EP1218631A2 - Pressure amplifier and a fuel injection system with a pressure amplifier - Google Patents

Pressure amplifier and a fuel injection system with a pressure amplifier

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Publication number
EP1218631A2
EP1218631A2 EP00979424A EP00979424A EP1218631A2 EP 1218631 A2 EP1218631 A2 EP 1218631A2 EP 00979424 A EP00979424 A EP 00979424A EP 00979424 A EP00979424 A EP 00979424A EP 1218631 A2 EP1218631 A2 EP 1218631A2
Authority
EP
European Patent Office
Prior art keywords
pressure
booster
injection
piston
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00979424A
Other languages
German (de)
French (fr)
Other versions
EP1218631B1 (en
Inventor
Martin Kropp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1218631A2 publication Critical patent/EP1218631A2/en
Application granted granted Critical
Publication of EP1218631B1 publication Critical patent/EP1218631B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification

Definitions

  • the invention relates to a pressure booster for increasing the injection pressure in direct-injection internal combustion engines, in particular diesel engines, with a booster piston, which has a relatively large end face, which is acted upon by a relatively low pressure, and a relatively small end face, on which in
  • the invention also relates to a fuel injection system, in particular a common rail system, with a high-pressure connection, which is connected to an injector, from which fuel is injected into the combustion chamber of an internal combustion engine.
  • Both pressure-controlled (DE 197 06 467 Cl) and stroke-controlled (DE 196 19 523 AI) injection systems are known for introducing fuel into direct-injection diesel engines. It is advantageous if the injection pressure is adapted to the load and speed, as can be the case with a common rail system.
  • a high-pressure pump possibly with the help of a pre-feed pump, conveys the fuel to be injected from a tank into the central high-pressure fuel reservoir, which is referred to as the common rail. Lead off the rail
  • the injectors are individually controlled by the engine electronics in order to inject fuel into the combustion chamber of the internal combustion engine.
  • the maximum injection pressures in common rail systems are currently limited to approx. 1600 to 1800 bar due to the high pressure resistance of pressure accumulators and high pressure pumps.
  • injection systems with pressure intensifiers are used.
  • Such a common rail system is e.g. described in EP 0 562 046 B1. It is a pressure-controlled common rail system with a pressure intensifier
  • Booster piston during injection pressure increased t P> o L ⁇ oo in
  • Booster piston which has a relatively large end face, which is subjected to a relatively low pressure, and a relatively small end face, on which there is an increased injection pressure in the delivery stroke, the difference in size between the two on the side facing away from the relatively large end face
  • the end faces of the booster piston result in a dead volume, solved in that the dead volume is connected to an outsourced spring accumulator that is local to each individual cylinder or central to all cylinders of the
  • Diameter ratios can be achieved.
  • a further advantage can arise in a central storage space / diaphragm space common to all cylinders, since the reset can be realized with a few additional components (if a reset was simply carried out using a pre-pressure on the high-pressure side, this pressure would only have to be generated, which would reduce the efficiency ).
  • a special embodiment of the invention is characterized in that the spring accumulator comprises a piston which is biased by a spring.
  • the maximum injection pressure is reduced accordingly by the spring, but this benefits rapid refilling.
  • a small spring may also be arranged in the dead space, which further supports refilling.
  • a special embodiment of the fuel injection system according to the invention is characterized in that the pressure booster is integrated in the injector. In a common rail system, the pressure booster can also be integrated into the rail.
  • such an arrangement can also be used in other injection systems which have such a pressure booster.
  • a pressure booster for example, in the case of a distributor pump, the 3/2 valve upstream of the pressure booster is omitted and is replaced by a distributor with the corresponding 2/2 valve.
  • a pressure booster 1 according to the invention is shown by way of example in the accompanying drawing.
  • the pressure booster 1 comprises a cylinder 2, in which a booster piston 3 is received.
  • the booster piston 3 can be moved back and forth in the cylinder 2 between a low-pressure side 4 and a high-pressure side 5.
  • Low pressure side 4 is actually high pressure, which is provided by a high pressure pump.
  • the booster piston 3 has two differently sized end faces. The end face of the booster piston 3 on the low-pressure side 4 is larger than the end face on the high-pressure side 5. This means that the pressure on the high-pressure side 5 increases when the piston moves from the low-pressure side 4 to the high-pressure side 5.
  • Two lines 6 and 7 extend from the low-pressure side 4 of the cylinder 2.
  • the line 6 is over a
  • 3/2-way valve 8 can be connected to a high-pressure connection 9 or an unpressurized leak return 10.
  • the line 6 In the position shown of the 3/2 way valve 8, the line 6 is connected to the leakage return 10. In this state, the cylinder 2 is filled with fuel on the high-pressure side 5.
  • the line 6 In the other position of the 3/2-way valve 8, the line 6 is connected to a central high-pressure fuel reservoir (rail) via the high-pressure connection 9. In this state, the delivery stroke takes place, during which the fuel located on the high pressure side 5 is compressed.
  • Line 7 is connected against the biasing force of a spring-loaded check valve 11 with two lines 12 and 13.
  • Line 12 leads to
  • High-pressure side 5 of the cylinder 2 ensures that fuel can reach the high-pressure side 5 when refilling.
  • the line 13 leads to a nozzle chamber 14 of an injector 15.
  • a nozzle needle 16 is received so as to be able to move back and forth against the biasing force of a nozzle spring 17.
  • fuel becomes from the nozzle chamber 14 into the combustion chamber 18 of the engine to be supplied injected.
  • a dead volume 20 is provided in the cylinder 2.
  • the dead volume 20 serves to accommodate the collar resulting from the difference in size of the differently sized end faces of the booster piston 3 in the delivery stroke.
  • the dead volume 20 is connected to a via a line 21
  • Spring 22 connected.
  • a piston 23 is accommodated so that it can move back and forth against the biasing force of a compression spring 24.
  • the fuel injection system shown enables improved refilling of the pressure booster 1.
  • the compression spring 24 is swapped out in the spring accumulator 22.
  • the dead volume 20 is pushed out into the spring accumulator 22 and stored there at a defined pressure.
  • the spring accumulator 22 can also be designed as a diaphragm accumulator.
  • the sketch shown is intended for the use of a pressure-controlled system.
  • a stroke-controlled system it is necessary that the line 7 in front of the valve 8 is permanently connected to the line 9 so that the nozzle chamber 14 is permanently under pressure (when the pressure booster is deactivated, under rail pressure).
  • Such a stroke-controlled system naturally also requires a pressure accumulator.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a pressure amplifier for increasing the injection pressure in multi-cylinder, direct-injection internal combustion engines, in particular, diesel engines. Said pressure amplifier comprises a multiplying piston (3), with a relatively large piston crown, which is operated by a relatively low pressure and a relatively small piston crown, where a relatively high pressure exists during the pumping stroke, which results in a dead volume (20) on the side of the relatively large piston crown, due to the size difference between the two crowns of the multiplying piston (3). The dead volume (20) is connected to an external spring-loaded reservoir (22), which is arranged locally to one individual cylinder, or centrally to all the cylinders of an internal combustion engine, whereby, even with small pressure amplification ratios a complete and rapid refilling of the pressure amplifier is assured. The invention further relates to a fuel injection system comprising such a pressure amplifier.

Description

Druckverstärker und Kraftstoffeinspritzsystem mit einem DruckverstärkerPressure booster and fuel injection system with a pressure booster
Stand der TechnikState of the art
Die Erfindung betrifft einen Druckverstärker zur Erhöhung des Einspritzdrucks in direkteinspritzenden Brennkraftmaschinen, insbesondere Dieselmotoren, mit einem Übersetzerkolben, der eine relativ große Stirnfläche, die mit einem relativ niedrigen Druck beaufschlagt ist, und eine relativ kleine Stirnfläche aufweist, an welcher imThe invention relates to a pressure booster for increasing the injection pressure in direct-injection internal combustion engines, in particular diesel engines, with a booster piston, which has a relatively large end face, which is acted upon by a relatively low pressure, and a relatively small end face, on which in
Förderhub ein erhöhter Einspritzdruck vorliegt, wobei sich auf der von der relativ großen Stirnfläche abgewandten Seite aus dem Größenunterschied zwischen den beiden Stirnflächen des Übersetzerkolbens ein Totvolumen ergibt. Die Erfindung betrifft auch ein Kraftstoffeinspritzsystem, insbesondere Common-Rail-System, mit einem Hochdruckanschluss, der mit einem Injektor in Verbindung steht, aus dem Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt wird.Delivery stroke there is an increased injection pressure, which results in a dead volume on the side facing away from the relatively large end face from the size difference between the two end faces of the booster piston. The invention also relates to a fuel injection system, in particular a common rail system, with a high-pressure connection, which is connected to an injector, from which fuel is injected into the combustion chamber of an internal combustion engine.
Zur Einbringung von Kraftstoff in direkteinspritzenden Dieselmotoren sind sowohl druckgesteuerte (DE 197 06 467 Cl) als auch hubgesteuerte (DE 196 19 523 AI) Einspritzsysteme bekannt. Es ist von Vorteil, wenn der Einspritzdruck an Last und Drehzahl angepasst wird, wie es bei einem Common-Rail-System der Fall sein kann. In Co mon-Rail -Einspritzsystemen fördert eine Hochdruckpumpe, eventuell unter Zuhilfenahme einer Vorförderpumpe, den einzuspritzenden Kraftstoff aus einem Tank in den zentralen Kraftstoffhochdruckspeicher, der als Common-Rail bezeichnet wird. Von dem Rail führenBoth pressure-controlled (DE 197 06 467 Cl) and stroke-controlled (DE 196 19 523 AI) injection systems are known for introducing fuel into direct-injection diesel engines. It is advantageous if the injection pressure is adapted to the load and speed, as can be the case with a common rail system. In Co mon-rail injection systems, a high-pressure pump, possibly with the help of a pre-feed pump, conveys the fuel to be injected from a tank into the central high-pressure fuel reservoir, which is referred to as the common rail. Lead off the rail
Kraftstoffleitungen zu den einzelnen Injektoren, die den Zylindern der Brennkraftmaschine zugeordnet sind. Die Injektoren werden in Abhängigkeit von den Betriebsparametern der Brennkraftmaschine einzeln von der Motorelektronik angesteuert, um Kraftstoff in den Brennraum der Brennkraftmaschine einzuspritzen. Die maximalen Einspritzdrücke bei Common Rail Systemen sind derzeit durch die Hochdruckfestigkeit von Druckspeichern und Hochdruckpumpen auf ca. 1600 bis 1800 bar begrenzt. Um den Einspritzdruck weiter zu steigern, werden Einspritzsysteme mit Druckübersetzern eingesetzt.Fuel lines to the individual injectors that are assigned to the cylinders of the internal combustion engine. Depending on the operating parameters of the internal combustion engine, the injectors are individually controlled by the engine electronics in order to inject fuel into the combustion chamber of the internal combustion engine. The maximum injection pressures in common rail systems are currently limited to approx. 1600 to 1800 bar due to the high pressure resistance of pressure accumulators and high pressure pumps. To further increase the injection pressure, injection systems with pressure intensifiers are used.
Ein derartiges Common-Rail-System ist z.B. in der EP 0 562 046 Bl beschrieben. Dabei handelt es sich um ein druckgesteuertes Common-Rail-System mit DruckübersetzerSuch a common rail system is e.g. described in EP 0 562 046 B1. It is a pressure-controlled common rail system with a pressure intensifier
(hohes Übersetzungsverhältnis von ca. 1:7) . Wie bei jedem druckübersetztem Einspritzsystem existiert auch hier ein Totvolumen, in dem eine Rückstellfeder angeordnet ist. Das Totvolumen ist über ein (federloses) Rückschlagventil mit einer Leckageleitung verbunden. Dies hat den Vorteil, dass die während des Förderhubes verdrängte Menge nicht wieder beim Rückstellen des Verstärkerkolbens aus der Leckageleitung angesaugt werden muss . Nachteilig ist jedoch, dass der Kraftstoff, der sich im Totvolumen befindet, während des Rückstellens kavitiert . Durch das Zusammenfallen der Kavitationsblasen entsteht eine zusätzliche Geräuschentwicklung .(high gear ratio of approx. 1: 7). As with any pressure-boosted injection system, there is also a dead volume in which a return spring is arranged. The dead volume is connected to a leakage line via a (springless) check valve. This has the advantage that the quantity displaced during the delivery stroke does not have to be sucked out of the leakage line again when the booster piston is reset. However, it is disadvantageous that the fuel that is in the dead volume cavitates during the resetting. The collapse of the cavitation bubbles creates additional noise.
Bei Aktivierung der Druckverstärkung ergibt sich aufgrund der unterschiedlichen Flächenverhältnisse amWhen the pressure boost is activated, the result is due to the different area ratios
Druckverstärkerkolben ein erhöhter Einspritzdruck während t P> o LΠ o o inBooster piston during injection pressure increased t P> o LΠ oo in
Übersetzerkolben, der eine relativ große Stirnfläche, die mit einem relativ niedrigen Druck beaufschlagt ist, und eine relativ kleine Stirnfläche aufweist, an welcher im Förderhub ein erhöhter Einspritzdruck vorliegt, wobei sich auf der von der relativ großen Stirnfläche abgewandten Seite aus dem Größenunterschied zwischen den beiden Stirnflächen des Übersetzerkolbens ein Totvolumen ergibt, dadurch gelöst, dass das Totvolumen mit einem ausgelagerten Federspeicher in Verbindung steht, der lokal zu jedem einzelnen Zylinder oder zentral zu allen Zylindern derBooster piston, which has a relatively large end face, which is subjected to a relatively low pressure, and a relatively small end face, on which there is an increased injection pressure in the delivery stroke, the difference in size between the two on the side facing away from the relatively large end face The end faces of the booster piston result in a dead volume, solved in that the dead volume is connected to an outsourced spring accumulator that is local to each individual cylinder or central to all cylinders of the
Brennkraftmaεchine angeordnet ist. Durch Auslagerung der Feder kann eine geeignete Federgeometrie (Durchmesser, Länge, Drahtstärke, Steifigkeit) gewählt werden, wodurch eine Optimierung der Kolbenform und somit weitere günstige Effekte (Reibungsminimierung, Dichtlängen,Brennkraftmaεchine is arranged. By outsourcing the spring, a suitable spring geometry (diameter, length, wire thickness, stiffness) can be selected, which optimizes the piston shape and thus further beneficial effects (minimizing friction, sealing lengths,
Durchmesserverhältnisse) erzielt werden können. Ein weiterer Vorteil kann in einem für alle Zylinder gemeinsamen zentralen Speicherraum/Membranraum entstehen, da hier mit wenigen zusätzlichen Bauteilen die Rückstellung realisiert werden kann (bei einer reinen Rückstellung über einen Vordruck auf der Hochdruckseite wäre dieser Druck erst zu erzeugen, was den Wirkungsgrad verschlechtern würde) .Diameter ratios) can be achieved. A further advantage can arise in a central storage space / diaphragm space common to all cylinders, since the reset can be realized with a few additional components (if a reset was simply carried out using a pre-pressure on the high-pressure side, this pressure would only have to be generated, which would reduce the efficiency ).
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Federspeicher einen Kolben umfasst, der durch eine Feder vorgespannt ist. Durch die Feder wird zwar der maximale Einspritzdruck entsprechend reduziert, was aber einer schnellen Wiederbefüllung zugute kommt. In dem Federraum ist genügend Bauraum für eine große Feder vorhanden. Eventuell kann im Totraum zusätzlich noch eine kleine Feder angeordnet sein, welche die Wiederbefüllung weiter unterstützt.A special embodiment of the invention is characterized in that the spring accumulator comprises a piston which is biased by a spring. The maximum injection pressure is reduced accordingly by the spring, but this benefits rapid refilling. There is enough space in the spring chamber for a large spring. A small spring may also be arranged in the dead space, which further supports refilling.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass der Federspeicher eine t to H HAnother special embodiment of the invention is characterized in that the spring accumulator t to HH
< 1 o l o in o ut<1 o l o in o ut
Eine besondere Ausführungsart des erfindungsgemäßen Kraftstoffeinspritzsystems ist dadurch gekennzeichnet, dass der Druckverstärker in den Injektor integriert ist. Bei einem Common-Rail-System kann der Druckverstärker auch in das Rail integriert sein.A special embodiment of the fuel injection system according to the invention is characterized in that the pressure booster is integrated in the injector. In a common rail system, the pressure booster can also be integrated into the rail.
Im Allgemeinen kann eine solche Anordnung auch bei anderen Einspritzsystemen verwendet werden, die einen solchen Druckverstärker besitzen. So kann z.B. bei einer Verteilerpumpe das 3/2 Ventil vor dem Druckverstärker entfallen und wird durch einen Verteiler mit entsprechendem 2/2 Ventil ersetzt.In general, such an arrangement can also be used in other injection systems which have such a pressure booster. For example, in the case of a distributor pump, the 3/2 valve upstream of the pressure booster is omitted and is replaced by a distributor with the corresponding 2/2 valve.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung ein Ausführungsbeispiel der Erfindung im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein.Further advantages, features and details of the invention result from the following description, in which an embodiment of the invention is described in detail with reference to the drawing. The features mentioned in the claims and in the description can each be essential to the invention individually or in any combination.
In der beiliegenden Zeichnung ist ein erfindungsgemäßer Druckverstärker 1 beispielhaft dargestellt. Der Druckverstärker 1 umfasst einen Zylinder 2, in dem ein Übersetzerkolben 3 aufgenommen ist. Der Übersetzerkolben 3 ist in dem Zylinder 2 zwischen einer Niederdruckseite 4 und einer Hochdruckseite 5 hin- und herbewegbar.A pressure booster 1 according to the invention is shown by way of example in the accompanying drawing. The pressure booster 1 comprises a cylinder 2, in which a booster piston 3 is received. The booster piston 3 can be moved back and forth in the cylinder 2 between a low-pressure side 4 and a high-pressure side 5.
Die Begriffe Niederdruck und Hochdruck sind im Zusammenhang mit der vorliegenden Erfindung relativ zu sehen. Auf derThe terms low pressure and high pressure are to be seen relatively in connection with the present invention. On the
Niederdruckseite 4 herrscht in Wirklichkeit Hochdruck, der von einer Hochdruckpumpe zur Verfügung gestellt wird. Auf der Hochdruckseite 5 herrscht im Förderhub des Übersetzerkolbens 3 ein erhöhter Einspritzdruck, der größer als der von der Hochdruckpumpe zur Verfügung gestellte Hochdruck ist. Der Übersetzerkolben 3 weist zwei unterschiedlich große Stirnflächen auf. Die Stirnfläche des Übersetzerkolbens 3 auf der Niederdruckseite 4 ist größer als die Stirnfläche auf der Hochdruckseite 5. Daraus ergibt sich, dass der Druck auf der Hochdruckseite 5 zunimmt, wenn sich der Kolben von der Niederdruckseite 4 zur Hochdruckseite 5 bewegt .Low pressure side 4 is actually high pressure, which is provided by a high pressure pump. On the high-pressure side 5, there is an increased injection pressure in the delivery stroke of the booster piston 3, which is greater than the high pressure provided by the high-pressure pump. The booster piston 3 has two differently sized end faces. The end face of the booster piston 3 on the low-pressure side 4 is larger than the end face on the high-pressure side 5. This means that the pressure on the high-pressure side 5 increases when the piston moves from the low-pressure side 4 to the high-pressure side 5.
Von der Niederdruckseite 4 des Zylinders 2 gehen zwei Leitungen 6 und 7 aus. Die Leitung 6 ist über einTwo lines 6 and 7 extend from the low-pressure side 4 of the cylinder 2. The line 6 is over a
3/2-Wegeventil 8 mit einem Hochdruckanschluss 9 oder einem drucklosen Leckagerücklauf 10 verbindbar. In der dargestellten Stellung des 3/2 -Wegeventils 8 ist die Leitung 6 mit dem Leckagerücklauf 10 verbunden. In diesem Zustand füllt sich der Zylinder 2 auf der Hochdruckseite 5 mit Kraftstoff. In der anderen Stellung des 3/2-Wegeventils 8 ist die Leitung 6 über den Hochdruckanschluss 9 mit einem zentralen Kraftstoffhochdruckspeicher (Rail) verbunden. In diesem Zustand findet der Förderhub statt, bei dem der auf der Hochdruckseite 5 befindliche Kraftstoff verdichtet wird.3/2-way valve 8 can be connected to a high-pressure connection 9 or an unpressurized leak return 10. In the position shown of the 3/2 way valve 8, the line 6 is connected to the leakage return 10. In this state, the cylinder 2 is filled with fuel on the high-pressure side 5. In the other position of the 3/2-way valve 8, the line 6 is connected to a central high-pressure fuel reservoir (rail) via the high-pressure connection 9. In this state, the delivery stroke takes place, during which the fuel located on the high pressure side 5 is compressed.
Die Leitung 7 ist gegen die Vorspannkraft eines federvorgespannten Rückschlagventils 11 mit zwei Leitungen 12 und 13 verbunden. Die Leitung 12 führt zurThe line 7 is connected against the biasing force of a spring-loaded check valve 11 with two lines 12 and 13. Line 12 leads to
Hochdruckseite 5 des Zylinders 2 und stellt somit sicher, dass beim Wiederbefüllen Kraftstoff von dem Hochdruckanschluss 9 auf die Hochdruckseite 5 gelangen kann.High-pressure side 5 of the cylinder 2 and thus ensures that fuel can reach the high-pressure side 5 when refilling.
Die Leitung 13 führt zu einem Düsenraum 14 eines Injektors 15. In dem Injektor 15 ist eine Düsennadel 16 gegen die Vorspannkraft einer Düsenfeder 17 hin- und herbewegbar aufgenommen. Wenn die Spitze der Düsennadel 16 von ihrem Sitz abhebt, wird Kraftstoff aus dem Düsenraum 14 in den Brennraum 18 der zur versorgenden Brennkraftmaschine eingespritz .The line 13 leads to a nozzle chamber 14 of an injector 15. In the injector 15, a nozzle needle 16 is received so as to be able to move back and forth against the biasing force of a nozzle spring 17. When the tip of the nozzle needle 16 lifts off its seat, fuel becomes from the nozzle chamber 14 into the combustion chamber 18 of the engine to be supplied injected.
Um die Hin- und Herbewegung des Übersetzerkolbens 3 zu ermöglichen, ist in den Zylinder 2 ein Totvolumen 20 vorgesehen. Das Totvolumen 20 dient dazu, den sich aus den Größenunterschied der unterschiedlich großen Stirnflächen des Übersetzerkolbens 3 ergebenden Bund im Förderhub aufzunehmen .In order to enable the translating piston 3 to move back and forth, a dead volume 20 is provided in the cylinder 2. The dead volume 20 serves to accommodate the collar resulting from the difference in size of the differently sized end faces of the booster piston 3 in the delivery stroke.
Das Totvolumen 20 ist über eine Leitung 21 mit einemThe dead volume 20 is connected to a via a line 21
Federspeicher 22 verbunden. In dem Federspeicher 22 ist ein Kolben 23 gegen die Vorspannkraft einer Druckfeder 24 hin- und herbewegbar aufgenommen .Spring 22 connected. In the spring accumulator 22, a piston 23 is accommodated so that it can move back and forth against the biasing force of a compression spring 24.
Das dargestellte Kraftstoffeinspritzsystem ermöglicht eine verbesserte Wiederbefüllung des Druckverstärkers 1.The fuel injection system shown enables improved refilling of the pressure booster 1.
Gemäß der vorliegenden Erfindung wird die Druckfeder 24 in den Federspeicher 22 ausgelagert. Im Betrieb des erfindungsgemäßen Druckverstärkers 1 wird das Totvolumen 20 in den Federspeicher 22 ausgeschoben und dort bei einem definierten Druck gelagert. Der Federspeicher 22 kann auch als Membranspeicher ausgeführt sein.According to the present invention, the compression spring 24 is swapped out in the spring accumulator 22. During operation of the pressure booster 1 according to the invention, the dead volume 20 is pushed out into the spring accumulator 22 and stored there at a defined pressure. The spring accumulator 22 can also be designed as a diaphragm accumulator.
Die gezeigte Skizze ist für die Anwendung eines druckgesteuerten Systems gedacht. Bei der Anwendung eines hubgesteuerten Systems ist es erforderlich, dass die Leitung 7 vor dem Ventil 8 mit der Leitung 9 permanent verbunden ist, damit der Düsenraum 14 permanent unter Druck (bei deaktiviertem Druckverstärker unter Raildruck) steht. Ein solches hubgesteuertes System benötigt selbstverständlich auch einen Druckspeicher . The sketch shown is intended for the use of a pressure-controlled system. When using a stroke-controlled system, it is necessary that the line 7 in front of the valve 8 is permanently connected to the line 9 so that the nozzle chamber 14 is permanently under pressure (when the pressure booster is deactivated, under rail pressure). Such a stroke-controlled system naturally also requires a pressure accumulator.

Claims

Ansprüche Expectations
1. Druckverstärker zur Erhöhung des Einspritzdrucks in direkteinspritzenden Brennkraftmaschinen mit mehreren Zylindern, insbesondere Dieselmotoren, mit einem Übersetzerkolben (3), der eine relativ große Stirnfläche, die mit einem relativ niedrigen Druck beaufschlagt ist, und eine relativ kleine Stirnfläche aufweist, an welcher im1.Pressure booster for increasing the injection pressure in direct-injection internal combustion engines with several cylinders, in particular diesel engines, with a booster piston (3), which has a relatively large end face, which is acted upon by a relatively low pressure, and a relatively small end face, on which in
Förderhub ein erhöhter Einspritzdruck vorliegt, wobei sich auf der von der relativ großen Stirnfläche abgewandten Seite aus dem Größenunterschied zwischen den beiden Stirnflächen des Übersetzerkolbens (3) ein Totvolumen (20) ergibt, dadurch gekennzeichnet, dass das Totvolumen (20) mit einem ausgelagerten Federspeicher (22) in Verbindung steht, der lokal zu jedem einzelnen Zylinder oder zentral zu allen Zylindern der Brennkraftmaschine angeordnet ist.Delivery stroke there is an increased injection pressure, a dead volume (20) resulting on the side facing away from the relatively large end face from the size difference between the two end faces of the booster piston (3), characterized in that the dead volume (20) with an outsourced spring memory ( 22) is connected, which is arranged locally to each individual cylinder or centrally to all cylinders of the internal combustion engine.
2. Druckverstärker nach einem der vorhergehenden2. Pressure booster according to one of the preceding
Ansprüche, dadurch gekennzeichnet, dass der Federspeicher (22) einen Kolben (23) umfasst, der durch eine Feder (24) vorgespannt ist .Claims, characterized in that the spring accumulator (22) comprises a piston (23) which is biased by a spring (24).
3. Druckverstärker nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Federspeicher eine vorgespannte Membran umfasst .3. Pressure booster according to claim 1 or 2, characterized in that the spring accumulator comprises a prestressed membrane.
4. Kraftstoffeinspritzsystem, insbesondere Common-Rail- System, mit einem Hochdruckanschluss (9) , der mit mindestens einem Injektor (15) mit einem Düsenraum (14) in Verbindung steht, aus dem Kraftstoff in den Brennraum (18) einer Brennkraftmaschine eingespritzt wird, dadurch gekennzeichnet, dass an einer beliebigen Stelle zwischen dem Hochdruckanschluss (9) und dem Düsenraum (14) des Injektors (15) ein Druckverstärker (1) nach einem der vorhergehenden Ansprüche angeordnet ist .4. Fuel injection system, in particular common rail system, with a high-pressure connection (9), which has at least one injector (15) with a nozzle chamber (14) Connection is made, from which fuel is injected into the combustion chamber (18) of an internal combustion engine, characterized in that a pressure booster (1) according to one of the following is located at any point between the high-pressure connection (9) and the nozzle chamber (14) of the injector (15) preceding claims is arranged.
5. Kraftstoffeinspritzsystem nach Anspruch 4, dadurch gekennzeichnet, dass der Druckverstärker in den Injektor oder in den Hochdruckspeicher integriert ist. 5. Fuel injection system according to claim 4, characterized in that the pressure booster is integrated in the injector or in the high pressure accumulator.
EP00979424A 1999-10-30 2000-10-12 Pressure amplifier and a fuel injection system with a pressure amplifier Expired - Lifetime EP1218631B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19952512 1999-10-30
DE19952512A DE19952512A1 (en) 1999-10-30 1999-10-30 Pressure booster and fuel injection system with a pressure booster
PCT/DE2000/003596 WO2001033067A2 (en) 1999-10-30 2000-10-12 Pressure amplifier and a fuel injection system with a pressure amplifier

Publications (2)

Publication Number Publication Date
EP1218631A2 true EP1218631A2 (en) 2002-07-03
EP1218631B1 EP1218631B1 (en) 2005-03-30

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EP00979424A Expired - Lifetime EP1218631B1 (en) 1999-10-30 2000-10-12 Pressure amplifier and a fuel injection system with a pressure amplifier

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US (1) US6634336B1 (en)
EP (1) EP1218631B1 (en)
JP (1) JP2003514169A (en)
KR (1) KR100708224B1 (en)
DE (2) DE19952512A1 (en)
WO (1) WO2001033067A2 (en)

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Also Published As

Publication number Publication date
DE19952512A1 (en) 2001-05-10
KR100708224B1 (en) 2007-04-17
WO2001033067A2 (en) 2001-05-10
WO2001033067A3 (en) 2002-04-25
JP2003514169A (en) 2003-04-15
EP1218631B1 (en) 2005-03-30
KR20010093232A (en) 2001-10-27
DE50009933D1 (en) 2005-05-04
US6634336B1 (en) 2003-10-21

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