EP2132434A1 - Kraftstoffeinspritzsystem sowie druckverstärkungseinrichtung für ein kraftstoffeinspritzsystem - Google Patents
Kraftstoffeinspritzsystem sowie druckverstärkungseinrichtung für ein kraftstoffeinspritzsystemInfo
- Publication number
- EP2132434A1 EP2132434A1 EP08701662A EP08701662A EP2132434A1 EP 2132434 A1 EP2132434 A1 EP 2132434A1 EP 08701662 A EP08701662 A EP 08701662A EP 08701662 A EP08701662 A EP 08701662A EP 2132434 A1 EP2132434 A1 EP 2132434A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel
- chamber
- compression
- injection system
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/022—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type having an accumulator storing pressurised fuel during pumping stroke of the piston for subsequent delivery to the injector
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/16—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps characterised by having multi-stage compression of fuel
Definitions
- the invention relates to a fuel injection system according to the preamble of claim 1 and to a pressure boosting device according to the preamble of claim 4.
- a fuel injection system for an internal combustion engine with a fuel high-pressure accumulator (common rail) and a plurality of injectors each having a pressure boosting device is known, wherein in the fuel delivery direction between the high-pressure fuel accumulator and the injectors a compensation device for minimizing pressure oscillations is arranged ,
- the large number of pressure boosters required for the realization of high injection pressures beyond 2000 bar is disadvantageous.
- Another disadvantage is the high space requirement of the entire injection system due to the large number of pressure amplifiers required.
- a further fuel injection system is known from EP 1 123 463 B1, in which a central pressure boosting device is realized, the pressure boosting device being arranged in the fuel delivery direction between the high-pressure fuel reservoir and the injectors.
- the pressure boosting device By means of a distribution device downstream of the pressure boosting device, the compressed fuel is produced distributed directly to the individual injectors.
- the disadvantages are the pressure oscillations in the high-pressure line system caused by the central pressure boosting device, which have a negative effect on the injection quantity measurement.
- the invention is therefore based on the object to propose a fuel injection system for an internal combustion engine with a central pressure boosting device in which the pressure oscillations in the high pressure line system are minimized. Furthermore, the object of the invention is to propose a pressure boosting device for a fuel injection system, which causes only slight pressure oscillations.
- the invention is based on the idea of arranging a central pressure boosting device, ie a pressure boosting device associated with at least two injectors, in the fuel delivery direction between the high-pressure fuel pump and the high-pressure fuel accumulator so that the fuel compressed by the pressure boosting device coincides a pressure of generally over 2500 bar is not directly conveyed to at least two injectors, but first in a high-pressure fuel storage (common rail). For this, the fuel is then distributed in a conventional manner to the injectors for injection into the combustion chambers of the internal combustion engine.
- the arrangement of the pressure boosting device in front of the fuel high-pressure accumulator has the advantage that the high-pressure fuel accumulator acts as a buffer, whereby any pressure oscillations are minimized.
- a differential pressure amount (control amount) of fuel from the pressure booster device in a low pressure region of the fuel injection system can be controlled.
- differential pressure chambers of the pressure amplification device which are still to be explained later, can be hydraulically connected to a low-pressure region of the injector. It is conceivable to calculate the differential pressure either directly in front of the high-pressure fuel pump and after For measuring the suction of the high-pressure fuel pump or in the direction of fuel delivery before the metering unit, return it to the fuel circuit.
- a fuel buffer is arranged in the fuel delivery direction after the high-pressure fuel pump and in front of the hydraulic pressure boosting device.
- the pressure boosting device is characterized in that it has at least two compression spaces which can be operated in an alternating compressive manner.
- the compression chambers are coupled such that the fuel pressure and the fuel volume during a refilling operation of the first compression space for compressing the fuel in the second compression space is utilized, ie the first compression space forms a control chamber for compression of the fuel in the second compression space.
- the second compression space in its refill phase forms a second control space for compressing the fuel in the first compression space.
- the realization of the described double-acting pressure boosting device makes, among other things, a improved controllability of the high pressure region of the fuel injection system achieved.
- each compression chamber is associated with a differential pressure chamber, which is acted upon for purposes of compression of the fuel in the associated compression chamber with low pressure, so that the compressive force acting as a control chamber compression space counteracting compressive force is reduced, which as a result, minimizing the volume of the compression space and, associated therewith, increasing the fuel pressure in the compression space.
- the two compression chambers of the pressure amplifying device are coupled to one another via a common pressure piston, which alternately compresses the fuel in the two, preferably opposite compression chambers, that is, is adjustable alternately into two opposite axial directions.
- a common pressure piston which alternately compresses the fuel in the two, preferably opposite compression chambers, that is, is adjustable alternately into two opposite axial directions.
- the differential pressure chambers are located on opposite axial sides (end faces) of the pressure piston.
- the common pressure piston arranged as a double hollow piston with two, preferably end, in each case a compression space and / or in each case a differential pressure chamber is formed delimiting hollow chambers.
- a simple double poppet can be used, wherein the compression chambers and / or the differential pressure chambers are preferably formed in this case in a guide housing of the double plunger.
- a control valve is provided for switching each functional unit consisting of compression space and differential pressure chamber, in particular designed as a 3/2-way valve.
- Control valves are actuated, for example, with electromagnetic or piezoelectric actuators.
- first compression chamber is connected to the high-pressure fuel pump and the second compression chamber associated (preferably arranged on the same side of the pressure pin) differential pressure chamber placed on low pressure, so that an adjustment of a pressure piston into the second compression chamber he follows.
- To compress the fuel in the first compression chamber after the completion of the compression process in the second compression chamber is proceeded in an analogous manner.
- each functional unit consisting of compression space and differential pressure chamber are assigned two check valves, wherein fuel can flow via a first check valve from the differential pressure chamber to the associated compression chamber and via a second check valve from the compression chamber to the high-pressure fuel accumulator.
- the embodiment described above makes it possible to connect the control valves, in which the pressure boosting device is deactivated, so that the fuel from the high-pressure pump can be conveyed through the pressure boosting device without triggering the compression function.
- the fuel injection system equipped with a described pressure boosting device can be operated (at least temporarily) without the pressure boosting function. In other words, the fuel can be conveyed through the pressure boosting device.
- At least one differential pressure chamber preferably both differential pressure chambers as radially outer annular spaces and at least one compression space, preferably both compression chambers as central spaces, ie radially inner and preferably axially spaced from the differential pressure chambers spaces are formed.
- this embodiment is due to a greater wall thickness of the hollow piston in terms of increased strength of the pressure booster, with respect to a facilitated manufacturability of the pressure piston and in terms of lower leaks in operation advantageous.
- the transmission ratio of the pressure booster is above 2, a design is preferred in which the arrangement of the differential pressure chambers and the associated compression spaces is reversed, so the compression chambers are designed as annular spaces and the differential pressure chambers as central spaces.
- the housing of the pressure booster from a pressure piston radially outwardly enclosing the housing sleeve and two adjacent to the end faces of the housing sleeve housing components is formed, which preferably by means of a respective union nut which cooperates with an external thread of the housing sleeve, axially against the Housing sleeve are clamped.
- the housing components preferably serve for holding or receiving the control valves and / or the check valves.
- FIG. 1 shows a schematic representation of a fuel injection system for internal combustion engines with a central pressure boosting device
- FIG. 2 shows a schematic representation of a possible construction of a pressure boosting device of the fuel injection system shown in FIG. 1
- FIG 3 shows a schematic representation of a possible construction of an alternative pressure boosting device.
- a fuel injection system 1 is shown for an internal combustion engine, not shown.
- fuel is conveyed by means of a prefeed pump 3 into a low-pressure region 15 of the fuel injection system 1.
- a metering device 4 is used in a conventional manner for suction control of a high-pressure fuel pump 5.
- fuel is conveyed in this embodiment about 1500 to 2000 bar in a central, shown in detail in Fig. 2 pressure boosting device 6.
- the pressure boosting device 6 is, as will be explained later, formed as a double-acting pressure booster.
- a not shown fuel tank can be arranged.
- the fuel compressed by the pressure amplification device 6 to a pressure of, for example, more than 2500 bar passes into a high-pressure accumulator 7 downstream of the pressure amplification device 6 and from there into a plurality of injectors 8, which respectively direct the fuel into a combustion chamber, not shown, of an internal combustion engine inject.
- the high-pressure fuel accumulator 7 is equipped with a pressure sensor 9.
- the pressure sensor 9 is signal-conducting connected to a control unit 10, which in turn together with the metering unit 4, a control loop for the high-pressure fuel pump
- control unit 10 is further signal-conducting with control valves 11, 12 of the pressure boosting device
- Fig. 2 in Fig. 1 only indicated pressure amplifying device 6 is shown schematically in detail.
- the two control valves 11, 12 are supplied by the high-pressure fuel pump 5 shown in FIG. 1 via a supply line 14 with compressed fuel.
- the control valves 11, 12 can be connected via the diversion line 13 to the low-pressure region 15 of the fuel injection system 1.
- the first differential pressure chamber 17 is designed as an annular space and is bounded by a first housing component 20, a housing sleeve 21 and by a first end face 22 of a pressure piston 23.
- the pressure piston 23 is designed as a double hollow piston and limited with a first pin 24 of the housing member 20 has a first compression space 25 which acts on a radially inner portion of the first end face 22 of the pressure piston 23.
- the first supply line 16 is hydraulically connected to a first connecting line 27 to or from the first compression chamber 25 and the first connecting line 27 in turn is connected by means of a second check valve 28 with the high-pressure fuel storage 7.
- the mirror-symmetrical pressure amplifying device 6 is constructed in the right half of the drawing of FIG.
- the second control valve 12 is connected via the second supply line 18 to the second differential pressure chamber 19, which of a second, the first end face 22 of the plunger 23 opposite end face 29, a second housing member 30 and the housing sleeve 21 limited.
- a second compression space 31 is provided which acts on a radially inner portion of the second end face 29 of the pressure piston 23.
- the second supply line 18 is hydraulically connected via a third check valve 32 to a second connection line 33, which is centered by a second pin 34 the second housing member 30 is guided and opens into the second compression chamber 31, connectable, wherein the second connecting line 33 in turn via a fourth check valve 35 with the high-pressure fuel storage 7 is connectable.
- the two housing components 20, 30 are bolted to the housing sleeve 21 via a respective union nut 36, 37.
- the housing components 20, 30 are preferably used to hold the only schematically indicated, each designed as a 3/2-way valve control valves 11, 12th
- the operation of the pressure booster 6 is as follows.
- the first differential pressure chamber 17 is connected to the low-pressure region 15 by means of the first control valve 11.
- the supply line 14 is hydraulically connected to the second supply line 18 by means of the second control valve 12, so that fuel delivered by the high-pressure fuel pump 5 is conducted into the second differential pressure chamber 19 and via the third check valve 32 into the second compression space 31 acting as a control chamber.
- the pressure piston 23 moves in the plane of the drawing to the left, whereby the fuel in the first compression space 25 is compressed and flows through the first connecting line 27 through the second check valve 28 into the high-pressure fuel accumulator 7.
- a fuel flow from the high-pressure fuel accumulator 7 into the second compression space 31 is prevented by the fourth check valve 35.
- the control valves 11, 12 are switched.
- the second dif- pressure chamber 19 connected by means of the second control valve 12 to the low pressure region 15 of the fuel injection system 1 and the first supply line 16 hydraulically connected to the supply line 14, so that fuel in both the first differential pressure chamber 17 and the first check valve 26 in the first, in this case acting as a control room compression chamber 22 flows. Due to the pressure force difference on the pressure piston 23, this moves in the plane of the drawing to the right and compresses the fuel in the second compression chamber 31, which flows through the second connecting line 33 and the check valve 35 into the high-pressure fuel accumulator 7. A fuel flow from the high-pressure fuel accumulator 7 into the first compression space 25 is prevented by the second check valve 28.
- the embodiment described above is particularly suitable for injection systems in which the transmission ratio of the pressure boosting device (pressure of the fuel compressed by the pressure booster 6 to pressure of the fuel in the flow direction behind the high-pressure fuel pump 5) of over 2.
- the embodiment of a pressure amplification device 6 shown in FIG. 3 essentially corresponds to the exemplary embodiment described above according to FIG. 2 with the essential difference that the first differential pressure chamber 17 and the first compression chamber 25 and the second differential pressure chamber 19 and the second compression chamber 31 are arranged, so the differential pressure chambers 17, 19 as central spaces and the compression spaces 25, 31 as of the pins 24, 34 of the first and second housing member 20, 30 interspersed in the axial direction annular spaces are formed.
- This embodiment is particularly suitable, in particular due to the greater wall thickness s of the pressure piston 23 radially outside of the pins 24, 34 at gear ratios of the pressure amplifying device 6 below 2.
- the pressure boosting device 6 is supplied with fuel delivered by the high-pressure fuel pump 5 (see FIG.
- the second differential pressure chamber 19 Central space connected by means of the second control valve 12 with the low-pressure region 15.
- the supply line 14 is hydraulically connected to the first supply line 16 by means of the first control valve 11, so that fuel is passed from the high-pressure fuel pump 5 into the first differential pressure chamber 17 and via the first check valve 26 into the first compression space 25 acting as a control chamber.
- the pressure piston moves in the plane of the drawing to the right, whereby the fuel is compressed in the second compression chamber 31 and flows through the second connecting line 33 through the fourth check valve 35 into the high-pressure fuel accumulator 7.
- a fuel flow from the high-pressure fuel accumulator 7 into the first compression space 25 (in FIG This case control space) is prevented by the second check valve 28.
- control valves 11, 12 are switched by means of the schematically indicated in Fig. 1 control unit 10 in such a way that the first compression chamber 17 is connected to the low pressure region 15 and at the same time the supply line 14 by means of the second control valve 12 is hydraulically connected to the second supply line 18, so that fuel delivered by the high-pressure fuel pump 5 is directed into the second differential pressure chamber 19 and the third check valve in acting as a control chamber second compression chamber 32, whereby the pressure piston 23 moves in the drawing plane to the left and the fuel in the first compression space 25 is compressed and conveyed via the second check valve 28 into the high pressure fuel accumulator 7. A fuel flow from the high-pressure fuel accumulator 7 into the second compression chamber 31 is prevented by the fourth check valve 35.
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11179810.4A EP2402588B1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007010495A DE102007010495A1 (de) | 2007-03-05 | 2007-03-05 | Kraftstoffeinspritzsystem sowie Druckverstärkungseinrichtung für ein Kraftstoffeinspritzsystem |
PCT/EP2008/050794 WO2008107220A1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem sowie druckverstärkungseinrichtung für ein kraftstoffeinspritzsystem |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11179810.4A Division EP2402588B1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem |
EP11179810.4 Division-Into | 2011-09-02 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2132434A1 true EP2132434A1 (de) | 2009-12-16 |
EP2132434B1 EP2132434B1 (de) | 2011-10-26 |
Family
ID=39430677
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11179810.4A Not-in-force EP2402588B1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem |
EP08701662A Not-in-force EP2132434B1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem sowie druckverstärkungseinrichtung für ein kraftstoffeinspritzsystem |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11179810.4A Not-in-force EP2402588B1 (de) | 2007-03-05 | 2008-01-24 | Kraftstoffeinspritzsystem |
Country Status (4)
Country | Link |
---|---|
EP (2) | EP2402588B1 (de) |
AT (1) | ATE530762T1 (de) |
DE (1) | DE102007010495A1 (de) |
WO (1) | WO2008107220A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010002033A1 (de) | 2010-02-17 | 2011-08-18 | Robert Bosch GmbH, 70469 | Hydrauliksystem und Kraftstoffeinspritzsystem für eine Brennkraftmaschine |
DE102012011583A1 (de) * | 2012-06-13 | 2013-12-19 | Robert Bosch Gmbh | Vorrichtung und Verfahren zur Druckerzeugung für fließfähige Medien |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE904858C (de) * | 1951-12-04 | 1954-02-22 | Wilhelm Reppel | Hin und her gehender Druckuebersetzer fuer pneumatische Anlagen |
DE1577188A1 (de) | 1966-01-13 | 1969-09-25 | Stahl Und Appbau Hans Leffer G | Hydraulische Druckerzeugungsanlage mit doppelt wirkendem Druckuebersetzer |
US3386384A (en) * | 1966-06-27 | 1968-06-04 | Cicero C Brown | Multiple power consuming devices |
DE19939423A1 (de) | 1999-08-20 | 2001-03-01 | Bosch Gmbh Robert | Kraftstoffeinspritzsystem für eine Brennkraftmaschine |
DE19939420B4 (de) * | 1999-08-20 | 2004-12-09 | Robert Bosch Gmbh | Kraftstoffeinspritzverfahren und -system für eine Brennkraftmaschine |
DE10151885A1 (de) * | 2001-10-20 | 2003-05-08 | Bosch Gmbh Robert | Kraftstoffeinspritzsystem |
DE10246208A1 (de) | 2002-10-04 | 2004-04-15 | Robert Bosch Gmbh | Einrichtung zur Unterdrückung von Druckwellen an Speichereinspritzsystemen |
US7464697B2 (en) * | 2005-08-19 | 2008-12-16 | The United States Of America, As Represented By The Administrator Of The U.S. Environmental Protection Agency | High-pressure fuel intensifier system |
-
2007
- 2007-03-05 DE DE102007010495A patent/DE102007010495A1/de not_active Withdrawn
-
2008
- 2008-01-24 EP EP11179810.4A patent/EP2402588B1/de not_active Not-in-force
- 2008-01-24 AT AT08701662T patent/ATE530762T1/de active
- 2008-01-24 WO PCT/EP2008/050794 patent/WO2008107220A1/de active Application Filing
- 2008-01-24 EP EP08701662A patent/EP2132434B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2008107220A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP2402588B1 (de) | 2015-07-01 |
DE102007010495A1 (de) | 2008-09-11 |
WO2008107220A1 (de) | 2008-09-12 |
EP2132434B1 (de) | 2011-10-26 |
EP2402588A1 (de) | 2012-01-04 |
ATE530762T1 (de) | 2011-11-15 |
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