WO2004085847A1 - High-pressure pump for a fuel-injection device of an internal combustion engine - Google Patents
High-pressure pump for a fuel-injection device of an internal combustion engine Download PDFInfo
- Publication number
- WO2004085847A1 WO2004085847A1 PCT/DE2003/003532 DE0303532W WO2004085847A1 WO 2004085847 A1 WO2004085847 A1 WO 2004085847A1 DE 0303532 W DE0303532 W DE 0303532W WO 2004085847 A1 WO2004085847 A1 WO 2004085847A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- ring
- pressure pump
- pump
- fuel
- shaft section
- Prior art date
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Classifications
-
- 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
- F04B1/0413—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
Definitions
- the invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine, according to the preamble of claim 1.
- Such a high pressure pump is known from DE 198 44 272 AI.
- This high-pressure pump has a rotationally driven drive shaft which has a shaft section which is formed eccentrically to its axis of rotation.
- a polygon ring is rotatably mounted on the eccentric shaft section.
- the high-pressure pump has at least one pump element with a pump piston which is driven at least indirectly by the drive shaft via the ring in a stroke movement.
- the ring is supported on the shaft section via a bearing bush.
- the high pressure pump according to the invention with the features according to claim 1 has the advantage that by A sufficiently wear-resistant mounting of the ring on the shaft section is achieved and the bearing bush can be omitted, so that the above-described problems with regard to migration are avoided.
- the ring can be given
- the high-pressure pump has a housing 10 which is formed in several parts and in which a drive shaft 12 is arranged.
- the drive shaft 12 is rotatably mounted in the housing 10 via two bearing points 14 and 16 spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12.
- the bearing points 14, 16 can be arranged in different parts of the housing 10.
- the drive shaft 12 has a shaft section 26 which is formed eccentrically to its axis of rotation 13 and on which a transmission element 28 in the form of a polygon ring is rotatably mounted via a bearing point 30.
- the high-pressure pump has at least one, preferably a plurality of pump elements 32 arranged in the housing 10, each with a pump piston 34 which is driven by the polygon ring 28 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
- the pump piston 34 is guided in a cylinder bore 36 in the housing 10 or an insert in the housing 10 in a tightly displaceable manner and delimits one in the cylinder bore 36 with its end face remote from the transmission element 28
- the pump work space 38 has a connection to a fuel feed, for example a feed pump, via a fuel feed channel 40 running in the housing 10.
- a fuel feed for example a feed pump
- a fuel feed channel 40 running in the housing 10.
- an inlet valve 42 opening into the pump working space 38 is arranged, which has a spring-loaded valve member 43.
- the pump working space 38 also has a connection to an outlet via a fuel drain channel 44 running in the housing 10, said outlet being connected, for example, to an accumulator.
- an outlet valve 46 opening out of the pump work space 38, which also has a spring-loaded valve member 47.
- the pump piston 34 is held by a prestressed spring 48 with its piston foot 50 directly or via a plunger 52 in contact with the polygon ring 28.
- the polygon ring 28 executes a movement perpendicular to the axis of rotation 13 of the drive shaft 12, which causes the stroke of the pump piston 34.
- the polygon ring 28 has in its outer jacket for each pump element 32 a flat 29 on which the piston foot 50 or the plunger 52 rests.
- the pump working chamber 38 is filled with fuel through the fuel inlet channel 40 with the inlet valve 42 open, the outlet valve 46 being closed.
- fuel is conveyed by the pump piston 34 under high pressure through the fuel drain channel 44 to the reservoir 110 with the outlet valve 46 open, the inlet valve 42 being closed.
- the polygon ring 28 is mounted directly on the shaft section 26 via the bearing point 30, that is to say without a bearing bush.
- the polygon ring 28 is on its inner surface facing the shaft section 26 with a
- Coating 54 provided from a lubricating varnish.
- the shaft section 26 can also be provided with a coating 54 made of a lubricating varnish on its outer surface facing the polygon ring 28.
- the coating 54 has a thickness between approximately 10 and 50 ⁇ m, preferably between approximately 15 and 30 ⁇ m.
- the coating 54 consists of a lubricating varnish with the required properties with regard to the coefficient of friction, wear resistance and temperature resistance for use at the bearing point 30 Fuel inside the housing 10 ensures low friction and sufficient wear resistance of the bearing point 30. Given a predetermined size of the outer cross section of the polygon ring 28, this can be made with a relatively large wall thickness because of the small thickness of the coating 54 and the small inner diameter that is possible as a result.
Abstract
The invention relates to a high-pressure pump comprising a rotationally driven drive shaft (12) with a shaft section (26) that is configured eccentrically in relation to its rotational axis (13) and that is provided with a rotatably mounted ring (28). The high pressure pump comprises at least one pump element (32) with a pump piston (34), whose stroke is driven at least indirectly by the drive shaft (12) via the ring (28). The inner surface of the ring (28) facing the shaft section (26) and/or the outer surface of the shaft section (26) facing the ring (28) is/are provided with an anti-friction lacquer coating.
Description
Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineHigh pressure pump for a fuel injector of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, nach der Gattung des Anspruchs 1.The invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine, according to the preamble of claim 1.
Eine solche Hochdruckpumpe ist durch die DE 198 44 272 AI bekannt. Diese Hochdruckpumpe weist eine rotierend angetriebene Antriebswelle auf, die einen exzentrisch zu ihrer Drehachse ausgebildeten Wellenabschnitt aufweist. Auf dem exzentrischen Wellenabschnitt ist ein Polygonring drehbar gelagert. Die Hochdruckpumpe weist wenigstens ein Pumpenelement mit einem zumindest mittelbar durch die Antriebswelle über den Ring in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Ring ist über eine Lagerbuchse auf dem Wellenabschnitt gelagert. Durch die Lagerbuchse wird zwar ein geringer Verschleiß erreicht, jedoch erhöht diese den Fertigungsaufwand der Hochdruckpumpe und die Lagerbuchse kann unter Umständen in Richtung der Drehachse der Antriebswelle auswandern, wodurch Abriebpartikel entstehen, die wiederum zu einem erhöhten Verschleiß von Bauteilen der Hochdruckpumpe führen. Um ein Auswandern der Lagerbuchse zu verhindern wären weitere aufwendige Maßnahmen erforderlich.Such a high pressure pump is known from DE 198 44 272 AI. This high-pressure pump has a rotationally driven drive shaft which has a shaft section which is formed eccentrically to its axis of rotation. A polygon ring is rotatably mounted on the eccentric shaft section. The high-pressure pump has at least one pump element with a pump piston which is driven at least indirectly by the drive shaft via the ring in a stroke movement. The ring is supported on the shaft section via a bearing bush. Although the bearing bushing achieves little wear, this increases the production outlay for the high-pressure pump, and the bearing bushing can possibly migrate in the direction of the axis of rotation of the drive shaft, which creates abrasion particles, which in turn lead to increased wear on components of the high-pressure pump. In order to prevent the bearing bush from migrating, further complex measures would be necessary.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die
Gleitlackbeschichtung eine ausreichend verschleißbeständige Lagerung des Rings auf dem Wellenabschnitt erreicht ist und die Lagerbuchse entfallen kann, so dass auch die vorstehend erläuterten Probleme hinsichtlich des Auswanderns vermieden sind. Darüberhinaus kann der Ring bei gegebenenThe high pressure pump according to the invention with the features according to claim 1 has the advantage that by A sufficiently wear-resistant mounting of the ring on the shaft section is achieved and the bearing bush can be omitted, so that the above-described problems with regard to migration are avoided. In addition, the ring can be given
Außenabmessungen mit größerer Wandstärke gegenüber einer Ausführung mit Lagerbuchse versehen werden, da die Gleitlackbeschichtung mit einer geringeren Dicke aufgebracht werden kann als die Lagerbuchse, für die eine bestimmte Mindestdicke erforderlich ist, die nicht unterschritten werden kann. Die größere Wandstärke bewirkt eine zusätzliche Versteifung des Rings, wodurch er im Belastungsfall weniger verformt wird. Außerdem entfällt das durch das Einpressen der Lagerbuchse verursachte Aufwölben des Rings, wodurch die Gleitbewegung der an diesem anliegenden Pumpenkolben oder Stößel negativ beeinflusst wird.External dimensions with a greater wall thickness than a version with a bearing bush can be provided, since the lubricating lacquer coating can be applied with a smaller thickness than the bearing bush, for which a certain minimum thickness is required, which cannot be undercut. The larger wall thickness results in additional stiffening of the ring, which means that it is less deformed when loaded. In addition, there is no bulging of the ring caused by the bearing bush being pressed in, as a result of which the sliding movement of the pump pistons or plunger abutting against it is negatively influenced.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben.Advantageous refinements and developments of the high-pressure pump according to the invention are specified in the dependent claims.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eineAn embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a
Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine mit einer Hochdruckpumpe und Figur 2 die Hochdruckpumpe in einem Querschnitt entlang Linie II-II in Figur 1.Fuel injection device of an internal combustion engine with a high pressure pump and FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In den Figuren 1 und 2 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet ist und in dem eine Antriebswelle
12 angeordnet ist. Die Antriebswelle 12 ist im Gehäuse 10 über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen 14 und 16 drehbar gelagert. Die Lagerstellen 14,16 können in verschiedenen Teilen des Gehäuses 10 angeordnet sein.1 and 2 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a housing 10 which is formed in several parts and in which a drive shaft 12 is arranged. The drive shaft 12 is rotatably mounted in the housing 10 via two bearing points 14 and 16 spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12. The bearing points 14, 16 can be arranged in different parts of the housing 10.
In einem zwischen den beiden Lagerstellen 14,16 liegenden Bereich weist die Antriebswelle 12 einen exzentrisch zu ihrer Drehachse 13 ausgebildeten Wellenabschnitt 26 auf, auf dem ein Übertragungselement 28 in Form eines Polygonrings über eine Lagerstelle 30 drehbar gelagert ist. Die Hochdruckpumpe weist wenigstens ein, vorzugsweise mehrere im Gehäuse 10 angeordnete Pumpenelemente 32 mit jeweils einem Pumpenkolben 34 auf, der durch den Polygonring 28 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebsewelle 12 angetrieben wird. Der Pumpenkolben 34 ist in einer Zylinderbohrung 36 im Gehäuse 10 oder einem Einsatz im Gehäuse 10 dicht verschiebbar geführt und begrenzt mit seiner dem Übertragungselement 28 abgewandten Stirnseite in der Zylinderbohrung 36 einenIn a region lying between the two bearing points 14, 16, the drive shaft 12 has a shaft section 26 which is formed eccentrically to its axis of rotation 13 and on which a transmission element 28 in the form of a polygon ring is rotatably mounted via a bearing point 30. The high-pressure pump has at least one, preferably a plurality of pump elements 32 arranged in the housing 10, each with a pump piston 34 which is driven by the polygon ring 28 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. The pump piston 34 is guided in a cylinder bore 36 in the housing 10 or an insert in the housing 10 in a tightly displaceable manner and delimits one in the cylinder bore 36 with its end face remote from the transmission element 28
Pumpenarbeitsraum 38. Der Pumpenarbeitsraum 38 weist über einen im Gehäuse 10 verlaufenden Kraftstoffzulaufkanal 40 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung des Kraftstoffzulaufkanals 40 in den Pumpenarbeitsraum 38 ist . ein in den Pumpenarbeitsraum 38 öffnendes Einlassventil 42 angeordnet, das ein federbelastetes Ventilglied 43 aufweist. Der Pumpenarbeitsraum 38 weist ausserdem über einen im Gehäuse 10 verlaufenden Kraftstoffablaufkanal 44 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Speicher verbunden ist. An der Mündung des Kraftstoffablaufkanals 44 in den Pumpenarbeitsraum 38 ist ein aus dem Pumpenarbeitsraum 38 öffnendes Auslassventil 46 angeordnet, das ebenfalls ein federbelastetes Ventilglied 47 aufweist.
Der Pumpenkolben 34 wird durch eine vorgespannte Feder 48 mit seinem Kolbenfuss 50 direkt oder über einen Stößel 52 in Anlage am Polygonring 28 gehalten. Bei der Drehbewegung der Antriebswelle 12 wird der Polygonring 28 nicht mit dieser mitbewegt, führt jedoch aufgrund des Exzenterabschnitts 26 eine Bewegung senkrecht zur Drehachse 13 der Antriebswelle 12 aus, die die Hubbewegung des Pumpenkolbens 34 bewirkt. Der Polygonring 28 weist in seinem Außenmantel für jedes Pumpenelement 32 eine Abflachung 29 auf, an der der Kolbenfuß 50 oder der Stößel 52 anliegt. Beim Saughub des Pumpenkolbens 34, bei dem sich dieser radial nach innen bewegt, wird der Pumpenarbeitsraum 38 durch den Kraftstoffzulaufkanal 40 bei geöffnetem Einlassventil 42 mit Kraftstoff befüllt, wobei das Auslassventil 46 geschlossen ist. Beim Förderhub des Pumpenkolbens 34, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 34 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 44 bei geöffnetem Auslassventil 46 zum Speicher 110 gefördert, wobei das Einlassventil 42 geschlossen ist.Pump work space 38. The pump work space 38 has a connection to a fuel feed, for example a feed pump, via a fuel feed channel 40 running in the housing 10. At the mouth of the fuel inlet channel 40 in the pump work space 38. an inlet valve 42 opening into the pump working space 38 is arranged, which has a spring-loaded valve member 43. The pump working space 38 also has a connection to an outlet via a fuel drain channel 44 running in the housing 10, said outlet being connected, for example, to an accumulator. At the mouth of the fuel drain channel 44 into the pump work space 38 there is an outlet valve 46 opening out of the pump work space 38, which also has a spring-loaded valve member 47. The pump piston 34 is held by a prestressed spring 48 with its piston foot 50 directly or via a plunger 52 in contact with the polygon ring 28. When the drive shaft 12 rotates, the polygon ring 28 is not moved with it, but, due to the eccentric section 26, executes a movement perpendicular to the axis of rotation 13 of the drive shaft 12, which causes the stroke of the pump piston 34. The polygon ring 28 has in its outer jacket for each pump element 32 a flat 29 on which the piston foot 50 or the plunger 52 rests. During the suction stroke of the pump piston 34, during which it moves radially inward, the pump working chamber 38 is filled with fuel through the fuel inlet channel 40 with the inlet valve 42 open, the outlet valve 46 being closed. During the delivery stroke of the pump piston 34, during which it moves radially outwards, fuel is conveyed by the pump piston 34 under high pressure through the fuel drain channel 44 to the reservoir 110 with the outlet valve 46 open, the inlet valve 42 being closed.
Der Polygonring 28 ist über die Lagerstellte 30 direkt, das heisst ohne Lagerbuchse, auf dem Wellenabschnitt 26 gelagert. Der Polygonring 28 ist auf seiner dem Wellenabschnitt 26 zugewandten Innenfläche mit einerThe polygon ring 28 is mounted directly on the shaft section 26 via the bearing point 30, that is to say without a bearing bush. The polygon ring 28 is on its inner surface facing the shaft section 26 with a
Beschichtung 54 aus einem Gleitlack versehen. Alternativ oder zusätzlich kann auch der Wellenabschnitt 26 auf seiner dem Polygonring 28 zugewandten Aussenfläche mit einer Beschichtung 54 aus einem Gleitlack versehen sein. Die Beschichtung 54 weist eine Dicke zwischen etwa 10 und 50 μm, vorzugsweise zwischen etwa 15 und 30 μm auf. Die Beschichtung 54 besteht aus einem Gleitlack mit den erforderlichen Eigenschaften hinsichtlich Reibwert, Verschleißbeständigkeit und Temperaturbeständigkeit zum Einsatz an der Lagerstelle 30. Durch die Beschichtung 54 wird auch bei Schmierung der Lagerstelle 30 nur durch den im
Inneren des Gehäuses 10 vorhandenen Kraftstoff eine geringe Reibung und eine ausreichende Verschleißbeständigkeit der Lagerstelle 30 sichergestellt. Bei einer vorgegebenen Größe des Aussenquerschnitts des Polygonrings 28 kann dieser wegen der geringen Dicke der Beschichtung 54 und des dadurch möglichen geringen Innendurchmessers mit relativ grosser Wandstärke ausgeführt werden.
Coating 54 provided from a lubricating varnish. Alternatively or additionally, the shaft section 26 can also be provided with a coating 54 made of a lubricating varnish on its outer surface facing the polygon ring 28. The coating 54 has a thickness between approximately 10 and 50 μm, preferably between approximately 15 and 30 μm. The coating 54 consists of a lubricating varnish with the required properties with regard to the coefficient of friction, wear resistance and temperature resistance for use at the bearing point 30 Fuel inside the housing 10 ensures low friction and sufficient wear resistance of the bearing point 30. Given a predetermined size of the outer cross section of the polygon ring 28, this can be made with a relatively large wall thickness because of the small thickness of the coating 54 and the small inner diameter that is possible as a result.
Claims
1. Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit einer rotierend angetriebenen Antriebswelle (12) , die einen zu ihrer Drehachse (13) exzentrisch ausgebildeten Wellenabschnitt (26) aufweist, auf dem ein Ring (28) drehbar gelagert ist, und mit wenigstens einem Pumpenelement (32) , das einen durch die Antriebswelle (12) über den Ring (28) zumindest mittelbar in einer Hubbewegung angetriebenen Pumpenkolben (34) aufweist, dadurch gekennzeichnet, dass der Ring (28) auf seiner dem Wellenabschnitt (26) zugewandten Innenfläche und/oder der Wellenabschnitt (26) auf seiner dem Ring (28) zugewandten Aussenfläche mit einer Beschichtung (54) aus einem Gleitlack versehen ist.1. High-pressure pump for a fuel injection device of an internal combustion engine, with a rotationally driven drive shaft (12) which has a shaft section (26) which is eccentric to its axis of rotation (13) and on which a ring (28) is rotatably mounted, and with at least one pump element (32), which has a pump piston (34) driven by the drive shaft (12) via the ring (28) at least indirectly in a lifting movement, characterized in that the ring (28) on its inner surface facing the shaft section (26) and / or the shaft section (26) is provided on its outer surface facing the ring (28) with a coating (54) of a lubricating varnish.
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Beschichtung (54) eine Dicke zwischen etwa 10 und 50 μm aufweist.2. High-pressure pump according to claim 1, characterized in that the coating (54) has a thickness between about 10 and 50 microns.
3. Hochdruckpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die Beschichtung (54) eine Dicke zwischen etwa 15 und 30 μm aufweist. 3. High pressure pump according to claim 2, characterized in that the coating (54) has a thickness between about 15 and 30 microns.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10313744.0 | 2003-03-27 | ||
| DE2003113744 DE10313744A1 (en) | 2003-03-27 | 2003-03-27 | High pressure pump for a fuel injector of an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2004085847A1 true WO2004085847A1 (en) | 2004-10-07 |
Family
ID=32946230
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/DE2003/003532 WO2004085847A1 (en) | 2003-03-27 | 2003-10-23 | High-pressure pump for a fuel-injection device of an internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE10313744A1 (en) |
| WO (1) | WO2004085847A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006034768A1 (en) * | 2006-07-27 | 2008-01-31 | Siemens Ag | Radial piston pump unit for high-pressure fuel supply in fuel injection systems |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4222714A (en) * | 1977-04-16 | 1980-09-16 | Rexroth Gmbh | Radial piston pump |
| DE4406803A1 (en) * | 1994-03-02 | 1995-09-07 | Rexroth Mannesmann Gmbh | Hydraulic piston pump |
| DE19829547A1 (en) * | 1998-07-02 | 2000-01-13 | Bosch Gmbh Robert | Radial piston pump especially for common rail fuel injection systems |
| DE19844272A1 (en) * | 1998-09-26 | 2000-04-06 | Bosch Gmbh Robert | Radial piston pump for high fuel pressure generation in fuel injection systems for motor vehicles has drive shaft section with polygonal ring and guide plate to prevent uncontrolled ring acceleration/decceleration |
-
2003
- 2003-03-27 DE DE2003113744 patent/DE10313744A1/en not_active Withdrawn
- 2003-10-23 WO PCT/DE2003/003532 patent/WO2004085847A1/en not_active Application Discontinuation
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4222714A (en) * | 1977-04-16 | 1980-09-16 | Rexroth Gmbh | Radial piston pump |
| DE4406803A1 (en) * | 1994-03-02 | 1995-09-07 | Rexroth Mannesmann Gmbh | Hydraulic piston pump |
| DE19829547A1 (en) * | 1998-07-02 | 2000-01-13 | Bosch Gmbh Robert | Radial piston pump especially for common rail fuel injection systems |
| DE19844272A1 (en) * | 1998-09-26 | 2000-04-06 | Bosch Gmbh Robert | Radial piston pump for high fuel pressure generation in fuel injection systems for motor vehicles has drive shaft section with polygonal ring and guide plate to prevent uncontrolled ring acceleration/decceleration |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10313744A1 (en) | 2004-10-07 |
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