CN1155324A - Fuel injector for IC engine - Google Patents
Fuel injector for IC engine Download PDFInfo
- Publication number
- CN1155324A CN1155324A CN95194557A CN95194557A CN1155324A CN 1155324 A CN1155324 A CN 1155324A CN 95194557 A CN95194557 A CN 95194557A CN 95194557 A CN95194557 A CN 95194557A CN 1155324 A CN1155324 A CN 1155324A
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- China
- Prior art keywords
- pressure
- piston
- pressure chamber
- spring
- fuel
- 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.)
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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
- 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
- F02M61/08—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 the valves opening in direction of fuel flow
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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
- 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
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
- F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
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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
A fuel injector (1) has a through-going fuel passage (6) opening out into a nozzle (7). A compression spring (17) acts on a longitudinally displaceable valve slider (13) in the closing direction. A first piston (21) at one end of the compression spring delimits, together with a stationary component (9), a first pressure chamber (28) which communicates with the fuel passage (6) through a channel (24). A second pressure chamber (34) is delimited by the first piston and a second piston (29). When the first piston is pressed away from an extreme position with a minimum volume in the chamber by the fuel pressure in the first pressure chamber, a flow connection (35) is opened between the two chambers so that pressure is built up in the second pressure chamber. The pressure build-up in the chambers generates an automatic loading of the compression spring. The oil confined in the second chamber keeps the compression spring loaded while the fuel injector is in its closed position.
Description
The present invention relates to fuel injector for IC engine, the oil sprayer of large two-stroke diesel engine especially, it has one and is loaded on shell in the cylinder cap and the fuel gallery in feeding nozzle that runs through; A valve slider, this slider can in a slider guiding element, vertically move and by pretensioned spring towards the valve seat direction application of force, and in the opposite direction by the fuel pressure application of force in the fuel gallery; In housing, can move axially and be positioned at an end of this pressure spring and have a first piston away from the first surface of this spring, this piston has constituted first pressure chamber that is communicated with the fuel gallery by a passage with fixed block, described pressure spring bias voltage first piston is to a limit position, the fuel oil volume minimum in this moment first pressure chamber.
This corresponding to the described oil sprayer of Japan Patent No.152619 in, the channels designs from the fuel gallery to first pressure chamber becomes throttling passage, makes the pressure of pressure chamber depend on the flowing pressure in the fuel gallery and have a hysteresis.When fuel pressure between injection period increased, the pressure the pressure chamber in also increased, and made first piston be pressed towards closing spring thereby increase spring towards the power of valve seat directive effect on the valve slider, and this has just increased the closing pressure of this oil sprayer.
This has just solved such problem, closing pressure, i.e. and pressure when fuel injection period finishes the valve slider towards its valve seat motion usually less than cracking pressure, promptly begins valve slider pressure in the fuel gallery when its valve seat lifts at fuel injection period.The reason that closing pressure is lower is: in the closed position of oil sprayer, it is little when being in the enable possition than valve slider that fuel pressure acts on useful area on the valve slider, because in the enable possition, pressure also acts on the following valve slider surface of valve base surface.
In the described oil sprayer of Danish Patent, between the oil sprayer fuel injection period, reach following closely, first piston is constantly adjusted motion, and this has just caused producing the wearing and tearing of can not ignore on this piston guide surface, has increased the leakage of pressure chamber thereupon.After each fuel injection period finished, pressure spring pushed back its limit position with first piston, this moment pressure chamber's fuel oil volume minimum, thereby the not hydraulic pressure of the spring load influence by compression of the cracking pressure of oil sprayer.
As everyone knows: the compression pressure in the engine cylinder depends on the load of motor, so the pressure when in-cylinder pressure is much higher than low-load at full capacity the time.For example, when full load, compression pressure can be about 120 crust, and this compression pressure then has only about 40 crust when unloaded.
When the valve slider was in its closed position, engine cylinder pressure was by the nozzle bore transmission and further be delivered on the slider surface below the valve base surface, promptly was in the slider part of the nozzle side of valve seat.Therefore, current compression pressure applies an active force at opening direction and acts on the valve slider.Thereby the compression pressure that increases along with engine load causes the injection starting pressure of known oil sprayer when engine load increases to descend.In the typical oil sprayer that for example in large two-stroke diesel engine, uses, 325 crust when 400 crust when this cracking pressure may be from zero load drop at full capacity.This injection starting pressure lower when full load can not improve the atomizing at fuel injection period initial stage fuel oil.
To low engine load, to supply with the fuel oil of minute quantity so that the flow resistance in the nozzle when oil pump fuel pressure is not existed when influence, the fuel pressure in the oil sprayer is determined by its injection starting pressure.Opposite with this, because the very big consequently oil sprayer intermediate fuel oil pressure of the oil mass that oil pump is supplied with is decided by the flow resistance in the nozzle, promptly in this case, fuel pressure is much higher than the injection starting pressure of oil sprayer when higher engine load.
In known oil sprayer, its injection starting pressure is by the decision of the preload of pressure spring.There is certain manufacturing tolerances in this spring when making, and has identical injection starting pressure thereby cause oil sprayer in the internal-combustion engine to differ to establish a capital accurately to set.After the long-term work of motor, because spring becomes lax when work, promptly its spring force becomes smaller, and it is more and more obvious that the variation of the injection starting pressure of oil sprayer just becomes.Therefore, oil sprayer if spray pressure exists the variation by service time decision, work satisfactorily in order to make motor, just need regularly control and tighten this pressure spring.This be require great effort very much and do not wish to take place.
The purpose of this invention is to provide a kind of oil sprayer that also increases and need hardly to safeguard with engine load increase injection starting pressure.
According to this purpose, being characterised in that of oil sprayer of the present invention: spring is connected with the second piston implementation power transmission, and this second piston has a second surface that deviates from this spring and constitute second pressure chamber's end wall; First piston makes the mobile joint between first pressure chamber and second pressure chamber open-minded when moving away from the direction of described limit position on the edge; The effective cross section of second pressure chamber is bigger than first pressure chamber; Affined draining passage links to each other this second pressure chamber with draining portion.
As mentioned above, when engine load increased, because the flow resistance in the nozzle, the pressure in the fuel gallery increased.Therefore, the pressure in first pressure chamber also increases, and this has just caused the mobile joint unlatching between moving of first piston so that this first and second pressure chamber, and fuel oil flows into second pressure chamber.Because the effective cross section of this pressure chamber is bigger than first pressure chamber, therefore the pressure of setting up in second pressure chamber makes first piston get back to the limit position that it has minimum fuel oil volume, and the amount of fuel in second pressure chamber is constrained because of first piston blocks the joint that flows between this two pressure chamber simultaneously.When second piston and spring carried out the power transmission and be connected, this spring was along with the full and corresponding shortening of each chamber, thereby spring force increases.Except a spot of fuel oil drains, other fuel oil all is limited in the pressure chamber, up to oil sprayer start again carry out new fuel injection till, therefore the spring force that increases is maintained, this just makes this oil sprayer not only have higher injection starting pressure but also have higher closing pressure.
If the maximum pressure between next injection period in the fuel gallery, because of the engine load increase becomes higher, then the fuel pressure of first pressure chamber will form a power that acts on the first piston, the spring force that this force rate is opposite is bigger, this has just caused this first piston to move, so the mobile joint between two pressure chambers is open-minded, the pressure of setting up in second pressure chamber produces till the pressure of an increase, and the fuel pressure that acts on the effective cross section of pressure ratio first pressure chamber of this increase is higher slightly.Then, the spring force of increase makes first piston be returned to its limit position again, blocks the mobile joint between two pressure chambers.
Affined draining passage is constantly discharged a spot of fuel oil from second pressure chamber.This load that has just guaranteed spring when the MTP in engine load and the fuel gallery descends also reduces.If engine load does not descend, then draining the amount of fuel of walking will be replaced by the new fuel oil between next injection period, make little pressure drop of formation in second pressure chamber owing to drain the fuel oil of walking, so first piston can be opened this mobile joint again.
The oil sprayer injection starting pressure in a certain concrete when load depends on the net sectional area of first pressure chamber in the high-load range of motor.Because this cross section can be with very little tolerance manufacturing, and the variation and the difference during operation thereof by the decision of manufacturing factor of the elastic characteristic aspect of pressure spring relax and will be compensated by length of spring compressed, up to this spring produce with the corresponding spring force of high fuel pressure of oil sprayer till, so all oil sprayers in the motor will be adjusted voluntarily and have identical injection starting pressure and identical closing pressure.This adjustment occurs in during the engine operation automatically, thereby has got rid of the needs to the regular manual tune of oil sprayer to a great extent.
Can design mobile joint with a side perforate, this side perforate can be covered or open when its displacement by first piston, but preferably this first piston has a valve seat, and this valve seat part partly contacts and the mobile joint between this first and second pressure chamber is stopped with respective valve seat on the fixed block.For many years, these valve seat part in the oil sprayer all be proved to be reliably and they produced can Chinese People's Anti-Japanese Military and Political College pressure reduction excellent sealing.
The size of draining passage can suitably be restricted to, and during an engine cycles, the fuel oil volume of being let out away when the motor full load is 1/2nd to 1/20th of second pressure chamber's intermediate fuel oil volume.If the fuel oil of letting out away surpasses 1/2nd, then be difficult to obtain the ideal increase of injection starting pressure, especially all the more so when engine low load, in addition, since when engine load is constant, all oilings again between each fuel injection period of second pressure chamber, and the motion amplitude of piston is bigger and more frequent.If the volume of the oil of draining is less than 1/20th, then injection starting pressure will slowly reduce when engine load reduces suddenly inadequately.Above-mentioned draining ratio is suitable for the motor full load.
In one embodiment, the net sectional area of first pressure chamber is littler than the opening area of valve slider.Consequently: when the injection starting pressure decision of fuel pressure by oil sprayer, and an injection starting pressure machinery by spring preloads when producing, and to low engine load, first piston will remain on the limes superiors position.Have only when fuel pressure when starting load to increase to rise, act on pressure on the net sectional area of first pressure chamber and just produce one and overcome spring force and make first piston move apart the power of its limit position.
The net sectional area of second pressure chamber cans be compared to most big several times of the net sectional area of first pressure chamber.Consequently: when second piston action on spring and the power on the first piston of therefore acting on when equaling fuel oil and acting on power on the first piston in the other direction, the pressure of pressure ratio first pressure chamber in second pressure chamber is correspondingly little several times.Therefore the big net sectional area of second pressure chamber causes this second pressure chamber to close when favourable low chamber pressure, and this just makes the very little and amount of fuel that drain from second pressure chamber of the pressure drop of draining passage also seldom.The big net sectional area of second pressure chamber has also brought such advantage, promptly has the amount of fuel of large volume to inject this chamber when a certain displacement place of second piston and the corresponding compression of spring.Both of these case helps all that spring force only changes slightly when oil sprayer is in closed position between two fuel injection periods.
Because relatively the first piston parts that are in stationary state are made of the valve slider, therefore two pistons might be positioned spring near the end of nozzle.The result of this design is: each piston participates in the adjustment campaign of this valve slider.In this case, each piston will play the effect of the quality that increases this slider, and this will make the oil sprayer adjustment movement slower.Owing to it has been generally acknowledged that this is a kind of shortcoming, so this first piston can alternatively be formed at the opposed end of spring.This has just caused such shortcoming, and promptly the mobile joint between two pressure chambers becomes elongated, and quite is difficult to make.In a preferred embodiment, avoid these shortcomings and simplified manufacturing, this oil sprayer is fabricated to feasible: in a manner known way pressure spring is contained between two spring guide pieces, this guiding element can vertically move on a center thrust piece that is fixed in the housing; Second piston is made on the upper spring guiding element, this guiding element is in the relative position of nozzle, and seal up with having a wiper seal the following tubular wall of this thrust piece and one than footpath within this lower wall bigger and wiper seal seal the last tubular wall of first piston, middleware couples together this two wall, and the upper surface of this middleware constitutes second surface; First piston be annular and be packaged between the upper wall of the thrust piece and second piston, and have inwardly lower protruding edge, the upper surface of this flange has constituted first surface, this surface upcountry is incorporated in the valve seat part; The respective valve seat of thrust piece partly faces down, and at the passage that extends through the fuel gallery with constitute between the lower area that the diameter of the mobile joint between this two pressure chamber reduces.
The draining passage can form an independent component, for example is the little boring form that pierces second pressure chamber by second piston, but this draining passage preferably is made of two walls and the annular of the wiper seal between first piston and the thrust piece slit of second piston respectively.These narrow annular slots in fact be difficult to make fully wiper seal.Draining the amount of fuel of walking will be lubricated the surface that slides relative to one another simultaneously.
Explain the example of the present invention's mode of execution in more detail hereinafter with reference to accompanying drawing, wherein:
Fig. 1 represents the partial, longitudinal cross-sectional of oil sprayer of the present invention;
The enlarged view of the part of pressure spring and associated part is described in Fig. 2 presentation graphs 1;
Fig. 3 is respectively injection starting pressure and the injection starting pressure that reaches oil sprayer of the present invention between the engine load and the graph of a relation between the engine load of the oil sprayer of known type.
Fig. 1 represents a kind of oil sprayer, and its integral body is represented by label 1, and had a frame 2 that is used for being contained in the cylinder cap.This housing be elongated and its upper end have one to the side outstanding and be connected in supporting member 3 on the cylinder cap by bolt, the contact surface 4 of its lower end is pressed on the corresponding contact surface that is formed on the cylinder cap.The fuel source of an oil pump (not shown) or a similar cycle supply high pressure fuel is connected on the fuel inlet 5 at place, oil sprayer top by high-pressure oil pipe, from here, fuel gallery 6 is passed this oil sprayer center and is arrived down in the nozzle 7 that has a central lumen 8, and the spray orifice (not shown) is provided with so that fuel oil sprays into cylinder from this nozzle 7 radiation ground.
This fuel gallery can have a valve, and this valve opens that heating oil enters in the oil sprayer so that make in advance between each injection period.The fixed component of thrust piece 9 forms is passed in this fuel gallery, and this thrust piece is contact member 10 up, and this element 10 is fixed in housing; This thrust piece 9 contacts middleware 11 down, and this middleware 11 is pressed on the slider guiding element 12 that is fixed in this housing securely.Valve slider 13 is installings like this, promptly can vertically move in its centre pilot hole 12 ' in the slider guiding element, and by the one end cylindrical part 11 ' outstanding down on the middleware be surrounded.This this slider of pilot hole centering, thus be positioned at this valve slider lower end and form the annular taper valve base surface 14 of an aciculiform portion coaxial with the respective valve seat on this slider guiding element 12.When this valve slider is in its closed position, and when its valve base surface is pressed against on the valve seat on the sliding guide piece, the tip of this aciculiform portion protrudes in the central cavity of nozzle, and be subjected to the effect of cylinder pressure of engines, this cylinder is pressed and is imported cavity into and apply a power on this valve slider at opening direction by nozzle bore.The lower end of valve slider and slider guiding element 12 limits and constitutes a pressure chamber 15 that is communicated with fuel gallery 6 by inclined hole 16.This valve slider annular end face is down defined by this aciculiform portion and forms, and when fuel pressure when opening direction effect one power is on the valve slider, this annular end face is subjected to the fuel pressure effect in the chamber 15.The open area of this valve slider is to be determined by the difference between the inner diameter of the outer diameter of cylindrical part 11 ' and pilot hole 12 ' basically.
This valve slider is the downward direction effect of being under pressure towards valve seat by pressure spring 17 in closing direction, end contacts with upper spring guiding element 18 on being contained in thrust piece 9 movably on this spring, and its lower end is bearing on this thrust piece 9 by the also lower spring guiding element 19 of removable guiding.By means of the thrust sleeve of a trough of belt, under this time guiding element 19 surface with valve slider 13 on contact towards upper flange.Therefore this spring force is passed to this valve slider 13 through spring guide piece 19 and thrust sleeve 20.
Annular first piston 21 is provided with movably around the upper axial of this thrust piece 9.The internal diameter of the slidingsurface 22 (Fig. 2) of this piston keeps suitable cooperation with the relative guide surface 23 on the thrust piece by following mode, and promptly the annular space between this two surface keeps sufficiently little, so that this piston encloses this thrust piece by the sealing means envelope.This guide surface 23 ends at one downwards and is arranged on the thrust piece and by in a passage 24 and the cylindrical depression that fuel gallery, center 6 in this thrust piece is communicated with.This depression is incorporated its outer diameter downwards into than in the little column part 25 of the diameter of this guide surface 23.Under this part 25, thrust piece has a ring-type sloped footing part 26 down.
This first piston 21 has a flange inwardly 27 by the bottom, and this flange 27 has a sloped footing part 26 ' up of being abutted against on base portion 26 with can relying on wiper seal.With this depression and column part 25 zone shoulder to shoulder, first piston and thrust piece have defined first pressure chamber 28, the net sectional area of this chamber is determined by the diameter difference between column part 25 and the guide surface 23.This effective cross section is positioned on the upper surface of this flange 27, promptly is on the first surface away from spring, so the fuel pressure of supplying with by the passage in this first pressure chamber 24 acts on the first piston, the power that applies is downward.
The bottom side of flange 27 can have one or more bumps or an annular protrusion that has otch, when side on this bump and the middleware 30 in abutting connection with the time, this otch makes part second pressure chamber 34 and the projection radially aligned keep being communicated with the mobile of attachment portion 35 that flow.(not shown) in the another one alternate embodiment, this bump can be a ring-type, and the diameter of the inboard of lower wall 31 can be less than the diameter of the inboard of flange 27, has up effective cross section so be positioned at the part of second pressure chamber of the most close joint 35 that should flow, when the bump on this flange 27 is resisted against the upside of this middleware 30 and stops when being connected with the other parts of pressure chamber 34, this cross section convection current part 35 that is dynamically connected is opened.Utilize the suitable voltage rise in the joint 35 that flows, this effective cross section will make second piston 29 move apart first piston 21 and open whole effective cross sections of second pressure chamber simultaneously.
The draining passage Continuous Contact of second pressure chamber 34 and constraint, this passage is made of the annular groove of wiper seal between the cylindrical outer side of the inboard of upper wall 32 and first piston and the inboard of lower wall 31 and the wiper seal formula circular groove between the guide surface on the thrust piece 33.
Now illustrate then how this two-piston automatically makes pressure spring 17 produce desirable elastic force.Work as engine cut-off, and fuel gallery 6 is not when pressurizeing, and two-piston is in position shown in the figure, and pressure spring 17 compressings second piston 29 that is added with load this moment in advance upwards, so that with first piston 21 against living, thereby by base portion 26 and 26 ' elastic force is passed to thrust piece 9.
When engine start and load increased, between each injection period, the pressure in the fuel gallery 6 rose to maximum pressure, and this pressure corresponding to the injection starting pressure of oil sprayer, and is determined by the flow resistance in the nozzle bore when high load when low-load.Therefore the pressure maximum in the fuel gallery increases with engine load.
Pressure in the fuel gallery 6 is passed to first pressure chamber 28 by passage 24, and when pressure reaches certain level, downward power on the first piston can overcome the preset force of spring, first piston is shifted to spring, this spring compresses between spring guide piece 18 and 19, simultaneously the flow through joint 35 that flows of fuel oil enters second pressure chamber, and this indoor pressure is raised to and makes first piston 21 be returned to the level that contacts with base 26, and second piston 29 remains on the position that this spring is applied additional load.
If the pressure between follow-up injection period in the fuel gallery 6 increases to higher level, then piston motion is carried out repeatedly, thus spring be subjected to one with fuel gallery 6 in the linear load of pressure maximum.
By pressure-tight circular groove, a spot of fuel oil constantly excretes from second pressure chamber, and the inner chamber of this fuel oil in housing 2 flows to (not shown) in the draining hole.
By this mode, oil sprayer of the present invention obtains a spring force and obtains an injection starting pressure as shown in Figure 3 thus, and this injection starting pressure increases with engine load.This just makes the injection starting pressure in the time of might reducing low engine load, and this oil sprayer required high injection starting pressure can automatically be created at full capacity the time.Therefore, this pressure spring can prefabricatedly have one and preload, this preloads the injection starting pressure that produces about 200 crust when low-load, this pressure makes motor working stability when sub load, and injection starting pressure is higher than the injection starting pressure of known oil sprayer when full load, the good atomizing of fuel oil when this has just promoted injection beginning.
Replace above-mentioned center path, this fuel gallery 6 also can comprise some passages by known mode, and extend in these passages outside along this spring in fixing middleware, and be opened on pressure chamber 15 through the slanted channel in the slider guiding element.Use this design, the open area of this valve slider is by the downward annular end face decision of cast-over shape portion.
Claims (7)
1. the oil sprayer of an internal-combustion engine, especially large two-stroke diesel engine, it has: one be loaded on that shell (2) in the cylinder cap and one runs through lead to fuel gallery (6) in the nozzle (7); The valve slider (13) that can in slider guiding element (12), vertically move, this slider by a preload pressure spring (17) towards the valve seat direction application of force and by the application of force in the opposite direction of the oil pressure in the fuel gallery; In housing, can move axially and be positioned at the first piston (21) of an end of this pressure spring, this piston has a first surface away from this spring, this piston is determined first pressure chamber (28) that is communicated with described fuel gallery by passage (24) with fixed block (9), described pressure spring is exerted pressure to this first piston, direction is towards a limit position, the fuel oil volume minimum in this first pressure chamber of this limit position; It is characterized in that: this spring is connected with one second piston (29) confining force transmission; This second piston has a second surface that deviates from this spring and constitute the end wall of second pressure chamber (34); When moving away from described limit position in court, opens this first piston (21) the mobile joint (35) between this first and second pressure chamber; The net sectional area of this second pressure chamber (34) is bigger than the net sectional area of first pressure chamber (28); And the draining passage of constraint connects this second pressure chamber and draining portion.
2. oil sprayer according to claim 1 is characterized in that: described first piston (21) have this base portion of base portion (26 ') by with fixed block on respective seat part (26) contact the mobile joint of blockading between described first and second pressure chambers (35).
3. oil sprayer as claimed in claim 1 or 2 is characterized in that: the size restrictions of this draining passage is 1/20th to 1/2nd of second pressure chamber (a 34) internal combustion oil volume for the fuel oil volume of draining away during when the motor full load in cycle period at motor.
4. as oil sprayer as described in each among the claim 1-3, it is characterized in that: the effective cross section of first pressure chamber (28) is less than the opening area of this valve slider.
5. as oil sprayer as described in each among the claim 1-4, it is characterized in that: the effective cross section of this second pressure chamber (34) is than big several times of the effective cross section of first pressure chamber (28).
6. as oil sprayer as described in each among the claim 1-5, it is characterized in that: by known mode, this pressure spring (17) is loaded between two spring guide pieces (18,19), and this two guiding element can vertically move on the center thrust piece (9) in being fixed in housing; This second piston (29) is formed on the upper spring guiding element (18), this guiding element (18) relatively is provided with nozzle (7) and has a wiper seal ground and seals following tubular wall (31) and last tubular wall (32) that encloses this thrust piece, within this upper wall (32) diameter than the inner diameter of lower wall big and wiper seal ground envelope enclose this first piston (21), middleware (30) connects two walls, and the surface constitutes second surface on this middleware; This first piston (21) be annular and the upper wall that is enclosed in this thrust piece and this second piston between, first piston also has a lower protruding edge (27) inwardly, the surface constitutes first surface on this flange (27), and this first surface is incorporated into base portion (26) inwardly; The respective seat of this thrust piece part (26) faces down, and is positioned at a penetrating via (24) that leads to fuel gallery (6) and one between the lower area that the diameter that constitutes the joint (35) that flows between two pressure chambers reduces.
7. as oil sprayer as described in the claim 6, it is characterized in that: this draining passage comprises two walls (31,32) and the annular of the wiper seal between this first piston (21) and this thrust piece (9) slit that lays respectively at this second piston.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK092794A DK171216B1 (en) | 1994-08-09 | 1994-08-09 | Fuel injector for an internal combustion engine |
| DK0927/1994 | 1994-08-09 | ||
| DK0927/94 | 1994-08-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1155324A true CN1155324A (en) | 1997-07-23 |
| CN1060250C CN1060250C (en) | 2001-01-03 |
Family
ID=8099107
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95194557A Expired - Fee Related CN1060250C (en) | 1994-08-09 | 1995-07-11 | Fuel injector for IC engine |
Country Status (14)
| Country | Link |
|---|---|
| EP (1) | EP0733163B1 (en) |
| JP (1) | JP3090473B2 (en) |
| KR (1) | KR970703488A (en) |
| CN (1) | CN1060250C (en) |
| AU (1) | AU3161295A (en) |
| DE (1) | DE69500259T2 (en) |
| DK (1) | DK171216B1 (en) |
| ES (1) | ES2101609T3 (en) |
| FI (1) | FI107470B (en) |
| HR (1) | HRP950445B1 (en) |
| NO (1) | NO306793B1 (en) |
| PL (1) | PL176852B1 (en) |
| RU (1) | RU2126095C1 (en) |
| WO (1) | WO1996005425A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10134868A1 (en) * | 2001-07-18 | 2003-02-13 | Bosch Gmbh Robert | Fuel injector with closing pressure compensation |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB762684A (en) * | 1954-01-20 | 1956-12-05 | David William Edgar Kyle | Improvements in and relating to liquid fuel injection equipment for internal combustion engines |
| DE1122769B (en) * | 1954-05-11 | 1962-01-25 | Nylands Verksted | Device for automatic regulation of the fuel injection point in internal combustion engines |
| DK152619C (en) * | 1984-04-16 | 1988-08-22 | Man B & W Diesel As | FUEL INJECTOR FOR DIESEL ENGINES |
-
1994
- 1994-08-09 DK DK092794A patent/DK171216B1/en not_active IP Right Cessation
-
1995
- 1995-07-11 ES ES95927656T patent/ES2101609T3/en not_active Expired - Lifetime
- 1995-07-11 PL PL95315571A patent/PL176852B1/en unknown
- 1995-07-11 EP EP95927656A patent/EP0733163B1/en not_active Expired - Lifetime
- 1995-07-11 RU RU96118505A patent/RU2126095C1/en active
- 1995-07-11 AU AU31612/95A patent/AU3161295A/en not_active Abandoned
- 1995-07-11 WO PCT/DK1995/000300 patent/WO1996005425A1/en active IP Right Grant
- 1995-07-11 CN CN95194557A patent/CN1060250C/en not_active Expired - Fee Related
- 1995-07-11 KR KR1019960706534A patent/KR970703488A/en not_active IP Right Cessation
- 1995-07-11 DE DE69500259T patent/DE69500259T2/en not_active Expired - Fee Related
- 1995-07-11 JP JP08506931A patent/JP3090473B2/en not_active Expired - Fee Related
- 1995-08-09 HR HR950445A patent/HRP950445B1/en not_active IP Right Cessation
-
1996
- 1996-07-22 FI FI962931A patent/FI107470B/en active
-
1997
- 1997-02-04 NO NO970494A patent/NO306793B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| PL315571A1 (en) | 1996-11-12 |
| FI962931A (en) | 1996-07-22 |
| NO970494L (en) | 1997-02-04 |
| WO1996005425A1 (en) | 1996-02-22 |
| FI962931A0 (en) | 1996-07-22 |
| HRP950445B1 (en) | 2000-08-31 |
| CN1060250C (en) | 2001-01-03 |
| AU3161295A (en) | 1996-03-07 |
| NO306793B1 (en) | 1999-12-20 |
| DE69500259T2 (en) | 1997-11-06 |
| KR970703488A (en) | 1997-07-03 |
| NO970494D0 (en) | 1997-02-04 |
| RU2126095C1 (en) | 1999-02-10 |
| DE69500259D1 (en) | 1997-05-28 |
| EP0733163B1 (en) | 1997-04-23 |
| EP0733163A1 (en) | 1996-09-25 |
| HRP950445A2 (en) | 1997-04-30 |
| JPH10503820A (en) | 1998-04-07 |
| DK171216B1 (en) | 1996-07-29 |
| ES2101609T3 (en) | 1997-07-01 |
| JP3090473B2 (en) | 2000-09-18 |
| PL176852B1 (en) | 1999-08-31 |
| DK92794A (en) | 1996-02-10 |
| FI107470B (en) | 2001-08-15 |
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