EP1415092A1 - High pressure feed pump - Google Patents
High pressure feed pumpInfo
- Publication number
- EP1415092A1 EP1415092A1 EP02742623A EP02742623A EP1415092A1 EP 1415092 A1 EP1415092 A1 EP 1415092A1 EP 02742623 A EP02742623 A EP 02742623A EP 02742623 A EP02742623 A EP 02742623A EP 1415092 A1 EP1415092 A1 EP 1415092A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- delivery
- piston
- spring element
- feed pump
- pressure
- 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.)
- Withdrawn
Links
Classifications
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- 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
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- 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
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- 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
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- 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
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- 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
- F04B1/0439—Supporting or guiding means for the pistons
Definitions
- the present invention relates to a high-pressure feed pump with the features of the preamble of patent claim 1.
- Such high-pressure feed pumps operating according to the reciprocating piston principle are used in particular for generating the injection pressure in fuel injection systems - e.g. Common rail systems - used for internal combustion engines.
- a generic high pressure feed pump is disclosed in EP-A-1 058 001.
- High-pressure feed pumps of the generic type have a high-pressure cylinder or plunger cylinder and a cylindrical feed piston or plunger piston which can be reciprocated therein, the volume of the delivery space within the high-pressure cylinder being changed by the stroke movement of the plunger piston.
- the delivery space can be connected via a filling valve to a storage space for a delivery medium, in order to fill the delivery space, which increases in displacement, with the delivery medium.
- the pressure in the delivery chamber increases until a pressure valve opens and thereby connects the delivery chamber to a high-pressure room, for example the Cornmon Rail.
- the plunger is driven by an eccentric drive, which comprises an eccentric mounted on an eccentric shaft, on which a rolling ring is rotatably mounted. To reduce its moment of inertia, it has a convex circumferential surface.
- an eccentric drive which comprises an eccentric mounted on an eccentric shaft, on which a rolling ring is rotatably mounted. To reduce its moment of inertia, it has a convex circumferential surface.
- the eccentric bears the delivery piston biased in the direction against the eccentric shaft with a plate-like extension provided on its end on this side of the rolling ring.
- the rolling ring rotates back and forth and changes its direction of rotation twice per revolution of the eccentric shaft.
- the Hertz surface pressure between the rolling ring and the delivery piston is considerably reduced in comparison with known high-pressure feed pumps. This is because, due to a plate-like spring element, a load-dependent adaptation to the curvature of the rolling ring takes place; the contact area between the rolling ring and the spring element moved with the delivery piston will increase with The load is also greater, which keeps the Hertz 'surface pressure between the rolling ring and the spring element as well as between this and the delivery piston within acceptable limits, even at very high delivery pressures.
- Fig. 1 shows a cross section through an inventive
- FIG. 2 shows the high-pressure feed pump shown in FIG. 1 in a longitudinal section along the line II-II of FIG. 1;
- FIGS. 1 and 2 show a partial section of part of the high-pressure feed pump shown in FIGS. 1 and 2 with a delivery piston which is concavely shaped on the end face and which rests on a bucket tappet, which on the other hand interacts with a rolling ring of a drive shaft;
- FIG. 4 shows, in the same representation as FIG. 3, a further embodiment of the high-pressure feed pump according to the invention with an adapter head movably mounted on a shaft of the feed piston;
- FIG. 5 shows a section along the line VV of the embodiment shown in FIG. 4; and 6, in the same representation as FIG. 3, a further embodiment in which the delivery piston is flat on the end face and the cup tappet has a concave recess.
- FIGS. 1 and 2 show a cross section and a longitudinal section through a high-pressure feed pump with a housing 10, into which a high-pressure cylinder 12, also called a plunger cylinder, is inserted, in which a delivery piston 14, also called a plunger piston, is located in the direction of the longitudinal axis 14 '. can move back and forth.
- the high-pressure cylinder 12 is clamped with a flange-like extension between the housing 10 and a valve housing 16.
- the valve housing 16 is screwed to the housing 10 by means of screw bolts 17.
- An inlet valve 18 and an outlet valve 20 are provided in the valve housing 16.
- the inlet valve 18 opens and closes a passage 22 to a storage container for the medium to be conveyed and the outlet valve 20 opens a passage 24 to a high-pressure container.
- fuel such as diesel or gasoline
- the high-pressure container is, for example, a common rail.
- An eccentric drive 26 for driving the delivery piston 14 is also arranged in the housing 10 of the high-pressure feed pump.
- This has a drive shaft 28 continuously driven in the direction of the arrow, which is mounted in a generally known manner, freely rotatable about a rotation axis 30 on the housing 10 and a cover 32 closing it, via bearings, not shown.
- the drive shaft 28 carries between the bearing points 34, 34 'an eccentric pin 36 arranged eccentrically with respect to the axis of rotation 30 of the drive shaft 28, the center axis 38 of which runs parallel to the axis of rotation 30.
- On a rolling ring 40 is rotatably mounted with respect to the eccentric pin 36.
- the radially outer circumferential surface 42 of the rolling ring 40 is domed, that is, convex.
- the delivery piston 14 In a circular-cylindrical through bore 44 of the high-pressure cylinder 12, the delivery piston 14 is guided in a sealingly sliding manner. It engages with its end region facing the drive shaft 28 into a cup tappet 46, on the bottom 48 of which it rests with the end face 50 of a mushroom or plate-like extension 52.
- the cup tappet 46 rests on the rolling ring 40 with its base 48.
- the reference numeral 54 designates the point of contact or contact area between the rolling ring 40 and the bottom 48 of the cup pusher 46.
- the delivery piston 14 is moved in the opposite direction by means of a compression spring 56, which is supported on the one hand on the high pressure cylinder 12 and on the other hand on the extension 52 the rolling ring 40 biased.
- the cup tappet 46 is guided with its jacket 58 on the housing 10 in the longitudinal direction and thus the direction of movement of the delivery piston 14.
- the transverse forces acting on the bucket tappet 46 from the drive shaft 28 and the rolling ring 40 are absorbed by the bucket tappet 46 and are not or only transmitted to the delivery piston 14 to a very small extent.
- the delivery piston 14 is moved up and down by the eccentric drive 26 and the compression spring 56.
- the delivery space 60 fills with the delivery medium via the inlet valve 18. If the delivery piston 14 moves upwards during the subsequent delivery stroke, the pressure in the delivery Room 60 with the inlet valve 18 closed until the outlet valve 20 opens and thereby connects the delivery chamber 60 to the high-pressure tank (common rail). The medium is pumped into the high pressure tank.
- FIG 3 shows, with reference to FIGS. 1 and 2, enlarged, the delivery piston 14, the compression spring 56, the cup tappet 46, the rolling ring 40 and part of the drive shaft 28 which can be driven in the direction of the arrow, with the eccentric pin 36.
- the cup tappet 46 is preferably made from hardened roller bearing steel.
- the plate-shaped bottom 48 of the cup tappet 46 which is flat in the unloaded state, has spring properties and, when interacting, serves on the one hand with the cambered circumferential surface 42 of the rolling ring 40 and on the other hand the concave end face 50 of the delivery piston 14 as a spring element 62 can be shaped, for example, as a cap or part of the lateral surface of a torus.
- the end face 50 of the delivery piston 14 has a flat annular surface 66, with which it rests on the bottom 48 in the unloaded or slightly loaded state and which, depending on the shape of the recess 64, can have an annular, oval or other shape ,
- the longitudinal axis 14 ′ of the delivery piston 14 runs centrally to the recess 64 or ring surface 66 and to the cup tappet 46. Further, the axis 14 'runs in a preferred manner in a direction perpendicular to Rotati ⁇ onsachse 30 of the drive shaft 28 extending plane, which extends centrally through the contact surface 54th
- the base 48 which acts as a spring element 62, bends of the cup tappet 46 into the recess 64 in such a way that, as the load increases, on the one hand the contact surface 54 between the base 48 and the rolling ring 40 and on the other hand the surface over which the base 48 bears against the delivery piston 14 are increased.
- the Hertz 'see surface pressure in the relevant parts is kept within limits, which enable a long service life of the high-pressure feed pump.
- the base 48 is preferably dimensioned in such a way that it rests over the entire area in the recess 64 on the delivery piston 14 when there is a certain load.
- the delivery piston 14 shown in FIGS. 4 and 5 has a shaft 68, on the hemispherically shaped end region facing the rolling ring 40, an essentially circular-cylindrical adapter 70 is seated.
- the end face 50 of the adapter 70 which cooperates with the bottom 48 of the cup tappet 46 is of the same design as that of the delivery plunger 14 according to FIG. 3.
- a recess 72 in the adapter 70 for receiving the end region of the shaft 68 on this side is of the same shape and shape has a circumferential groove 74 in a cylindrical casing part adjoining the hemisphere surface.
- the shaft 68 is provided with a circumferential groove 76.
- a straight through bore 78 runs through the adapter 70, the axis of which extends through the circular center line of the toroidal one delimited by the groove 74 and the circumferential groove 76 Affects space.
- a section of a securing element formed from spring steel wire 80 runs through the through hole 78 and runs around it with a further section for attachment to the adapter 70.
- the adapter 70 is mounted on the shaft 68 with limited movement in a spherical manner. This enables only axial forces and no bending forces to act on the delivery piston 14.
- the compression spring 56 is supported on a flange ring 82 which engages around two half flanges 84 and is in turn supported on these.
- the half flanges 84 engage with a bead 86 in a circumferential groove of the shaft 68 and are fastened to the shaft 68 in this way in the axial direction.
- FIG. 6 The embodiment of the high-pressure feed pump according to the invention shown in FIG. 6 is very similar to that according to FIG. 3, the valve body 14 being flat on its end face 50 and the bottom 48 of the cup tappet 46 through a recess 64 'on that of the feed piston 14 facing side is concave.
- the delivery piston 14 rests with an annular surface 66 on the bottom 48 of the cup tappet 46 acting as a spring element 62.
- the mode of operation is the same as described above in connection with the other embodiments.
- the delivery piston 14 can be configured in the same way as shown in FIG. 3 or 4.
- the transition between the annular surface 66 and the recess 64 'itself is shaped in such a way according to the spring characteristic of the spring element 62 that, as the load increases, the surface with which rather the spring element rests on the delivery piston, increases continuously.
- the recess 64 ' can be matched to the coating of the rolling ring 40 in such a way that in the recess 64' at least approximately over the entire area of the spring element 62, this also bears against this over at least approximately the entire width of the rolling ring 40.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a high pressure feed pump which comprises a delivery plunger (14) guided within a high pressure cylinder. Said delivery plunger is driven by a drive shaft (28) by way of an eccentric (36) on which a rounded-off multi-stage ring (40) is rotatably received. A plate-shaped spring element (62) is disposed between the multi-stage ring (40) and the delivery plunger (14) and is, for example, configured by the bottom (48) of a bucket tappet (46). The delivery plunger (14) has a concavely shaped section on its front end (50), thereby allowing the spring element (62) to bend into the recess (64) in accordance with the load on the delivery plunger (14). The contact surface (54) of the spring element (62) with the multi-stage ring (40) and the annular surface (62) with which the spring element (62) rests on the delivery plunger (14) is thereby increased. Surface pressure can thus be restricted to an acceptable degree even at very high working pressures.
Description
HochdruσkförderpumpeHochdruσkförderpumpe
Die vorliegende Erfindung betrifft eine Hochdruckförderpumpe mit den Merkmalen des Oberbegriffs des Patentanspruchs 1.The present invention relates to a high-pressure feed pump with the features of the preamble of patent claim 1.
Solche nach dem Hubkolbenprinzip arbeitenden Hochdruckförderpumpen werden insbesondere für die Erzeugung des Einspritzdruckes in Kraftstoff-Einspritzsystemen - z.B. Common-Rail-Systemen - für Verbrennungsmotoren eingesetzt. Eine gattungsgemässe Hochdruckförderpumpe ist in der EP-A- 1 058 001 offenbart.Such high-pressure feed pumps operating according to the reciprocating piston principle are used in particular for generating the injection pressure in fuel injection systems - e.g. Common rail systems - used for internal combustion engines. A generic high pressure feed pump is disclosed in EP-A-1 058 001.
Hochdruckförderpumpen der gattungsgemässen Art weisen einen Hochdruckzylinder bzw. Plungerzylinder und einen in diesem hin- und herbewegbaren zylindrischen Förderkolben bzw. Plungerkolben auf, wobei das Volumen des Förderraums innerhalb des Hochdruckzylinders durch die Hubbewegung des Plungerkolbens verändert wird. Bei einem Füllhub des Plungerkolbens ist der Förderraum über ein Füllventil mit einem Vorratsraum für ein Fördermedium verbindbar, um den im Hubvolumen sich vergrössernden Förderraum mit dem För- dermedium zu füllen. Während eines folgenden Förderhubs bei geschlossenem Füllventil steigt der Druck im Förderraum bis ein Druckventil öffnet und dadurch den Förderraum mit einem Hochdruckraum, beispielsweise dem Cornmon-Rail verbindet.High-pressure feed pumps of the generic type have a high-pressure cylinder or plunger cylinder and a cylindrical feed piston or plunger piston which can be reciprocated therein, the volume of the delivery space within the high-pressure cylinder being changed by the stroke movement of the plunger piston. During a filling stroke of the plunger, the delivery space can be connected via a filling valve to a storage space for a delivery medium, in order to fill the delivery space, which increases in displacement, with the delivery medium. During a subsequent delivery stroke with the filling valve closed, the pressure in the delivery chamber increases until a pressure valve opens and thereby connects the delivery chamber to a high-pressure room, for example the Cornmon Rail.
Der Antrieb des Plungerkolbens erfolgt durch einen Exzentertrieb, der einen auf einer Exzenterwelle gelagerten Exzenter umfasst, auf dem ein Abwälzring drehbar gelagert ist. Dieser weist zur Reduktion seines Trägheitsmoments eine bombierte Umfangsflache auf. Während der Drehung des
Exzenters liegt der in Richtung gegen die Exzenterwelle vorgespannte Förderkolben mit einer an seinem diesseitigen Ende vorgesehenen tellerartigen Erweiterung an dem Abwälzring an. Im Betrieb dreht sich der Abwälzring hierbei hin und her und wechselt pro Umdrehung der Exzenterwelle zweimal seine Drehrichtung. Die Ausgestaltung und Funktionsweise der Hochdruckpumpe ist in der EP-A-1 058 001 beschrieben, deren Offenbarung durch diese Bezugnahme ausdrücklich zum Inhalt der vorliegenden Anmeldung gemacht wird.The plunger is driven by an eccentric drive, which comprises an eccentric mounted on an eccentric shaft, on which a rolling ring is rotatably mounted. To reduce its moment of inertia, it has a convex circumferential surface. During the rotation of the The eccentric bears the delivery piston biased in the direction against the eccentric shaft with a plate-like extension provided on its end on this side of the rolling ring. During operation, the rolling ring rotates back and forth and changes its direction of rotation twice per revolution of the eccentric shaft. The design and mode of operation of the high-pressure pump is described in EP-A-1 058 001, the disclosure of which is expressly made the content of the present application by this reference.
Bei Hochdruckförderpumpen der genannten Art, insbesondere wenn sie für Dieseleinspritzsysteme verwendet werden, sind die Materialbelastungen bei den Berührungspartien zwischen dem Abwälzring und dem Förderkolben hoch. Dadurch sind entweder die mit solchen Pumpen erzielbaren Förderdrücke beschränkt, oder die betreffenden Elemente gross zu dimensionieren.In the case of high-pressure feed pumps of the type mentioned, in particular if they are used for diesel injection systems, the material loads in the areas of contact between the rolling ring and the delivery piston are high. As a result, either the delivery pressures achievable with such pumps are limited, or the elements in question are dimensioned large.
Es ist deshalb eine Aufgabe der vorliegenden Erfindung, eine Hochdruckförderpumpe zu schaffen, welche die genann- ten Probleme überwindet.It is therefore an object of the present invention to provide a high-pressure feed pump which overcomes the problems mentioned.
Diese Aufgabe wird mit einer gattungsgemässen Hochdruckförderpumpe gelöst, die die Merkmale im Kennzeichen des Anspruchs 1 aufweist.This object is achieved with a generic high-pressure feed pump, which has the features in the characterizing part of claim 1.
Bei einer erfindungsgemässen Hochdruckförderpumpe ist die Hertz 'sehe Flächenpressung zwischen Abwälzring und Förderkolben (Plunger) im Vergleich mit bekannten Hochdruckförderpumpen erheblich reduziert. Dies, weil infolge eines plattenartigen Federelements eine belastungsabhängige Anpassung an die Bombierung des Abwälzrings stattfindet; die Kontaktfläche zwischen dem Abwälzring und dem mit dem Förderkolben bewegten Federelement wird bei grösser wer-
dender Belastung auch grösser, was die Hertz 'sehe Flächenpressung sowohl zwischen dem Abwälzring und dem Federelement als auch zwischen diesem und dem Förderkolben, selbst bei sehr hohen Förderdrücken, in annehmbaren Gren- zen hält .In a high-pressure feed pump according to the invention, the Hertz surface pressure between the rolling ring and the delivery piston (plunger) is considerably reduced in comparison with known high-pressure feed pumps. This is because, due to a plate-like spring element, a load-dependent adaptation to the curvature of the rolling ring takes place; the contact area between the rolling ring and the spring element moved with the delivery piston will increase with The load is also greater, which keeps the Hertz 'surface pressure between the rolling ring and the spring element as well as between this and the delivery piston within acceptable limits, even at very high delivery pressures.
Bevorzugte Ausbildungsformen der erfindungsgemässen Hochdruckförderpumpe sind in den abhängigen Patentansprüchen angegeben.Preferred embodiments of the high-pressure feed pump according to the invention are specified in the dependent claims.
Die Erfindung wird anhand in der Zeichnung dargestellten Ausführungsformen näher erläutert. Es zeigen rein schematisch:The invention is explained in more detail with reference to the embodiments shown in the drawing. It shows purely schematically:
Fig. 1 einen Querschnitt durch eine erfindungsgemässeFig. 1 shows a cross section through an inventive
Hochdruckförderpumpe entlang der Schnittlinie I- I der Fig. 2;High-pressure feed pump along the section line I-I of Fig. 2;
Fig. 2 die in der Fig. 1 gezeigte Hochdruckförderpumpe in einem Längsschnitt entlang der Linie II-II der Fig. 1;FIG. 2 shows the high-pressure feed pump shown in FIG. 1 in a longitudinal section along the line II-II of FIG. 1;
Fig. 3 teilweise geschnitten einen Teil der in den Fig. 1 und 2 gezeigten Hochdruckförderpumpe mit einem stirnseitig konkav geformten Förderkolben, der an einem Tassenstössel -anliegt, welcher andererseits mit einem Abw lzring einer Antriebswelle zusammenwirkt;3 shows a partial section of part of the high-pressure feed pump shown in FIGS. 1 and 2 with a delivery piston which is concavely shaped on the end face and which rests on a bucket tappet, which on the other hand interacts with a rolling ring of a drive shaft;
Fig. 4 in gleicher Darstellung wie Fig. 3 eine weitere Ausbildungsform der erfindungsgemässen Hochdruckförderpumpe mit einem an einem Schaft des Förderkolbens beweglich gelagerten Adapterkopf;4 shows, in the same representation as FIG. 3, a further embodiment of the high-pressure feed pump according to the invention with an adapter head movably mounted on a shaft of the feed piston;
Fig. 5 einen Schnitt entlang der Linie V-V der in der Fig. 4 gezeigten Ausbildungsform; und
Fig. 6 in gleicher Darstellung wie Fig. 3 eine weitere Ausbildungsform, bei welcher der Förderkolben stirnseitig eben ausgebildet ist und der Tassen- stössel eine konkave Ausnehmung aufweist.5 shows a section along the line VV of the embodiment shown in FIG. 4; and 6, in the same representation as FIG. 3, a further embodiment in which the delivery piston is flat on the end face and the cup tappet has a concave recess.
Die Fig. 1 und 2 zeigen einen Querschnitt und einen Längsschnitt durch eine Hochdruckförderpumpe mit einem Gehäuse 10, in das ein Hochdruckzylinder 12, auch Plungerzylinder genannt, eingelassen ist, in dem sich ein Förderkolben 14, auch Plungerkolben genannt, in Richtung der Längsachse 14' hin und herbewegen kann. Der Hochdruckzylinder 12 ist mit einer flanschartigen Erweiterung zwischen dem Gehäuse 10 und einem Ventilgehäuse 16 eingespannt. Das Ventilgehäuse 16 ist mittels Schraubenbolzen 17 mit dem Gehäuse 10 verschraubt. Im Ventilgehäuse 16 ist ein Einlassventil 18 so- wie ein Auslassventil 20 vorgesehen. Das Einlassventil 18 öffnet und schliesst einen Durchgang 22 zu einem Vorratsbehälter für das zu fördernde Medium und das Auslassventil 20 einen Durchgang 24 zu einem Hochdruckbehälter. Im Falle eines Hochdruckeinspritzsystems für Verbrennungsmotoren befindet sich im Vorratsbehälter Brennstoff, wie Diesel oder Benzin, und handelt es sich beim Hochdruckbehälter beispielsweise um ein Common-Rail .1 and 2 show a cross section and a longitudinal section through a high-pressure feed pump with a housing 10, into which a high-pressure cylinder 12, also called a plunger cylinder, is inserted, in which a delivery piston 14, also called a plunger piston, is located in the direction of the longitudinal axis 14 '. can move back and forth. The high-pressure cylinder 12 is clamped with a flange-like extension between the housing 10 and a valve housing 16. The valve housing 16 is screwed to the housing 10 by means of screw bolts 17. An inlet valve 18 and an outlet valve 20 are provided in the valve housing 16. The inlet valve 18 opens and closes a passage 22 to a storage container for the medium to be conveyed and the outlet valve 20 opens a passage 24 to a high-pressure container. In the case of a high-pressure injection system for internal combustion engines, fuel, such as diesel or gasoline, is located in the storage container, and the high-pressure container is, for example, a common rail.
In dem Gehäuse 10 der Hochdruckförderpumpe ist weiter ein Exzentertrieb 26 für den Antrieb -des Förderkolbens 14 an- geordnet. Dieser weist eine in Richtung des Pfeiles kontinuierlich angetriebene Antriebswelle 28 auf, die in allgemein bekannter Art und Weise über nicht gezeigte Lager frei um eine Rotationsachse 30 drehbar am Gehäuse 10 und einem dieses verschliessenden Deckel 32 gelagert ist. Die Antriebswelle 28 trägt zwischen den Lagerstellen 34, 34' einen bezüglich der Rotationsachse 30 der Antriebswelle 28 exzentrisch angeordneten Exzenterzapfen 36, dessen Zentrumsachse 38 parallel zur Rotationsachse 30 verläuft. Auf
dem Exzenterzapfen 36 ist ein Abwälzring 40 drehbar gegenüber dem Exzenterzapfen 36 gelagert. Die radial aussen liegende Umfangsflache 42 des Abwälzrings 40 ist bombiert, d.h. konvex ausgebildet.An eccentric drive 26 for driving the delivery piston 14 is also arranged in the housing 10 of the high-pressure feed pump. This has a drive shaft 28 continuously driven in the direction of the arrow, which is mounted in a generally known manner, freely rotatable about a rotation axis 30 on the housing 10 and a cover 32 closing it, via bearings, not shown. The drive shaft 28 carries between the bearing points 34, 34 'an eccentric pin 36 arranged eccentrically with respect to the axis of rotation 30 of the drive shaft 28, the center axis 38 of which runs parallel to the axis of rotation 30. On a rolling ring 40 is rotatably mounted with respect to the eccentric pin 36. The radially outer circumferential surface 42 of the rolling ring 40 is domed, that is, convex.
In einer kreiszylinderförmigen Durchgangsbohrung 44 des Hochdruckzylinders 12 ist der Förderkolben 14 dichtend gleitend verschiebbar geführt. Er greift mit seinem der Antriebswelle 28 zugewandten Endbereich in einen Tassen- stössel 46 ein, an dessen Boden 48 er mit der Stirnseite 50 einer pilz- oder tellerartigen Erweiterung 52 anliegt. Der Tassenstössel 46 sitzt mit seinem Boden 48 andererseits auf dem Abwälzring 40 auf. Dabei bezeichnet das Bezugszeichen 54 die Berührungsstelle bzw. Kontaktfläche zwischen dem Abwälzring 40 und dem Boden 48 des Tassenstö- ssels 46. Mittels einer Druckfeder 56, die sich einerseits am Hochdruckzylinder 12 und andererseits an der Erweiterung 52 abstützt, wird der Förderkolben 14 in Richtung gegen den Abwälzring 40 vorgespannt.In a circular-cylindrical through bore 44 of the high-pressure cylinder 12, the delivery piston 14 is guided in a sealingly sliding manner. It engages with its end region facing the drive shaft 28 into a cup tappet 46, on the bottom 48 of which it rests with the end face 50 of a mushroom or plate-like extension 52. The cup tappet 46, on the other hand, rests on the rolling ring 40 with its base 48. The reference numeral 54 designates the point of contact or contact area between the rolling ring 40 and the bottom 48 of the cup pusher 46. The delivery piston 14 is moved in the opposite direction by means of a compression spring 56, which is supported on the one hand on the high pressure cylinder 12 and on the other hand on the extension 52 the rolling ring 40 biased.
Der Tassenstössel 46 ist mit seinem Mantel 58 am Gehäuse 10 in Längsrichtung und somit Bewegungsrichtung des Förderkolbens 14 gleitend geführt. Die von der Antriebswelle 28 und dem Abwalzring 40 auf den Tassenstössel 46 wirkenden Querkräfte werden von diesem aufgenommen und nicht bzw. nur in sehr geringem Masse an den Förderkolben 14 übertragen.The cup tappet 46 is guided with its jacket 58 on the housing 10 in the longitudinal direction and thus the direction of movement of the delivery piston 14. The transverse forces acting on the bucket tappet 46 from the drive shaft 28 and the rolling ring 40 are absorbed by the bucket tappet 46 and are not or only transmitted to the delivery piston 14 to a very small extent.
Zur Kompression und Förderung des Fördermediums wird der Förderkolben 14 durch den Exzentertrieb 26 und der Druckfeder 56 auf und ab bewegt. Wenn sich der Förderkolben 14 bei einem Füllhub nach unten bewegt, füllt sich der För- derrau 60 über das Einlassventil 18 mit dem Fördermedium. Wenn sich der Förderkolben 14 bei dem folgenden Förderhub in Richtung nach oben bewegt, steigt der Druck im Förder-
räum 60 bei geschlossenem Einlassventil 18, bis das Aus- lassventil 20 öffnet und dadurch den Förderraum 60 mit dem Hochdruckbehälter (Common-Rail) verbindet. Dabei wird das Fördermedium in den Hochdruckbehälter gefördert.To compress and convey the medium, the delivery piston 14 is moved up and down by the eccentric drive 26 and the compression spring 56. When the delivery piston 14 moves downwards during a filling stroke, the delivery space 60 fills with the delivery medium via the inlet valve 18. If the delivery piston 14 moves upwards during the subsequent delivery stroke, the pressure in the delivery Room 60 with the inlet valve 18 closed until the outlet valve 20 opens and thereby connects the delivery chamber 60 to the high-pressure tank (common rail). The medium is pumped into the high pressure tank.
Fig. 3 zeigt bezüglich den Fig. 1 und 2 vergrössert, den Förderkolben 14, die Druckfeder 56, den Tassenstössel 46, den Abwälzring 40 und einen Teil der in Pfeilrichtung antreibbaren Antriebswelle 28 mit dem Exzenterzapfen 36.3 shows, with reference to FIGS. 1 and 2, enlarged, the delivery piston 14, the compression spring 56, the cup tappet 46, the rolling ring 40 and part of the drive shaft 28 which can be driven in the direction of the arrow, with the eccentric pin 36.
Der Tassenstössel 46 ist in bevorzugter Weise aus gehärte- tem Wälzlagerstahl gefertigt. Der im unbelasteten Zustand ebene plattenförmige Boden 48 des Tassenstössels 46 weist Federeigenschaften auf und dient beim Zusammenwirken einerseits mit der bombierten Umfangsfläche 42 des Abwälzrings 40 und andererseits der konkav ausgebildeten Stirn- seite 50 des Förderkolbens 14 als Federelement 62. Die stirnseitige Vertiefung 64 im Förderkolben 14 kann beispielsweise als Kalotte oder Teil der Mantelfläche eines Torus geformt sein. Um die Vertiefung 64 herum weist die Stirnseite 50 des Förderkolbens 14 eine ebene Ringfläche 66 auf, mit der er im unbelasteten oder leicht belasteten Zustand am Boden 48 anliegt und welche in Abhängigkeit von der Form der Vertiefung 64 eine kreisringförmige, ovale oder andere Form aufweisen kann.The cup tappet 46 is preferably made from hardened roller bearing steel. The plate-shaped bottom 48 of the cup tappet 46, which is flat in the unloaded state, has spring properties and, when interacting, serves on the one hand with the cambered circumferential surface 42 of the rolling ring 40 and on the other hand the concave end face 50 of the delivery piston 14 as a spring element 62 can be shaped, for example, as a cap or part of the lateral surface of a torus. Around the recess 64, the end face 50 of the delivery piston 14 has a flat annular surface 66, with which it rests on the bottom 48 in the unloaded or slightly loaded state and which, depending on the shape of the recess 64, can have an annular, oval or other shape ,
Es ist anzustreben, dass die Längsachse 14' des Förderkol- bens 14 zentrisch zur Vertiefung 64 bzw. Ringfläche 66 und zum Tassenstössel 46 verläuft. Weiter verläuft die Achse 14' in bevorzugter Weise in einer rechtwinklig zur Rotati¬ onsachse 30 der Antriebswelle 28 verlaufenden Ebene, welche mittig durch die Kontaktfläche 54 verläuft.The aim should be that the longitudinal axis 14 ′ of the delivery piston 14 runs centrally to the recess 64 or ring surface 66 and to the cup tappet 46. Further, the axis 14 'runs in a preferred manner in a direction perpendicular to Rotati ¬ onsachse 30 of the drive shaft 28 extending plane, which extends centrally through the contact surface 54th
In Abhängigkeit von der Belastung des Förderkolbens 14 verbiegt sich der als Federelement 62 wirkende Boden 48
des Tassenstössels 46 in die Vertiefung 64 hinein derart, dass bei höher werdender Belastung einerseits die Kontaktfläche 54 zwischen dem Boden 48 und dem Abwälzring 40 und andererseits die Fläche über welcher der Boden 48 am För- derkolben 14 anliegt, vergrössert werden. Dadurch wird die Hertz 'sehe Flächenpressung in den betreffenden Teilen in Grenzen gehalten, die eine lange Lebensdauer der Hochdruckförderpumpe ermöglichen. In bevorzuger Weise ist der Boden 48 derart dimensioniert, dass er bei einer bestimm- ten Belastung ganzflächig in der Vertiefung 64 am Förderkolben 14 anliegt.Depending on the load on the delivery piston 14, the base 48, which acts as a spring element 62, bends of the cup tappet 46 into the recess 64 in such a way that, as the load increases, on the one hand the contact surface 54 between the base 48 and the rolling ring 40 and on the other hand the surface over which the base 48 bears against the delivery piston 14 are increased. As a result, the Hertz 'see surface pressure in the relevant parts is kept within limits, which enable a long service life of the high-pressure feed pump. The base 48 is preferably dimensioned in such a way that it rests over the entire area in the recess 64 on the delivery piston 14 when there is a certain load.
Bei der in den Fig. 4 und 5 gezeigten Ausbildungsform ist einzig der Förderkolben 14 im Vergleich mit der in den Fig. 1 bis 3 gezeigten Ausbildungsform unterschiedlich. Die Funktionsweise ist gleich wie weiter oben beschrieben. Es wird deshalb einzig auf die Ausbildung des Förderkolbens 14 eingegangen.In the embodiment shown in FIGS. 4 and 5, only the delivery piston 14 is different in comparison with the embodiment shown in FIGS. 1 to 3. The mode of operation is the same as described above. Therefore, only the formation of the delivery piston 14 will be discussed.
Der in den Fig. 4 und 5 gezeigte Förderkolben 14 weist einen Schaft 68 auf, auf dessen halbkugelförmig geformten, dem Abwälzring 40 zugewandten Endbereich ein im wesentlichen kreiszylinderförmiger Adapter 70 sitzt. Die mit dem Boden 48 des Tassenstössels 46 zusammenwirkende Stirnseite 50 des Adapters 70 ist gleich ausgebildet wie jene beim Förderkolben 14 gemäss Fig. 3. Eine Ausnehmung 72 des Ad- apters 70 für die Aufnahme des diesseitigen Endbereichs des Schaftes 68 ist zu diesem gegengleich geformt und weist in einem an die Halbkugeloberfläche anschliessenden zylindrischen Mantelteil eine umlaufende Nut 74 auf. Entsprechend ist der Schaft 68 mit einer Umfangsnut 76 verse- hen. Wie dies insbesondere aus der Fig. 5 hervorgeht, verläuft eine geradlinige Durchgangsbohrung 78 durch den Adapter 70, deren Achse die kreisförmige Mittellinie des von der Nut 74 und der Umfangsnut 76 begrenzten, torusförmigen
Raums tangiert. Durch die Durchgangsbohrung 78 hindurch verläuft ein Abschnitt eines aus Federstahldraht 80 gebildeten Sicherungselements, das mit einem weiteren Abschnitt zur Befestigung am Adapter 70 um diesen herum verläuft. Der Adapter 70 ist auf diese Art und Weise am Schaft 68 beschränkt beweglich kugelartig gelagert. Dies ermöglicht, dass ausschliesslich Axialkräfte und keine Biegekräfte auf den Förderkolben 14 wirken können.The delivery piston 14 shown in FIGS. 4 and 5 has a shaft 68, on the hemispherically shaped end region facing the rolling ring 40, an essentially circular-cylindrical adapter 70 is seated. The end face 50 of the adapter 70 which cooperates with the bottom 48 of the cup tappet 46 is of the same design as that of the delivery plunger 14 according to FIG. 3. A recess 72 in the adapter 70 for receiving the end region of the shaft 68 on this side is of the same shape and shape has a circumferential groove 74 in a cylindrical casing part adjoining the hemisphere surface. Correspondingly, the shaft 68 is provided with a circumferential groove 76. As can be seen in particular in FIG. 5, a straight through bore 78 runs through the adapter 70, the axis of which extends through the circular center line of the toroidal one delimited by the groove 74 and the circumferential groove 76 Affects space. A section of a securing element formed from spring steel wire 80 runs through the through hole 78 and runs around it with a further section for attachment to the adapter 70. In this way, the adapter 70 is mounted on the shaft 68 with limited movement in a spherical manner. This enables only axial forces and no bending forces to act on the delivery piston 14.
Die Druckfeder 56 stützt sich an einem Flanschring 82 ab, der zwei Halbflansche 84 umgreift und sich seinerseits an diesen abstützt. Die Halbflansche 84 greifen mit einem Wulst 86 in eine Umlaufnut des Schaftes 68 ein und sind derart an diesem in axialer Richtung befestigt.The compression spring 56 is supported on a flange ring 82 which engages around two half flanges 84 and is in turn supported on these. The half flanges 84 engage with a bead 86 in a circumferential groove of the shaft 68 and are fastened to the shaft 68 in this way in the axial direction.
Die in der Fig. 6 gezeigte Ausbildungsform der erfindungs- gemässen Hochdruckförderpumpe ist jener gemäss Fig. 3 sehr ähnlich, wobei der Ventilkörper 14 an seiner Stirnseite 50 eben ausgebildet ist und der Boden 48 des Tassenstössels 46 durch eine Ausnehmung 64' auf der dem Förderkolben 14 zugewandten Seite konkav geformt ist. Auch hier liegt im unbelasteten und leicht belasteten Zustand der Förderkolben 14 mit einer Ringfläche 66 am als Federelement 62 wirkenden Boden 48 des Tassenstössels 46 an. Die Wirkungsweise ist dieselbe wie weiter oben im Zusammenhang mit den anderen Ausführungsformen beschrieben.The embodiment of the high-pressure feed pump according to the invention shown in FIG. 6 is very similar to that according to FIG. 3, the valve body 14 being flat on its end face 50 and the bottom 48 of the cup tappet 46 through a recess 64 'on that of the feed piston 14 facing side is concave. Here, too, in the unloaded and slightly loaded state, the delivery piston 14 rests with an annular surface 66 on the bottom 48 of the cup tappet 46 acting as a spring element 62. The mode of operation is the same as described above in connection with the other embodiments.
Bei der in der Fig. 6 gezeigten Ausbildungsform kann der Förderkolben 14 gleich ausgebildet sein wie in der Fig. 3 oder 4 gezeigt.In the embodiment shown in FIG. 6, the delivery piston 14 can be configured in the same way as shown in FIG. 3 or 4.
In bevorzugter Weise ist der Übergang zwischen der Ringfläche 66 und der Vertiefung 64' selber derart entspre- chend der Federcharakteristik des Federelements 62 geformt, dass bei steigender Belastung die Fläche, mit wel-
eher das Federelement am Förderkolben anliegt, sich kontinuierlich vergrössert.Preferably, the transition between the annular surface 66 and the recess 64 'itself is shaped in such a way according to the spring characteristic of the spring element 62 that, as the load increases, the surface with which rather the spring element rests on the delivery piston, increases continuously.
Die Vertiefung 64 ' kann derart auf die Bo bierung des Abwälzrings 40 abgestimmt sein, dass bei in der Vertiefung 64 ' wenigstens annähernd ganzflächig anliegendem Federelement 62, dieses auch über wenigstens annähernd die ganze Breite des Abwälzrings 40 an diesem anliegt.
The recess 64 'can be matched to the coating of the rolling ring 40 in such a way that in the recess 64' at least approximately over the entire area of the spring element 62, this also bears against this over at least approximately the entire width of the rolling ring 40.
Claims
1. Hoehdruckförderpumpe mit einem Hochdruckzylinder (12), einem darin geführten Förderkolben (14), und einem auf einer Antriebswelle (28) angeordneten Ex- zenter (36) , auf dem ein eine bombierte Umfangsflache (42) aufweisender Abwälzring (40) für den Antrieb des Förderkolbens (14) drehbar gelagert ist, dadurch gekennzeichnet, dass zwischen dem Förderkolben (14) und dem Abwälzring (40) ein plattenartiges Federelement (62) angeordnet ist, das einerseits über eine Kontaktfläche (54) an der Umfangsflache (42) des Abwälzrings (40) und andererseits über eine Ringfläche (66) an der Stirnseite (50) des Förderkolbens (14) anliegt .1. High-pressure delivery pump with a high-pressure cylinder (12), a delivery piston (14) guided therein, and an eccentric (36) arranged on a drive shaft (28), on which a rolling ring (40) having a cambered peripheral surface (42) for the Drive of the feed piston (14) is rotatably mounted, characterized in that a plate-like spring element (62) is arranged between the feed piston (14) and the rolling ring (40), which on the one hand has a contact surface (54) on the peripheral surface (42) of the Rolling ring (40) and on the other hand abuts an annular surface (66) on the end face (50) of the delivery piston (14).
2. Hoehdruckförderpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Förderkolben (14) an seiner Stirnseite (50) konkav ausgebildet ist.2. High-pressure feed pump according to claim 1, characterized in that the delivery piston (14) is concave on its end face (50).
3. Hoehdruckförderpumpe nach Anspruch 1 oder 2, άadurch gekennzeichnet, dass das Federelement (62) auf seiner dem Förderkolben (14) zugewandten Seite konkav ausgebildet ist.3. High pressure feed pump according to claim 1 or 2, characterized in that the spring element (62) is concave on its side facing the feed piston (14).
4. Hoehdruckförderpumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Förderkolben (14) in seinem dem Federelement (62) zugewandten Endbe- reich eine pilzförmige oder tellerförmige Erweiterung (52) aufweist.4. High-pressure feed pump according to one of claims 1 to 3, characterized in that the feed piston (14) has a mushroom-shaped or plate-shaped extension (52) in its end region facing the spring element (62).
5. Hoehdruckförderpumpe nach Anspruch 3, dadurch gekennzeichnet, dass die Erweiterung (52) von einem, vor- zugsweise an einem Schaft (68) des Förderkolbens (14) beweglich gelagerten Adapter (70) gebildet ist.5. High-pressure feed pump according to claim 3, characterized in that the extension (52) by one, pre- is preferably formed on a shaft (68) of the delivery piston (14) movably mounted adapter (70).
6. Hoehdruckförderpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Federelement (62) durch den Boden (48) eines mit seiner zylinderischen Mantelfläche (58) in Bewegungsrichtung des Förderkolbens (14) geführten Tassenstössels (46) gebildet ist .6. High-pressure feed pump according to one of claims 1 to 5, characterized in that the spring element (62) through the bottom (48) of a with its cylindrical outer surface (58) in the direction of movement of the delivery piston (14) guided tappet (46) is formed.
7. Hoehdruckförderpumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Federelement (62)7. High pressure feed pump according to one of claims 1 to 6, characterized in that the spring element (62)
- bei maximaler Druckbelastung - mit dem der Kontaktfläche (54) gegenüberliegenden Bereich flächig an der Stirnseite (50) des Förderkolbens (14) anliegt. - At maximum pressure load - with the area opposite the contact surface (54) lies flat against the end face (50) of the delivery piston (14).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH14602001 | 2001-08-08 | ||
CH146001 | 2001-08-08 | ||
PCT/CH2002/000374 WO2003014569A1 (en) | 2001-08-08 | 2002-07-09 | High pressure feed pump |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1415092A1 true EP1415092A1 (en) | 2004-05-06 |
Family
ID=4565497
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02742623A Withdrawn EP1415092A1 (en) | 2001-08-08 | 2002-07-09 | High pressure feed pump |
Country Status (6)
Country | Link |
---|---|
US (1) | US20040156733A1 (en) |
EP (1) | EP1415092A1 (en) |
JP (1) | JP2004537005A (en) |
KR (1) | KR20040035730A (en) |
CN (1) | CN1539060A (en) |
WO (1) | WO2003014569A1 (en) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006514195A (en) * | 2003-02-11 | 2006-04-27 | ガンサー−ハイドロマグ アーゲー | High pressure pump |
DE10344459B4 (en) * | 2003-09-25 | 2012-06-14 | Robert Bosch Gmbh | Piston pump, in particular high-pressure piston pump |
ATE439517T1 (en) * | 2005-03-24 | 2009-08-15 | Delphi Tech Inc | FUEL PUMP |
JP4467469B2 (en) * | 2005-06-08 | 2010-05-26 | ボッシュ株式会社 | Fuel supply pump and tappet structure |
DE102005056683B3 (en) * | 2005-11-28 | 2007-05-03 | Industriehansa Consulting & Engineering Gmbh | Displacement unit for high pressure pump, has power transmission unit with curved regions standing in intervention with curved region of side of rod and curved region of tappet base, respectively, where regions are curved concave or convex |
DE102006043187B3 (en) * | 2006-09-14 | 2008-04-03 | Siemens Ag | Fluid pump, in particular high-pressure fuel pump for injection systems of internal combustion engines |
DE102006045897B4 (en) * | 2006-09-28 | 2008-09-11 | Continental Automotive Gmbh | Radial piston pump for high-pressure fuel supply |
JP4407754B2 (en) * | 2008-01-29 | 2010-02-03 | 株式会社デンソー | pump |
DE102008008438A1 (en) * | 2008-02-11 | 2009-08-13 | Continental Automotive Gmbh | High-pressure pump has tappet, which serves for indirect support of piston with longitudinal axis at drive shaft over roller, which is pivotally coupled with tappet |
DE102008000824A1 (en) * | 2008-03-26 | 2009-10-01 | Robert Bosch Gmbh | Pump, in particular high-pressure fuel pump |
DE102009027272A1 (en) * | 2009-06-29 | 2010-12-30 | Robert Bosch Gmbh | high pressure pump |
EP2405139B1 (en) * | 2010-07-09 | 2017-08-16 | Grundfos Management A/S | Metering pump aggregate |
DE102010042484A1 (en) * | 2010-10-15 | 2012-04-19 | Robert Bosch Gmbh | High pressure pump for a fuel injection device |
CN103047100A (en) * | 2013-01-10 | 2013-04-17 | 无锡开普机械有限公司 | Rotor pump with cam shaft sleeve |
CN105862979A (en) * | 2016-05-12 | 2016-08-17 | 张萍 | Efficient intelligentized air water generator |
NL2019045B1 (en) * | 2017-06-09 | 2018-12-17 | Delft Offshore Turbine B V | Wind turbine generator with hydraulic pump |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2126985A (en) * | 1935-02-01 | 1938-08-16 | Timken Roller Bearing Co | Fuel injection pump |
US2079821A (en) * | 1935-03-21 | 1937-05-11 | Timken Roller Bearing Co | Fuel injection pump |
DE1183515B (en) * | 1963-05-09 | 1964-12-17 | Hanns Dieter Paschke Dipl Ing | Rotary piston machine |
US3272088A (en) * | 1964-06-17 | 1966-09-13 | Westinghouse Air Brake Co | Conversion brake cylinder |
DE3505176C1 (en) * | 1985-02-15 | 1986-04-24 | Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co Kg, 4300 Essen | Radial-piston pump for hydraulic media |
DE19705205A1 (en) * | 1997-02-12 | 1998-08-13 | Bosch Gmbh Robert | Piston pump, esp. high pressure fuel injection pump for IC engine |
DE19814506A1 (en) * | 1998-04-01 | 1999-10-14 | Bosch Gmbh Robert | Radial piston pump for high-pressure fuel supply |
DE50009529D1 (en) * | 1999-05-31 | 2005-03-24 | Crt Common Rail Tech Ag | High pressure feed pump |
DE19956092A1 (en) * | 1999-11-22 | 2000-10-26 | Siemens Ag | Piston pump, especially high-pressure radial piston pump |
-
2002
- 2002-07-09 JP JP2003519265A patent/JP2004537005A/en active Pending
- 2002-07-09 CN CNA028155068A patent/CN1539060A/en active Pending
- 2002-07-09 KR KR10-2004-7002022A patent/KR20040035730A/en not_active Application Discontinuation
- 2002-07-09 WO PCT/CH2002/000374 patent/WO2003014569A1/en not_active Application Discontinuation
- 2002-07-09 EP EP02742623A patent/EP1415092A1/en not_active Withdrawn
-
2004
- 2004-02-04 US US10/771,574 patent/US20040156733A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO03014569A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2003014569A1 (en) | 2003-02-20 |
KR20040035730A (en) | 2004-04-29 |
US20040156733A1 (en) | 2004-08-12 |
CN1539060A (en) | 2004-10-20 |
JP2004537005A (en) | 2004-12-09 |
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