EP1076174B1 - Single cylinder high pressure pump - Google Patents

Single cylinder high pressure pump Download PDF

Info

Publication number
EP1076174B1
EP1076174B1 EP20000116573 EP00116573A EP1076174B1 EP 1076174 B1 EP1076174 B1 EP 1076174B1 EP 20000116573 EP20000116573 EP 20000116573 EP 00116573 A EP00116573 A EP 00116573A EP 1076174 B1 EP1076174 B1 EP 1076174B1
Authority
EP
European Patent Office
Prior art keywords
pump
cylinder
pressure
pressure pump
closing element
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
Application number
EP20000116573
Other languages
German (de)
French (fr)
Other versions
EP1076174A3 (en
EP1076174A2 (en
Inventor
Helmut Rembold
Peter Ropertz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1076174A2 publication Critical patent/EP1076174A2/en
Publication of EP1076174A3 publication Critical patent/EP1076174A3/en
Application granted granted Critical
Publication of EP1076174B1 publication Critical patent/EP1076174B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0421—Cylinders
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners
    • F04B53/168—Mounting of cylinder liners in cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped

Definitions

  • the invention relates to a single-cylinder high-pressure pump for High pressure supply in common rail injection systems of Internal combustion engines, with one in a pump housing received pump element which has a pump piston which in a pump cylinder against the Biasing force of a compression spring movable back and forth taken up and driven by a cam to with High-pressure fuel to promote a rail.
  • the pump element from below, i. of the Cam drive side to put into the pump housing and to clamp with a screw.
  • the contact surface to the Recording of the clamping forces is located at the upper side facing away from the cam drive side of the Pump cylinder.
  • the clamping forces are over the full Length passed through the pump cylinder.
  • the Pump cylinder can be made of a stainless steel and the Pump housing be made of aluminum. Because of the different thermal expansion coefficient of the It is necessary to use different materials To increase the preload forces of the screw connection. Only so can a secure clamping in all operating conditions, e.g. from -40 ° C to + 140 ° C.
  • the high Preload forces can lead to a banana-shaped deformation of the Pump cylinder and thus to a clamping of the pump piston in Run operation.
  • the object of the invention is a single-cylinder high-pressure pump the kind described above with a longer life provide.
  • the inventive Single-cylinder high-pressure pump simple and inexpensive be produced.
  • the task is in a single-cylinder high-pressure pump for High-pressure fuel supply in common-rail injection systems of internal combustion engines according to the preamble of claim 1 solved by a pressure damping device in the Closing element is integrated.
  • a pressure damping device in the Closing element is integrated.
  • the closure element seals not only the mounting hole to Environment, but reliably prevents the release of the Pump element in operation and can be constructed differently be.
  • a particular embodiment of the invention is characterized characterized in that facing away from the cam drive End of the pump cylinder, a collar is formed in the Assembled state of the high pressure pump with a complementary stage cooperates in the pump housing.
  • Bund comes with the assembly of the pump element to the Pump housing to the plant and is e.g. with the help of a Fixed screw. This solution is manufacturing technology especially easy to realize.
  • Another particular embodiment of the invention is characterized in that at the end facing away from the cam drive end the pump cylinder is a cone formed in the assembled state of the high pressure pump with a complementary cone cooperates in the pump housing.
  • the cooperating cones ensure a particularly stable Fixation of the pump cylinder in the pump housing.
  • Another particular embodiment of the invention is characterized characterized in that on the closure element has an external thread is formed with one on the pump housing trained internal thread cooperates.
  • Another particular embodiment of the invention is characterized characterized in that the closure element with Help of several screw connections on the pump housing is attached.
  • the screw connections can be on one Bolt circle be arranged concentric to the Pump cylinder is. This will release the Pump element safely prevented during operation.
  • FIG. 1 Another particular embodiments of the invention are characterized in that a pressure damping device in the closure element and an inlet valve in the Closing element or the pump cylinder are integrated.
  • a pressure damping device in the closure element and an inlet valve in the Closing element or the pump cylinder are integrated.
  • the illustrated in Fig. 1 first embodiment of a Single-cylinder high-pressure pump according to the invention comprises a Pump housing 1.
  • the pump housing 1 of the high-pressure pump is installed in the housing 2 of an internal combustion engine.
  • a pump cylinder 4 is received in an elongated mounting opening 3 in the pump housing.
  • a pump piston 5 is movable back and forth added.
  • One end 6 of the pump piston 5 is by means of a Compression spring 7 against a cam 8 of a camshaft Engine biased.
  • the Compression spring 7 between two spring plates 9 and 10th clamped.
  • the spring plate 9 is supported on the to the Cam drive end facing the pump cylinder 4 from.
  • Of the Spring plate 10 is at the end 6 of the pump piston fifth supported.
  • the facing away from the cam drive 8 end face 11 of the Pump piston 5 defines a cylinder chamber 12 in the Pump cylinder 4. Opposite the end face 11 of the Pump piston 5 is the cylinder chamber 12 through a Closing element 13 is limited, in which an inlet valve 14th is arranged. Through the inlet valve 14 reaches the conveying fuel into the cylinder chamber 12. When the Pump piston 5 is moved into the cylinder chamber 12, the fuel in it is at high pressure applied. The high pressure fuel passes through an outlet valve 15 to the (not shown) Rail.
  • the closure element 13 has the shape of a cup in the Bottom of the inlet valve 14 is arranged. In the interior the cup is a pressure damper 17 added.
  • the first embodiment is at the of the Cam drive 8 facing away from the end of the pump cylinder 4 a Bund 18 trained.
  • the covenant 18 is based on a corresponding stage of the pump housing 1 from.
  • About one the closure element 13 formed thread 19 is the Covenant 18 of the pump cylinder 4 against the pump housing. 1 pressed. In this way, the pump cylinder 4 fixed in the pump housing 1.
  • the mounting hole 3 in the pump housing 1 has the shape a through hole with different Diameter sections. The smallest diameter is up the side facing the cam drive 8 and the largest diameter on the of the cam drive. 8 arranged opposite side of the pump housing 1.
  • FIG. 2 second embodiment of Invention largely corresponds to the first Embodiment.
  • first Embodiment For simplicity, be Designation of the same parts the same reference numerals used. To avoid repetition, the above detailed description of the first Embodiment with reference to FIG. 1 referenced.
  • the invention is that of the cam drive. 8 opposite end of the pump cylinder 4 instead of the federal one Cone 20 formed.
  • the cone 20 acts with a corresponding cone on the pump housing 1 together.
  • the Cone 20 on the pump cylinder 4 tapers to the Cam drive 8 out.
  • the closure element 13 With the aid of the closure element 13 the cone 20 is in contact with the corresponding Held counter cone of the pump housing 1.
  • the Closure element 13 in turn is by means of screws 21 and 22 attached to the pump housing 1.
  • the inlet valve 14 in the second shown in Fig. 2 Embodiment not in the closure element 13th but is integrated into the end of the pump cylinder 4. Otherwise, the second embodiment corresponds to first embodiment.

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

Stand der TechnikState of the art

Die Erfindung betrifft eine Einzylinder-Hochdruckpumpe zur Hochdruckversorgung in Common-Rail-Einspritzsystemen von Brennkraftmaschinen, mit einem in einem Pumpengehäuse aufgenommenen Pumpenelement, das einen Pumpenkolben umfasst, der in einem Pumpenzylinder gegen die Vorspannkraft einer Druckfeder hin und her bewegbar aufgenommen und durch einen Nocken angetrieben ist, um mit Hochdruck beaufschlagten Kraftstoff in ein Rail zu fördern.The invention relates to a single-cylinder high-pressure pump for High pressure supply in common rail injection systems of Internal combustion engines, with one in a pump housing received pump element which has a pump piston which in a pump cylinder against the Biasing force of a compression spring movable back and forth taken up and driven by a cam to with High-pressure fuel to promote a rail.

Bei einer aktuellen Konstruktion der Anmelderin ist vorgesehen, das Pumpenelement von unten, d.h. von der Nockenantriebsseite her, in das Pumpengehäuse zu stecken und mit einer Schraube zu verspannen. Die Anlagefläche zur Aufnahme der Verspannkräfte befindet sich dabei an der oberen, von dem Nockenantrieb abgewandten Seite des Pumpenzylinders. Die Verspannkräfte werden über die volle Länge durch den Pumpenzylinder hindurchgeleitet. Der Pumpenzylinder kann aus einem nicht rostenden Stahl und das Pumpengehäuse aus Aluminium gefertigt sein. Wegen der unterschiedlichen Wärmeausdehnungskoeffizienten der verschiedenen Materialien ist es erforderlich, die Vorspannkräfte der Verschraubung zu erhöhen. Nur so kann eine sichere Verpannung in allen Betriebszuständen, z.B. von -40° C bis +140° C, gewährleistet werden. Die hohen Vorspannkräfte können zu einer bananenförmigen Verformung des Pumpenzylinders und damit zu einem Klemmen des Pumpenkolbens im Betrieb führen.In a current design of the applicant is provided, the pump element from below, i. of the Cam drive side to put into the pump housing and to clamp with a screw. The contact surface to the Recording of the clamping forces is located at the upper side facing away from the cam drive side of the Pump cylinder. The clamping forces are over the full Length passed through the pump cylinder. Of the Pump cylinder can be made of a stainless steel and the Pump housing be made of aluminum. Because of the different thermal expansion coefficient of the It is necessary to use different materials To increase the preload forces of the screw connection. Only so can a secure clamping in all operating conditions, e.g. from -40 ° C to + 140 ° C. The high Preload forces can lead to a banana-shaped deformation of the Pump cylinder and thus to a clamping of the pump piston in Run operation.

Aus der DE 197 42 611 A1 und der EP 0878 621 A2 sind Kraftstoffhochdruckpumpen bekannt bei denen das Pumpenelement durch eine auf der vom Nockenantrieb abgewandten Seite angeordnete Montageöffnung in das Pumpengehäuse eingeführt wird. In beiden Fällen wird das Pumpenelement durch ein Verschlusselement im Pumpengehäuse fixiert.From DE 197 42 611 A1 and EP 0878 621 A2 are High-pressure fuel pumps known where the pump element by a side facing away from the cam drive side arranged mounting opening is inserted into the pump housing. In both cases, the pump element by a Locking element fixed in the pump housing.

Aus der DE 41 07 979 A1 ist eine Kolbenpumpe für Kraftfahrzeug-Bremsanlagen mit einer druckseitigen Dämpferkammer bekannt. Diese Dämpferkammer ist im Pumpengehäuse ausgebildet und.wird von einem eingepressten Deckel verschlossen.From DE 41 07 979 A1 discloses a piston pump for motor vehicle brake systems known with a pressure-side damper chamber. This damper chamber is formed in the pump housing and is closed by a pressed-in lid.

Aufgabe der Erfindung ist es, eine Einzylinder-Hochdruckpumpe der eingangs geschilderten Art mit einer längeren Lebensdauer bereitzustellen. Darüber hinaus soll die erfindungsgemäße Einzylinder-Hochdruckpumpe einfach aufgebaut und kostengünstig herstellbar sein.The object of the invention is a single-cylinder high-pressure pump the kind described above with a longer life provide. In addition, the inventive Single-cylinder high-pressure pump simple and inexpensive be produced.

Die Aufgabe ist bei einer Einzylinder-Hochdruckpumpe zur Kraftstoffhochdruckversorgung in Common-Rail-Einspritzsystemen von Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1 dadurch gelöst, dass eine Druckdämpfungseinrichtung in das Verschlusselement integriert ist. Durch die Integration der relativ viel Bauraum beanspruchenden Druckdämpfungseinrichtung in das Verschlusselement wird eine äußerst kompakte Bauform der Hochdruckpumpe ermöglicht. Durch die kompakte Bauform hält die Hochdruckpumpe auch hohen Drücken stand.The task is in a single-cylinder high-pressure pump for High-pressure fuel supply in common-rail injection systems of internal combustion engines according to the preamble of claim 1 solved by a pressure damping device in the Closing element is integrated. By integrating the Relatively much space consuming pressure damping device in the closure element is an extremely compact design High pressure pump allows. Due to the compact design holds the High pressure pump also withstand high pressures.

Im Rahmen der vorliegenden Erfindung hat sich herausgestellt, dass eine Abstützung über einen Flansch am unteren Ende des Zylinders wegen des begrenzten Bauraums nicht möglich ist. Eine derartige Abstützung würde einen deutlich größeren Durchmesser des Pumpenzylinders erforderlich machen, was den vorgegebenen Bauraum sprengen würde. Durch die erfindungsgemäße Umkehrung der Montagerichtung ist es nicht mehr erforderlich, die zur Fixierung benötigten Kräfte durch den Bereich des Pumpenzylinders zu führen, in dem der Pumpenkolben geführt und abgedichtet wird. Dadurch wird ein Klemmen des Pumpenkolbens aufgrund der Vorspannkräfte sicher verhindert.In the context of the present invention, it has been found that a support via a flange at the lower end of Cylinder is not possible because of the limited space. A Such support would have a much larger diameter make the pump cylinder required, which is the default Space would blow up. By reversing the invention Assembly direction, it is no longer necessary to the Fixation required forces through the area of To lead pump cylinder, in which the pump piston out and is sealed. This will cause a jamming of the pump piston safely prevented due to the preload forces.

Das Verschlusselement dichtet nicht nur die Montagebohrung zur Umgebung ab, sondern verhindert zuverlässig ein Lösen des Pumpenelements im Betrieb und kann unterschiedlich aufgebaut sein.The closure element seals not only the mounting hole to Environment, but reliably prevents the release of the Pump element in operation and can be constructed differently be.

Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an dem vom Nockenantrieb abgewandten Ende des Pumpenzylinders ein Bund ausgebildet ist, der im zusammengebauten Zustand der Hochdruckpumpe mit einer komplementären Stufe in dem Pumpengehäuse zusammenwirkt. Der Bund kommt bei der Montage des Pumpenelements an dem Pumpengehäuse zur Anlage und wird z.B. mit Hilfe einer Schraubverbindung fixiert. Diese Lösung ist fertigungstechnisch besonders einfach zu realisieren.A particular embodiment of the invention is characterized characterized in that facing away from the cam drive End of the pump cylinder, a collar is formed in the Assembled state of the high pressure pump with a complementary stage cooperates in the pump housing. Of the Bund comes with the assembly of the pump element to the Pump housing to the plant and is e.g. with the help of a Fixed screw. This solution is manufacturing technology especially easy to realize.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an dem vom Nockenantrieb abgewandten Ende des Pumpenzylinders ein Konus ausgebildet ist, der im zusammengebauten Zustand der Hochdruckpumpe mit einem komplementären Konus in dem Pumpengehäuse zusammenwirkt. Die zusammenwirkenden Konusse sorgen für eine besonders stabile Fixierung des Pumpenzylinders in dem Pumpengehäuse.Another particular embodiment of the invention is characterized in that at the end facing away from the cam drive end the pump cylinder is a cone formed in the assembled state of the high pressure pump with a complementary cone cooperates in the pump housing. The cooperating cones ensure a particularly stable Fixation of the pump cylinder in the pump housing.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass an dem Verschlusselement ein Außengewinde ausgebildet ist, das mit einem an dem Pumpengehäuse ausgebildeten Innengewinde zusammenwirkt. Durch die erfindungsgemäße Konstruktion ist sichergestellt, dass in einem vorgegebenen Bauraum die erforderliche Gewindelänge für eine dauerhaltbare Verbindung untergebracht werden kann.Another particular embodiment of the invention is characterized characterized in that on the closure element has an external thread is formed with one on the pump housing trained internal thread cooperates. By the The construction according to the invention ensures that in one given space the required thread length for a durable connection can be accommodated.

Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, dass das Verschlusselement mit Hilfe von mehreren Schraubverbindungen an dem Pumpengehäuse befestigt ist. Die Schraubverbindungen können auf einem Lochkreis angeordnet sein, der konzentrisch zu dem Pumpenzylinder ist. Dadurch wird ein Lösen des Pumpenelements im Betrieb sicher verhindert.Another particular embodiment of the invention is characterized characterized in that the closure element with Help of several screw connections on the pump housing is attached. The screw connections can be on one Bolt circle be arranged concentric to the Pump cylinder is. This will release the Pump element safely prevented during operation.

Weitere besondere Ausführungsarten der Erfindung sind dadurch gekennzeichnet, dass eine Druckdämpfungseinrichtung in das Verschlusselement und ein Einlassventil in das Verschlusselement oder den Pumpenzylinder integriert sind. Durch die Integration diverser Bauteile in das Verschlusselement bzw. den Pumpenzylinder wird eine äußerst kompakte Bauform der Hochdruckpumpe ermöglicht, die auch hohen Drücken standhält.Other particular embodiments of the invention are characterized in that a pressure damping device in the closure element and an inlet valve in the Closing element or the pump cylinder are integrated. By integrating various components in the Closure element or the pump cylinder is an extremely compact design of the high-pressure pump allows, too withstand high pressures.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnung zwei Ausführungsbeispiele der Erfindung im einzelnen beschrieben sind. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. In der Zeichnung zeigen:

  • Fig. 1: ein erstes Ausführungsbeispiel einer erfindungsgemäßen Hochdruckpumpe im Längsschnitt; und
  • Fig. 2: einen Ausschnitt aus Fig. 1 gemäß einem zweiten Ausführungsbeispiel.
    • Further advantages, features and details of the invention will become apparent from the following description in which two embodiments of the invention are described in detail with reference to the drawings. The features mentioned in the claims and in the description may each be essential to the invention individually or in any desired combination. In the drawing show:
  • 1 shows a first embodiment of a high-pressure pump according to the invention in longitudinal section; and
  • 2 shows a detail of FIG. 1 according to a second embodiment.

    • Das in Fig. 1 dargestellte erste Ausführungsbeispiel einer erfindungsgemäßen Einzylinder-Hochdruckpumpe umfasst ein Pumpengehäuse 1. Das Pumpengehäuse 1 der Hochdruckpumpe ist in das Gehäuse 2 einer Brennkraftmaschine eingebaut. In einer länglichen Montageöffnung 3 in dem Pumpengehäuse 1 ist ein Pumpenzylinder 4 aufgenommen. In dem Pumpenzylinder 4 wiederum ist ein Pumpenkolben 5 hin und her bewegbar aufgenommen.The illustrated in Fig. 1 first embodiment of a Single-cylinder high-pressure pump according to the invention comprises a Pump housing 1. The pump housing 1 of the high-pressure pump is installed in the housing 2 of an internal combustion engine. In an elongated mounting opening 3 in the pump housing. 1 a pump cylinder 4 is received. In the pump cylinder 4, in turn, a pump piston 5 is movable back and forth added.

    Ein Ende 6 des Pumpenkolbens 5 ist mit Hilfe einer Druckfeder 7 gegen einen Nocken 8 einer Nockenwelle der Brennkraftmaschine vorgespannt. Zu diesem Zweck ist die Druckfeder 7 zwischen zwei Federtellern 9 und 10 eingespannt. Der Federteller 9 stützt sich an dem zu dem Nockenantrieb gewandten Ende des Pumpenzylinders 4 ab. Der Federteller 10 ist an dem Ende 6 des Pumpenkolbens 5 abgestützt.One end 6 of the pump piston 5 is by means of a Compression spring 7 against a cam 8 of a camshaft Engine biased. For this purpose, the Compression spring 7 between two spring plates 9 and 10th clamped. The spring plate 9 is supported on the to the Cam drive end facing the pump cylinder 4 from. Of the Spring plate 10 is at the end 6 of the pump piston fifth supported.

    Die von dem Nockenantrieb 8 abgewandte Stirnfläche 11 des Pumpenkolbens 5 begrenzt einen Zylinderraum 12 in dem Pumpenzylinder 4. Gegenüber der Stirnfläche 11 des Pumpenkolbens 5 ist der Zylinderraum 12 durch ein Verschlusselement 13 begrenzt, in dem ein Einlassventil 14 angeordnet ist. Durch das Einlassventil 14 gelangt der zu fördernde Kraftstoff in den Zylinderraum 12. Wenn der Pumpenkolben 5 in den Zylinderraum 12 hineinbewegt wird, wird der darin befindliche Kraftstoff mit Hochdruck beaufschlagt. Der mit Hochdruck beaufschlagte Kraftstoff gelangt über ein Auslassventil 15 zu dem (nicht dargestellten) Rail.The facing away from the cam drive 8 end face 11 of the Pump piston 5 defines a cylinder chamber 12 in the Pump cylinder 4. Opposite the end face 11 of the Pump piston 5 is the cylinder chamber 12 through a Closing element 13 is limited, in which an inlet valve 14th is arranged. Through the inlet valve 14 reaches the conveying fuel into the cylinder chamber 12. When the Pump piston 5 is moved into the cylinder chamber 12, the fuel in it is at high pressure applied. The high pressure fuel passes through an outlet valve 15 to the (not shown) Rail.

    Mit Hilfe eines Magnetsteuerventils 16 kann die Fördermenge der Kraftstoffhochdruckpumpe eingestellt werden.With the aid of a solenoid control valve 16, the flow rate of the high-pressure fuel pump.

    Das Verschlusselement 13 hat die Form einer Tasse, in deren Boden das Einlassventil 14 angeordnet ist. In dem Innenraum der Tasse ist ein Druckdämpfer 17 aufgenommen.The closure element 13 has the shape of a cup in the Bottom of the inlet valve 14 is arranged. In the interior the cup is a pressure damper 17 added.

    Bei dem ersten Ausführungsbeispiel ist an dem von dem Nockenantrieb 8 abgewandten Ende des Pumpenzylinders 4 ein Bund 18 ausgebildet. Der Bund 18 stützt sich an einer entsprechenden Stufe des Pumpengehäuses 1 ab. Über ein an dem Verschlusselement 13 ausgebildeten Gewinde 19 wird der Bund 18 des Pumpenzylinders 4 gegen das Pumpengehäuse 1 gedrückt. Auf diese Art und Weise wird der Pumpenzylinder 4 in dem Pumpengehäuse 1 fixiert.In the first embodiment is at the of the Cam drive 8 facing away from the end of the pump cylinder 4 a Bund 18 trained. The covenant 18 is based on a corresponding stage of the pump housing 1 from. About one the closure element 13 formed thread 19 is the Covenant 18 of the pump cylinder 4 against the pump housing. 1 pressed. In this way, the pump cylinder 4 fixed in the pump housing 1.

    Die Montageöffnung 3 in dem Pumpengehäuse 1 hat die Form einer Durchgangsbohrung mit unterschiedlichen Durchmesserabschnitten. Der kleinste Durchmesser ist auf der zu dem Nockenantrieb 8 hingewandten Seite und der größte Durchmesser auf der von dem Nockenantrieb 8 abgewandten Seite des Pumpengehäuses 1 angeordnet.The mounting hole 3 in the pump housing 1 has the shape a through hole with different Diameter sections. The smallest diameter is up the side facing the cam drive 8 and the largest diameter on the of the cam drive. 8 arranged opposite side of the pump housing 1.

    Das in Fig. 2 dargestellte zweite Ausführungsbeispiel der Erfindung entspricht weitgehend dem ersten Ausführungsbeispiel. Der Einfachheit halber werden zur Bezeichnung gleicher Teile dieselben Bezugszeichen verwendet. Um Wiederholungen zu vermeiden, wird auf die vorstehende ausführliche Beschreibung des ersten Ausführungsbeispiels unter Bezugnahme auf Fig. 1 verwiesen.The illustrated in Fig. 2 second embodiment of Invention largely corresponds to the first Embodiment. For simplicity, be Designation of the same parts the same reference numerals used. To avoid repetition, the above detailed description of the first Embodiment with reference to FIG. 1 referenced.

    Bei dem in Fig. 2 dargestellten zweiten Ausführungsbeispiel der Erfindung ist an dem von dem Nockenantrieb 8 abgewandten Ende des Pumpenzylinders 4 statt des Bundes ein Konus 20 ausgebildet. Der Konus 20 wirkt mit einem entsprechenden Konus an dem Pumpengehäuse 1 zusammen. Der Konus 20 an dem Pumpenzylinder 4 verjüngt sich zu dem Nockenantrieb 8 hin. Mit Hilfe des Verschlusselements 13 wird der Konus 20 in Anlage an den entsprechenden Gegenkonus des Pumpengehäuses 1 gehalten. Das Verschlusselement 13 wiederum ist mit Hilfe von Schrauben 21 und 22 an dem Pumpengehäuse 1 befestigt.In the illustrated in Fig. 2 second embodiment The invention is that of the cam drive. 8 opposite end of the pump cylinder 4 instead of the federal one Cone 20 formed. The cone 20 acts with a corresponding cone on the pump housing 1 together. Of the Cone 20 on the pump cylinder 4 tapers to the Cam drive 8 out. With the aid of the closure element 13 the cone 20 is in contact with the corresponding Held counter cone of the pump housing 1. The Closure element 13 in turn is by means of screws 21 and 22 attached to the pump housing 1.

    Ein weiterer Unterschied zwischen den beiden Ausführungsbeispielen besteht darin, dass das Einlassventil 14 bei dem in Fig. 2 dargestellten zweiten Ausführungsbeispiel nicht in das Verschlusselement 13 sondern in das Ende des Pumpenzylinders 4 integriert ist. Ansonsten entspricht das zweite Ausführungsbeispiel dem ersten Ausführungsbeispiel.Another difference between the two Embodiments is that the inlet valve 14 in the second shown in Fig. 2 Embodiment not in the closure element 13th but is integrated into the end of the pump cylinder 4. Otherwise, the second embodiment corresponds to first embodiment.

    Claims (7)

    1. Single-cylinder high-pressure pump for a high-pressure supply in common-rail injection systems of internal combustion engines, with a pump element which is received in a pump casing (1) and comprises a pump piston (5) which is received in a pump cylinder (4) so as to be capable of being moved to and fro counter to the prestressing force of a compression spring (7) and which is driven by a cam (8), in order to convey into a rail fuel which is subjected to high pressure, a mounting orifice (3) for receiving the pump element being provided in the pump casing (1) on the side facing away from the cam drive (8), and, in the installed state, the pump element being braced with the aid of a closing element (13) in the mounting orifice (3) for receiving the pump element, characterized in that a pressure-damping device (17) is integrated into the closing element (13).
    2. Single-cylinder high-pressure pump according to Claim 1, characterized in that, at that end of the pump cylinder (4) which faces away from the cam drive (8), a collar (18) is formed, which, in the assembled state of the high-pressure pump, cooperates with a complementary step in the pump casing (1).
    3. Single-cylinder high-pressure pump according to Claim 1, characterized in that, at that end of the pump cylinder (4) which faces away from the cam drive (8), a cone (20) is formed, which, in the assembled state of the high-pressure pump, cooperates with a complementary cone in the pump casing (1).
    4. Single-cylinder high-pressure pump according to one of the preceding claims, characterized in that the closing element (13) has formed on it an external thread (19) which cooperates with an internal thread formed on the pump casing (1).
    5. Single-cylinder high-pressure pump according to one of Claims 1 to 3, characterized in that the closing element (13) is fastened to the pump casing (1) with the aid of a plurality of screw connections (21, 22).
    6. Single-cylinder high-pressure pump according to one of the preceding claims, characterized in that an inlet valve (14) is integrated into the closing element (13).
    7. Single-cylinder high-pressure pump according to one of Claims 1 to 5, characterized in that an inlet valve (14) is integrated into the pump cylinder (4).
    EP20000116573 1999-08-13 2000-08-01 Single cylinder high pressure pump Expired - Lifetime EP1076174B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE1999138504 DE19938504A1 (en) 1999-08-13 1999-08-13 Single cylinder high pressure pump
    DE19938504 1999-08-13

    Publications (3)

    Publication Number Publication Date
    EP1076174A2 EP1076174A2 (en) 2001-02-14
    EP1076174A3 EP1076174A3 (en) 2003-11-19
    EP1076174B1 true EP1076174B1 (en) 2005-11-02

    Family

    ID=7918356

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP20000116573 Expired - Lifetime EP1076174B1 (en) 1999-08-13 2000-08-01 Single cylinder high pressure pump

    Country Status (3)

    Country Link
    EP (1) EP1076174B1 (en)
    JP (1) JP2001073907A (en)
    DE (2) DE19938504A1 (en)

    Cited By (1)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE102013224797A1 (en) 2013-12-04 2015-06-11 Robert Bosch Gmbh Fuel pump with a piston, at its end facing a drive end a spring divider is arranged

    Families Citing this family (11)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    JPWO2002055870A1 (en) * 2001-01-05 2004-05-20 株式会社日立製作所 High pressure fuel supply pump
    DE10134069B4 (en) * 2001-07-13 2011-07-07 Robert Bosch GmbH, 70469 Fuel pump for a fuel system of an internal combustion engine
    DE10156428A1 (en) * 2001-11-16 2003-06-12 Bosch Gmbh Robert Fuel-cooled pump element and high-pressure pump for a fuel injection system
    DE10362375B3 (en) * 2003-05-20 2016-11-17 Robert Bosch Gmbh High-pressure piston pump for internal combustion engines with direct injection
    DE10322603B4 (en) * 2003-05-20 2013-04-25 Robert Bosch Gmbh Piston pump, in particular high-pressure piston pump for internal combustion engines with direct injection
    DE102004063075B4 (en) * 2004-12-28 2015-11-26 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine with a stepped piston and a quantity control valve
    DE102004063074B4 (en) * 2004-12-28 2013-03-07 Robert Bosch Gmbh Piston pump, in particular high-pressure fuel pump for an internal combustion engine
    DE102006061231A1 (en) * 2006-12-22 2008-06-26 Robert Bosch Gmbh High pressure piston pump
    WO2009049776A1 (en) * 2007-10-15 2009-04-23 Ixetic Bad Homburg Gmbh Radial piston pump
    EP2557306A1 (en) * 2011-08-08 2013-02-13 Delphi Technologies Holding S.à.r.l. Fuel pump
    JP6361337B2 (en) * 2014-07-10 2018-07-25 株式会社デンソー High pressure pump

    Family Cites Families (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    JPS635158A (en) * 1986-06-24 1988-01-11 Diesel Kiki Co Ltd Unit injector
    DE4107979C2 (en) * 1991-03-13 1998-07-09 Bosch Gmbh Robert Hydraulic high pressure pump for motor vehicle brake systems
    DE19527720A1 (en) * 1995-07-31 1997-02-06 Woodward Governor Germany Gmbh Procedure for changing the start of delivery of fuel injection pumps and fuel injection pump
    JP3309765B2 (en) * 1997-05-16 2002-07-29 三菱電機株式会社 High pressure fuel supply pump
    DE19742611A1 (en) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Piston pump

    Cited By (1)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE102013224797A1 (en) 2013-12-04 2015-06-11 Robert Bosch Gmbh Fuel pump with a piston, at its end facing a drive end a spring divider is arranged

    Also Published As

    Publication number Publication date
    DE19938504A1 (en) 2001-03-08
    EP1076174A3 (en) 2003-11-19
    DE50011493D1 (en) 2005-12-08
    JP2001073907A (en) 2001-03-21
    EP1076174A2 (en) 2001-02-14

    Similar Documents

    Publication Publication Date Title
    EP1771653B1 (en) Valve for use in a fuel line of a motor vehicle
    EP1076174B1 (en) Single cylinder high pressure pump
    EP1561026B1 (en) Fuel metering unit for the fuel injection system of a combustion engine
    DE102006028638A1 (en) piston pump
    DE10322603B4 (en) Piston pump, in particular high-pressure piston pump for internal combustion engines with direct injection
    EP1753989B1 (en) Check valve
    DE4213798A1 (en) Radial piston fuel pump for combustion engine - uses valve plate contained entirely within recess in cylinder head
    EP0433659B1 (en) Thermostatic valve
    WO2005029029A1 (en) Frost-resistant liquid pressure sensor for exhaust reducing systems (diesel engine)
    WO2008049699A1 (en) Fuel injector
    EP0990792A2 (en) Common-Rail fuel injection system
    DE102007044451A1 (en) Connection plate for a hydrostatic piston machine
    DE10036939B4 (en) check valve
    DE10161258A1 (en) High-pressure fuel pump with integrated blocking vane feed pump
    EP1208321B1 (en) Valve for controlling liquids
    EP1310669A2 (en) Fuel injector with simple mounting structure through an integral valve cover
    DE102007004560A1 (en) Valve, particularly gas injection valve of internal combustion engine for controlling gaseous medium, has alve seat with spring element which takes pre-stressed position when valve is closed
    EP2053235B1 (en) Combustion engine with fuel injectors
    EP0667458B1 (en) Proportional solenoid-valve unit
    DE202021105982U1 (en) pressure vessel
    DE102012003151A1 (en) Internal gear pump for use in motor vehicle, has housing comprising inlet and outlet for fluid to be delivered, where housing is arranged with latching element through which two pump stages are connected with each other
    DE10115856C1 (en) High-pressure fuel pump for a direct injection internal combustion engine, fuel system for a direct injection internal combustion engine, and direct injection internal combustion engine
    DE102022132018A1 (en) Valve stem guide of an exhaust valve of an internal combustion engine
    DE3202405C2 (en) Fuel injection pump for internal combustion engines
    DE10005236A1 (en) Servomotor for automobile power-assisted steering has working piston fitted with cover held under tension for compensating manufacturing tolerances

    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

    AK Designated contracting states

    Kind code of ref document: A2

    Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

    AX Request for extension of the european patent

    Free format text: AL;LT;LV;MK;RO;SI

    PUAL Search report despatched

    Free format text: ORIGINAL CODE: 0009013

    AK Designated contracting states

    Kind code of ref document: A3

    Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

    AX Request for extension of the european patent

    Extension state: AL LT LV MK RO SI

    RIC1 Information provided on ipc code assigned before grant

    Ipc: 7F 02M 59/48 B

    Ipc: 7F 02M 63/02 B

    Ipc: 7F 02M 59/44 A

    Ipc: 7F 02M 59/10 B

    Ipc: 7F 04B 53/16 B

    17P Request for examination filed

    Effective date: 20040519

    AKX Designation fees paid

    Designated state(s): DE FR GB IT

    17Q First examination report despatched

    Effective date: 20040820

    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 FR GB IT

    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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

    Effective date: 20051102

    Ref country code: GB

    Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

    Effective date: 20051102

    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: 50011493

    Country of ref document: DE

    Date of ref document: 20051208

    Kind code of ref document: P

    GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

    Effective date: 20051102

    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: 20060803

    EN Fr: translation not filed
    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: FR

    Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

    Effective date: 20061222

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: FR

    Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

    Effective date: 20051102

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: DE

    Payment date: 20101025

    Year of fee payment: 11

    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: 20130301

    REG Reference to a national code

    Ref country code: DE

    Ref legal event code: R119

    Ref document number: 50011493

    Country of ref document: DE

    Effective date: 20130301