EP1141539B1 - Piston pump for high-pressure fuel generation - Google Patents
Piston pump for high-pressure fuel generation Download PDFInfo
- Publication number
- EP1141539B1 EP1141539B1 EP99963253A EP99963253A EP1141539B1 EP 1141539 B1 EP1141539 B1 EP 1141539B1 EP 99963253 A EP99963253 A EP 99963253A EP 99963253 A EP99963253 A EP 99963253A EP 1141539 B1 EP1141539 B1 EP 1141539B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- return valve
- valve
- fuel
- closing member
- 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
- 239000000446 fuel Substances 0.000 title claims description 31
- 238000002347 injection Methods 0.000 claims description 8
- 239000007924 injection Substances 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 6
- 238000002485 combustion reaction Methods 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 206010015137 Eructation Diseases 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 208000027687 belching Diseases 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005429 filling process Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000003860 storage Methods 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
- 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
- F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/043—Arrangements for driving reciprocating piston-type 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
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
- F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/1002—Ball valves
- F04B53/1005—Ball valves being formed by two closure members working in series
Definitions
- the invention is based on a piston pump according to the Genus of claim 1.
- the piston pump according to the invention with the features of Patent claim 1 has the advantage that the Partial filling of the respective pump element is no longer in the essential of the interaction of the delivery pressure of Feed pump, the spring force of the first check valve and depends on the vacuum generated by the pump piston, but the duration of the filling of the pump element of the im essentially loaded only by delivery pressure and spring force second check valve is determined which at low flow rate of the fuel supplied also the Filling limited while the first check valve in the printing phase of the conveying process only substantially serving to the cylinder space of the pump element against the shut off the second check valve. Of the Fuel metering is thus no longer of the Opening duration of the first check valve determined. beginning and end of the metering process according to the invention from Delivery pressure of the fuel introduced and limited.
- FIG. 1 shows a Hydraulic circuit diagram of part of a Fuel injection system with a piston pump for High-pressure fuel supply system and Figure 2 a Section through a pump element of the piston pump.
- the hydraulic circuit diagram shown in Figure 1 shows a Pump arrangement for high-pressure fuel production for a in Internal combustion engine used fuel injection system, in particular common-rail injection system.
- the Pump arrangement has a low-pressure feed pump 1, which on the suction side, for example, a diesel fuel containing fuel tank 2 is connected. Of the Feed pump 1 is on the pressure side, a delivery line 3, in which a flow control valve 4 is arranged.
- the pump assembly also includes a high pressure piston pump 6 with three pump elements 7 on which, respectively a pump piston 8 in a cylinder chamber 9, a suction side first and second check valves 10 and 11 as well pressure side comprise a pressure valve 12.
- the under one Angular distance of 120 ° arranged pump piston 8 are supported by spring force on a cam ring 13, which of an eccentric shaft 14 is driven.
- the delivery line 3 is after the flow control valve. 4 branches and in each case to the second check valve 11 of the Pump elements 7 connected.
- the two against spring force in the direction of the cylinder chamber 9 opening check valves 10 and 11 are arranged in series, with the first Check valve 10 close to the cylinder in the respective Delivery line branch lies.
- From the pressure valves 12 of the Pump elements 7 go line branches one High-pressure fuel line 15 off, which is not one illustrated high - pressure fuel storage of the Fuel injection system leads.
- the low-pressure feed pump 1 and the high-pressure piston pump 6 are constant pumps.
- In the simplified hydraulic circuit diagram of Figure 1 are no belonging to the pump assembly pressure control and limit valves, return lines and fuel filters shown.
- a pump piston 8 in one Cylinder space 9 of a housing 17.
- To the cylinder chamber 9 is connected to the pressure valve 12 of the pump element 7.
- Of the Cylinder space 9 is characterized by an annular disc-shaped Valve plate 18 completed. This one is through Housing member 19 in the form of a in the housing 17th held down screwed screw plug.
- the Housing member 19 engages with a sealing edge 20 on the cylinder side facing away from the valve plate 18 and is circumferentially with a sealing ring 21 relative to the housing 17 sealed.
- the valve plate 18 is circumferentially of an annular space 22 surrounded, in which a line branch of the Delivery line 3 opens.
- the valve plate 18 is a coaxial with the Cylinder chamber 9 extending, stepped through hole 24 provided. Coaxial to the through hole 24 is in the housing member 19, a blind hole 25 is formed.
- the valve plate 18 is also provided with a radial running stitch channel 26 provided, which is located between the circumferential annular space 22 of the housing 10 and the stepped through bore 24 extends.
- the stitch channel 26 opens into a bore section 27 of the Through hole 24, between a cylinder space side annular collar 28 and a facing away from the cylinder space bore section 29 of Valve plate 18 is located.
- Cylinder space side is on the annular collar 28 of the valve plate 18th a hollow cone-shaped valve seat 31 of the first Check valve 10 is formed.
- This one has plate-shaped closing member 32, which against the Valve seat 31 is conically limited. Because of each other Deviating cone angle touch closure member 32 and Valve seat 31 along an edge whose diameter at the same time the clear diameter of the annular collar 28 is. Notwithstanding the embodiment, the closing member 32nd also only be disc-shaped and with a flat valve seat 31 cooperate with the valve plate 18.
- the Closing member 32 is a shaft 33, which the Through hole 24 of the valve plate 18 at a distance penetrates and in the blind hole 25 of the Casing component 20 ends.
- a hollow cone-shaped valve seat 35 of the second Check valve 11 is formed.
- Taper angle agrees the sealing diameter of the second Check valve 11 with the clear diameter of the Ringbund 28 coincide.
- the sleeve-shaped closing member 36 of second check valve 11 is remote in the cylinder space Bore portion 29 of the valve plate 18 largely pressure-tight and extends into the blind hole 25 of the housing member 19.
- the sleeve-shaped closing member 36 includes with his bottom 37, the shaft 33 of the closing member 32 with radial play.
- a prestressed Compressed spring 39 received, which on the one hand to the cylinder side facing away from the sleeve bottom 37 and on the other hand to a stop 40 on the closing member shaft attacks.
- the two compression springs 38 and 39 practice one each Closing force on the associated check valve 10 and 11 respectively out.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung geht aus von einer Kolbenpumpe nach der Gattung des Patentanspruchs 1.The invention is based on a piston pump according to the Genus of claim 1.
Es ist schon eine solche Kolbenpumpe mit drei Pumpenelementen bekannt (DE 42 13 798 A1), welche jeweils saugseitig über ein federbelastetes Rückschlagventil an eine Niederdruckversorgung angeschlossen sind. Die bekannte Kolbenpumpe ist von ihrer Bauart her eine Konstantpumpe, deren Pumpenelemente auf einen im Kraftstoffeinspritzsystem maximal nötigen Volumenstrom eingestellt sind. Bei einer niederdruckseitigen Mengenregelung des Kraftstoffstromes ergibt sich jedoch der Nachteil, daß bei einem gegenüber dem maximalen Volumenstrom kleineren Volumenstrom aufgrund von Toleranzen der saugseitigen Rückschlagventile eine ungleiche Füllung der einzelnen Pumpenelemente erfolgt. Dies hat seine Ursache darin, daß das auf einen niedrigen öffnungshub eingestellte saugseitige Rückschlagventil der Pumpenelemente während des Saughubs des Pumpenkolbens und während eines Teils des Förderhubs geöffnet ist. Dabei können Überschneidungen der Öffnungszeiten der Saugventile anderer Pumpenelemente auftreten. Da aber bei kleinem Volumenstrom der Druck im Niederdrucksystem sehr niedrig ist und sich mit der Befüllung eines Pumpenelements vermindert, kann es bei zu langer Öffnungsdauer eines Saugventils zu einer Minderfüllung oder Nichtbefüllung eines anderes Pumpenelements kommen. Hierdurch entstehen jedoch im hochdruckseitigen Teil des Kraftstoffeinspritzsystems Druckschwankungen, welche sich nachteilig auf den Lauf der angeschlossenen Brennkraftmaschine auswirken. It is already such a piston pump with three Pump elements known (DE 42 13 798 A1), each of which suction side via a spring-loaded check valve to a Low pressure supply are connected. The well-known Piston pump is by design a fixed displacement pump, their pump elements on a fuel injection system maximum required volume flow are set. At a Low-pressure side flow control of the fuel flow However, there is the disadvantage that when compared to the maximum volume flow smaller volume flow due to Tolerances of the suction side check valves an unequal Filling of the individual pump elements takes place. This has his Cause in that on a low opening stroke set suction-side check valve of the pump elements during the suction stroke of the pump piston and during a Part of the delivery is open. It can Overlaps of the opening times of the suction valves of others Pump elements occur. But with a small volume flow the pressure in the low pressure system is very low and consistent with reduces the filling of a pump element, it can at Too long opening duration of a suction valve to a Filling or not filling another Pump element come. However, this results in the high-pressure side part of the fuel injection system Pressure fluctuations, which adversely affect the course of connected internal combustion engine.
Aus GB 564 725 ist eine Kolbenpumpe mit zwei in Reihe geschalteten, saugseitigen Rückschlagventilen bekannt. Die baugleichen Rückschlagventile besitzen eine nicht federbelastete Kugel als Schließglied, welches unter Schwerkraftwirkung seine Schließstellung einnimmt. Mit der Zweifachanordnung des saugseitigen Rückschlagventils soll eine verbesserte Dichtigkeit und Effektivität der Pumpe erzielt werden.From GB 564 725 a piston pump with two in series switched, suction-side check valves known. The identical check valves do not have one spring-loaded ball as closing member, which under Gravity effect assumes its closed position. With the Double arrangement of the suction-side check valve should an improved tightness and effectiveness of the pump be achieved.
Die erfindungsgemäße Kolbenpumpe mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß die Teilbefüllung des jeweiligen Pumpenelements nicht mehr im wesentlichen vom Zusammenwirken des Förderdrucks der Förderpumpe, der Federkraft des ersten Rückschlagventils und des vom Pumpenkolben erzeugten Unterdrucks abhängt, sondern die Dauer der Befüllung des Pumpenelements von dem im wesentlichen nur von Förderdruck und Federkraft belasteten zweiten Rückschlagventil bestimmt wird, welches bei niedrigem Volumenstrom des zugeführten Kraftstoffs auch die Befüllung begrenzt, während das erste Rückschlagventil in der Druckphase des Fördervorgangs nur noch im wesentlichen dazu dient, den Zylinderraum des Pumpenelements gegen das zweite Rückschlagventil abzusperren. Der Kraftstoffzumeßvorgang wird somit nicht mehr von der Öffnungsdauer des ersten Rückschlagventils bestimmt. Beginn und Ende des Zumeßvorgangs werden erfindungsgemäß vom Förderdruck des Kraftstoff eingeleitet und begrenzt.The piston pump according to the invention with the features of Patent claim 1 has the advantage that the Partial filling of the respective pump element is no longer in the essential of the interaction of the delivery pressure of Feed pump, the spring force of the first check valve and depends on the vacuum generated by the pump piston, but the duration of the filling of the pump element of the im essentially loaded only by delivery pressure and spring force second check valve is determined which at low flow rate of the fuel supplied also the Filling limited while the first check valve in the printing phase of the conveying process only substantially serving to the cylinder space of the pump element against the shut off the second check valve. Of the Fuel metering is thus no longer of the Opening duration of the first check valve determined. beginning and end of the metering process according to the invention from Delivery pressure of the fuel introduced and limited.
Eine Einbauvolumen im Gehäuse eines Pumpenelements sparende Ausführungsform der beiden Rückschlagventile ist in den Unteransprüchen angegeben.An installation volume in the housing of a pump element saving Embodiment of the two check valves is in the Subclaims specified.
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Hydraulikschaltplan eines Teils eines Kraftstoffeinspritzsystems mit einer Kolbenpumpe zur Kraftstoffhochdruckversorgung des Systems und Figur 2 einen Schnitt durch ein Pumpenelement der Kolbenpumpe.An embodiment of the invention is in the drawing simplified and in the following Description explained in more detail. FIG. 1 shows a Hydraulic circuit diagram of part of a Fuel injection system with a piston pump for High-pressure fuel supply system and Figure 2 a Section through a pump element of the piston pump.
Der in Figur 1 dargestellte Hydraulikschaltplan zeigt eine
Pumpenanordnung zur Kraftstoffhochdruckerzeugung für ein in
Brennkraftmaschinen eingesetztes Kraftstoffeinspritzsystem,
insbesonders Common-Rail-Einspritzsystem. Die
Pumpenanordnung weist eine Niederdruck-Förderpumpe 1 auf,
welche saugseitig an einen beispielsweise Dieselkraftstoff
enthaltenden Kraftstoffbehälter 2 angeschlossen ist. Von der
Förderpumpe 1 geht druckseitig eine Förderleitung 3 aus, in
welcher ein Stromregelventil 4 angeordnet ist.The hydraulic circuit diagram shown in Figure 1 shows a
Pump arrangement for high-pressure fuel production for a in
Internal combustion engine used fuel injection system,
in particular common-rail injection system. The
Pump arrangement has a low-pressure feed pump 1,
which on the suction side, for example, a diesel fuel
containing
Die Pumpenanordnung weist außerdem eine Hochdruck-Kolbenpumpe
6 mit drei Pumpenelementen 7 auf, welche jeweils
einen Pumpenkolben 8 in einem Zylinderraum 9, saugseitig ein
erstes und ein zweites Rückschlagventil 10 und 11 sowie
druckseitig ein Druckventil 12 umfassen. Die unter einem
Winkelabstand von 120° angeordneten Pumpenkolben 8 sind
durch Federkraft an einem Hubring 13 abgestützt, welcher von
einer Exzenterwelle 14 antreibbar ist.The pump assembly also includes a high
Die Förderleitung 3 ist nach dem Stromregelventil 4
verzweigt und jeweils an das zweite Rückschlagventil 11 der
Pumpenelemente 7 angeschlossen. Die beiden gegen Federkraft
in Richtung zum Zylinderraum 9 öffnenden Rückschlagventile
10 und 11 sind in Reihe angeordnet, wobei das erste
Rückschlagventil 10 zylinderraumnah in dem jeweiligen
Förderleitungszweig liegt. Von den Druckventilen 12 der
Pumpenelemente 7 gehen Leitungszweige einer
Kraftstoffhochdruckleitung 15 aus, welche zu einem nicht
dargestellten Kraftstoffhochdruckspeicher des
Kraftstoffeinspritzsystems führt.The
Die Niederdruck-Förderpumpe 1 und die Hochdruck-Kolbenpumpe
6 sind Konstantpumpen. Eine verbrauchsabhängige
Mengenregelung des Kraftstoffstroms von der Förderpumpe 1
zur Kolbenpumpe 6 erfolgt mittels des Stromregelventils 4.
In dem vereinfachten Hydraulikschaltplan gemäß Figur 1 sind
keine zu der Pumpenanordnung gehörende Druckregel- und
-begrenzungsventile, Rücklaufleitungen sowie Kraftstoffilter
dargestellt.The low-pressure feed pump 1 and the high-
Bei dem in Figur 2 wiedergegebenen Längsschnitt eines
Pumpenelements 7 erkennt man einen Pumpenkolben 8 in einem
Zylinderraum 9 eines Gehäuses 17. An den Zylinderraum 9 ist
das Druckventil 12 des Pumpenelements 7 angeschlossen. Der
Zylinderraum 9 ist durch eine ringscheibenförmige
Ventilplatte 18 abgeschlossen. Diese ist durch ein
Gehäusebauteil 19 in der Form einer in das Gehäuse 17
eingeschraubten Verschlußschraube niedergehalten. Das
Gehäusebauteil 19 greift mit einer Dichtkante 20 an der
zylinderraumabgewandten Seite der Ventilplatte 18 an und ist
umfangsseitig mit einem Dichtring 21 gegenüber dem Gehäuse
17 abgedichtet. Die Ventilplatte 18 ist umfangsseitig von
einem Ringraum 22 umgeben, in welchen ein Leitungszweig der
Förderleitung 3 mündet.In the reproduced in Figure 2 longitudinal section of a
Die Ventilplatte 18 ist mit einer achsgleich zum
Zylinderraum 9 verlaufenden, abgestuften Durchgangsbohrung
24 versehen. Gleichachsig zur Durchgangsbohrung 24 ist in
dem Gehäusebauteil 19 eine Sacklochbohrung 25 ausgebildet. The
Die Ventilplatte 18 ist außerdem mit einem radial
verlaufenden Stichkanal 26 versehen, welcher sich zwischen
dem umfangsseitigen Ringraum 22 des Gehäuses 10 und der
abgestuften Durchgangsbohrung 24 erstreckt. Der Stichkanal
26 mündet in einen Bohrungsabschnitt 27 der
Durchgangsbohrung 24, der zwischen einem
zylinderraumseitigen Ringbund 28 und einem
zylinderraumabgewandten Bohrungsabschnitt 29 der
Ventilplatte 18 gelegen ist.The
Zylinderraumseitig ist am Ringbund 28 der Ventilplatte 18
ein hohlkegelförmiger Ventilsitz 31 des ersten
Rückschlagventils 10 ausgebildet. Dieses weist ein
tellerförmiges Schließglied 32 auf, welches gegen den
Ventilsitz 31 kegelförmig begrenzt ist. Aufgrund voneinander
abweichender Kegelwinkel berühren sich Schließglied 32 und
Ventilsitz 31 entlang einer Kante, deren Durchmesser
zugleich der lichte Durchmesser des Ringbundes 28 ist.
Abweichend vom Ausführungsbeispiel kann das Schließglied 32
auch nur scheibenförmig sein und mit einem ebenen Ventilsitz
31 mit der Ventilplatte 18 zusammenarbeiten. Von dem
Schließglied 32 geht ein Schaft 33 aus, welcher die
Durchgangsbohrung 24 der Ventilplatte 18 mit Abstand
durchdringt und in der Sacklochbohrung 25 des
Gehäusebauteils 20 endet.Cylinder space side is on the
An der zylinderraumabgewandten Seite des Ringbundes 28 ist
ein hohlkegelförmiger Ventilsitz 35 des zweiten
Rückschlagventils 11 ausgebildet. Diesem ist ein
Schließglied 36 in der Form einer Hülse zugeordnet, deren
Boden 37 eine mit dem Ventilsitz 35 zusammenwirkende
Kegelkontur aufweist. Durch entsprechend gewählte
Kegelwinkel stimmt der Dichtdurchmesser des zweiten
Rückschlagventils 11 mit dem lichten Durchmesser des
Ringbundes 28 überein. Das hülsenförmige Schließglied 36 des
zweiten Rückschlagventils 11 ist im zylinderraumabgewandten
Bohrungsabschnitt 29 der Ventilplatte 18 weitgehend
druckdicht geführt und erstreckt sich in die Sacklochbohrung
25 des Gehäusebauteils 19. Innerhalb der Sacklochbohrung 25
befindet sich eine vorgespannte Druckfeder 38, welche
einerseits bodenseitig am Schließglied 36 und andererseits
am Grund der Sacklochbohrung 25 am Gehäusebauteil 19
abgestützt ist. Das hülsenförmige Schließglied 36 umfaßt mit
seinem Boden 37 den Schaft 33 des Schließgliedes 32 mit
radialem Spiel. Auf dem Schaft 33 ist eine vorgespannte
Druckfeder 39 aufgenommen, welche einerseits an der
zylinderraumabgewandten Seite des Hülsenbodens 37 und
andererseits an einem Anschlag 40 am Schließgliedschaft
angreift. Die beiden Druckfedern 38 und 39 üben jeweils eine
Schließkraft auf das zugeordnete Rückschlagventil 10 bzw. 11
aus.At the side remote from the cylinder chamber of the
Zur Erläuterung der Arbeitsweise der beiden saugseitigen
Rückschlagventile 10 und 11 sei angenommen, daß das erste
Rückschlagventil 10 auf einen Öffnungsdruck von 0,3bar und
das zweite Rückschlagventil 11 auf einen Öffnungsdruck von
1bar eingestellt sei. Außerdem sei angenommen, daß beide
Rückschlagventile 10 und 11 ihre Schließstellung einnehmen.
Der Druck des von der Förderpumpe 1 geförderten und von dem
Stromregelventil 4 mengengeregelt bemessenen Kraftstoff-Förderstroms
steht im Bohrungsabschnitt 27 der
Durchgangsbohrung 24 in der Ventilplatte 18 vor dem
geschlossenen zweiten Rückschlagventil 7 an. Während des
Saughubes des Pumpenkolbens 8 entsteht im Zylinderraum 9 ein
Unterdruck, welcher die Federkraft der Druckfeder 39
überwindet und das erste Rückschlagventil 10 in die
Offenstellung (wie gezeichnet) überführt. Während die
Sacklochbohrung 25 im Gehäusebauteil 20 zum Zylinderraum 9
hin druckentlastet ist, wirkt der im Bohrungsabschnitt 27
der Durchgangsbohrung 24 der Ventilplatte 18 anstehende
Druck des Kraftstoffs auf eine kreisringförmige Wirkfläche
am Schließglied 36 des zweiten Rückschlagventils 11, welche
einerseits durch den Dichtdurchmesser des Ventilsitzes 35
und andererseits durch den Dichtdurchmesser des
Bohrungsabschnitts 29 begrenzt ist. Überschreitet der Druck
des Kraftstoffs die auf dem Schließglied 36 lastende
Vorspannkraft der Druckfeder 38, so öffnet das zweite
Rückschlagventil 11 und Kraftstoff fließt in den
Zylinderraum 9 des Pumpenelements 7. Der in seiner Höhe vom
zugeführten Förderstrom abhängige Druck des Kraftstoffs
bricht während des Füllvorganges vor dem zweiten
Rückschlagventil 11 zusammen, so daß dieses aus der
gezeichneten Offenstellung in die Schließstellung übergeht.
Die Zumessung der Kraftstoffmenge in den Zylinderraum 9 des
Pumpenelements 7 erfolgt somit durch das zweite
Rückschlagventil 11. Während der folgenden Förderphase des
Pumpenkolbens 8 erhöht sich der Druck im Zylinderraum 9 und
das erste Rückschlagventil 10 nimmt seine Schließstellung
ein. Das gegenläufig zum ersten Rückschlagventil 10
arbeitende zweite Rückschlagventil 11 wird somit vor dem
Aufstoßen durch den vom Pumpenkolben 8 verdichteten
Kraftstoff geschützt. Während der Schließstellung des
zweiten Rückschlagventils 11 steigt der Druck des von der
Förderpumpe 1 geförderten Kraftstoffs wieder an und bewirkt
die beschriebene Ventilfunktion am nächsten in die Saugphase
gehenden Pumpenelement 7. Am Ende der Förderphase des
Pumpenelements 7 öffnet das Druckventil 12 und der
verdichtete Kraftstoff wird in die Hochdruckleitung 15
ausgestoßen.To explain the operation of the two suction
Claims (5)
- Piston pump (6) having a plurality of pump elements (7) for the high-pressure supply of fuel in fuel injection systems of internal combustion engines, in particular in a common rail injection system, having the following features:characterized by the following features:the pump elements (7) are connected on the suction side to a delivery pump (1) which delivers fuel at low pressure and in a regulated amount,each pump element (7) is assigned a first non-return valve (10) on the suction side, which non-return valve (10) can be used to control the supply of fuel into a cylinder chamber (9) of the pump element (7), which cylinder chamber (9) has a pump piston (8),the first non-return valve (10) opens counter to spring force in the suction phase of the pump element (7) and closes in the delivery phase,a second non-return valve (11) is connected ahead of the first non-return valve (10) on the inflow side,the second non-return valve (11) opens counter to spring force and closes with the assistance of spring force at pressures of the fuel delivered by the delivery pump (1) which are higher than the vacuum produced in the cylinder (9) of the pump element (7).
- Piston pump according to Claim 1, characterized by the following features:a valve plate (18) is provided which adjoins the cylinder chamber (9),a stepped through-hole (24) is formed in the valve plate (18),a first valve seat (31) to be acted on by a closing member (32) of the first non-return valve (10) is formed on an annular collar (28) of the through-hole (24) on the cylinder-chamber side, and a second valve seat (35) to be acted on by a closing member (36) of the second non-return valve (11) is formed on the said annular collar (28) of the through-hole (24) on the side remote from the cylinder chamber,in the valve plate (18) on the side remote from the cylinder chamber, the closing member (36) of the second non-return valve (11) is longitudinally displaceably guided in the through-hole (24) in a largely pressure-tight manner, the diameter of the guiding hole section (29) being greater than the sealing diameter of the associated valve seat (35),fuel is delivered by the delivery pump (1) into a hole section (27) of the through-hole (24), the said hole section (27) lying between the valve seat (35) of the second non-return valve (11) and the guiding hole section (29).
- Piston pump according to Claim 2, characterized in that the closing member (36) of the second non-return valve (11) has the shape of a sleeve whose base (37) which acts on the associated valve seat (35) is penetrated by a shank (33) of the closing member (32) of the first non-return valve (10) coaxially and with play.
- Piston pump according to Claim 3, characterized in that the closing member (36) of the second non-return valve (11) is supported on a housing component (19) of the pump element (7) on the side remote from the cylinder chamber by a prestressed compression spring (38).
- Piston pump according to Claim 3, characterized in that accommodated on the shank (33) of the closing member (32) of the first non-return valve (10) is a prestressed compression spring (39) which acts on one side on the side remote from the cylinder chamber of the sleeve base (37) of the second non-return valve (11) and on the other side on a stop (40) on the closing-member shank (33).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19860672A DE19860672A1 (en) | 1998-12-29 | 1998-12-29 | Piston pump for high-pressure fuel generation |
| DE19860672 | 1998-12-29 | ||
| PCT/DE1999/003643 WO2000039450A1 (en) | 1998-12-29 | 1999-11-16 | Piston pump for high-pressure fuel generation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1141539A1 EP1141539A1 (en) | 2001-10-10 |
| EP1141539B1 true EP1141539B1 (en) | 2005-02-23 |
Family
ID=7893086
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99963253A Expired - Lifetime EP1141539B1 (en) | 1998-12-29 | 1999-11-16 | Piston pump for high-pressure fuel generation |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6568927B1 (en) |
| EP (1) | EP1141539B1 (en) |
| JP (1) | JP2002533612A (en) |
| DE (2) | DE19860672A1 (en) |
| WO (1) | WO2000039450A1 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10139054C1 (en) * | 2001-08-08 | 2003-01-30 | Bosch Gmbh Robert | Operating method for direct fuel injection engine has controlled inlet valve with variable opening duration controlling fuel quantity supplied to common-rail for fuel injection valves |
| ITTO20011039A1 (en) * | 2001-10-30 | 2003-04-30 | Ct Studi Componenti Per Veicol | SUCTION VALVE FOR A HIGH PRESSURE PUMP, IN PARTICULAR FOR FUEL OF AN ENDOTHERMAL ENGINE. |
| DE10229396A1 (en) * | 2002-06-29 | 2004-01-22 | Robert Bosch Gmbh | Radial piston pump for high-pressure fuel supply in injection systems of internal combustion engines with improved efficiency |
| DE10247564A1 (en) * | 2002-10-11 | 2004-04-22 | Robert Bosch Gmbh | Operating common rail fuel injection system for combustion engine involves driving pressure regulating valve if fuel quantity less than threshold so defined leakage occurs at pressure regulating valve |
| KR20060127128A (en) | 2004-02-11 | 2006-12-11 | 로베르트 보쉬 게엠베하 | High pressure pumps, especially for fuel injectors in engine |
| DE602004005051T2 (en) * | 2004-11-12 | 2007-11-22 | C.R.F. S.C.P.A. | High-pressure pump with a device for controlling the flow for a fuel injection system |
| US20060255657A1 (en) * | 2005-05-13 | 2006-11-16 | De Ojeda William | High pressure fluid system inlet throttle and method |
| DE102005023323A1 (en) * | 2005-05-20 | 2006-11-23 | Siemens Ag | Non-return valve for fitting into machine housings has casing, in which valve stem and plate are mounted which are biased towards open position by spring above them |
| DE102005057301A1 (en) * | 2005-12-01 | 2007-06-14 | Robert Bosch Gmbh | Brake system for a vehicle |
| DE102006017036A1 (en) * | 2006-04-11 | 2007-10-18 | Siemens Ag | Radial piston pump for fuel high pressure supply in an internal combustion engine |
| ATE487055T1 (en) * | 2006-06-09 | 2010-11-15 | Fiat Ricerche | FUEL INJECTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE |
| DE102007004605B4 (en) * | 2007-01-30 | 2009-08-13 | Continental Automotive Gmbh | High pressure pump and injection system for an internal combustion engine with a high pressure pump |
| US20090139494A1 (en) * | 2007-12-04 | 2009-06-04 | Denso International America, Inc. | Dual piston direct injection fuel pump |
| GB0812888D0 (en) * | 2008-07-15 | 2008-08-20 | Delphi Tech Inc | Improvements relating to fuel pumps |
| KR100992227B1 (en) * | 2008-10-27 | 2010-11-05 | 현대중공업 주식회사 | Cavitation damage prevention device of diesel engine fuel injection pump |
| JP5256458B2 (en) * | 2010-09-21 | 2013-08-07 | Ｎｓｓｌ株式会社 | Circulating filtration separation method for high viscosity material, and circulation filtration separation apparatus using the same |
| US10288023B2 (en) * | 2014-12-24 | 2019-05-14 | Robert Bosch Gmbh | Pump unit for feeding fuel, preferably diesel fuel, to an internal combustion engine |
| DE102016200232A1 (en) * | 2016-01-12 | 2017-07-13 | Continental Automotive Gmbh | Fuel injection system |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB564725A (en) * | 1943-07-01 | 1944-10-10 | Robert Pettigrew Finlay | Improvements in or relating to reciprocating ram pumps |
| DE3144361A1 (en) * | 1981-11-07 | 1983-05-19 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES |
| WO1986000667A1 (en) * | 1984-07-03 | 1986-01-30 | Baralaba Pty Ltd | Liquid pump |
| DE3741638C1 (en) * | 1987-12-09 | 1988-12-01 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines, in particular diesel internal combustion engines |
| DE4135595A1 (en) * | 1991-10-29 | 1993-05-06 | Robert Bosch Gmbh, 7000 Stuttgart, De | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE4213798C2 (en) | 1992-04-27 | 2002-10-24 | Bosch Gmbh Robert | Radial piston pump, in particular fuel pump for internal combustion engines |
| JPH074332A (en) * | 1993-06-18 | 1995-01-10 | Yamaha Motor Co Ltd | High pressure fuel pump for internal combustion engine |
| US6257499B1 (en) * | 1994-06-06 | 2001-07-10 | Oded E. Sturman | High speed fuel injector |
| DE19549108A1 (en) * | 1995-12-29 | 1997-07-03 | Bosch Gmbh Robert | High-pressure fuel generation system for a fuel injection system used in internal combustion engines |
| EP0816672B1 (en) * | 1996-07-05 | 2003-04-09 | Nippon Soken, Inc. | High-pressure pump |
| DE19644915A1 (en) * | 1996-10-29 | 1998-04-30 | Bosch Gmbh Robert | high pressure pump |
| DE19729790C2 (en) * | 1997-07-11 | 2002-08-29 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
| DE19744577A1 (en) * | 1997-10-09 | 1999-04-22 | Bosch Gmbh Robert | Radial piston pump for high pressure fuel supply in motor vehicles |
| DE19802475A1 (en) * | 1998-01-23 | 1999-07-29 | Bosch Gmbh Robert | Radial piston pump to supply fuel at high pressure for fuel injection system of internal combustion engine |
| DE19834120A1 (en) * | 1998-07-29 | 2000-02-03 | Bosch Gmbh Robert | Fuel supply system of an internal combustion engine |
| DE19848040A1 (en) * | 1998-10-17 | 2000-04-20 | Bosch Gmbh Robert | Radial piston pump for high fuel pressure in IC engines with common-rail injection systems has two plates engaging fully on each other, and second back pressure valve between first plate and pump housing |
-
1998
- 1998-12-29 DE DE19860672A patent/DE19860672A1/en not_active Withdrawn
-
1999
- 1999-11-16 EP EP99963253A patent/EP1141539B1/en not_active Expired - Lifetime
- 1999-11-16 US US09/869,524 patent/US6568927B1/en not_active Expired - Fee Related
- 1999-11-16 DE DE59911667T patent/DE59911667D1/en not_active Expired - Lifetime
- 1999-11-16 WO PCT/DE1999/003643 patent/WO2000039450A1/en active IP Right Grant
- 1999-11-16 JP JP2000591322A patent/JP2002533612A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE19860672A1 (en) | 2000-07-13 |
| JP2002533612A (en) | 2002-10-08 |
| EP1141539A1 (en) | 2001-10-10 |
| WO2000039450A1 (en) | 2000-07-06 |
| US6568927B1 (en) | 2003-05-27 |
| WO2000039450A8 (en) | 2000-08-17 |
| DE59911667D1 (en) | 2005-03-31 |
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