EP1185784B1 - Pressure translator for a fuel injection system pertaining to an internal combustion engine - Google Patents
Pressure translator for a fuel injection system pertaining to an internal combustion engine Download PDFInfo
- Publication number
- EP1185784B1 EP1185784B1 EP00979422A EP00979422A EP1185784B1 EP 1185784 B1 EP1185784 B1 EP 1185784B1 EP 00979422 A EP00979422 A EP 00979422A EP 00979422 A EP00979422 A EP 00979422A EP 1185784 B1 EP1185784 B1 EP 1185784B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- space
- control
- stepped piston
- oil return
- 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.)
- Expired - Lifetime
Links
- 238000002347 injection Methods 0.000 title claims description 46
- 239000007924 injection Substances 0.000 title claims description 46
- 239000000446 fuel Substances 0.000 title claims description 22
- 238000002485 combustion reaction Methods 0.000 title claims description 6
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Images
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
- F02M57/00—Fuel-injectors combined or associated with other devices
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
Definitions
- the invention relates to a pressure intensifier for a Fuel injection system for internal combustion engines according to the Preamble of claim 1.
- EP 0879 954 A2 describes a pressure intensifier for a Fuel injection system known in which after the completion of a First injection into a second pressure chamber from the fuel an injector is pumped, is completely emptied. The second pressure chamber is then filled again. The beginning The filling of the second pressure chamber is placed so that the volume of the second pressure chamber of the fuel quantity to be injected on Start of injection of the next injection has been reached. I.e. the Metering a certain injection quantity is with several Inaccurate. The end of the injection is reached if a pressure relief bore in the stepped piston coincides with a low pressure connection in the control valve housing. This means that the termination of the injection is not sudden, but takes place relatively gently. So are both beginning and End of an injection with certain inaccuracies.
- the invention is based on the object Provide fuel injection system in which the on the Pressure intensifiers acting hydraulic forces are reduced and where the pressure intensifier can be controlled easily and precisely.
- higher injection pressures should be possible and at the same time the load and the drive power requirement of the injection pump be reduced.
- This pressure translator which is very simply constructed according to the invention, has the advantage that between the injections on the Step piston acting pressure forces are reduced so that the Step piston after the end of the injection after the end of the Injection regardless of the prevailing pressures with a small actuating force in its starting position on the pump side can be brought back.
- the return spring required for this requires little installation space.
- the pressure intensifier according to the invention can despite its simple Structure can be controlled very precisely because the stepped piston is too Start of each injection at a defined point, namely the pump-side stop.
- the injection is also made very precisely by the pressure intensifier Closing of the control valve ended because immediately after the Closing the control valve the pressure in the second pressure chamber suddenly collapses
- the injection quantity can be measured very precisely be what is beneficial to the operational behavior as well Emissions and fuel consumption of the internal combustion engine effect.
- the leakage and Throttle losses in the fuel injection system resulting in a Reduction of the drive power requirement leads and the hydraulic Improved fuel injection system efficiency.
- the high injection pressures enable smaller spray hole diameters the injector, which causes the mixture formation in all operating points improved.
- first end face and the ring face are essentially the same size are so that the hydraulic forces on the stepped piston between the injections are fully balanced.
- control room has a Inlet throttle hydraulically connected to the first pressure chamber stands so that a pressure equalization between first pressure chamber and control room is prevented.
- control chamber can be depressurized via a control valve, in particular a 2/2 control valve, so that the start of delivery of the pressure booster can be controlled by opening the control valve.
- the heel is detachable with connected to the stepped piston, so that manufacture and assembly be simplified.
- Another variant of the invention provides that the second Pressure chamber is filled from the leak oil return, and that between a check valve is arranged in the second pressure chamber and leakage oil return is that the return flow of fuel from the second pressure chamber to Leak oil return locks, so that the filling is easy and between injections only a low pressure in the second Pressure room prevails.
- the pressure in Leakage oil return is lower than the opening pressure of the injection nozzle, so the injector is safe between injections closes.
- the stepped piston is Simplification of manufacture and assembly carried out in two parts.
- An embodiment of the invention provides that the tax amount of Control valve is discharged into the drain oil return, so that a simple hydraulic circuit is achieved.
- control piston in a sleeve is guided so that the guide of the stepped piston is improved.
- FIG. 1 schematically shows a fuel injection system with an injector 1 and an injection pump 3, the one High pressure part 5 has.
- the high pressure part 5 is over a control line 9 and a high pressure path 10 with the Injector 1 in operative connection.
- a Pressure intensifier arranged between the Control line 9 and the high pressure path 10 .
- the pressure intensifier 11 has in a housing 12 a first pressure chamber 13, a second pressure chamber 15, a one- or multi-part stepped piston 17, which in a Bore 18 is guided, and a control room 19.
- the first pressure chamber 13 and the end face of the stepped piston 17 with the diameter d 1 projecting into the first pressure chamber 13 form the low-pressure side of the pressure booster 11.
- the second pressure chamber 15 and the end face of the stepped piston 17 with the diameter d projecting into the second pressure chamber 15 3 form the high pressure side of the pressure intensifier 11.
- the control chamber 19 is an annular surface 20 of the Step piston 17 and a paragraph in the housing 12 of the Pressure intensifier 11 limited in the longitudinal direction.
- a 2/2-way control valve 21 connected to the control chamber 19 is closed between the injections.
- First pressure chamber 13 and control chamber 19 are connected by a connecting line 23, which has an inlet throttle 25, so that when control valve 21 is closed, the same pressure prevails in rooms 13 and 19.
- a slight overcompensation of the hydraulic force acting on the end face of the stepped piston 17 can be advantageous.
- the injection is triggered by the control valve 21 is opened.
- the one located in the control room 19 Fuel flows through the control valve 21 into one Leak oil return 27.
- the inlet throttle 25 causes at open control valve 21 the pressure in the control chamber 19 under that of the first pressure chamber 13 drops. As a result, the Force balance between that in the first pressure chamber 13 projecting end face of the stepped piston 17 and the Annular surface 20 no longer exist.
- the stepped piston 17 begins to promote.
- the second pressure chamber 15 is with a leakage oil pressure acted upon supply line 31 filled.
- a check valve 33 arranged in this Supply line 31 .
- the check valve 27 can be spring-loaded, such as shown in Fig. 2, or without a spring and prevents the backflow of fuel during the Injection.
- the leakage oil pressure is below the Injector opening pressure 1.
- the stepped piston 17 is guided with its diameter d 1 of a sleeve 35th
- the sleeve 35 is fixed radially in the housing 12.
- a shoulder 37 of the housing 12 and a plate spring 39 ensure the fixing of the sleeve 35.
- the housing 12 can be divided along the shoulder 37 in order to facilitate the manufacture and assembly of the pressure intensifier 11 according to the invention.
- the plate spring 39 prevents the stepped piston 17 from sitting “hard” on its pump-side stop.
- the return spring 29 is between the sleeve 35 and one Paragraph 41 of the stepped piston 17 clamped. 2 is an embodiment shown in which the paragraph 41 in the stepped piston 17 is screwed in. However, there are also other embodiments are conceivable.
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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)
Description
Die Erfindung betrifft einen Druckübersetzer für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a pressure intensifier for a Fuel injection system for internal combustion engines according to the Preamble of claim 1.
Die Verschärfung der Abgasnormen verlangt immer höhere Einspritzdrücke zur Verbesserung der Gemischbildung und der Verbrennung. Daraus ergeben sich höhere mechanische und thermische Belastungen des Kraftstoffeinspritzsystems. Außerdem nimmt der Antriebsleistungsbedarf überproportional zu, weil mit dem Druck auch die Verluste in dem Kraftstoffeinspritzsystem ansteigen.The tightening of emissions standards requires ever higher ones Injection pressures to improve mixture formation and Combustion. This results in higher mechanical and thermal Loads on the fuel injection system. In addition, the Drive power requirement disproportionately too, because with the pressure too the losses in the fuel injection system increase.
Aus der EP 0879 954 A2 ist ein Druckübersetzer für ein Kraftstoffeinspritzsystem bekannt, bei dem nach Beendigung einer Einspritzung zunächst ein zweiter Druckraum aus dem Kraftstoff in einen Injektor gefördert wird, vollständig entleert wird. Anschließend wird der zweite Druckraum wieder gefüllt. Der Beginn der Füllung des zweiten Druckraums wird so gelegt, dass das Volumen des zweiten Druckraums der einzuspritzenden Kraftstoffmenge am Einspritzbeginn der nächsten Einspritzung erreicht ist. D. h. die Zumessung einer bestimmten Einspritzmenge ist mit mehreren Ungenauigkeiten behaftet. Das Ende der Einspitzung ist erreicht, wenn eine Druckentlastungsbohrung im Stufenkolben zu Deckung mit einem Niederdruckanschluß im Steuerventilgehäuse kommt. Dies bedeutet, dass die Beendigung der Einspritzung nicht schlagartig, sondern relativ sanft erfolgt. Somit sind sowohl Anfang als auch Ende einer Einspritzung mit gewissen Ungenauigkeiten behaftet.EP 0879 954 A2 describes a pressure intensifier for a Fuel injection system known in which after the completion of a First injection into a second pressure chamber from the fuel an injector is pumped, is completely emptied. The second pressure chamber is then filled again. The beginning The filling of the second pressure chamber is placed so that the volume of the second pressure chamber of the fuel quantity to be injected on Start of injection of the next injection has been reached. I.e. the Metering a certain injection quantity is with several Inaccurate. The end of the injection is reached if a pressure relief bore in the stepped piston coincides with a low pressure connection in the control valve housing. This means that the termination of the injection is not sudden, but takes place relatively gently. So are both beginning and End of an injection with certain inaccuracies.
Der Erfindung liegt die Aufgabe zugrunde, ein Kraftstoffeinspritzsystem bereitzustellen, bei dem die auf den Druckübersetzer wirkenden hydraulischen Kräfte reduziert werden und bei dem der Druckübersetzer einfach und präzise steuerbar ist. Außerdem sollen höhere Einspritzdrücke ermöglicht und gleichzeitig die Beanspruchung und der Antriebsleistungsbedarf der Einspritzpumpe verringert werden.The invention is based on the object Provide fuel injection system in which the on the Pressure intensifiers acting hydraulic forces are reduced and where the pressure intensifier can be controlled easily and precisely. In addition, higher injection pressures should be possible and at the same time the load and the drive power requirement of the injection pump be reduced.
Diese Aufgabe wird erfindungsgemäß gelöst durch einen Druckübersetzer für ein Kraftstoffeinspritzsystem für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Anspruchs 1.This object is achieved by a Pressure intensifier for a fuel injection system for Internal combustion engines with the characterizing features of the claim 1.
Dieser erfindungsgemäß sehr einfach aufgebaute Druckübersetzer hat den Vorteil, dass zwischen den Einspritzungen die auf den Stufenkolben wirkenden Druckkräfte reduziert werden, so dass der Stufenkolben nach Beendigung der Einspritzung nach Beendigung der Einspritzung unabhängig von den herrschenden Drücken mit einer kleinen Stellkraft in seine pumpenseitige Ausgangslage zurückgebracht werden kann. Die dazu erforderliche Rückstellfeder benötigt nur wenig Einbauraum.This pressure translator, which is very simply constructed according to the invention, has the advantage that between the injections on the Step piston acting pressure forces are reduced so that the Step piston after the end of the injection after the end of the Injection regardless of the prevailing pressures with a small actuating force in its starting position on the pump side can be brought back. The return spring required for this requires little installation space.
Der erfindungsgemäße Druckübersetzer kann trotz seines einfachen Aufbaus sehr präzise gesteuert werden, da sich der Stufenkolben zu Beginn jeder Einspritzung an einer definierten Stelle, nämlich dem pumpenseitigen Anschlag befindet. Bei dem erfindungsgemäßen Druckübersetzer wird die Einspritzung auch sehr exakt durch das Schließen des Steuerventils beendet, da unmittelbar nach dem Schließen des Steuerventils der Druck im zweiten Druckraum schlagartig zusammenbrichtThe pressure intensifier according to the invention can despite its simple Structure can be controlled very precisely because the stepped piston is too Start of each injection at a defined point, namely the pump-side stop. In the invention The injection is also made very precisely by the pressure intensifier Closing of the control valve ended because immediately after the Closing the control valve the pressure in the second pressure chamber suddenly collapses
In Folge dessen kann die Einspritzmenge sehr genau zugemessen werden, was sich vorteilhaft auf das Betriebsverhalten sowie die Emissionen und den Kraftstoffverbrauch der Brennkraftmaschine auswirkt. Außerdem verringern sich auch die Leck- und Drosselverluste des Kraftstoffeinspritzsystems, was zu einer Reduktion des Antriebsleistungsbedarfs führt und den hydraulischen Wirkungsgrad des Kraftstoffeinspritzsystems verbessert. Zusätzlich ermöglichen die hohen Einspritzdrücke kleinere Spritzlochdurchmesser der Einspritzdüse, was die Gemischbildung in allen Betriebspunkten verbessert.As a result, the injection quantity can be measured very precisely be what is beneficial to the operational behavior as well Emissions and fuel consumption of the internal combustion engine effect. In addition, the leakage and Throttle losses in the fuel injection system, resulting in a Reduction of the drive power requirement leads and the hydraulic Improved fuel injection system efficiency. additionally the high injection pressures enable smaller spray hole diameters the injector, which causes the mixture formation in all operating points improved.
Bei einer weiteren Ausgestaltung der Erfindung ist vorgesehen, dass die erste Stirnfläche und die Ringfläche im Wesentlichen gleich groß sind, so dass die hydraulischen Kräfte auf den Stufenkolben zwischen den Einspritzungen vollständig ausgeglichen werden.In a further embodiment of the invention it is provided that the first end face and the ring face are essentially the same size are so that the hydraulic forces on the stepped piston between the injections are fully balanced.
Eine andere Ausführungsform sieht vor, dass der Steuerraum über eine Zulaufdrossel mit dem ersten Druckraum hydraulisch in Verbindung steht, so dass während der Einspritzung ein Druckausgleich zwischen erstem Druckraum und Steuerraum verhindert wird.Another embodiment provides that the control room has a Inlet throttle hydraulically connected to the first pressure chamber stands so that a pressure equalization between first pressure chamber and control room is prevented.
Bei einer Ausführungsform der Erfindung
ist der Steuerraum über ein Steuerventil, insbesondere ein 2/2-Steuerventil
druckentlastbar, so dass der Förderbeginn des
Druckübersetzers durch Öffnen des Steuerventils steuerbar ist. In one embodiment of the invention
the control chamber can be depressurized via a control valve, in particular a 2/2 control valve, so that the start of delivery of the pressure booster can be controlled by opening the control valve.
Bei einer erfindungsgemäßen Ausgestaltung ist der Absatz lösbar mit dem Stufenkolben verbunden, so dass Herstellung und Montage vereinfacht werden.In an embodiment according to the invention, the heel is detachable with connected to the stepped piston, so that manufacture and assembly be simplified.
Bei einer weiteren Ausgestaltung der Erfindung fließt der Kraftstoff aus dem ersten Druckraum über eine Ablaufdrossel in einen Leckölrücklauf, so dass das Druckniveau im Leckölrücklauf mittelbar durch die Einspritzpumpe erzeugt wird.In a further embodiment of the invention, the Fuel from the first pressure chamber into an outlet throttle Leak oil return, so that the pressure level in the leak oil return is generated indirectly by the injection pump.
Eine weitere Variante der Erfindung sieht vor, dass der zweite Druckraum aus dem Leckölrücklauf befüllt wird, und dass zwischen zweitem Druckraum und Leckölrücklauf ein Rückschlagventil angeordnet ist, das den Rückfluss von Kraftstoff vom zweiten Druckraum zum Leckölrücklauf sperrt, so dass die Befüllung einfach ist und zwischen den Einspritzungen nur ein niedriger Druck im zweiten Druckraum herrscht.Another variant of the invention provides that the second Pressure chamber is filled from the leak oil return, and that between a check valve is arranged in the second pressure chamber and leakage oil return is that the return flow of fuel from the second pressure chamber to Leak oil return locks, so that the filling is easy and between injections only a low pressure in the second Pressure room prevails.
In Ergänzung der Erfindung ist vorgesehen, dass der Druck im Leckölrücklauf geringer als der Öffnungsdruck der Einspritzdüse ist, so dass die Einspritzdüse zwischen den Einspritzungen sicher schließt.In addition to the invention it is provided that the pressure in Leakage oil return is lower than the opening pressure of the injection nozzle, so the injector is safe between injections closes.
Bei einer Ausgestaltung der Erfindung ist der Stufenkolben zur Vereinfachung von Herstellung und Montage zweiteilig ausgeführt.In one embodiment of the invention, the stepped piston is Simplification of manufacture and assembly carried out in two parts.
Eine Ausführung der Erfindung sieht vor, dass die Steuermenge des Steuerventils in den Leckölrücklauf abgeführt wird, so dass eine einfache hydraulische Schaltung erreicht wird.An embodiment of the invention provides that the tax amount of Control valve is discharged into the drain oil return, so that a simple hydraulic circuit is achieved.
Bei einer anderen Variante ist vorgesehen, dass der Steuerkolben in einer Hülse geführt wird, so dass die Führung des Stufenkolbens verbessert wird. In another variant it is provided that the control piston in a sleeve is guided so that the guide of the stepped piston is improved.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the Invention are the following description, the Drawing and the claims can be removed.
Ausführungsbeispiele des Gegenstands der Erfindung sind in
der Zeichnung dargestellt und im Folgenden näher
beschrieben. Es zeigen:
Fig. 1 zeigt schematisch ein Kraftstoffeinspritzsystem mit
einer Einspritzdüse 1 und einer Einspritzpumpe 3, die einen
Hochdruck-Teil 5 aufweist. Der Hochdruck-Teil 5 steht über
eine Steuerleitung 9 und einen Hochdruckpfad 10 mit der
Einspritzdüse 1 in Wirkverbindung. Zwischen der
Steuerleitung 9 und dem Hochdruckpfad 10 ist ein
Druckübersetzer angeordnet.1 schematically shows a fuel injection system with
an injector 1 and an
In Fig. 2 ist ein erfindungsgemäßer Druckübersetzer 11
dargestellt. Der Druckübersetzer 11 weist in einem Gehäuse
12 einen ersten Druckraum 13, einen zweiten Druckraum 15,
einen ein- oder mehrteiligen Stufenkolben 17, der in einer
Bohrung 18 geführt wird, sowie einen Steuerraum 19 auf.2 is a
Der erste Druckraum 13 und die in den ersten Druckraum 13
ragende Stirnfläche des Stufenkolbens 17 mit dem
Durchmesser d1 bilden die Niederdruck-Seite des
Druckübersetzers 11. Der zweite Druckraum 15 und die in den
zweiten Druckraum 15 ragende Stirnfläche des Stufenkolbens
17 mit dem Durchmesser d3 bilden die Hochdruck-Seite des
Druckübersetzers 11.The
Der Steuerraum 19 wird von einer Ringfläche 20 des
Stufenkolbens 17 und einem Absatz in dem Gehäuse 12 des
Druckübersetzers 11 in Längsrichtung begrenzt.The
Zwischen den Einspritzungen ist ein mit dem Steuerraum 19
verbundenes 2/2-Steuerventil 21 geschlossen. Erster
Druckraum 13 und Steuerraum 19 sind durch eine
Verbindungsleitung 23, die eine Zulaufdrossel 25 aufweist,
verbunden, so dass bei geschlossenem Steuerventil 21 in den
Räumen 13 und 19 der gleiche Druck herrscht. Über die in
den ersten Druckraum 13 ragende Stirnfläche des
Stufenkolbens 17 und die Ringfläche 20 findet ein Ausgleich
der hydraulischen Kräfte statt. Der Ausgleich ist
vollständig, wenn die Bedingung
Die Einspritzung wird ausgelöst, indem das Steuerventil 21
geöffnet wird. Der in dem Steuerraum 19 befindliche
Kraftstoff fließt durch das Steuerventil 21 in einen
Leckölrücklauf 27. Die Zulaufdrossel 25 bewirkt, dass bei
geöffnetem Steuerventil 21 der Druck im Steuerraum 19 unter
den des ersten Druckraums 13 sinkt. In Folge dessen ist der
Kraftausgleich zwischen der in den ersten Druckraum 13
ragenden Stirnfläche des Stufenkolbens 17 und der
Ringfläche 20 nicht mehr gegeben. Der Stufenkolben 17
beginnt zu fördern.The injection is triggered by the
Durch das Verhältnis der in den ersten Druckraum 13 und der
in den zweiten Druckraum 15 ragenden Stirnflächen ist das
Verhältnis der Drücke in erstem und zweitem Druckraum 13
und 15 vorgegeben. Sobald der Druck im zweitem Druckraum 15
bzw. im Hochdruckpfad 10 den Öffnungsdruck der
Einspritzdüse 1 überschreitet, öffnet die Einspritzdüse 1
und die Einspritzung beginnt.By the ratio of the in the
Sobald das Steuerventil 21 wieder geschlossen wird, findet
zwischen erstem Druckraum 13 und Steuerraum 21 wieder ein
Druck- und Kraftausgleich statt, so dass der Stufenkolben
17 durch eine Rückstellfeder 29 in Richtung des ersten
Druckraums 13 in die in Fig. 2 dargestellte Position bewegt
wird. Sobald sich der Stufenkolben 17 in Richtung des
ersten Druckraums 13 bewegt, bricht der Druck im zweiten
Druckraum 15 zusammen und die Einspritzdüse 1 schließt.As soon as the
Der zweite Druckraum 15 wird über eine mit Lecköldruck
beaufschlagte Versorgungsleitung 31 gefüllt. In dieser
Versorgungsleitung 31 ist ein Rückschlagventil 33
angeordnet. Das Rückschlagventil 27 kann federbelastet, wie
in Fig. 2 dargestellt, oder ohne Feder ausgeführt sein und
verhindert den Rückfluss von Kraftstoff während der
Einspritzung. Der Lecköldruck liegt unterhalb des
Öffnungsdrucks der Einspritzdüse 1.The
Der Stufenkolben 17 wird mit seinem Durchmesser d1 von
einer Hülse 35 geführt. Die Hülse 35 ist radial in dem
Gehäuse 12 fixiert. In axialer Richtung sorgen ein Absatz
37 des Gehäuses 12 und eine Tellerfeder 39 für die
Fixierung der Hülse 35. Das Gehäuse 12 kann entlang des
Absatzes 37 geteilt sein, um Herstellung und Montierbarkeit
des erfindungsgemäßen Druckübersetzers 11 zu erleichtern.
Die Tellerfeder 39 verhindert ein "hartes" Aufsitzen des
Stufenkolbens 17 auf seinem pumpenseitigen Anschlag.The stepped
Die Rückstellfeder 29 ist zwischen Hülse 35 und einem
Absatz 41 des Stufenkolbens 17 eingespannt. In Fig. 2 ist
eine Ausführungsform dargestellt bei der der Absatz 41 in
den Stufenkolben 17 eingeschraubt ist. Es sind jedoch auch
andere Ausführungsformen denkbar.The
Über eine Ablaufdrossel 43 fließt Kraftstoff aus dem ersten
Druckraum 13 in den Leckölrücklauf. Über die Ablaufdrossel
43 kann das Druckniveau des Leckölrücklaufs beeinflusst
werden.Fuel flows from the first via an
Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.All in the description, the following claims and The features shown in the drawing can be both individually as well as in any combination with each other be essential to the invention.
Claims (11)
- Pressure intensifier for a fuel injection system for internal combustion engines, with an injection nozzle (1) and with an injection pump (3) having a high-pressure part (5), the high-pressure part (5) of the injection pump (3) being operatively connected to the injection nozzle (1) via a control line (9) connected to the low-pressure side of the pressure intensifier (11) and via a high pressure path (10) connected to the high-pressure side of the pressure intensifier (11), the pressure intensifier (11) having a stepped piston (17) which is displaceable in a bore (18) and the end faces of which each delimit a pressure space, a first larger end face of the stepped piston (17) delimiting a first pressure space (13) connected to the control line (9) and a second opposite smaller end face of the stepped piston (17) delimiting a second pressure space (15) connected to the high-pressure path (10), an annular surface (20) located opposite the first end face delimiting a control space (19), and the pressure in the first pressure space (13) and in the control space (19) being identical between the injections, characterized in that the first pressure space (13) has clamped into it a return spring (29) which is supported on a bearing means (35) and a step (41) of a stepped piston (17) and which presses the stepped piston (17) against its pump-side abutment between the injections as a function of the pressure in the first pressure space (13) and of the pressure in the control space (19).
- Pressure intensifier according to Claim 1, characterized in that the first end face and the annular surface (20) are essentially of equal size.
- Pressure intensifier according to one of Claims 1 and 2, characterized in that the control space (19) is hydraulically connected to the first pressure space (13) via an inflow throttle (25).
- Pressure intensifier according to one of the preceding claims, characterized in that the control space (19) is capable of being relieved of pressure via a control valve (21), in particular a 2/2-way control valve (21).
- Pressure intensifier according to one of the preceding claims, characterized in that the step (41) is releasably connected to the stepped piston (17).
- Pressure intensifier according to one of the preceding claims, characterized in that fuel flows out of the first pressure space (13) into a leakage-oil return (27) via an outflow throttle (43).
- Pressure intensifier according to one of the preceding claims, characterized in that the second pressure space (15) is filled from the leakage-oil return (27), and in that between the second pressure space (15) and the leakage-oil return (27) is arranged a non-return valve (33) which blocks the flowback of fuel from the second pressure space (15) to the leakage-oil return (27).
- Pressure intensifier according to Claim 7, characterized in that the pressure in the leakage-oil return (27) is lower than the opening pressure of the injection nozzle (1).
- Pressure intensifier according to one of the preceding claims, characterized in that the stepped piston (17) is designed in two parts.
- Pressure intensifier according to one of Claims 4-9, characterized in that the control quantity of the control valve (21) is discharged into the leakage-oil return (27).
- Pressure intensifier according to one of the preceding claims, characterized in that the control piston (17) is guided in a sleeve (35).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19949848 | 1999-10-15 | ||
| DE19949848A DE19949848A1 (en) | 1999-10-15 | 1999-10-15 | Pressure converter for fuel injection system includes compensation for hydraulic forces acting between injections on the low pressure side |
| PCT/DE2000/003594 WO2001029396A2 (en) | 1999-10-15 | 2000-10-12 | Pressure translator for a fuel injection system pertaining to an internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1185784A2 EP1185784A2 (en) | 2002-03-13 |
| EP1185784B1 true EP1185784B1 (en) | 2003-10-08 |
Family
ID=7925825
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP00979422A Expired - Lifetime EP1185784B1 (en) | 1999-10-15 | 2000-10-12 | Pressure translator for a fuel injection system pertaining to an internal combustion engine |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US6427664B1 (en) |
| EP (1) | EP1185784B1 (en) |
| JP (1) | JP2003512574A (en) |
| KR (1) | KR20010093156A (en) |
| BR (1) | BR0007458A (en) |
| CZ (1) | CZ295572B6 (en) |
| DE (2) | DE19949848A1 (en) |
| WO (1) | WO2001029396A2 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19946833C2 (en) * | 1999-09-30 | 2002-02-21 | Bosch Gmbh Robert | Valve for controlling liquids |
| DE10019765B4 (en) * | 2000-04-20 | 2004-12-09 | Robert Bosch Gmbh | Valve for controlling liquids |
| DE10019764B4 (en) * | 2000-04-20 | 2004-09-23 | Robert Bosch Gmbh | Length measuring device for measuring dimensions of bodies, particularly inner- and outer diameters, used in mechanical drive- and transmission elements and in circular body, has carrier element, which is adapted to body to be measured |
| DE10126685A1 (en) * | 2001-06-01 | 2002-12-19 | Bosch Gmbh Robert | Fuel injection system, at an IC motor, has a pressure amplifier to give a flat pressure increase without pressure oscillations |
| WO2004088122A1 (en) * | 2003-04-02 | 2004-10-14 | Robert Bosch Gmbh | Fuel injector provided with provided with a pressure transmitter controlled by a servo valve |
| DE10315016A1 (en) * | 2003-04-02 | 2004-10-28 | Robert Bosch Gmbh | Fuel injector with a leak-free servo valve |
| DE10355041A1 (en) * | 2003-11-25 | 2005-06-23 | Robert Bosch Gmbh | Pressure intensifier with guide insert for a fuel injector |
| JP3994990B2 (en) | 2004-07-21 | 2007-10-24 | 株式会社豊田中央研究所 | Fuel injection device |
| DE102004051757A1 (en) * | 2004-10-23 | 2006-04-27 | Robert Bosch Gmbh | Fuel injector with hydraulically operated pressure intensifier for injecting fuel in combustion chamber of internal combustion engine with minimum injector opening |
| JP4459183B2 (en) * | 2006-03-16 | 2010-04-28 | 株式会社デンソー | Injector |
| JP4609351B2 (en) * | 2006-03-17 | 2011-01-12 | 株式会社デンソー | Injector |
| JP2007255328A (en) * | 2006-03-23 | 2007-10-04 | Toyota Motor Corp | Injection fuel boosting device |
| JP6583304B2 (en) * | 2017-02-17 | 2019-10-02 | トヨタ自動車株式会社 | Control device for internal combustion engine |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3102697A1 (en) * | 1980-12-20 | 1982-10-21 | Volkswagenwerk Ag, 3180 Wolfsburg | Fuel injection device |
| JP2885076B2 (en) * | 1994-07-08 | 1999-04-19 | 三菱自動車工業株式会社 | Accumulator type fuel injection device |
| US5641121A (en) * | 1995-06-21 | 1997-06-24 | Servojet Products International | Conversion of non-accumulator-type hydraulic electronic unit injector to accumulator-type hydraulic electronic unit injector |
| DE19531870C2 (en) * | 1995-08-30 | 2002-07-18 | Bosch Gmbh Robert | Fuel injection system |
| DE19701879A1 (en) * | 1997-01-21 | 1998-07-23 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| US5878720A (en) * | 1997-02-26 | 1999-03-09 | Caterpillar Inc. | Hydraulically actuated fuel injector with proportional control |
| US5852997A (en) * | 1997-05-20 | 1998-12-29 | Stanadyne Automotive Corp. | Common rail injector |
| DE19738804B4 (en) * | 1997-09-05 | 2004-07-22 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
-
1999
- 1999-10-15 DE DE19949848A patent/DE19949848A1/en not_active Ceased
-
2000
- 2000-10-12 US US09/868,046 patent/US6427664B1/en not_active Expired - Fee Related
- 2000-10-12 DE DE50004006T patent/DE50004006D1/en not_active Expired - Lifetime
- 2000-10-12 CZ CZ20012115A patent/CZ295572B6/en not_active IP Right Cessation
- 2000-10-12 KR KR1020017007311A patent/KR20010093156A/en not_active Application Discontinuation
- 2000-10-12 WO PCT/DE2000/003594 patent/WO2001029396A2/en not_active Application Discontinuation
- 2000-10-12 EP EP00979422A patent/EP1185784B1/en not_active Expired - Lifetime
- 2000-10-12 JP JP2001532358A patent/JP2003512574A/en active Pending
- 2000-10-12 BR BR0007458-6A patent/BR0007458A/en active Search and Examination
Also Published As
| Publication number | Publication date |
|---|---|
| DE19949848A1 (en) | 2001-04-19 |
| US6427664B1 (en) | 2002-08-06 |
| BR0007458A (en) | 2001-10-16 |
| KR20010093156A (en) | 2001-10-27 |
| CZ20012115A3 (en) | 2002-06-12 |
| DE50004006D1 (en) | 2003-11-13 |
| WO2001029396A3 (en) | 2001-12-27 |
| CZ295572B6 (en) | 2005-08-17 |
| WO2001029396A2 (en) | 2001-04-26 |
| EP1185784A2 (en) | 2002-03-13 |
| JP2003512574A (en) | 2003-04-02 |
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