EP1314882A1 - High-pressure pump - Google Patents
High-pressure pump Download PDFInfo
- Publication number
- EP1314882A1 EP1314882A1 EP02020978A EP02020978A EP1314882A1 EP 1314882 A1 EP1314882 A1 EP 1314882A1 EP 02020978 A EP02020978 A EP 02020978A EP 02020978 A EP02020978 A EP 02020978A EP 1314882 A1 EP1314882 A1 EP 1314882A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pressure pump
- section
- drive shaft
- recess
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 claims abstract description 15
- 238000002347 injection Methods 0.000 claims abstract description 11
- 239000007924 injection Substances 0.000 claims abstract description 11
- 238000002485 combustion reaction Methods 0.000 claims abstract description 10
- 239000000243 solution Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- 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
- 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
- F04B1/0408—Pistons
-
- 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
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
Definitions
- the invention relates to a high pressure pump for fuel supply of fuel injection systems for internal combustion engines, in particular of common rail injection systems, according to in the preamble of claim 1 closer defined type.
- a generic high-pressure pump is from the MTZ 58 (1997) S. 572 and DE 197 56 087 A1.
- the principal Mode of action of this high-pressure pump is for the common-rail principle working internal combustion engines very well suited
- the special construction ensures the same not a perfect function in all operating states, so that it is quite damaging the high-pressure pump and possibly even damage to the Internal combustion engine can come.
- a high-pressure pump for fuel supply of fuel injection systems for internal combustion engines which provide a has very high reliability in operation and the Advantages of the principle mode of action generic Maintains high pressure pumps.
- the high pressure pump 1 has a drive shaft 2, the Drive offset by three in the present case by 120 ° to each other Piston 3 is provided. Since the high-pressure pump 1 is symmetrical is executed, the following applies to one of the three pistons 3 explained also for the other two pistons 3. In this context, it is of course possible on the circumference of the drive shaft 2 a larger or smaller Number of piston 3 to install.
- the pistons 3 are provided for the compression of fuel, the subsequently a high-pressure accumulator, not shown is supplied.
- the high pressure pump 1 is used for fuel supply a fuel injection system, not shown for an internal combustion engine, also not shown, especially for a common rail injection system, which also is described in DE 197 56 087 A1.
- the drive shaft 2 for example, by a crank mechanism the internal combustion engine are driven. Alternatively it is also, a connection of the drive shaft 2 directly with a Camshaft of the internal combustion engine or a perfect separate drive of the same conceivable.
- the drive shaft 2 with the Piston 3 In the area in which the drive shaft 2 with the Piston 3 is in operative connection, it is eccentric, i.e. it has an eccentric shaft section 2a on.
- the shaft portion 2a is at its periphery with a so-called polygon ring 4 provided in the present case has three flats 5, which directly with the piston 3 in contact.
- the polygon ring 4 has a the number of pistons 3 corresponding number of flats 5 on.
- the polygon ring 4 is opposite the drive shaft. 2 rotatable and brings in this way one in the radial direction acting force on the piston 3, thereby successively to perform an oscillating movement.
- each piston plates 6 which have a recess 7 in which a first section 8 of the piston 3 is mounted.
- the piston plates 6 lead the Polygon ring 4 in its movement.
- Each piston 3 is the further associated with a spring element 9, the provision the respective piston 3 is used.
- the piston 3 has in addition to the with the polygon ring 4 in connection standing section 8 more piston sections 10, 11th and 12 on. This sets the largest diameter of the piston 3, that of the piston portion 12, the delivery volume the high-pressure pump 1 at a certain speed and a certain stroke.
- the high pressure pump 1 then works optimally when each piston 3 is exactly perpendicular to the associated piston plate 6 and not tilted. Due to the free mobility of the polygon ring 4 in operation, however, such a tilt can quite occur and is not always prevent how this also Fig. 2 shows. For this reason, the in the Recess 7 mounted portion 8 of the piston 3 and thus also the recess 7 itself a larger diameter than the subsequent section 10 of the piston 3.
- the diameter of section 8 depends on the loads from which the high pressure pump 1 exposed is. Furthermore, created by this enlarged diameter of section 8 a circumferential projection 13, on which a bracket 14 is supported as an assembly aid for the Piston plate 6 with the piston 3 is used and not in Fig. 1 is shown.
- the recess 7 facing portion 8 of the piston 3 is provided with a radius 15, in general 10 to 50 times the diameter of section 8 is so much smaller than before. To this Way is achieved that in case of a possible tilting the Piston 3 against the polygon ring 4 of the piston 3 faster returns to its basic position, since the restoring force this is greater. In general, the radius should be less being 45 times the diameter of section 8, to achieve this effect. In Fig. 2, the radius is 15th however, shown greatly enlarged.
- the diameter of the piston 3 is in a range between 8 - 10 mm and the radius is 15 about 200 mm, so that the radius 15 about 20 to 25 times the diameter of the piston 3 is, which is the practice very well suited. If the diameter of section 8 is larger, consequently, the radius 15 is larger.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Die Erfindung betrifft eine Hochdruckpumpe zur Kraftstoffversorgung von Kraftstoffeinspritzsystemen für Brennkraftmaschinen, insbesondere von Common-Rail-Einspritzsystemen, nach der im Oberbegriff von Anspruch 1 näher definierten Art.The invention relates to a high pressure pump for fuel supply of fuel injection systems for internal combustion engines, in particular of common rail injection systems, according to in the preamble of claim 1 closer defined type.
Eine gattungsgemäße Hochdruckpumpe ist aus der MTZ 58 (1997) S. 572 bzw. der DE 197 56 087 A1 bekannt. Die prinzipielle Wirkungsweise dieser Hochdruckpumpe ist für nach dem Common-Rail-Prinzip arbeitende Brennkraftmaschinen sehr gut geeignet, die spezielle Konstruktion derselben gewährleistet jedoch nicht in allen Betriebszuständen eine einwandfreie Funktion, so dass es durchaus zu Beschädigungen der Hochdruckpumpe und in Folge dessen eventuell sogar zu Beschädigungen der Brennkraftmaschine kommen kann.A generic high-pressure pump is from the MTZ 58 (1997) S. 572 and DE 197 56 087 A1. The principal Mode of action of this high-pressure pump is for the common-rail principle working internal combustion engines very well suited However, the special construction ensures the same not a perfect function in all operating states, so that it is quite damaging the high-pressure pump and possibly even damage to the Internal combustion engine can come.
Es ist daher Aufgabe der vorliegenden Erfindung, eine Hochdruckpumpe zur Kraftstoffversorgung von Kraftstoffeinspritzsystemen für Brennkraftmaschinen zu schaffen, welche eine sehr hohe Zuverlässigkeit im Betrieb aufweist und dabei die Vorteile der prinzipiellen Wirkungsweise gattungsgemäßer Hochdruckpumpen beibehält.It is therefore an object of the present invention, a high-pressure pump for fuel supply of fuel injection systems for internal combustion engines, which provide a has very high reliability in operation and the Advantages of the principle mode of action generic Maintains high pressure pumps.
Erfindungsgemäß wird diese Aufgabe durch die in Anspruch 1 genannten Merkmale gelöst.According to the invention this object is achieved by the in claim 1 solved mentioned features.
Durch die erfindungsgemäße Vergrößerung des in der Aussparung der Kolbenplatte untergebrachten Abschnitts des Kolbens gegenüber dem restlichen Teil des Kolbens werden im Betrieb der Hochdruckpumpe auftretende Verkippungen der Kolbenplatte gegenüber dem Kolben sehr viel besser aufgenommen, was insgesamt zu einer erheblich geringeren Verkippung des Kolbens führt. Dies ermöglicht einen bezüglich auftretender Störungen erheblich verbesserten Betrieb der erfindungsgemäßen Hochdruckpumpe und lässt des weiteren eine Vergrößerung des möglichen Betriebsbereiches der Hochdruckpumpe zu.Due to the enlargement of the invention in the recess the piston plate accommodated portion of the piston opposite the remaining part of the piston are in operation of the High pressure pump occurring tilting of the piston plate opposite The piston is much better absorbed, which in total to a much lower tilt of the piston leads. This enables a related interference significantly improved operation of the high-pressure pump according to the invention and further allows an enlargement of the possible Operating range of the high pressure pump too.
Eine weitere Lösung der Aufgabe ergibt sich aus den Merkmalen
des Anspruches 3.Another solution to the problem arises from the features
of
Dadurch, dass der Radius des der Aussparung zugewandten Abschnittes
des Kolbens das 10- bis 50-fache des Durchmessers
des Abschnittes beträgt und damit erheblich geringer ist als
bisher, ergibt sich auch hierdurch eine geringere Möglichkeit
zur Verkippung des Kolbens, was die bereits oben erwähnten
Vorteile mit sich bringt.Characterized in that the radius of the recess facing portion
of the
In der Praxis hat sich eine Kombination der beiden erfindungsgemäßen Lösungen als besonders vorteilhaft bezüglich der Zuverlässigkeit und des möglichen Betriebsbereiches der Hochdruckpumpe erwiesen.In practice, a combination of the two invention Solutions as particularly advantageous in terms of Reliability and possible operating range of the high pressure pump proved.
Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen sowie aus dem nachfolgend anhand der Zeichnung prinzipmäßig dargestellten Ausführungsbeispiel.Advantageous embodiments and developments of the invention emerge from the dependent claims and from the following Based on the drawing in principle illustrated embodiment.
- Fig. 1Fig. 1
- einen Teil der erfindungsgemäßen Hochdruckpumpe; unda part of the high-pressure pump according to the invention; and
- Fig. 2Fig. 2
- eine vergrößerte Darstellung der Hochdruckpumpe aus Fig. 1.an enlarged view of the high pressure pump Fig. 1.
Der prinzipielle Aufbau der in Fig. 1 dargestellten Hochdruckpumpe 1 ist aus der DE 197 56 087 A1 bekannt, weshalb im folgenden nur kurz auf die prinzipielle Wirkungsweise derselben eingegangen wird. Außerdem sind nicht alle zur Funktion der Hochdruckpumpe 1 erforderlichen Bauteile dargestellt. Hierzu wird ebenfalls auf die DE 197 56 087 A1 verwiesen.The basic structure of the high-pressure pump shown in FIG 1 is known from DE 197 56 087 A1, which is why in The following only briefly on the principal mode of action of the same will be received. Besides, not all are functional the high-pressure pump 1 required components shown. Reference is also made to DE 197 56 087 A1.
Die Hochdruckpumpe 1 weist eine Antriebswelle 2 auf, die zum
Antrieb von im vorliegenden Fall drei um 120° zueinander versetzte
Kolben 3 vorgesehen ist. Da die Hochdruckpumpe 1 symmetrisch
ausgeführt ist, gilt das im folgenden für einen der
drei Kolben 3 erläuterte auch für die anderen beiden Kolben
3. In diesem Zusammenhang ist es selbstverständlich möglich,
am Umfang der Antriebswelle 2 eine größere oder auch eine geringere
Anzahl an Kolben 3 anzubringen.The high pressure pump 1 has a drive shaft 2, the
Drive offset by three in the present case by 120 ° to each other
Piston 3 is provided. Since the high-pressure pump 1 is symmetrical
is executed, the following applies to one of the
three
Die Kolben 3 sind zur Verdichtung von Kraftstoff vorgesehen,
der anschließend einem nicht dargestellten Hochdruckspeicher
zugeführt wird. Die Hochdruckpumpe 1 dient zur Kraftstoffversorgung
eines nicht dargestellten Kraftstoffeinspritzsystems
für eine ebenfalls nicht dargestellte Brennkraftmaschine,
insbesondere für ein Common-Rail-Einspritzsystem, welches ebenfalls
in der DE 197 56 087 A1 beschrieben ist.The
Die Antriebswelle 2 kann beispielsweise von einem Kurbeltrieb der Brennkraftmaschine angetrieben werden. Alternativ ist auch eine Verbindung der Antriebswelle 2 unmittelbar mit einer Nockenwelle der Brennkraftmaschine oder ein vollkommen separater Antrieb derselben denkbar.The drive shaft 2, for example, by a crank mechanism the internal combustion engine are driven. Alternatively it is Also, a connection of the drive shaft 2 directly with a Camshaft of the internal combustion engine or a perfect separate drive of the same conceivable.
In demjenigen Bereich, in dem die Antriebswelle 2 mit den
Kolben 3 in Wirkverbindung steht, ist sie exzentrisch ausgebildet,
d.h. sie weist einen exzentrischen Wellenabschnitt 2a
auf. Der Wellenabschnitt 2a ist an seinem Umfang mit einem
sogenannten Polygonring 4 versehen, der im vorliegenden Fall
drei Abflachungen 5 aufweist, die unmittelbar mit den Kolben
3 in Kontakt stehen. Allgemein weist der Polygonring 4 eine
der Anzahl der Kolben 3 entsprechende Anzahl an Abflachungen
5 auf. Der Polygonring 4 ist gegenüber der Antriebswelle 2
verdrehbar und bringt auf diese Weise eine in radialer Richtung
wirkende Kraft auf die Kolben 3 auf, wodurch diese nacheinander
eine oszillierende Bewegung ausführen.In the area in which the drive shaft 2 with the
Piston 3 is in operative connection, it is eccentric,
i.e. it has an eccentric shaft section 2a
on. The shaft portion 2a is at its periphery with a
so-called
Wie in der vergrößerten Darstellung gemäß Fig. 2 besser erkennbar
ist, sind zwischen den Kolben 3 und der Antriebswelle
2 bzw. dem Polygonring 4 jeweils Kolbenplatten 6 angeordnet,
die eine Aussparung 7 aufweisen, in der ein erster Abschnitt
8 des Kolbens 3 gelagert ist. Die Kolbenplatten 6 führen den
Polygonring 4 bei seiner Bewegung. Jedem Kolben 3 ist des
weiteren ein Federelement 9 zugeordnet, der zur Rückstellung
des jeweiligen Kolbens 3 dient.As in the enlarged view of FIG. 2 better visible
is, are between the
Der Kolben 3 weist neben dem mit dem Polygonring 4 in Verbindung
stehenden Abschnitt 8 weitere Kolbenabschnitte 10, 11
und 12 auf. Hierbei legt der größte Durchmesser des Kolbens
3, also derjenige des Kolbenabschnitts 12, das Fördervolumen
der Hochdruckpumpe 1 bei einer bestimmten Drehzahl und einem
bestimmten Hub fest.The
Die Hochdruckpumpe 1 arbeitet dann optimal, wenn jeder Kolben
3 genau senkrecht zu der zugehörigen Kolbenplatte 6 steht und
nicht verkippt ist. Durch die freie Beweglichkeit des Polygonrings
4 im Betrieb kann eine solche Verkippung allerdings
durchaus auftreten und ist nicht immer zu verhindern, wie
dies auch Fig. 2 zeigt. Aus diesem Grund weisen der in der
Aussparung 7 gelagerte Abschnitt 8 des Kolbens 3 und somit
auch die Aussparung 7 selbst einen größeren Durchmesser als
der nachfolgende Abschnitt 10 des Kolbens 3 auf.The high pressure pump 1 then works optimally when each
Durch diese Maßnahme wird sichergestellt, dass der Punkt, an
dem die Kraft von der Kolbenplatte 6 auf den Kolben 3 übertragen
wird, in jeder Winkellage des Kolbens 3 auf demselben
liegt. Hierdurch ergibt sich in jedem Betriebszustand eine
sichere Übertragung der Bewegung des Polygonrings 4 auf die
Kolben 3. Der Durchmesser des Abschnittes 8 hängt dabei von
den Belastungen ab, denen die Hochdruckpumpe 1 ausgesetzt
ist. Des weiteren entsteht durch diesen vergrößerten Durchmesser
des Abschnitts 8 ein umlaufender Vorsprung 13, an dem
sich eine Klammer 14 abstützt, die als Montagehilfe für die
Kolbenplatte 6 mit dem Kolben 3 dient und in Fig. 1 nicht
dargestellt ist.This measure ensures that the point at
the force transmitted from the
Des weiteren ist der der Aussparung 7 zugewandte Abschnitt 8
des Kolbens 3 mit einem Radius 15 versehen, der im allgemeinen
das 10- bis 50-fache des Durchmessers des Abschnitts 8
beträgt, also sehr viel kleiner als bisher ist. Auf diese
Weise wird erreicht, dass bei einem eventuellen Verkippen der
Kolben 3 gegenüber dem Polygonring 4 der Kolben 3 schneller
in seine Grundstellung zurückkehrt, da die Rückstellkraft
hierfür größer ist. Im allgemeinen sollte der Radius weniger
als das 45-fache des Durchmessers des Abschnitts 8 betragen,
um diese Wirkung zu erreichen. In Fig. 2 ist der Radius 15
allerdings stark vergrößert dargestellt.Furthermore, the
Im vorliegenden Fall liegt der Durchmesser des Kolbens 3 in
einem Bereich zwischen 8 - 10 mm und der Radius 15 beträgt
ca. 200 mm, so dass der Radius 15 ca. das 20- bis 25-fache
des Durchmessers des Kolbens 3 beträgt, was für die Praxis
sehr gut geeignet ist. Wenn der Durchmesser des Abschnitts 8
größer ist, ist folglich auch der Radius 15 größer.In the present case, the diameter of the
Claims (6)
dadurch gekennzeichnet, dass
die Aussparung (7) und der der Aussparung (7) zugewandte Abschnitt (8) des Kolbens (3) einen größeren Querschnitt aufweisen als ein nachfolgender, von der Kolbenplatte (6) abgewandter Abschnitt (10) des Kolbens (3).High-pressure pump for fuel supply of fuel injection systems for internal combustion engines, in particular of common rail injection systems, with a drive shaft and at least two movable from the drive shaft piston for compressing the fuel, wherein between the drive shaft and the at least two pistons each having a piston plate is arranged, the one Recess has, in which a portion of the piston is mounted,
characterized in that
the recess (7) and the section (8) of the piston (3) facing the recess (7) have a larger cross-section than a subsequent section (10) of the piston (3) facing away from the piston plate (6).
dadurch gekennzeichnet, dass
der der Aussparung (7) zugewandte Abschnitt (8) des Kolbens (3) an seiner der Kolbenplatte (6) zugewandten Seite einen Radius (15) aufweist, der das 10- bis 50-fache des Durchmessers des Abschnittes (8) beträgt.High-pressure pump according to claim 1,
characterized in that
the recess (7) facing portion (8) of the piston (3) on its piston plate (6) facing side has a radius (15) which is 10 to 50 times the diameter of the portion (8).
dadurch gekennzeichnet, dass
der der Aussparung (7) zugewandte Abschnitt (8) des Kolbens (3) an seiner der Kolbenplatte (6) zugewandten Seite einen Radius (15) aufweist, der das 10- bis 50-fache des Durchmessers des Abschnittes (8) beträgt.High-pressure pump for fuel supply of fuel injection systems for internal combustion engines, in particular of common rail injection systems, with a drive shaft and at least two movable from the drive shaft piston for compressing the fuel, wherein between the drive shaft and the at least two pistons each having a piston plate is arranged, the one Recess has, in which a portion of the piston is mounted,
characterized in that
the recess (7) facing portion (8) of the piston (3) on its piston plate (6) facing side has a radius (15) which is 10 to 50 times the diameter of the portion (8).
dadurch gekennzeichnet, dass
die Aussparung (7) und der der Aussparung (7) zugewandte Abschnitt (8) des Kolbens (3) einen größeren Querschnitt aufweisen als ein nachfolgender, von der Kolbenplatte (6) abgewandter Abschnitt (10) des Kolbens (3).High-pressure pump according to claim 1,
characterized in that
the recess (7) and the section (8) of the piston (3) facing the recess (7) have a larger cross-section than a subsequent section (10) of the piston (3) facing away from the piston plate (6).
dadurch gekennzeichnet, dass
die Antriebswelle (2) in demjenigen Bereich, in dem sie mit den Kolben (3) in Wirkverbindung steht, exzentrisch ausgebildet ist.High-pressure pump according to one of claims 1 to 4,
characterized in that
the drive shaft (2) is formed eccentrically in the region in which it is in operative connection with the piston (3).
dadurch gekennzeichnet, dass
die Antriebswelle (2) in demjenigen Bereich, in dem sie mit den Kolben (3) in Wirkverbindung steht, mit einem Ring (4) versehen ist, der eine der Anzahl der Kolben (3) entsprechende Anzahl an Abflachungen (5) aufweist.High-pressure pump according to one of claims 1 to 5,
characterized in that
the drive shaft (2) in the region in which it is in operative connection with the piston (3), provided with a ring (4) having a number of flats (5) corresponding to the number of pistons (3).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10157375 | 2001-11-22 | ||
| DE2001157375 DE10157375A1 (en) | 2001-11-22 | 2001-11-22 | high pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1314882A1 true EP1314882A1 (en) | 2003-05-28 |
| EP1314882B1 EP1314882B1 (en) | 2008-04-23 |
Family
ID=7706632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02020978A Expired - Lifetime EP1314882B1 (en) | 2001-11-22 | 2002-09-20 | High-pressure pump |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP1314882B1 (en) |
| DE (2) | DE10157375A1 (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19756087A1 (en) | 1997-12-17 | 1999-06-24 | Bosch Gmbh Robert | High pressure pump for fuel supply in fuel injection systems of internal combustion engines |
| WO1999037916A1 (en) * | 1998-01-23 | 1999-07-29 | Robert Bosch Gmbh | Radial piston pump for producing high pressure fuel |
| WO1999045271A1 (en) * | 1998-03-05 | 1999-09-10 | Robert Bosch Gmbh | Radial piston pump for fuel high pressure generation |
| DE19943160A1 (en) * | 1998-09-10 | 2000-03-16 | Denso Corp | Fuel injection pump for supplying high pressure fuel to internal combustion engine comprises pump housing, cylinder and cavity arranged concentrically to each other in pump housing |
| US6077056A (en) * | 1997-02-12 | 2000-06-20 | Robert Bosch Gmbh | Reciprocating pump |
| DE10018708A1 (en) * | 1999-04-16 | 2000-11-02 | Denso Corp | Fuel injection pump has bias device for movable unit for subjecting fuel in fuel pressure chamber to pressure, reciprocal motion regulator that operates if unit raised above upper dead point |
| DE10044997A1 (en) * | 2000-09-11 | 2002-03-21 | Schaeffler Waelzlager Ohg | Compression plate of radial piston pump has piston rest with conical or curved profile |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10150351A1 (en) * | 2001-10-15 | 2003-05-08 | Bosch Gmbh Robert | Pump element and piston pump for high-pressure fuel generation |
-
2001
- 2001-11-22 DE DE2001157375 patent/DE10157375A1/en not_active Withdrawn
-
2002
- 2002-09-20 DE DE50212139T patent/DE50212139D1/en not_active Expired - Lifetime
- 2002-09-20 EP EP02020978A patent/EP1314882B1/en not_active Expired - Lifetime
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6077056A (en) * | 1997-02-12 | 2000-06-20 | Robert Bosch Gmbh | Reciprocating pump |
| DE19756087A1 (en) | 1997-12-17 | 1999-06-24 | Bosch Gmbh Robert | High pressure pump for fuel supply in fuel injection systems of internal combustion engines |
| WO1999037916A1 (en) * | 1998-01-23 | 1999-07-29 | Robert Bosch Gmbh | Radial piston pump for producing high pressure fuel |
| WO1999045271A1 (en) * | 1998-03-05 | 1999-09-10 | Robert Bosch Gmbh | Radial piston pump for fuel high pressure generation |
| DE19943160A1 (en) * | 1998-09-10 | 2000-03-16 | Denso Corp | Fuel injection pump for supplying high pressure fuel to internal combustion engine comprises pump housing, cylinder and cavity arranged concentrically to each other in pump housing |
| DE10018708A1 (en) * | 1999-04-16 | 2000-11-02 | Denso Corp | Fuel injection pump has bias device for movable unit for subjecting fuel in fuel pressure chamber to pressure, reciprocal motion regulator that operates if unit raised above upper dead point |
| DE10044997A1 (en) * | 2000-09-11 | 2002-03-21 | Schaeffler Waelzlager Ohg | Compression plate of radial piston pump has piston rest with conical or curved profile |
Also Published As
| Publication number | Publication date |
|---|---|
| DE50212139D1 (en) | 2008-06-05 |
| EP1314882B1 (en) | 2008-04-23 |
| DE10157375A1 (en) | 2003-06-05 |
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