by the second segment 3.2 of high pressure pipe line 3.As explaining by Fig. 1, on the open end of first paragraph 3.1, be the there that it passes into common rail 114, pressure wave reflection also changes its symbol.In other words, become increased pressure from pressure decreased.
The reflex time situation is different on the closed end 9 of pressure wave at second segment 3.2.There, pressure wave only changes its direction of propagation, but does not change its amplitude symbol.Pressure wave by closed end 9 reflections of second segment 3.2 is pressure decreased all the time.This moment, the reflected pressure ripple of first paragraph was increased pressure, the reflected pressure ripple of second segment 3.2 is pressure decreased all the time, if this moment, these two pressure waves met in the there that they pass into sparger 1, then the reflected pressure ripple of first paragraph 3.1 and second segment 3.2 is cancelled out each other, so that the pressure in the sparger 1 " p " keeps constant in time.
In other words, can the fuel quantity that spray not had a negative impact by opening sparger 1 spontaneous pressure wave.
Another embodiment of a high pressure pipe line 3 of the present invention shown in Figure 3.Between sparger 1 and first paragraph 3.1 and second segment 3.2, to have the 3rd section 3.3 of high pressure pipe line with a basic distinction embodiment illustrated in fig. 2.Has hydraulic diameter D for the 3rd section 3.3
3And length L
3Advantageously, hydraulic diameter D
1And D
2Quadratic sum D
1 2+ D
2 2Equal the 3rd section 3.3 hydraulic diameter D
3Square D
3 2In this embodiment, in first paragraph 3.1 and the process in second segment 3.2 corresponding to before by those processes of explanation embodiment illustrated in fig. 2.
To be illustrated more clearly in again the mode of action with the second segment 3.2 of closed end 9 by this second embodiment.High pressure pipe line the right and the left side with the p-x graphical representation of I mark from sparger 1 to common rail 114 and the pressure wave to the path of closed end 9.In the p-x plotted curve with the II mark on high pressure pipe line 3 left sides, represented from common rail 114 through the reflected pressure ripple of first paragraphs 3.1 to the path of sparger 1.
By the explanation of Fig. 1 is explained, pressure wave is reflex time experience sign reversing on common rail 114, so that become increased pressure from pressure decreased as.
As appreciable by the p-x plotted curve I and the II that relatively are arranged in second segment 3.2 the right, the sign reversing of amplitude does not occur when pressure wave reflex time on the end 9 of sealing, in other words, pressure decreased is only reflection on closed end 9, and namely it changes its direction of propagation but does not change its symbol.If in Fig. 3 with meeting each other in the there that first paragraph 3.1 and second segment 3.2 pass in the 3rd section 3.3 the p-x plotted curve of II mark pressure wave at this moment, then these pressure waves are offset fully owing to their different symbols, so that no longer there is pressure wave in the 3rd section 3.3 and in sparger 1.
Embodiment illustrated in fig. 4 to a great extent corresponding to embodiment shown in Figure 3, wherein, only in second segment 3.2, be provided with a restriction 11.Be connected to sparger 1 on the 3rd section 3.3 at Fig. 4, do not illustrate for the position reason in 5,6 and 7.
By restriction 11, pressure wave is attenuated in second segment 3.2, so that the fully counteracting of pressure wave no longer occurs in the bifurcation of first paragraph 3.1 and second segment 3.2.But this to compare obvious shortcoming may be favourable with Fig. 3 embodiment under the applicable cases of determining, at first is when the modern fuels injection apparatus work of considering to have multi-injection and when the very large speed range of internal-combustion engine is carried out such multi-injection.Because the speed range of internal-combustion engine is wide, the time lag of multi-injection is very not identical yet, decides on internal-combustion engine rotational speed.By in second segment 3.2, settling restriction 11 according to the present invention, can improve on the whole in some cases on the whole speed range and all load conditions under the internal combustion engine operation situation, even when certain POL and rotating speed, may not can reach the fully counteracting of pressure wave.
In the embodiment according to Fig. 5, restriction 11 is not arranged in the second segment of pipeline 3, but it interconnects first paragraph 3.1 and second segment 3.2 on the contrary.Because the pressure wave that leaves from sparger has identical symbol the first paragraph of pipeline 3 and second segment, restriction affect-does not produce pressure reduction to this ripple on restriction.But on common rail or at the ripple that the closed end of second segment reflects, has different symbols.If it arrives restriction 11, the pressure balance of decay then occurs between first paragraph and second segment and reflected wave is with the form that strongly weakens but have the reciprocal symbol of continuation and advance to merging the position thus, they are offset fully there.In the embodiment of Fig. 6, second segment 3.2 also is at the 3rd section 3.3 hydraulic connecting between the rail 114 together, but wherein has a restriction 11 and a safety check 13 in second segment 3.2.Safety check 13 allows fuel to reflux to common rail from second segment 3.2.In 13 cut-offs of other direction upper check valve.This safety check keeps cutting out when the subtractive pressure wave of tool arrives, thereby forms the closed end that this ripple is had constant function.
Arrive on the safety check if having on the contrary the pressure wave of positive sign, then this valve is opened, and the pressure wave experience is as the restriction 11 of duct end, and it or reflection on this restriction are perhaps only reflected very weakly.
In the embodiment according to Fig. 7, high pressure pipe line 3 again single type ground is realized and is had a zone 3.4 that a diameter is widened.In the embodiment shown in fig. 7, zone 3.4 taper configurations that diameter is widened wherein have larger-diameter end and pass in the common rail 114.But the present invention is not limited to the diameter of taper and widens, but also can comprise for example step-like or without ladder but nonlinear diameter widen.An important result in the zone 3.4 that this diameter is widened is, the pressure wave that makes arrival is not that impact type ground reflects at pipe end, but the zone 3.4 that it is widened by whole diameter is partly reflected.Arriving altogether the residual pressure ripple of rail 114 reflects in the previous mode that illustrated there and changes its symbol.By the part reflection of pressure wave in the zone 3.4 that diameter is widened, " smoothing " of pressure wave profile directly occurs there, it shows as echo amplitude and descends (seeing the leftmost p-x plotted curve of Fig. 7), particularly shows as the much milder edge dp/dt of reflected pressure ripple.Like this, the result is that the pressure surge of sparger 1 inside reduces owing to this reflected wave and extends in the longer time period.Like this, the result so that the interval between twice injection the impact of spraying is for the second time obviously reduced, thereby improved the measuring accuracy of emitted dose.
Claims (14)
1. be used for the fuel injection system of internal-combustion engine, the high pressure pipe line (3) of fuel is provided for sparger (1), wherein, this high pressure pipe line (3) is comprised of a first paragraph (3.1) and a second segment (3.2), and, first paragraph (3.1) and second segment (3.2) are connected in parallel, it is characterized in that, first paragraph (3.1) has a unlimited end, second segment (3.2) has the end of a sealing, and, merge in this first paragraph (3.1) and the zone of this second segment (3.2) on being connected to sparger (1), and, the length (L of first paragraph (3.1)
1) and the length (L of second segment (3.2)
2) basic identical.
2. high pressure pipe line according to claim 1 is characterized in that, is provided with a restriction (11) in second segment (3.2).
3. high pressure pipe line according to claim 2 is characterized in that, is provided with a safety check (13) that is connected in series with restriction (11) in second segment (3.2).
4. high pressure pipe line according to claim 3 is characterized in that, this safety check (13) and restriction (11) are placed on the end of second segment (3.2) and this safety check allows fuel to flow out from second segment (3.2).
5. according to the described high pressure pipe line of one of aforementioned claim, it is characterized in that, first paragraph (3.1) and second segment (3.2) are by a restriction (11) hydraulic connecting.
6. according to claim 1 to one of 4 described high pressure pipe lines, it is characterized in that, this high pressure pipe line (3) has one the 3rd section (3.3), and not only first paragraph (3.1) but also second segment (3.2) all pass in the 3rd section (3.3).
7. according to claim 1 to one of 4 described high pressure pipe lines, it is characterized in that the hydraulic diameter (D of first paragraph (3.1)
1) and the hydraulic diameter (D of second segment (3.2)
2) basic identical.
8. high pressure pipe line according to claim 6 is characterized in that, the hydraulic diameter (D of first paragraph (3.1)
1) and the hydraulic diameter (D of second segment (3.2)
2) and substantially equal the hydraulic diameter (D of the 3rd section (3.3)
3).
9. according to claim 1 to one of 4 described high pressure pipe lines, it is characterized in that, an end of the first paragraph (3.1) of this high pressure pipe line (3) has a diameter widening portion (3.4).
10. high pressure pipe line according to claim 9 is characterized in that, the diameter of this high pressure pipe line (3) continues to increase in the zone of diameter widening portion (3.4).
11. high pressure pipe line according to claim 9 is characterized in that, this diameter widening portion (3.4) truncated cone shape structure.
12. high pressure pipe line according to claim 9 is characterized in that, the diameter of this high pressure pipe line (3) stepped shaft in the zone of diameter widening portion (3.4) increases.
13. according to claim 3 or one of 4 described high pressure pipe lines, it is characterized in that, the described unlimited end of first paragraph (3.1) is connected on the common rail (114), is connected 11 with safety check (13) with restriction) section (3.2) also together rail (114) connect.
14. be used for the fuel injection system (102) of internal-combustion engine, having one is total to each sparger (1) of each cylinder of rail (114) and internal-combustion engine and has a high pressure pipe line (3) that will be total to rail (114) and sparger (1) hydraulic connecting, it is characterized in that, this high pressure pipe line (3) is according to the described high pressure pipe line of one of aforementioned claim (3).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2003107871 DE10307871A1 (en) | 2003-02-25 | 2003-02-25 | High pressure line for a fuel injection system |
| DE10307871.1 | 2003-02-25 | ||
| PCT/DE2003/002795 WO2004076846A1 (en) | 2003-02-25 | 2003-08-21 | High-pressure line for a fuel injection system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1745243A CN1745243A (en) | 2006-03-08 |
| CN1745243B true CN1745243B (en) | 2013-05-01 |
Family
ID=32797714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN03826031.XA Expired - Fee Related CN1745243B (en) | 2003-02-25 | 2003-08-21 | High-pressure line for a fuel injection system |
Country Status (5)
| Country | Link |
|---|---|
| EP (2) | EP2230397B1 (en) |
| JP (1) | JP2006514201A (en) |
| CN (1) | CN1745243B (en) |
| DE (1) | DE10307871A1 (en) |
| WO (1) | WO2004076846A1 (en) |
Families Citing this family (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BRPI0613413B1 (en) | 2005-07-18 | 2019-08-27 | Ganser Hydromag | accumulator injection system for an internal combustion engine |
| AT501573B1 (en) * | 2006-06-13 | 2008-05-15 | Avl List Gmbh | HYDRAULIC DEVICE WITH AT LEAST ONE PRESSURE MEMORY |
| DE102005051005A1 (en) * | 2005-10-25 | 2007-04-26 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engine has inflow-side end of valve housing in form of long connection shell deformable by radial forces |
| DE102005060021A1 (en) * | 2005-12-15 | 2007-06-28 | Siemens Ag | Ingested throttle at the ends of high-pressure lines for injection systems |
| AT503660B1 (en) * | 2006-06-13 | 2007-12-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
| DE102007025617A1 (en) | 2007-06-01 | 2008-12-04 | Robert Bosch Gmbh | Fuel injector with low wear |
| DE102008015143A1 (en) * | 2008-03-20 | 2009-09-24 | GM Global Technology Operations, Inc., Detroit | Fuel supply system for motor vehicle, has fuel conveying device and combined fuel distribution line, where two injection lines are connected with combined fuel distribution line |
| FR2929344A3 (en) * | 2008-03-31 | 2009-10-02 | Renault Sas | Fuel return circuit for fuel injecting device in internal combustion engine, has attenuation pipe made of deformable material i.e. rubber, and closed towards one of its ends such that pressure waves introduced in circuit are attenuated |
| AT509877B1 (en) * | 2010-11-02 | 2011-12-15 | Bosch Gmbh Robert | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE |
| JP2013079594A (en) * | 2011-10-03 | 2013-05-02 | Usui Kokusai Sangyo Kaisha Ltd | Common rail type fuel injection system |
| US9272437B2 (en) | 2012-10-31 | 2016-03-01 | Flow International Corporation | Fluid distribution components of high-pressure fluid jet systems |
| JP6031728B2 (en) * | 2013-10-24 | 2016-11-24 | 愛三工業株式会社 | Fuel supply device |
| US9884406B2 (en) | 2014-01-15 | 2018-02-06 | Flow International Corporation | High-pressure waterjet cutting head systems, components and related methods |
| EP3032086A1 (en) * | 2014-12-08 | 2016-06-15 | Wärtsilä Finland Oy | Fuel injection arrangement |
| JP6409685B2 (en) * | 2015-06-03 | 2018-10-24 | 株式会社デンソー | Fuel supply device |
| US10596717B2 (en) | 2015-07-13 | 2020-03-24 | Flow International Corporation | Methods of cutting fiber reinforced polymer composite workpieces with a pure waterjet |
| CN105840373B (en) * | 2016-03-24 | 2019-06-25 | 中国北方发动机研究所(天津) | A kind of device controlling oil spout " water attack " pressure wave |
| CN109268343B (en) * | 2017-07-18 | 2022-02-22 | 罗伯特·博世有限公司 | Method and recording medium for determining a malfunction of an actuator of a hydraulic system |
| DE102017126642A1 (en) | 2017-11-13 | 2019-05-16 | Volkswagen Aktiengesellschaft | Device for reducing pressure wave oscillations in an injection device |
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| FR2786225A1 (en) * | 1998-11-24 | 2000-05-26 | Inst Francais Du Petrole | Pressure fluctuation damping for IC engine direct fuel injection system, comprises series or teed tubes, and/or absorbent inserts, added to injector delivery pipes, or to common rail |
| EP1217202A1 (en) * | 2000-12-22 | 2002-06-26 | Renault | Method of damping pressure waves in a hydraulic pipe and common rail injection system using this method |
| DE10105031A1 (en) * | 2001-02-05 | 2002-08-14 | Bosch Gmbh Robert | Device for damping pressure pulsations in high-pressure injection systems |
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| GB2293412A (en) * | 1994-09-13 | 1996-03-27 | Cummins Engine Co Ltd | Control of turbocharged engine fuel injection |
| JPH1030521A (en) * | 1996-07-12 | 1998-02-03 | Denso Corp | Fuel injector |
| JPH10213045A (en) * | 1996-11-30 | 1998-08-11 | Usui Internatl Ind Co Ltd | Connecting structure for branch connecting body in common rail |
| JPH11200987A (en) * | 1998-01-07 | 1999-07-27 | Toyota Autom Loom Works Ltd | Inertia supercharging system of pressure accumulation type fuel injection system for internal combustion engine |
| SE521406C2 (en) * | 1998-10-23 | 2003-10-28 | Scania Cv Ab | Combustion engine fuel injection device |
| DE19959105A1 (en) * | 1999-12-08 | 2001-06-21 | Bosch Gmbh Robert | Connection piece and housing, in particular high-pressure fuel accumulator, with prestressed welded connection piece for a fuel injection system for internal combustion engines |
| DE10057683B4 (en) * | 2000-11-21 | 2005-10-06 | Robert Bosch Gmbh | Fuel injection system |
| DE10060811A1 (en) | 2000-12-07 | 2002-06-13 | Bosch Gmbh Robert | Fuel injection system for internal combustion engines |
-
2003
- 2003-02-25 DE DE2003107871 patent/DE10307871A1/en not_active Withdrawn
- 2003-08-21 JP JP2004568632A patent/JP2006514201A/en active Pending
- 2003-08-21 WO PCT/DE2003/002795 patent/WO2004076846A1/en active Application Filing
- 2003-08-21 EP EP10007052.3A patent/EP2230397B1/en not_active Expired - Lifetime
- 2003-08-21 EP EP03811301A patent/EP1611342B1/en not_active Expired - Lifetime
- 2003-08-21 CN CN03826031.XA patent/CN1745243B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2786225A1 (en) * | 1998-11-24 | 2000-05-26 | Inst Francais Du Petrole | Pressure fluctuation damping for IC engine direct fuel injection system, comprises series or teed tubes, and/or absorbent inserts, added to injector delivery pipes, or to common rail |
| EP1217202A1 (en) * | 2000-12-22 | 2002-06-26 | Renault | Method of damping pressure waves in a hydraulic pipe and common rail injection system using this method |
| DE10105031A1 (en) * | 2001-02-05 | 2002-08-14 | Bosch Gmbh Robert | Device for damping pressure pulsations in high-pressure injection systems |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2004076846A1 (en) | 2004-09-10 |
| EP1611342A1 (en) | 2006-01-04 |
| EP2230397B1 (en) | 2016-10-12 |
| JP2006514201A (en) | 2006-04-27 |
| EP2230397A1 (en) | 2010-09-22 |
| EP1611342B1 (en) | 2012-02-29 |
| CN1745243A (en) | 2006-03-08 |
| DE10307871A1 (en) | 2004-09-02 |
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