EP0801710B1 - Fuel injection device for internal combustion engines - Google Patents
Fuel injection device for internal combustion engines Download PDFInfo
- Publication number
- EP0801710B1 EP0801710B1 EP19960934351 EP96934351A EP0801710B1 EP 0801710 B1 EP0801710 B1 EP 0801710B1 EP 19960934351 EP19960934351 EP 19960934351 EP 96934351 A EP96934351 A EP 96934351A EP 0801710 B1 EP0801710 B1 EP 0801710B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- bore
- injection device
- fuel injection
- 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
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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
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/464—Inlet valves of the check valve type
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7838—Plural
Definitions
- the invention is based on a fuel injection device for internal combustion engines according to the preamble of the patent claim 1 off.
- Fuel injection system promotes a high pressure pump Fuel from a low pressure reservoir into a high pressure plenum, of which a variety of injectors is supplied.
- the low pressure reservoir at known injection device through a fuel tank formed from the fuel with a low pre-pressure through a feed pump via a feed line into the Pump work space designed as a piston pump High pressure pump is promoted.
- the high pressure pump into the low pressure reservoir and out to prevent the high pressure plenum in the high pressure pump is one in the housing of the high pressure pump Integrated pressure valve in the delivery line and in the High pressure line used.
- the fuel injection device according to the invention for Internal combustion engines with the characteristic features of the Claim 1 has the advantage that the Pressure valves of the delivery line and the high pressure line in a common valve bank are integrated. It is this common valve bank also advantageously inserted into the housing of the high pressure pump, so that a compact and very low-strength design achieved can be. In addition, the separate installation of the Pressure valves in the individual lines, what the Installation effort significantly reduced.
- Another advantage is the axially one behind the other Arrangement of the individual pressure valves in the Valve bank achieved the greatest possible wall thickness in the area of the pressure rooms with constant External dimensions enabled.
- An embodiment of the invention Is fuel injection device for internal combustion engines shown in the drawing and will be described in more detail below explained.
- FIG. 1 shows a section through part of the High pressure pump and through the valve bank as well as the schematic representation of the connecting lines.
- the fuel injection device shown in Figure 1 for internal combustion engines has one High pressure pump 1, in the housing 3 a Cylinder bore 5 is provided, in which a pump piston 7 axially from a cam drive (not shown) and driven here.
- the pump piston 7 limits doing so with its end face facing away from the cam drive a pump work space 9 in the cylinder bore 5, the the side away from the pump piston from one to the other Bore extension of the cylinder bore 5 used Valve bank 11 is limited.
- the pump work space 9 is thereby via the valve bank 11 with a delivery line 13 connectable, which starts from a fuel tank 15 and in a feed pump 17 is inserted through which the Fuel from the fuel tank 15 via the delivery line 13 and the valve bank 11 with a low pre-pressure in the pump work space 9 of the high pressure pump 1 is promoted.
- a high-pressure line is still connected to the valve bank 11 19 connected via which the pump work space 9 with a High-pressure plenum 21 can be connected, of which a large number from injection lines 23 to the individual in the combustion chamber of the internal combustion engine protruding injection valves 25 dissipate.
- valve bank 11 first has a valve body 27, which is inserted into the pump housing 3 in this way, that he had one end face on one between the Cylinder bore 5 and its diameter expansion formed bore paragraph 29 of the pump housing 3 to the system arrives.
- valve body 27 from one in the Bore of the pump housing 3 screwed connection piece 33 acts on the valve body 27 axially against the a stopper-forming bore paragraph 29 clamped and on whose end protruding from the pump housing 3 High pressure line 19 is connected.
- the valve body 27 has an end face 31 thereof outgoing guide bore 35 in which a first Valve member 37 is guided axially. That on the peripheral surface Flattened cylindrical first valve member 37 has a conical arranged on an annular collar Sealing surface 39 with which it is conical with a first Valve seat 41 cooperates on the valve body 27, which on Exit of the guide bore 35 on the end face 31 is formed.
- the first valve member 37 also dips its end protruding from the valve body 27 into a through hole 43 adjoining the first valve seat 41 in the connecting piece 33 in which a first valve spring 45 is arranged between the first valve member 37 and a support part 47 which is supported on a shoulder of the bore is clamped with a through opening and the thereby first valve member 37 in contact with the first valve seat 41 keeps pressed.
- first valve member 37 there is also one of its lower end face 49 facing away from the connecting piece 33 outgoing blind bore 51 is provided in the second Valve member 53 is guided axially.
- This second valve member 53 has at its end protruding from the blind bore 51 conical or formed by a reduction in cross section spherical sealing surface 55 with which it with a second valve seat 57 cooperates on the valve body 27.
- the second valve seat 57 is adjacent to an Diameter expanded pressure chamber 59 in the valve body 27, which along the first valve member 37 in the Guide bore 35 up to the first valve seat 41 extends.
- a second one Valve spring 61 clamped, which the second valve member 53 in System on the second valve seat 57 keeps pressed.
- one Cross bore 63 in the wall of the first valve member 37 provided the pressure chamber 59 with which the second Valve spring 61 receiving reset space 65 connects.
- an annular space 67 is arranged, which is connected to the delivery line 13 is connected and via a bore 69 in Valve body 27 is connected to a bag space 71 which along the second valve member 53 to the End of the second valve seat 57 facing away from the pressure chamber 59 extends.
- Another connecting hole 73 opens from Pump work space 9 of the high pressure pump 1 starting in the Pressure chamber 59 of valve bank 11.
- the fuel injection device according to the invention works in the following way.
- the High-pressure pump 1 flows under the pre-delivery pressure Fuel from the fuel tank 15 via the delivery line 13 and the annular space 67 first into the pocket space 71 arises with simultaneous suction stroke movement of the Pump piston 7 towards bottom dead center one Pressure difference between the bag space 71 and the pressure space 59, so that the second valve member 53 counter to the Restoring force of the second valve spring 61 from the second Valve seat 57 lifts off and the fuel from bag space 71 over the opening cross section at the second valve seat 57 in the Pressure chamber 59 and via the connection bore 73 further in the pump work space 9 can flow.
- the connection of the pressure chamber 59 with the high pressure line 19 is closed by the first valve member 37, the force of the first valve spring 45 being greater than the pressure force of the inflowing fuel is designed.
- the pressure in the high pressure line 19 acts Closing direction of the first valve member 37.
- the second valve member 53 becomes an additional force the second valve spring 61, which is under high pressure, via the transverse bore 63 into the reset space 65 fuel flowing into the second valve seat 57 pressed so that the second valve member 53 despite the axial Opening stroke movement of the first valve member 37 safely in System remains on the second valve seat 57 and so on Backflow of fuel into the delivery line 13 prevented.
Abstract
Description
Die Erfindung geht von einer Kraftstoffeinspritzeinrichtung
für Brennkraftmaschinen nach der Gattung des Patentanspruchs
1 aus. Bei einer derartigen aus der WO-A-95/25887 bekannten
Kraftstoffeinspritzeinrichtung fördert eine Hochdruckpumpe
Kraftstoff aus einem Niederdruckreservoir in einen Hochdrucksammelraum,
von dem eine Vielzahl von Einspritzventilen
versorgt wird. Dabei wird das Niederdruckreservoir bei der
bekannten Einspritzeinrichtung durch einen Kraftstofftank
gebildet, aus dem Kraftstoff mit einem niedrigen Vordruck
durch eine Förderpumpe über eine Förderleitung in den
Pumpenarbeitsraum der als Kolbenpumpe ausgebildeten
Hochdruckpumpe gefördert wird.The invention is based on a fuel injection device
for internal combustion engines according to the preamble of the
Um ein Zurückströmen von Kraftstoff aus dem Pumpenarbeitsraum der Hochdruckpumpe in das Niederdruckreservoir und aus dem Hochdrucksammelraum in den Hochdruckpumpe zu verhindern ist jeweils ein in das Gehäuse der Hochdruckpumpe integriertes Druckventil in die Förderleitung und in die Hochdruckleitung eingesetzt.To return fuel from the pump workspace the high pressure pump into the low pressure reservoir and out to prevent the high pressure plenum in the high pressure pump is one in the housing of the high pressure pump Integrated pressure valve in the delivery line and in the High pressure line used.
Dabei weist die bekannten Einspritzeinrichtungen jedoch den Nachteil auf, daß die einzelnen Druckventile jeweils in den im Gehäuse der Hochdruckpumpe verlaufenden Teilen der Hochdruckleitung und der Förderleitung eingesetzt sind, was einen erheblichen Bau- und Montageaufwand zur Folge hat. However, the known injection devices have the Disadvantage that the individual pressure valves in each parts of the running in the housing of the high pressure pump High pressure line and the delivery line are used, what has a considerable construction and assembly effort.
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung für
Brennkraftmaschinen mit den kennzeichnenden Merkmalen des
Patentanspruchs 1 hat demgegenüber den Vorteil, daß die
Druckventile der Förderleitung und der Hochdruckleitung in
einen gemeinsamen Ventilverband integriert sind. Dabei ist
dieser gemeinsame Ventilverband zudem in vorteilhafter Weise
in das Gehäuse der Hochdruckpumpe eingesetzt, so daß eine
kompakte und sehr festigkeitsgünstige Bauform erreicht
werden kann. Zudem entfällt nun der getrennte Einbau der
Druckventile in die einzelnen Leitungen, was den
Montageaufwand erheblich verringert.The fuel injection device according to the invention for
Internal combustion engines with the characteristic features of the
Durch das Führen der einzelnen Ventilglieder ineinander kann der benötigte Bauraum zudem noch einmal verringert werden, so daß der Ventilverband in konstruktiv einfacher Weise in Achsrichtung des Pumpenkolbens in das Pumpengehäuse eingesetzt werden kann. Dabei bildet ein Teil des Ventilverbandes die Begrenzung des Pumpenarbeitsraumes auf Durch das Führen der einzelnen Ventilglieder ineinander kann der benötigte Bauraum zudem noch einmal verringert werden, so daß der Ventilverband in konstruktiv einfacher Weise in Achsrichtung des Pumpenkolbens in das Pumpengehäuse eingesetzt werden kann. Dabei bildet ein Teil des Ventilverbandes die Begrenzung des Pumpenarbeitsraumes auf der dem Pumpenkolben abgewandten Seite und ein weiterer Teil bildet zugleich den ohnehin benötigten Anschlußstutzen der Hochdruckpumpe an die Hochdruckleitung.By guiding the individual valve elements into one another the installation space required is also reduced again, so that the valve bank in a structurally simple manner in Axial direction of the pump piston in the pump housing can be used. It forms part of the Valve group on the limitation of the pump work space By guiding the individual valve elements into one another the installation space required is also reduced again, so that the valve bank in a structurally simple manner in Axial direction of the pump piston in the pump housing can be used. It forms part of the Valve group on the limitation of the pump work space the side facing away from the pump piston and another part at the same time forms the connection piece required anyway High pressure pump to the high pressure line.
Ein weiterer Vorteil wird durch die axial hintereinanderliegende Anordnung der einzelnen Druckventile im Ventilverband erreicht, die eine möglichst große Wandstärke im Bereich der Druckräume bei gleichbleibenden Außenabmessungen ermöglicht.Another advantage is the axially one behind the other Arrangement of the individual pressure valves in the Valve bank achieved the greatest possible wall thickness in the area of the pressure rooms with constant External dimensions enabled.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the The invention relates to the drawing, the Description and the patent claims.
Ein Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen ist in der Zeichnung dargestellt und wird im folgenden näher erläutert.An embodiment of the invention Is fuel injection device for internal combustion engines shown in the drawing and will be described in more detail below explained.
Es zeigt die Figur 1 einen Schnitt durch einen Teil der Hochdruckpumpe und durch den Ventilverband sowie die schematische Darstellung der Anschlußleitungen.1 shows a section through part of the High pressure pump and through the valve bank as well as the schematic representation of the connecting lines.
Die in der Figur 1 dargestellte Kraftstoffeinspritzeinrichtung
für Brennkraftmaschinen weist eine
Hochdruckpumpe 1 auf, in deren Gehäuse 3 eine
Zylinderbohrung 5 vorgesehen ist, in der ein Pumpenkolben 7
von einem nicht näher dargestellten Nockenantrieb axial hin-
und hergehend angetrieben wird. Der Pumpenkolben 7 begrenzt
dabei mit seiner dem Nockenantrieb abgewandten Stirnfläche
einen Pumpenarbeitsraum 9 in der Zylinderbohrung 5, der auf
der pumpenkolbenfernen Seite von einem in eine
Bohrungserweiterung der Zylinderbohrung 5 eingesetzten
Ventilverband 11 begrenzt wird. Der Pumpenarbeitsraum 9 ist
dabei über den Ventilverband 11 mit einer Förderleitung 13
verbindbar, die von einem Kraftstofftank 15 ausgeht und in
die eine Förderpumpe 17 eingesetzt ist, durch die der
Kraftstoff aus dem Kraftstofftank 15 über die Förderleitung
13 und den Ventilverband 11 mit einem niedrigen Vordruck in
den Pumpenarbeitsraum 9 der Hochdruckpumpe 1 gefördert wird.
An den Ventilverband 11 ist weiterhin eine Hochdruckleitung
19 angeschlossen, über die der Pumpenarbeitsraum 9 mit einem
Hochdrucksammelraum 21 verbindbar ist, von dem eine Vielzahl
von Einspritzleitungen 23 zu den einzelnen in den Brennraum
der Brennkraftmaschine ragenden Einspritzventilen 25
abführen.The fuel injection device shown in Figure 1
for internal combustion engines has one
Um dabei ein ungewolltes Rückströmen von Kraftstoff aus dem
Pumpenarbeitsraum 9 in die Förderleitung 13 und von der
Hochdruckleitung 19 in den Pumpenarbeitsraum 9 zu vermeiden,
ist jeweils ein Druckventil in die Hochdruckleitung 19 und
die Förderleitung 13 eingesetzt, die im gemeinsamen, in das
Pumpengehäuse 3 eingesetzten Ventilverband 11 untergebracht
sind.To prevent an unwanted backflow of fuel from the
Pump
Dazu weist der Ventilverband 11 zunächst einen Ventilkörper
27 auf, der derart in das Pumpengehäuse 3 eingesetzt ist,
daß er mit seiner einen Stirnseite an einem zwischen der
Zylinderbohrung 5 und deren Durchmessererweiterung
gebildeten Bohrungsabsatz 29 des Pumpengehäuses 3 zur Anlage
gelangt. An seiner dem Bohrungsabsatz 29 abgewandten
Stirnfläche 31 wird der Ventilkörper 27 von einem in die
Bohrung des Pumpengehäuses 3 eingeschraubten Anschlußstutzen
33 beaufschlagt, der den Ventilkörper 27 axial gegen den
einen Anschlag bildenden Bohrungsabsatz 29 verspannt und an
dessen aus dem Pumpengehäuse 3 ragenden Ende die
Hochdruckleitung 19 angeschlossen ist.For this purpose, the valve bank 11 first has a
Der Ventilkörper 27 weist eine von seiner Stirnfläche 31
ausgehende Führungsbohrung 35 auf, in der ein erstes
Ventilglied 37 axial geführt ist. Das an der Umfangsfläche
Abflachungen aufweisende zylinderförmige erste Ventilglied
37 weist dabei eine an einem Ringbund angeordnete konische
Dichtfläche 39 auf, mit der es mit einem ersten konischen
Ventilsitz 41 am Ventilkörper 27 zusammenwirkt, der am
Austritt der Führungsbohrung 35 an der Stirnfläche 31
gebildet ist. Dabei taucht das erste Ventilglied 37 mit
seinem aus dem Ventilkörper 27 herausragenden Ende in eine,
an den ersten Ventilsitz 41 angrenzende Durchgangsbohrung 43
im Anschlußstutzen 33, in der eine erste Ventilfeder 45
angeordnet ist, die zwischen dem ersten Ventilglied 37 und
einem sich an einem Bohrungsabsatz abstützenden Stützteil 47
mit Durchgangsöffnung eingespannt ist und die dabei das
erste Ventilglied 37 in Anlage an den ersten Ventilsitz 41
gepreßt hält.The
Im ersten Ventilglied 37 ist weiterhin eine von dessen
unterer, dem Anschlußstutzen 33 abgewandter Stirnfläche 49
ausgehende Sackbohrung 51 vorgesehen, in der ein zweites
Ventilglied 53 axial geführt ist. Dieses zweite Ventilglied
53 weist an seinem aus der Sackbohrung 51 ragenden Ende eine
durch eine Querschnittsverringerung gebildete konische oder
kugelförmige Dichtfläche 55 auf, mit der es mit einem
zweiten Ventilsitz 57 am Ventilkörper 27 zusammenwirkt.
Dabei grenzt der zweite Ventilsitz 57 an einen im
Durchmesser erweitereten Druckraum 59 im Ventilkörper 27,
der sich entlang des ersten Ventilgliedes 37 in der
Führungsbohrung 35 bis an den ersten Ventilsitz 41
erstreckt.In the
Zwischen dem geschlossenen Ende der Sackbohrung 51 und dem
darin geführten zweiten Ventilglied 53 ist eine zweite
Ventilfeder 61 eingespannt, die das zweite Ventilglied 53 in
Anlage am zweiten Ventilsitz 57 gepreßt hält. Zudem ist eine
Querbohrung 63 in der Wand des ersten Ventilgliedes 37
vorgesehen, die den Druckraum 59 mit dem die zweite
Ventilfeder 61 aufnehmenden Rückstellraum 65 verbindet.
Zwischen dem Ventilkörper 27 und der Wand des Pumpengehäuses
3 ist ein Ringraum 67 angeordnet, der mit der Förderleitung
13 verbunden ist und der über eine Bohrung 69 im
Ventilkörper 27 mit einem Sackraum 71 verbunden ist, der
sich entlang des zweiten Ventilgliedes 53 bis an das dem
Druckraum 59 abgewandte Ende des zweiten Ventilsitzes 57
erstreckt.Between the closed end of the
Eine weitere Verbindungsbohrung 73 mündet vom
Pumpenarbeitsraum 9 der Hochdruckpumpe 1 ausgehend in den
Druckraum 59 des Ventilverbandes 11.Another connecting
Die erfindungsgemäße Kraftstoffeinspritzeinrichtung arbeitet in folgender Weise.The fuel injection device according to the invention works in the following way.
Während des Befüllens des Pumpenarbeitsraumes 9 der
Hochdruckpumpe 1 strömt der unter Vorförderdruck stehende
Kraftstoff aus dem Kraftstofftank 15 über die Förderleitung
13 und den Ringraum 67 zunächst in den Sackraum 71. Dabei
entsteht bei gleichzeitiger Saughubbewegung des
Pumpenkolbens 7 in Richtung unterer Totpunkt eine
Druckdifferenz zwischen dem Sackraum 71 und dem Druckraum
59, so daß das zweite Ventilglied 53 entgegen der
Rückstellkraft der zweiten Ventilfeder 61 vom zweiten
Ventilsitz 57 abhebt und der Kraftstoff aus dem Sackraum 71
über den Öffnungsquerschnitt am zweiten Ventilsitz 57 in den
Druckraum 59 und über die Verbindungsbohrung 73 weiter in
den Pumpenarbeitsraum 9 strömen kann.While filling the
Die Verbindung des Druckraumes 59 mit der Hochdruckleitung
19 ist dabei durch das erste Ventilglied 37 verschlossen,
wobei die Kraft der ersten Ventilfeder 45 dabei größer als
die Druckkraft des einströmenden Kraftstoffes ausgelegt ist.
Zudem wirkt der Druck in der Hochdruckleitung 19 in
Schließrichtung auf das erste Ventilglied 37.The connection of the
Während des sich nach Durchfahren des unteren Totpunktes
anschließenden Förderhubs des Pumpenkolbens 7 steigt der
Druck im Pumpenarbeitsraum 9 an, wobei bei Erreichen eines
Druckausgleichs zwischen Sackraum 71 und Druckraum 59 die
zweite Ventilfeder 61 das zweite Ventilglied 53 zur Anlage
an den zweiten Ventilsitz 57 zurückverschiebt, so daß die
Verbindung zwischen der Förderleitung 13 und dem
Pumpenarbeitsraum 9 verschlossen ist. Wird während des
weiteren Förderhubs des Pumpenkolbens 7 die durch den Druck
im Hochdrucksammelraum 21 und die Kraft der ersten
Ventilfeder 45 bestimmte Öffnungskraft am ersten Ventilglied
37 überschritten, hebt dieses vom ersten Ventilsitz 41 ab,
so daß der unter hohem Druck stehende Kraftstoff aus dem
Pumpenarbeitsraum 9 über die Verbindungsbohrung 73, den
Druckraum 59, den öffnungsquerschnitt am ersten Ventilsitz
41 und die Durchgangsbohrung 43 im Anschlußstutzen 33 in die
Hochdruckleitung 19 zum Hochdrucksammelraum 21 strömen kann.
Dabei wird das zweite Ventilglied 53 zusätzlich zur Kraft
der zweiten Ventilfeder 61, von unter hohem Druck stehenden,
über die Querbohrung 63 in den Rückstellraum 65
einströmenden Kraftstoff auf den zweiten Ventilsitz 57
gepreßt, so daß das zweite Ventilglied 53 trotz der axialen
Öffnungshubbewegung des ersten Ventigliedes 37 sicher in
Anlage am zweiten Ventilsitz 57 verbleibt und so ein
Rückströmen von Kraftstoff in die Förderleitung 13
verhindert.While going through bottom dead center
subsequent delivery stroke of the
Nach Absinken des Förderdruckes im Pumpenarbeitsraum 9kehrt
das erste Ventilglied 37 an seinen Ventilsitz 41 zurück und
verschließt die Hochdruckleitung 19 wieder gegen den
Pumpenarbeitsraum 9 der Hochdruckpumpe 1.After the delivery pressure in the
Claims (8)
- Fuel injection device for internal combustion engines, having a high-pressure pump (1) whose pump operating chamber (9), on the suction side, can be connected via a delivery line (13) to a fuel tank (15) and, on the pressure side, can be connected via a high-pressure line (19) to a high-pressure common rail (21), from which a multiplicity of injection lines (23) lead away to the individual injection valves (25), and having pressure valves which are respectively arranged in the delivery line (13) and in the high-pressure line (19), are arranged in a common valve assembly (11) and via which reverse flow of fuel from the pump operating chamber (9) into the delivery line (13) and from the high-pressure line (19) into the pump operating chamber (9) is prevented, the pressure valves in the delivery line (13) and the high-pressure line (19) being arranged in a common valve assembly (11), characterized in that the valve assembly (11) is formed by a valve body (27) inserted into a bore in the pump housing (3) and a connecting piece (33) which braces the said valve body axially against a stop (29) and belongs to the high-pressure line (19), a first valve element (37) being guided axially in a guide bore (35) in the valve body (27) and having a sealing face (39), with which it interacts with the first valve seat (41) on the valve body (27), and with a second valve element (53), which is guided axially in a blind bore (51) in the first valve element (37) and which has a sealing face (55) with which it interacts with a second valve seat (57) on the valve body (27).
- Fuel injection device according to Claim 1, characterized in that the first valve element (37) projects with its one end into a through bore (43) which belongs to the connecting piece (33) and adjoins the first valve seat (41), and in which there is arranged a first valve spring (45), which is clamped in between the first valve element (37) and an offset in the through bore (43), and which presses the first valve element (37) into contact with the first valve seat (41).
- Fuel injection device according to Claim 2, characterized in that, between that end of the second valve element (53) which projects into the blind bore (51) in the first valve element (37), and the closed wall of the blind bore (51), a second valve spring (61) is clamped in and presses the second valve element (53) against the second valve seat (57).
- Fuel injection device according to Claim 3, characterized in that, between the valve body (27) and the wall of the pump housing (3) an annular chamber (67) is provided, into which the delivery line (13) opens and which is connected via a bore (69) to a blind chamber (71) in the valve body (27), which extends as far as the second valve seat (57).
- Fuel injection device according to Claim 4, characterized in that the end of the second valve seat (57) which faces away from the blind chamber (71) is adjoined by a pressure chamber (59), which is continuously connected to the pump operating chamber (9) via a connecting bore (73) and which extends along the first valve element (37) as far as the first valve seat (41).
- Fuel injection device according to Claim 5, characterized in that a transverse bore (63) is provided in the first valve element (37) and, starting from the pressure chamber (59), opens into the closed end of the blind bore (51).
- Fuel injection device according to Claim 1, characterized in that the first and second valve seats (41, 57) on the valve body (27), and also the sealing faces (39, 55) interacting with these on the first and second valve elements (37, 53) are of conical design.
- Fuel injection device according to Claim 1, characterized in that the pressure valves of the high-pressure line (19) and of the delivery line (13) are designed as non-return valves.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19541507 | 1995-11-08 | ||
| DE1995141507 DE19541507A1 (en) | 1995-11-08 | 1995-11-08 | Fuel injection device for internal combustion engines |
| PCT/DE1996/001497 WO1997017538A1 (en) | 1995-11-08 | 1996-08-09 | Fuel injection device for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0801710A1 EP0801710A1 (en) | 1997-10-22 |
| EP0801710B1 true EP0801710B1 (en) | 2002-03-06 |
Family
ID=7776849
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP19960934351 Expired - Lifetime EP0801710B1 (en) | 1995-11-08 | 1996-08-09 | Fuel injection device for internal combustion engines |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US5839414A (en) |
| EP (1) | EP0801710B1 (en) |
| JP (1) | JP3830524B2 (en) |
| KR (1) | KR100445715B1 (en) |
| BR (1) | BR9606893A (en) |
| DE (2) | DE19541507A1 (en) |
| RU (1) | RU2170363C2 (en) |
| WO (1) | WO1997017538A1 (en) |
Families Citing this family (26)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19710891A1 (en) * | 1997-03-15 | 1998-09-17 | Bosch Gmbh Robert | Pressure valve |
| DE19919430C1 (en) * | 1999-04-29 | 2000-10-19 | Bosch Gmbh Robert | Injection pump |
| DE10059425A1 (en) * | 2000-11-30 | 2002-06-06 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engines, in particular diesel engines |
| DE10129308C1 (en) * | 2001-06-18 | 2002-11-28 | Man B & W Diesel As Kopenhagen | Fuel feed device for 2-stroke diesel engine used for e.g., for a ships drive, has at least one valve closure of fuel injection valves for each engine cylinder de-activated at partial load by associated control piston |
| DE10136925C1 (en) * | 2001-07-30 | 2002-12-12 | Orange Gmbh | Fuel injector for internal combustion engine with high-pressure piston pump and valves has pump working area linked on intake to low-pressure source and on compression to high-pressure reservoir |
| DE10136926C1 (en) * | 2001-07-30 | 2003-01-16 | Orange Gmbh | Fuel injection device, for internal combustion engine, has working space of high pressure pump coupled to low pressure source and high pressure reservoir during suction and compression strokes |
| DE10220281A1 (en) * | 2002-05-07 | 2003-11-27 | Bosch Gmbh Robert | Fuel pump, in particular for an internal combustion engine with direct injection |
| US7086388B2 (en) * | 2003-08-04 | 2006-08-08 | Delphi Technologies, Inc. | Combination valve for fuel system |
| DE10357612A1 (en) * | 2003-12-10 | 2005-07-07 | Robert Bosch Gmbh | Valve arrangement, in particular inlet valve of a high-pressure fuel pump |
| JP2006183647A (en) * | 2004-12-28 | 2006-07-13 | Bosch Corp | Fuel supply pump |
| US7412971B2 (en) * | 2005-01-27 | 2008-08-19 | Advanced Global Equities And Intellectual Properties, Inc. | Selectively detachable helix ring for a fuel injector |
| JP2008215148A (en) * | 2007-03-01 | 2008-09-18 | Yanmar Co Ltd | Supply pump |
| US7628140B2 (en) * | 2007-09-27 | 2009-12-08 | Caterpillar Inc. | High-pressure pump or injector plug or guide with decoupled sealing land |
| DE102009027273A1 (en) | 2009-06-29 | 2010-12-30 | Robert Bosch Gmbh | High-pressure pump for fuel injection device of internal-combustion engine of common-rail-system of passenger car, has pump element including pump piston that is partially arranged in cylinder head, which is formed as multipart |
| US8132558B2 (en) * | 2009-12-01 | 2012-03-13 | Stanadyne Corporation | Common rail fuel pump with combined discharge and overpressure relief valves |
| US8997716B2 (en) * | 2010-11-15 | 2015-04-07 | Governors America Corp. | Controlled nozzle injection method and apparatus |
| JP5653288B2 (en) * | 2011-04-27 | 2015-01-14 | 株式会社デンソー | Constant residual pressure valve |
| US9464631B2 (en) * | 2013-01-08 | 2016-10-11 | Cummins Inc. | Fuel pump for an internal combustion engine |
| CN104018968B (en) * | 2013-03-01 | 2019-04-23 | 罗伯特·博世有限公司 | High-pressure fuel-feed pump and diesel engine with this high-pressure fuel-feed pump |
| DE102013209021A1 (en) * | 2013-05-15 | 2014-11-20 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump of an internal combustion engine |
| DE102013226953B4 (en) | 2013-12-20 | 2016-10-06 | Robert Bosch Gmbh | High pressure pump with a valve piece |
| CN206320002U (en) * | 2016-10-14 | 2017-07-11 | 罗伯特·博世有限公司 | High-pressure plunger pump and its high potential assembly, inlet valve |
| US11015558B2 (en) * | 2019-02-15 | 2021-05-25 | Delphi Technologies Ip Limited | Combination outlet valve and pressure relief valve and fuel pump using the same |
| CN110529315B (en) * | 2019-08-06 | 2021-03-19 | 一汽解放汽车有限公司 | Oil inlet valve, high-pressure oil pump and engine |
| US10907600B1 (en) * | 2019-12-16 | 2021-02-02 | Delphi Technologies Ip Limited | Fuel pump and outlet valve seat thereof |
| US11352994B1 (en) | 2021-01-12 | 2022-06-07 | Delphi Technologies Ip Limited | Fuel pump and combination outlet and pressure relief valve thereof |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR962293A (en) * | 1950-06-07 | |||
| FR1239134A (en) * | 1958-11-10 | 1960-08-19 | Muenchner Motorzubehor G M B H | Valve device for piston pumps |
| CH399072A (en) * | 1963-01-21 | 1966-03-31 | Sulzer Ag | Fuel injection pump for a piston internal combustion engine |
| US3726612A (en) * | 1970-12-07 | 1973-04-10 | Greene Res Eng Co | Pump |
| US4026322A (en) * | 1976-02-11 | 1977-05-31 | Flow Industries, Inc. | Reciprocating pump check valve assembly |
| US4277229A (en) * | 1977-11-21 | 1981-07-07 | Partek Corporation Of Houston | High pressure fluid delivery system |
| JPS572458A (en) * | 1980-06-05 | 1982-01-07 | Nippon Denso Co Ltd | Fuel injection device |
| US4340084A (en) * | 1980-08-28 | 1982-07-20 | Houdaille Industries, Inc. | Check valve |
| US4729401A (en) * | 1987-01-29 | 1988-03-08 | Burron Medical Inc. | Aspiration assembly having dual co-axial check valves |
| DE3820707A1 (en) * | 1988-06-18 | 1989-12-21 | Bosch Gmbh Robert | INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| US5176175A (en) * | 1989-03-29 | 1993-01-05 | Cooper Industries, Inc. | Valve assembly |
| DE59504990D1 (en) * | 1994-03-23 | 1999-03-11 | Siemens Ag | ARRANGEMENT FOR INJECTING FUEL INTO THE CYLINDERS OF AN INTERNAL COMBUSTION ENGINE |
| US5636975A (en) * | 1994-04-04 | 1997-06-10 | Reynolds Metals Company | Inlet and discharge valve arrangement for a high pressure pump |
| IL110288A0 (en) * | 1994-07-12 | 1994-10-21 | Bron Dan | Self-cleaning inlet head for a fluid |
| US5605449A (en) * | 1996-01-25 | 1997-02-25 | Wendy Buskop | Suction and discharge valve arrangement for a high pressure piston pump |
-
1995
- 1995-11-08 DE DE1995141507 patent/DE19541507A1/en not_active Withdrawn
-
1996
- 1996-08-09 EP EP19960934351 patent/EP0801710B1/en not_active Expired - Lifetime
- 1996-08-09 DE DE59608839T patent/DE59608839D1/en not_active Expired - Lifetime
- 1996-08-09 WO PCT/DE1996/001497 patent/WO1997017538A1/en active IP Right Grant
- 1996-08-09 BR BR9606893A patent/BR9606893A/en not_active IP Right Cessation
- 1996-08-09 KR KR1019970704640A patent/KR100445715B1/en not_active IP Right Cessation
- 1996-08-09 RU RU97113466A patent/RU2170363C2/en active
- 1996-08-09 JP JP51772897A patent/JP3830524B2/en not_active Expired - Fee Related
- 1996-08-09 US US08/860,588 patent/US5839414A/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH10512649A (en) | 1998-12-02 |
| RU2170363C2 (en) | 2001-07-10 |
| KR19980701251A (en) | 1998-05-15 |
| JP3830524B2 (en) | 2006-10-04 |
| EP0801710A1 (en) | 1997-10-22 |
| US5839414A (en) | 1998-11-24 |
| BR9606893A (en) | 1997-10-28 |
| WO1997017538A1 (en) | 1997-05-15 |
| KR100445715B1 (en) | 2004-11-06 |
| DE19541507A1 (en) | 1997-05-15 |
| DE59608839D1 (en) | 2002-04-11 |
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