EP1339968B1 - Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines - Google Patents
Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines Download PDFInfo
- Publication number
- EP1339968B1 EP1339968B1 EP01997636A EP01997636A EP1339968B1 EP 1339968 B1 EP1339968 B1 EP 1339968B1 EP 01997636 A EP01997636 A EP 01997636A EP 01997636 A EP01997636 A EP 01997636A EP 1339968 B1 EP1339968 B1 EP 1339968B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- low
- pressure
- solenoid
- piston
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000002347 injection Methods 0.000 title claims description 25
- 239000007924 injection Substances 0.000 title claims description 25
- 239000000446 fuel Substances 0.000 title claims description 16
- 238000002485 combustion reaction Methods 0.000 title claims 2
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000012528 membrane Substances 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
- F02M59/44—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
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
- F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
- F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
Definitions
- the invention relates to a solenoid valve controlled fuel injection pump according to the preamble of claim 1.
- those fuel injection pumps of the invention are relevant according to the invention Distributor type, in which a so-called I-solenoid valve is used.
- These Valve design is characterized by the fact that the flow during Abêtn radially directed from the outside inwards. Due to the flow deflection in the low pressure range an opening (positive) force is achieved. The force shortens the valve opening times.
- a basic characteristic of the type of valve in question can be seen in that is a very large low pressure area compared to the pressure step area in the high pressure region of the solenoid valve results. Therefore, even at low Pressure fluctuations in the low pressure range relatively large forces. These forces cause opening time variations that lead to injection quantity spreads (from hub to hub). To the forces mentioned - at least partly - to compensate and thus their adverse effects largely To avoid, in the valve type in question is a low-pressure compensating piston provided, which cooperates with the solenoid valve.
- the low pressure compensation piston So has the function of a stable opening behavior of Solenoid valve to effect.
- the object of the present invention is to take appropriate measures that undesirable delays in the opening process of the solenoid valve avoided become.
- US-A-5,318,001 discloses a solenoid valve controlled fuel injection pump known wherein the injection duration via the opening of the solenoid valve is controlled.
- the solenoid valve has a valve needle, via a valve seat in the pump body a High pressure area separates from a low pressure area or combines. When separating is in a pressure regulator or Pressure relief valve designated membrane group Storage volume formed when fueling nachschiebt and thus supports the intake process or accelerated.
- the invention is illustrated in the drawing with reference to an embodiment, which will be described in detail below.
- the drawing shows - in vertical longitudinal section and partially - an embodiment of a fuel injection pump the distributor type.
- a (not shown) pump working chamber is connected via a pressure channel 11 in Distributor 10 is connected to a distributor groove 12 on the circumference of the distributor 10, from the (not shown) extending in the pump housing injection lines take their exit.
- the injection lines in turn lead to a (also not shown) injection valve.
- a Connecting channel 14 which opens into an annular groove 15.
- the annular groove 15 forms a valve seat 16 for a valve needle 17 of a (partially shown) total designated 18 solenoid valve.
- a valve needle 17 of a (partially shown) total designated 18 solenoid valve Above the solenoid valve needle 17, at 19, an electromagnet which actuates the solenoid valve 18 follows, The well-known prior art is why a detailed account omitted can.
- valve seat 16 Below the valve seat 16 extends a total of 20 numbered Blind hole bore, which has an extension 21, of which a (further) Connecting channel 22 takes its output.
- the connecting channel 22 leads to the (not shown) low-pressure part of the fuel injection pump. Consequently define valve seat 16 and solenoid valve needle 17 within the manifold 10 a high pressure area 14, 15 and a low pressure area 21.
- a low pressure balancing piston arranged axially movable, the - respectively half - left side of a common longitudinal central axis 23 of solenoid valve needle 17 and low pressure balancing pistons in total with 24 and right side the longitudinal central axis 23 is numbered 25 in total.
- the right side drawn by the longitudinal center axis 23 type 25th the low pressure balance piston marks the current state of Technique, wherein the low pressure balancing piston 25 - at 26 - in one piece is connected to the solenoid valve needle 17.
- the left side of the longitudinal central axis 23 illustrated low-pressure compensating piston 24 to the invention Design type.
- the special feature here is that solenoid valve needle 17 and low pressure balancing piston 24 as two separate and thus independently (axially) movable components are formed.
- to Guide the low-pressure compensating piston 24 has this a piston rod 27 tapered diameter, in one in the solenoid valve needle 17 introduced guide bore 28 engages. Through the guide 27/28 becomes an (otherwise possible) tilting of the low pressure balance piston 24 effectively avoided.
- the guide bore 28 is a blind hole formed, with its (upper) end 29 acts as a stop, with the free end 30 of the piston rod 27 of the low-pressure compensation piston 24th interacts.
- a compression spring (low pressure compensation spring) 32 at the rear is supported on the 33 numbered bottom of the blind hole 20.
- the low-pressure compensation spring 32 of the low-pressure compensating piston 24 pressed against the (upper) stop 29 of the guide bore 28.
- Another special feature is that at the (lower) end face 31 the low-pressure balance piston 24 a rod-shaped, from the low-pressure compensation spring 32 surrounded counterstop 34 is arranged the at the end of 35 with the same time as (lower) stroke stop for the Low-pressure balancing piston 24 acting bottom 33 of the blind hole 20 cooperates.
- the rod-shaped counter-stop 34 is used at the same time to protect the low-pressure compensation spring 32nd
- the described arrangement and design of the low pressure balance piston 24 affects the operation of the fuel injection pump as follows.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung bezieht sich auf eine magnetventilgesteuerte Kraftstoffeinspritzpumpe nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a solenoid valve controlled fuel injection pump according to the preamble of claim 1.
Hierbei handelt es sich vornehmlich um eine Kraftstoffeinspritzpumpe der sogenannten Verteilerbauart. Bei derartigen magnetventilgesteuerten Einspritzpumpen, die bevorzugt in Dieselmotoren eingesetzt werden, wird die Einspritzdauer durch das Öffnen des Magnetventils gesteuert. Damit der Dieselmotor gute Abgaswerte erreicht, muß der Druck in der Leitung möglichst schnell abfallen. Dies kann nur durch ein schnell öffnendes Magnetventil erreicht werden. Eine magnetventilgesteuerte Voreinspritzung ist nur mit einem schnell öffnenden Magnetventil möglich. Das Magnetventil muß daher so ausgeführt werden, dass sich seine Öffnungszeit durch hydraulische Kräfte verringern läßt.This is primarily a fuel injection pump of so-called distribution type. In such solenoid valve controlled injection pumps, which are preferably used in diesel engines, the injection duration controlled by opening the solenoid valve. So that the diesel engine good exhaust emissions reached, the pressure in the line must drop as quickly as possible. This can can only be achieved by a quick-opening solenoid valve. A solenoid valve controlled Pre-injection is only possible with a fast-opening solenoid valve. The solenoid valve must therefore be designed so that its opening time reduced by hydraulic forces.
Erfindungsgemäß relevant sind insbesondere solche Kraftstoffeinspritzpumpen der Verteilerbauart, in denen ein sogenanntes I-Magnetventil eingesetzt wird. Diese Ventilbauart zeichnet sich dadurch aus, dass die Strömung beim Absteuern radial von aussen nach innen gerichtet ist. Durch die Strömungsumlenkung im Niederdruckbereich wird eine öffnende (positive) Kraft erzielt. Die Kraft verkürzt die Ventilöffnungszeiten. In particular, those fuel injection pumps of the invention are relevant according to the invention Distributor type, in which a so-called I-solenoid valve is used. These Valve design is characterized by the fact that the flow during Absteuern radially directed from the outside inwards. Due to the flow deflection in the low pressure range an opening (positive) force is achieved. The force shortens the valve opening times.
Ein Grundcharakteristikum der in Rede stehenden Ventilbauart ist darin zu sehen, dass sich eine sehr große Niederdruckfläche im Vergleich zur Druckstufenfläche im Hochdruckbereich des Magnetventils ergibt. Deshalb treten schon bei geringen Druckschwankungen im Niederdruckbereich verhältnismäßig große Kräfte auf. Diese Kräfte verursachen Öffnungszeitschwankungen, die zu Einspritzmengenstreuungen (von Hub zu Hub) führen. Um die genannten Kräfte - wenigstens teilweise - zu kompensieren und damit ihre nachteiligen Auswirkungen weitgehend zu vermeiden, ist bei der in Rede stehenden Ventilbauart ein Niederdruckausgleichskolben vorgesehen, der mit dem Magnetventil zusammenwirkt. Der Niederdruckausgleichskolben hat also die Funktion, ein stabiles Öffnungsverhalten des Magnetventils zu bewirken.A basic characteristic of the type of valve in question can be seen in that is a very large low pressure area compared to the pressure step area in the high pressure region of the solenoid valve results. Therefore, even at low Pressure fluctuations in the low pressure range relatively large forces. These forces cause opening time variations that lead to injection quantity spreads (from hub to hub). To the forces mentioned - at least partly - to compensate and thus their adverse effects largely To avoid, in the valve type in question is a low-pressure compensating piston provided, which cooperates with the solenoid valve. The low pressure compensation piston So has the function of a stable opening behavior of Solenoid valve to effect.
Zu dem im Vorstehenden geschilderten Stand der Technik wird die DE 4339948 A1 genannt, die eine gattungsmäßige Kraftstoffeinspritzpumpe zum Gegenstand hat. Bei der bekannten Kraftstoffeinspritzpumpe ist der Niederdruck-Ausgleichskolben einteilig mit der Magnetventilnadel ausgeführt und koaxial zu dieser angeordnet, wobei er praktisch eine Fortsetzung der Magnetventilnadel über den Ventilsitz hinaus bildet.For the above-described prior art DE 4339948 A1 called, the subject of a generic fuel injection pump. In the known fuel injection pump is the low-pressure compensation piston made in one piece with the solenoid valve needle and arranged coaxially to this, he practically a continuation of the solenoid valve needle over the valve seat forms out.
Der Nachteil besteht darin, dass es beim Absteuem zu einer Strömungsumlenkung
auf dem Niederdruck-Ausgleichskolben kommt. Diese Strömungsumlenkung
bewirkt eine Druckerhöhung, aus der sich eine schließende Nadelkraft ergibt.
Die nachteilige Folge ist eine Verzögerung der Öffnung des Magnetventils beim
Absteuern.The disadvantage is that when Absteuem comes to a flow deflection on the low-pressure balance piston. This flow deflection causes an increase in pressure, resulting in a closing needle force.
The adverse consequence is a delay in the opening of the solenoid valve during Absteuern.
Aufgabe der vorliegenden Erfindung ist es, geeignete Maßnahmen dafür zu treffen, dass unerwünschte Verzögerungen beim Öffnungsvorgang des Magnetventils vermieden werden. The object of the present invention is to take appropriate measures that undesirable delays in the opening process of the solenoid valve avoided become.
Ferner ist durch die US-A-5 318 001 eine magnetventilgesteuerte Kraftstoffeinspritzpumpe bekannt, wobei die Einspritzdauer über das Öffnen des Magnetventils gesteuert wird. Das Magnetventil weist eine Ventilnadel auf, die über einen Ventilsitz im Pumpenkörper einen Hochdruckbereich von einem Niederdruckbereich trennt oder verbindet. Beim Trennen wird in einer als Druckregler oder Druckbegrenzungsventil bezeichneten Membrangruppe ein Speichervolumen gebildet, das beim Verbinden Kraftstoff nachschiebt und somit den Ansaugvorgang unterstützt bzw. beschleunigt. Further, US-A-5,318,001 discloses a solenoid valve controlled fuel injection pump known wherein the injection duration via the opening of the solenoid valve is controlled. The solenoid valve has a valve needle, via a valve seat in the pump body a High pressure area separates from a low pressure area or combines. When separating is in a pressure regulator or Pressure relief valve designated membrane group Storage volume formed when fueling nachschiebt and thus supports the intake process or accelerated.
Gemäß der Erfindung wird die Aufgabe bei einer Kraftstoffeinspritzpumpe der eingangs bezeichneten Art durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst.According to the invention, the object in a fuel injection pump of Initially designated type by the characterizing features of the claim 1 solved.
Vorteilhafte Weiterbildungen des Grundgedankens der Erfindung sind den Patentansprüchen 2 - 8 zu entnehmen.Advantageous developments of the basic idea of the invention are the Claims to take 2 - 8.
Durch die erfindungsgemäßen Merkmale gelingt es, die für die Funktion des Magnetventils in dessen geschlossenem Zustand wichtigen Vorteile des vorhandenen Niederdruck-Ausgleichskolbens zu erhalten. Zugleich entfallen aber die bisherigen negativen Wirkungen des Niederdruck-Ausgleichskolbens beim Öffnen des Magnetventils.Due to the features of the invention, it is possible for the function of the Solenoid valve in its closed state important advantages of the existing To obtain low pressure balancing piston. At the same time omitted the previous negative effects of the low-pressure balance piston when Opening the solenoid valve.
Die Erfindung ist in der Zeichnung anhand eines Ausführungsbeispiels veranschaulicht, das im Folgenden detailliert beschrieben wird. Die Zeichnung zeigt - im vertikalen Längsschnitt und teilweise - eine Ausführungsform einer Kraftstoffeinspritzpumpe der Verteilerbauart.The invention is illustrated in the drawing with reference to an embodiment, which will be described in detail below. The drawing shows - in vertical longitudinal section and partially - an embodiment of a fuel injection pump the distributor type.
Es bezeichnet 10 einen Verteiler, der in einem (nicht dargestellten) Pumpengehäuse
in bekannter und daher nicht näher gezeigter Weise geführt ist. Der Antrieb
des Verteilers 10 erfolgt ebenfalls in üblicher Weise, weshalb auch diesbezüglich
auf eine detaillierte Beschreibung verzichtet werden kann. It indicates 10 a distributor, which in a (not shown) pump housing
in a known and therefore not shown in detail manner is performed. The drive
the
Ein (nicht dargestellter) Pumpenarbeitsraum ist über einen Druckkanal 11 im
Verteiler 10 mit einer Verteilernut 12 am Umfang des Verteilers 10 verbunden,
von der (nicht gezeigte) im Pumpengehäuse verlaufende Einspritzleitungen
ihren Ausgang nehmen. Die Einspritzleitungen führen wiederum zu einem (ebenfalls
nicht gezeigten) Einspritzventil.A (not shown) pump working chamber is connected via a
Des Weiteren geht von der Verteilernut 12 im Inneren des Verteilers 10 ein
Verbindungskanal 14 aus, der in eine Ringnut 15 mündet. Die Ringnut 15 bildet
einen Ventilsitz 16 für eine Ventilnadel 17 eines (nur teilweise dargestellten)
insgesamt mit 18 bezeichneten Magnetventils. Oberhalb der Magnetventilnadel
17, bei 19, schließt sich ein das Magnetventil 18 betätigender Elektromagnet an,
der bekannter Stand der Technik ist, weshalb eine detaillierte Darstellung entfallen
kann.Furthermore, from the
Unterhalb des Ventilsitzes 16 erstreckt sich eine insgesamt mit 20 bezifferte
Sacklochbohrung, die eine Erweiterung 21 aufweist, von der ein (weiterer)
Verbindungskanal 22 seinen Ausgang nimmt. Der Verbindungskanal 22 führt
zum (nicht dargestellten) Niederdruckteil der Kraftstoffeinspritzpumpe. Somit
definieren Ventilsitz 16 und Magnetventilnadel 17 innerhalb des Verteilers 10
einen Hochdruckbereich 14, 15 und einen Niederdruckbereich 21.Below the valve seat 16 extends a total of 20 numbered
Blind hole bore, which has an extension 21, of which a (further)
Connecting
Innerhalb der Sacklochbohrung 20 und koaxial zu der Magnetventilnadel 17 ist
ein Niederdruck-Ausgleichskolben axial beweglich angeordnet, der - jeweils
hälftig - linksseitig einer gemeinsamen Längsmittelachse 23 von Magnetventilnadel
17 und Niederdruck-Ausgleichskolben insgesamt mit 24 und rechtsseitig
der Längsmittelachse 23 insgesamt mit 25 beziffert ist. Within the blind bore 20 and coaxial with the
Die rechtsseitig von der Längsmittelachse 23 gezeichnete Bauart 25
des Niederdruck-Ausgleichskolbens markiert den bisherigen Stand der
Technik, wobei der Niederdruck-Ausgleichskolben 25 - bei 26 - einstückig
mit der Magnetventilnadel 17 verbunden ist.The right side drawn by the
Dagegen handelt es sich bei dem linksseitig der Längsmittelachse 23
(hälftig) dargestellten Niederdruck-Ausgleichskolben 24 um die erfindungsgemäße
Bauart. Die Besonderheit besteht hier darin, dass Magnetventilnadel
17 und Niederdruck-Ausgleichskolben 24 als zwei getrennte und damit
unabhängig voneinander (axial) bewegliche Bauteile ausgebildet sind. Zur
Führung des Niederdruck-Ausgleichskolbens 24 weist dieser eine Kolbenstange
27 verjüngten Durchmessers auf, die in eine in die Magnetventilnadel
17 eingebrachte Führungsbohrung 28 eingreift. Durch die Führung 27/28
wird ein (andernfalls mögliches) Kippen des Niederdruck-Ausgleichskolbens
24 wirksam vermieden. Die Führungsbohrung 28 ist als Sacklochbohrung
ausgebildet, wobei ihr (oberes) Ende 29 als Anschlag fungiert, der mit dem
freien Ende 30 der Kolbenstange 27 des Niederdruck-Ausgleichskolbens 24
zusammenwirkt.By contrast, the left side of the longitudinal central axis 23
(Half) illustrated low-pressure compensating piston 24 to the invention
Design type. The special feature here is that
An einer rückwärtigen Stirnfläche 31 des Niederdruck-Ausgleichskolbens 24
liegt eine Druckfeder (Niederdruck-Ausgleichsfeder) 32 an, die sich rückwärtig
an dem mit 33 bezifferten Boden der Sacklochbohrung 20 abstützt.
Durch die Niederdruck-Ausgleichsfeder 32 wird der Niederdruck-Ausgleichskolben
24 gegen den (oberen) Anschlag 29 der Führungsbohrung 28 gedrückt.At a
Eine weitere Besonderheit besteht darin, dass an der (unteren) Stirnfläche 31
des Niederdruck-Ausgleichskolbens 24 ein stangenförmiger, von der Niederdruck-Ausgleichsfeder
32 umgebener Gegenanschlag 34 angeordnet ist,
der an seinem Ende 35 mit dem zugleich als (unterer) Hubanschlag für den
Niederdruck-Ausgleichskolben 24 fungierenden Boden 33 der Sacklochbohrung
20 zusammenwirkt. Der stangenförmige Gegenanschlag 34 dient
auch gleichzeitig zum Schutz der Niederdruck-Ausgleichsfeder 32. Another special feature is that at the (lower)
Die beschriebene Anordnung und Ausbildung des Niederdruck-Ausgleichskolbens 24 wirkt sich im Betrieb der Kraftstoffeinspritzpumpe wie folgt aus.The described arrangement and design of the low pressure balance piston 24 affects the operation of the fuel injection pump as follows.
Beim Öffnen des Magnetventils 18 wird der Druck im Hochdruckbereich 14, 15
über den Ventilsitz 16 abgebaut. Es kommt zu einer lokalen Druckerhöhung auf
der Magnetventilnadel 17 und dem Niederdruck-Ausgleichskolben 24.
Der Niederdruck-Ausgleichskolben 24 trennt sich nun von der Magnetventilnadel
17. Die in Schließrichtung gerichtete Niederdruck-Ausgleichskolbenkraft wird
über den Hubanschlag 33, 34, 35 am Verteilergehäuse 10 abgestützt. Die Magnet-Ventilkraft
führt zu einem schnellen Öffnen des Magnetventils 18.When opening the
The low-pressure compensating piston 24 now separates from the
Die auf den Niederdruck-Ausgleichskolben 24 aufgeübten hydraulischen Kräfte,
welche bei der bisherigen einstückigen Ausbildung von Magnetventilnadel und
Niederdruck-Ausgleichskolben nachteiligerweise in Schließrichtung der
Magnetventilnadel wirkten, entfallen somit durch die erfindungsgemäße Separatausbildung
von Magnetventilnadel 17 einerseits und Niederdruck-Ausgleichskolben
24 andererseits. Die vom Elektromagneten 19 auf die Magnetventilnadel 17
ausgeübte Öffnungskraft hat somit ein ungehindertes und damit schnellstmögliches
Öffnen des Magnetventils 18 zur gewünschten Folge.The exerted on the low-pressure compensating piston 24 hydraulic forces, which acted disadvantageously in the closing direction of the solenoid valve needle in the previous one-piece design of solenoid valve needle and low-pressure piston, thus eliminating the invention by separate formation of
Claims (5)
- Solenoid-valve-controlled fuel injection pump for internal combustion engines, in particular diesel engines, having a solenoid valve (18), the valve needle (17) of which separates a high-pressure region (14, 15) from a low-pressure region (21) via a valve seat (16) in the pump body or connects the high-pressure region and the low-pressure region, the injection duration being controlled by opening the solenoid valve (18), and having a low-pressure compensating piston (24) arranged in the low-pressure region (21) for compensating for pressure fluctuations in the low-pressure region (21), the low-pressure compensating piston (24) being arranged coaxially with respect to the solenoid-valve needle (17) as a separate component from it, characterized in that, at its end which faces the solenoid valve (18), the low-pressure compensating piston (24) has a piston rod (27) which protrudes into a guide hole (28) made in the solenoid-valve needle (17) in the region of the solenoid-valve seat (16), the said guide hole (28) serving to guide the low-pressure compensating piston (24).
- Solenoid-valve-controlled fuel injection pump according to Claim 1, the low-pressure compensating piston (24) being arranged so as to be axially movable, counter to the resistance of a low-pressure compensating spring (32) acting on the rear side of the low-pressure compensating piston (24), in a low-pressure compensating-piston chamber (20) which adjoins the low-pressure region (21) coaxially in the pump body, characterized in that a stroke stop (33) for the low-pressure compensating piston (24) is provided at the rear end of the low-pressure compensating-piston chamber (20) facing away from the solenoid-valve needle (17), in order to protect the low-pressure compensating spring (32).
- Solenoid-valve-controlled fuel injection pump according to Claim 2, characterized in that a corresponding stop (34, 35) which interacts with the stroke stop (33) and has a smaller diameter than the diameter of the low-pressure piston (24) is arranged on that (rear) end face (31) of the low-pressure compensating piston (24) which faces away from the solenoid-valve needle (17).
- Solenoid-valve-controlled fuel injection pump according to Claim 3, characterized in that the guide hole (28) has a stop (29) for the piston rod (27) and thus for the low-pressure compensating piston (24).
- Solenoid-valve-controlled fuel injection pump according to Claim 4, characterized in that the low-pressure compensating spring (32) is designed in such a way that, when the solenoid valve (18) is closed, the piston rod (27) of the low-pressure compensating piston (24) comes into contact with the stop (29) in the guide hole (28) as a result of the force of the low-pressure compensating spring (32).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10058011A DE10058011A1 (en) | 2000-11-23 | 2000-11-23 | Solenoid valve controlled fuel injection pump for internal combustion engines, in particular diesel engines |
| DE10058011 | 2000-11-23 | ||
| PCT/DE2001/004319 WO2002042634A1 (en) | 2000-11-23 | 2001-11-16 | Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1339968A1 EP1339968A1 (en) | 2003-09-03 |
| EP1339968B1 true EP1339968B1 (en) | 2005-06-22 |
Family
ID=7664285
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP01997636A Expired - Lifetime EP1339968B1 (en) | 2000-11-23 | 2001-11-16 | Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US6884041B2 (en) |
| EP (1) | EP1339968B1 (en) |
| JP (1) | JP2004514824A (en) |
| DE (2) | DE10058011A1 (en) |
| ES (1) | ES2243599T3 (en) |
| WO (1) | WO2002042634A1 (en) |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5215449A (en) * | 1991-12-05 | 1993-06-01 | Stanadyne Automotive Corp. | Distributor type fuel injection pump |
| DE4323683A1 (en) * | 1993-07-15 | 1995-01-19 | Bosch Gmbh Robert | Fuel injection pump |
| DE4339948A1 (en) * | 1993-11-24 | 1995-06-01 | Bosch Gmbh Robert | Fuel injection pump |
| US5954487A (en) * | 1995-06-23 | 1999-09-21 | Diesel Technology Company | Fuel pump control valve assembly |
| DE19616084A1 (en) | 1996-04-23 | 1997-10-30 | Bosch Gmbh Robert | Fuel injector |
| DE19717494A1 (en) * | 1997-04-25 | 1998-10-29 | Bosch Gmbh Robert | Distributor type fuel injection pump |
-
2000
- 2000-11-23 DE DE10058011A patent/DE10058011A1/en not_active Withdrawn
-
2001
- 2001-11-16 EP EP01997636A patent/EP1339968B1/en not_active Expired - Lifetime
- 2001-11-16 ES ES01997636T patent/ES2243599T3/en not_active Expired - Lifetime
- 2001-11-16 JP JP2002544537A patent/JP2004514824A/en not_active Withdrawn
- 2001-11-16 WO PCT/DE2001/004319 patent/WO2002042634A1/en active IP Right Grant
- 2001-11-16 US US10/181,867 patent/US6884041B2/en not_active Expired - Fee Related
- 2001-11-16 DE DE50106595T patent/DE50106595D1/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| WO2002042634A1 (en) | 2002-05-30 |
| JP2004514824A (en) | 2004-05-20 |
| DE10058011A1 (en) | 2002-05-29 |
| US20040131486A1 (en) | 2004-07-08 |
| DE50106595D1 (en) | 2005-07-28 |
| US6884041B2 (en) | 2005-04-26 |
| ES2243599T3 (en) | 2005-12-01 |
| EP1339968A1 (en) | 2003-09-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0686763B1 (en) | Fuel injection valve for internal combustion engines | |
| DE102009046582A1 (en) | Method for manufacturing a fuel injection valve and fuel injection valve | |
| DE4440182C2 (en) | Fuel injection valve for internal combustion engines | |
| EP1395744B1 (en) | Fuel injection device for combustion motors, especially common rail injector, fuel system and internal combustion engine | |
| DE3801929C2 (en) | Fuel injector | |
| DE19941688C2 (en) | Injection device for an internal combustion engine with direct injection | |
| DE4106813A1 (en) | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES | |
| EP1339968B1 (en) | Electromagnetic valve-controlled fuel injection pump for internal combustion engines, especially diesel engines | |
| EP1651858B1 (en) | Fuel injection device for a combustion engine | |
| DE10126686A1 (en) | Fuel injection system, for an IC motor, has a pressure amplifier with a sliding piston and controlled outflow cross section stages to set the fuel pressure according to the piston stroke and give a boot injection action | |
| WO2003054375A1 (en) | Fuel injection device for an internal combustion engine | |
| WO2003004861A1 (en) | Fuel injector comprising a force-balanced control valve | |
| DE102008041561B4 (en) | Fuel injector and design method for a fuel injector | |
| DE102006050033A1 (en) | Injector, in particular common rail injector | |
| DE10315489B3 (en) | Fuel injector for use in internal combustion engine has integrated damping piston and has pressure increasing system connected to fuel pressure reservoir | |
| DE3807965A1 (en) | Pump nozzle | |
| WO2010000528A1 (en) | Solenoid valve for a fuel injector, and fuel injector | |
| EP1397591B1 (en) | Fuel injection device comprising a pressure amplifier | |
| EP3184803B1 (en) | Fuel injector | |
| EP1606511B1 (en) | Fuel injection device for a combustion engine | |
| EP1654454B1 (en) | Fuel injection device for a combustion engine | |
| WO2008095743A1 (en) | Injector for injecting fuel into combustion chambers of internal combustion engines | |
| EP2486265A1 (en) | Fuel injection valve | |
| WO2006034910A1 (en) | Fuel injection device | |
| DE102004048322A1 (en) | fuel injector |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| 17P | Request for examination filed |
Effective date: 20030623 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
| RBV | Designated contracting states (corrected) |
Designated state(s): DE ES FR GB IT |
|
| 17Q | First examination report despatched |
Effective date: 20040422 |
|
| GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE ES FR GB IT |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REF | Corresponds to: |
Ref document number: 50106595 Country of ref document: DE Date of ref document: 20050728 Kind code of ref document: P |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) | ||
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20051117 Year of fee payment: 5 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20051118 Year of fee payment: 5 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20051122 Year of fee payment: 5 |
|
| REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2243599 Country of ref document: ES Kind code of ref document: T3 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20060127 Year of fee payment: 5 |
|
| ET | Fr: translation filed | ||
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20060323 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20061130 Year of fee payment: 6 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070601 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20061116 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20070731 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20061116 |
|
| REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20061117 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20061117 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20061130 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20071116 |