EP2872778B1 - High-pressure pump - Google Patents
High-pressure pump Download PDFInfo
- Publication number
- EP2872778B1 EP2872778B1 EP13736844.5A EP13736844A EP2872778B1 EP 2872778 B1 EP2872778 B1 EP 2872778B1 EP 13736844 A EP13736844 A EP 13736844A EP 2872778 B1 EP2872778 B1 EP 2872778B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- pump
- housing
- drive
- pressure pump
- 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.)
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Links
- 239000012530 fluid Substances 0.000 claims description 11
- 239000000314 lubricant Substances 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 238000005086 pumping Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
- F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
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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
-
- 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
- F04B1/0448—Sealing means, e.g. for shafts or housings
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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
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/006—Crankshafts
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
Definitions
- the invention relates to a high-pressure pump.
- such a high-pressure pump is used as a pump for delivering fluid for a storage injection system for internal combustion engines of motor vehicles.
- Storage injection systems for internal combustion engines of motor vehicles should be able to provide the necessary volume flow and the required fluid pressure.
- the high-pressure pump is subject to strong loads in memory injection systems for motor vehicles, in particular mechanical stresses. In particular, large forces must be able to be absorbed by such high-pressure pumps. This places high demands on the material as well as on the construction of the high pressure pump.
- DE 22 63 837 A1 discloses a high-pressure pump for delivering a fluid having a pump housing, a rotatably mounted drive shaft and a fixedly coupled to the drive shaft drive element, which is designed to drive the drive shaft.
- a housing recess of the pump housing is provided, in which the drive shaft is mounted.
- the high-pressure pump on a bearing element which is fixedly coupled to the pump housing, and having a recess for a shaft bearing.
- the recess of the bearing element is arranged relative to the housing recess such that the Drive element viewed in the axial direction between the recess of the bearing element and the housing recess is arranged.
- DE 199 20 168 relates to a radial piston pump, with radially aligned to a rotational axis of an eccentric shaft cylinders in the cylinders radially movable against the force of a spring element arranged piston, the pistons are pressed by a rotational movement of an eccentric radially outward and by the spring element radially inwardly, the piston at least have an inlet opening, which comes in radially inner position of the piston with an inlet chamber of a pumping medium in communication, and the pumping medium is pressed in radial outward movement of the piston in a pressure range, and the eccentric shaft is mounted in both sides of the eccentric plain bearings and driven by a traction means is. It is envisaged that there is a pressure connection between the pressure area and at least one of the plain bearings.
- DE 196 05 781 A1 relates to a radial piston pump which has a collecting space designed as a ring-type filter, which surrounds the front bearing of the drive shaft. At higher pressures, the bearing clearance caused by the belt load can be reduced by having a portion of the pump body press the bearing tightly against the drive shaft.
- the pulley is cup-shaped, which extends over the exhaust valves and the piston plane. The object of the invention is to provide a high-pressure pump which enables reliable and precise operation even under heavy mechanical stresses. At the same time, the high-pressure pump should be inexpensive to produce.
- the invention is characterized by a high-pressure pump for delivering a fluid, with a pump housing, extending in the direction of a longitudinal axis axle member which is mounted in a housing recess of the pump housing, a rotatably mounted on the axle drive shaft, and a fixedly coupled to the drive shaft Drive element, which is designed to drive the drive shaft.
- the high-pressure pump has a bearing element which is fixedly coupled to the pump housing or formed integrally with the pump housing, and which has a recess in which the axle is mounted.
- the recess of the bearing element is arranged relative to the housing recess such that the drive element is arranged axially between the recess of the bearing element and the housing recess.
- the drive element extends substantially in a plane perpendicular to the longitudinal axis.
- a sliding bearing is arranged in the plane in which the forces of the drive element act. This can be avoided that edges of components of the high-pressure pump act on the sliding bearing.
- the plain bearing allow low friction between the axle and the drive shaft, too when the forces exerted by the drive element on the drive shaft and the axle element are large.
- the high-pressure pump has at least one pump unit which can be driven by the drive shaft and which extends essentially in a further plane perpendicular to the longitudinal axis.
- the further plane is arranged axially between the recess of the bearing element and the housing recess.
- At least one further sliding bearing is arranged radially in the further plane between the axle element and the drive shaft.
- the bearing element is designed as a bracket, which is coupled to a first bracket portion fixed to the pump housing.
- the bearing element has the recess of the bearing element on a second bracket section which is distal with respect to the first bracket section.
- FIG. 1 shows a high-pressure pump 10 with a pump housing 12.
- the pump housing 12 is preferably formed wholly or partly of a metal.
- the pump housing 12 is in the illustrated embodiment in two parts from a first part 12 a and a second part 12 b executed.
- the first part 12 a is in particular pot-shaped.
- the second part 12 b is formed in particular as a flange.
- the pump housing 12 may also be made in one piece or have more than two parts.
- the high-pressure pump 10 has a pump unit 14 in the embodiment shown here. In further embodiments, however, the high-pressure pump 10 may also have two or more pump units.
- the high-pressure pump 10 has centrally an axle 15.
- the shaft element 15 has a longitudinal axis Z.
- the pump housing 12 has a housing recess 13.
- the axle element 15 is mounted in the housing recess 13.
- the formed as a flange second part 12 b of the pump housing 12 is fixedly coupled to the first part 12 a of the pump housing 12.
- the axle 15 is in operative connection with a drive shaft 16 designed as a camshaft.
- a drive shaft 16 designed as a camshaft instead of the drive shaft 16 designed as a camshaft, an eccentric shaft can also be used.
- the pump unit 14 essentially consists of a cylinder housing 17 coupled to the pump housing 12, a cylinder chamber 18 arranged in the cylinder housing 17, a spring 20 and a high-pressure piston 21.
- the cylinder housing 17, the cylinder chamber 18, the high-pressure piston 21 and the spring 20 are mutually aligned arranged coaxially.
- the high-pressure piston 21 is mounted axially movable in the cylinder chamber 18 of the cylinder housing 17.
- the high-pressure piston 21 is held in constant operative connection with the drive shaft 16 by means of the spring 20, which is preferably supported on the cylinder housing 17 and cooperates with the high-pressure piston 21.
- the cylinder housing 17 has a supply line 22, in which preferably an inlet valve 24 is arranged.
- the inlet valve 24 facilitates the filling of the cylinder chamber 18 and prevents the backflow of the fluid from the feed line 22 during the compression phase.
- the cylinder housing 17 further has a drain line 26 and an outlet valve 28 arranged therein. Via the drain line 26 and the outlet valve 28, the fluid can be ejected from the cylinder chamber 18.
- the pump unit 14 has a roller tappet 32 coupled to the high pressure piston 21.
- the roller tappet 32 is operatively connected to the drive shaft 16 via a cylindrical roller 30.
- the pump unit 14 may also be used be formed with an eccentric ring and coupled to the high pressure piston shoe.
- a sliding bearing 36 and a further sliding bearing 38 are arranged.
- more than two plain bearings between the axle 15 and the drive shaft 16 may be arranged.
- the sliding bearings 36, 38 allow that only a slight friction between the shaft member 15 and the drive shaft 16 occurs, even if the forces occurring between the shaft member 15 and the drive shaft 16 are large.
- the high-pressure pump 10 further has a drive element 40.
- the drive element 40 is fixedly coupled to the drive shaft 16.
- the drive element 40 is preferably designed as a belt pulley or as a sprocket.
- a nut 42 is arranged with a thread 44.
- the drive member 40 may be fixedly coupled to the drive shaft 16. This can be avoided in particular a displacement or tilting of the drive member 40 relative to the axle 15 and the drive shaft 16.
- the high-pressure pump 10 also has a bearing element 46.
- the bearing element 46 is fixedly coupled to the pump housing 12.
- the bearing element 46 may also be formed integrally with the pump housing.
- the bearing element 46 has a recess 48.
- the bearing element 46 is formed as a bracket.
- the trained as a bracket bearing element 46 has a first bracket portion 50.
- the first bracket portion 50 is fixedly coupled to the pump housing 12.
- the trained as a bracket bearing element 46 has a respect to the first bracket portion 50 distal second bracket portion 52. In the second bracket portion 52, the recess 48 is arranged.
- the bearing member 46 further has an intermediate portion 54 which connects the first bracket portion 50 with the second bracket portion 52.
- the bearing member 46 of the first bracket portion 50, the second bracket portion 52 and the intermediate portion 54 is integrally formed.
- the axle element 15 is mounted in the recess 48 of the bearing element 46.
- the drive element 40 is arranged axially between the recess 48 and the housing recess 13. This has the advantage that a very precise alignment of the shaft member 15 can be achieved. If, in particular, large forces are transmitted from the drive element 40 via the drive shaft 16 to the shaft element 15, then a secure mounting of the shaft element 15 in the pump housing 12 and in the bearing element 46 can be achieved. Thus, a slight wear on the axle 15 and on the drive shaft 16 can be achieved. This can also be achieved that the required for overcoming the frictional forces drive power for the high-pressure pump 10 can be small.
- the drive element 40 extends substantially in a plane E1, which is perpendicular to the longitudinal axis z.
- a stable mounting of the shaft member 15 and the drive shaft 16 can be achieved.
- the sliding bearing 36 can be further achieved that a low friction between the shaft member 15 and the drive shaft 16 occurs, even if the outgoing of the drive member 40 forces on the drive shaft 16 and the shaft member 15 are large.
- the pump unit 14 extends substantially in a further plane E2 perpendicular to the longitudinal axis Z.
- the other sliding bearing 38 is radially between the shaft member 15 and the Drive shaft 16 arranged in the further plane E2.
- the other sliding bearing 38 is thus in the further plane E2, in which the forces of the pump unit 14, in particular the high-pressure piston 21 act. It is thus possible to achieve that the further sliding bearing 38 only leads to a low friction between the axle element 15 and the drive shaft 16. This is true even if the forces between the drive shaft 16 and the shaft member 15 are large.
- a lubricant supply passage 56 is formed, by means of which it is possible, in particular a space between the shaft member 15 and the drive shaft 16, in which the sliding bearings 36, 38 are arranged to rinse with a lubricant.
- the lubricant can then be removed from the gap between the shaft member 15 and the drive shaft 16 preferably via the drive shaft 16 and the pump housing 12 via a lubricant return passage 58 from the high-pressure pump 10.
- FIG. 2 a detail view of parts of the high-pressure pump 10 is shown.
- the drive element 40 embodied as a belt pulley or as a sprocket is shown, which is coupled to a transmission element 60. Via the transmission element 60, a driving force can be transmitted, for example, from the internal combustion engine to the drive element 40.
- the transmission element 60 is preferably formed according to the formation of the drive member 40 as a belt or as a chain.
- FIG. 2 formed as a bracket bearing element 46, in which the axle 15 is mounted.
- the bearing element 46 is fastened by means of fastening elements 62 to a motor housing, not shown.
- a suction stroke is first performed, that is, a movement of the high-pressure piston 21 in the direction of the longitudinal axis z of the shaft member 15 back.
- fluid is conveyed from the supply line 22 via the inlet valve 24 into the cylinder chamber 18, wherein the outlet valve 28 is closed.
- a pumping stroke is then performed, that is, a movement of the high pressure piston 21 from the longitudinal axis Z of the shaft member 15 away.
- the fluid located in the cylinder chamber 18 is compressed or discharged via the outlet valve 28 under high pressure, wherein the inlet valve 24 is closed.
- the high-pressure pump 10 is, for example, a high-pressure fuel pump of an injection system of an internal combustion engine, the fluid subjected to high pressure can reach a high-pressure fuel reservoir, the so-called common rail.
- the arrangement of the plain bearings 36, 38 in the planes E1, E2 radially between the shaft member 15 and the drive shaft 16 can further be avoided that the slide bearings 36, 38 with respect to the axle 15 and the drive shaft 16 tilt.
- the wear on the axle 15 and the drive shaft 16 can be kept low.
- a small friction between the axle 15 and the drive shaft 16 can be achieved.
- the high-pressure pump 10 can be formed as a compact unit.
- a defined interface for the customer can be provided.
Description
Die Erfindung betrifft eine Hochdruckpumpe.The invention relates to a high-pressure pump.
Vorzugsweise wird eine derartige Hochdruckpumpe als Förderpumpe zur Förderung von Fluid für ein Speichereinspritzsystem für Brennkraftmaschinen von Kraftfahrzeugen verwendet.Preferably, such a high-pressure pump is used as a pump for delivering fluid for a storage injection system for internal combustion engines of motor vehicles.
Speichereinspritzsysteme für Brennkraftmaschinen von Kraftfahrzeugen, beispielsweise in Common-Rail-Systemen, sollen den notwendigen Volumenstrom und den erforderlichen Fluiddruck bereitstellen können. Die Hochdruckpumpe unterliegt in Speichereinspritzsystemen für Kraftfahrzeuge starken Belastungen, insbesondere mechanischen Beanspruchungen. Insbesondere müssen von derartigen Hockdruckpumpen große Kräfte aufgenommen werden können. Damit werden sowohl hohe Anforderungen an das Material als auch an die Konstruktion der Hockdruckpumpe gestellt.Storage injection systems for internal combustion engines of motor vehicles, for example in common-rail systems, should be able to provide the necessary volume flow and the required fluid pressure. The high-pressure pump is subject to strong loads in memory injection systems for motor vehicles, in particular mechanical stresses. In particular, large forces must be able to be absorbed by such high-pressure pumps. This places high demands on the material as well as on the construction of the high pressure pump.
Da Hochdruckpumpen Drücken von beispielsweise bis zu über 2000 bar ausgesetzt sind, müssen sie hohen Beanspruchungen standhalten.Since high-pressure pumps are exposed to pressures of up to more than 2000 bar, for example, they have to withstand high stresses.
Die Aufgabe der Erfindung ist es, eine Hochdruckpumpe zu schaffen, die auch bei starken mechanischen Beanspruchungen einen zuverlässigen und präzisen Betrieb ermöglicht. Zugleich soll die Hochdruckpumpe kostengünstig herstellbar sein.
The object of the invention is to provide a high-pressure pump which enables reliable and precise operation even under heavy mechanical stresses. At the same time, the high-pressure pump should be inexpensive to produce.
Die Aufgabe wird gelöst durch die Merkmale des unabhängigen Anspruchs. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of the independent claim. Advantageous embodiments of the invention are characterized in the subclaims.
Die Erfindung zeichnet sich aus durch eine Hochdruckpumpe zur Förderung eines Fluids, mit einem Pumpengehäuse, einem sich in Richtung einer Längsachse erstreckenden Achselement, das in einer Gehäuseausnehmung des Pumpengehäuses gelagert ist, einer auf dem Achselement drehbar gelagerten Antriebswelle, und einem fest mit der Antriebswelle gekoppelten Antriebselement, das ausgebildet ist zum Antreiben der Antriebswelle. Die Hochdruckpumpe weist ein Lagerelement auf, das fest mit dem Pumpengehäuse gekoppelt oder einstückig mit dem Pumpengehäuse ausgebildet ist, und das eine Ausnehmung aufweist, in der das Achselement gelagert ist. Die Ausnehmung des Lagerelements ist relativ zu der Gehäuseausnehmung derart angeordnet, dass das Antriebselement axial zwischen der Ausnehmung des Lagerelements und der Gehäuseausnehmung angeordnet ist.The invention is characterized by a high-pressure pump for delivering a fluid, with a pump housing, extending in the direction of a longitudinal axis axle member which is mounted in a housing recess of the pump housing, a rotatably mounted on the axle drive shaft, and a fixedly coupled to the drive shaft Drive element, which is designed to drive the drive shaft. The high-pressure pump has a bearing element which is fixedly coupled to the pump housing or formed integrally with the pump housing, and which has a recess in which the axle is mounted. The recess of the bearing element is arranged relative to the housing recess such that the drive element is arranged axially between the recess of the bearing element and the housing recess.
Dies hat den Vorteil, dass eine sehr präzise Ausrichtung des Achselements erreicht werden kann. Dies gilt insbesondere auch dann, wenn von dem Antriebselement große Kräfte über die Antriebswelle auf das Achselement übertragen werden. Des Weiteren kann erreicht werden, dass nur ein geringer Verschleiß an dem Achselement und an der Antriebswelle auftritt. Damit kann erreicht werden, dass die für die Überwindung der Reibungskräfte erforderliche Antriebsleistung klein ist.This has the advantage that a very precise alignment of the shaft element can be achieved. This is especially true when large forces are transmitted from the drive element via the drive shaft to the axle. Furthermore, it can be achieved that only a slight wear on the axle and the drive shaft occurs. It can thus be achieved that the drive power required to overcome the frictional forces is small.
In einer vorteilhaften Ausführungsform erstreckt sich das Antriebselement im Wesentlichen in einer Ebene senkrecht zu der Längsachse. In der Ebene radial zwischen dem Achselement und der Antriebswelle ist ein Gleitlager angeordnet. Dies hat den Vorteil, dass das Gleitlager in der Ebene liegt, in der auch die Kräfte des Antriebselements wirken. Damit kann vermieden werden, dass Kanten von Komponenten der Hochdruckpumpe auf das Gleitlager einwirken. Damit kann das Gleitlager eine geringe Reibung zwischen dem Achselement und der Antriebswelle ermöglichen, auch dann, wenn die von dem Antriebselement ausgehenden Kräfte auf die Antriebswelle und das Achselement groß sind.In an advantageous embodiment, the drive element extends substantially in a plane perpendicular to the longitudinal axis. In the plane radially between the axle and the drive shaft, a sliding bearing is arranged. This has the advantage that the sliding bearing lies in the plane in which the forces of the drive element act. This can be avoided that edges of components of the high-pressure pump act on the sliding bearing. Thus, the plain bearing allow low friction between the axle and the drive shaft, too when the forces exerted by the drive element on the drive shaft and the axle element are large.
In einer weiteren vorteilhaften Ausführungsform weist die Hochdruckpumpe mindestens eine von der Antriebswelle antreibbare Pumpeneinheit auf, die sich im Wesentlichen in einer weiteren Ebene senkrecht zu der Längsachse erstreckt. Die weitere Ebene ist axial zwischen der Ausnehmung des Lagerelements und der Gehäuseausnehmung angeordnet. Dies hat den Vorteil, dass eine sehr präzise Ausrichtung des Achselements erreicht werden kann. Dies gilt insbesondere auch dann, wenn von der Antriebswelle große Kräfte auf die Pumpeneinheit übertragen werden. Des Weiteren kann erreicht werden, dass nur ein geringer Verschleiß an dem Achselement und an der Antriebswelle auftritt. Damit kann erreicht werden, dass die für die Überwindung der Reibungskräfte erforderliche Antriebsleistung klein ist.In a further advantageous embodiment, the high-pressure pump has at least one pump unit which can be driven by the drive shaft and which extends essentially in a further plane perpendicular to the longitudinal axis. The further plane is arranged axially between the recess of the bearing element and the housing recess. This has the advantage that a very precise alignment of the shaft element can be achieved. This is especially true when large forces are transmitted from the drive shaft to the pump unit. Furthermore, it can be achieved that only a slight wear on the axle and the drive shaft occurs. It can thus be achieved that the drive power required to overcome the frictional forces is small.
In einer weiteren vorteilhaften Ausführungsform ist in der weiteren Ebene radial zwischen dem Achselement und der Antriebswelle mindestens ein weiteres Gleitlager angeordnet. Dies hat den Vorteil, dass das weitere Gleitlager in der Ebene liegt, in der auch die Kräfte der Pumpeneinheit wirken. Damit kann das Gleitlager eine geringe Reibung zwischen dem Achselement und der Antriebswelle ermöglichen, auch dann, wenn die Kräfte zwischen der Antriebswelle und dem Achselement groß sind.In a further advantageous embodiment, at least one further sliding bearing is arranged radially in the further plane between the axle element and the drive shaft. This has the advantage that the further sliding bearing lies in the plane in which the forces of the pump unit also act. Thus, the sliding bearing allow a low friction between the axle and the drive shaft, even if the forces between the drive shaft and the axle are large.
In einer weiteren vorteilhaften Ausführungsform ist das Lagerelement als Bügel ausgebildet, der an einem ersten Bügelabschnitt fest mit dem Pumpengehäuse gekoppelt ist. Das Lagerelement weist an einem bezüglich des ersten Bügelabschnitts distalen zweiten Bügelabschnitt die Ausnehmung des Lagerelements auf. Dies hat den Vorteil, dass die Hochdruckpumpe einfach aufgebaut sein kann. Damit kann die Hochdruckpumpe einfach zu montieren und damit zu geringen Kosten zu fertigen sein.In a further advantageous embodiment, the bearing element is designed as a bracket, which is coupled to a first bracket portion fixed to the pump housing. The bearing element has the recess of the bearing element on a second bracket section which is distal with respect to the first bracket section. This has the advantage that the high pressure pump can be easily constructed. This allows the high pressure pump to be easy to assemble and thus be manufactured at low cost.
Ausführungsbeispiele der Erfindung sind im Folgenden anhand der schematischen Zeichnungen näher erläutert.Embodiments of the invention are explained in more detail below with reference to the schematic drawings.
Es zeigen:
- Figur 1
- eine teilweise geschnittene, teilweise perspektivische Ansicht einer Hochdruckpumpe, und
- Figur 2
- eine Detailansicht der Hochdruckpumpe.
- FIG. 1
- a partially sectioned, partial perspective view of a high-pressure pump, and
- FIG. 2
- a detailed view of the high pressure pump.
Elemente gleicher Konstruktion oder Funktion sind figurenübergreifend mit den gleichen Bezugszeichen versehen.Elements of the same construction or function are provided across the figures with the same reference numerals.
Die Hochdruckpumpe 10 weist zentral ein Achselement 15 auf. Das Achselement 15 hat eine Längsachse Z. Das Pumpengehäuse 12 hat eine Gehäuseausnehmung 13. Das Achselement 15 ist in der Gehäuseausnehmung 13 gelagert.The high-
Das als Flansch ausgebildete zweite Teil 12b des Pumpengehäuses 12 ist mit dem ersten Teil 12a des Pumpengehäuses 12 fest gekoppelt. Das Achselement 15 steht mit einer als Nockenwelle ausgebildeten Antriebswelle 16 in Wirkverbindung. Anstelle der als Nockenwelle ausgebildeten Antriebswelle 16 kann auch eine Exzenterwelle zum Einsatz kommen.The formed as a flange
Die Pumpeneinheit 14 besteht im Wesentlichen aus einem mit dem Pumpengehäuse 12 gekoppelten Zylindergehäuse 17, einer in dem Zylindergehäuse 17 angeordneten Zylinderkammer 18, einer Feder 20 und einem Hochdruckkolben 21. Das Zylindergehäuse 17, die Zylinderkammer 18, der Hochdruckkolben 21 und die Feder 20 sind zueinander koaxial angeordnet.The
Der Hochdruckkolben 21 ist axial bewegbar in der Zylinderkammer 18 des Zylindergehäuses 17 gelagert. Der Hochdruckkolben 21 wird mittels der Feder 20, die sich vorzugsweise am Zylindergehäuse 17 abstützt und mit dem Hochdruckkolben 21 zusammenwirkt, in ständiger Wirkverbindung mit der Antriebswelle 16 gehalten.The high-
Um die Zylinderkammer 18 mit Fluid befüllen zu können, weist das Zylindergehäuse 17 eine Zulaufleitung 22 auf, in der vorzugsweise ein Einlassventil 24 angeordnet ist. Das Einlassventil 24 erleichtert die Befüllung der Zylinderkammer 18 und verhindert während der Kompressionsphase das Zurückströmen des Fluids aus der Zulaufleitung 22. Das Zylindergehäuse 17 weist weiter eine Ablaufleitung 26 und ein in dieser angeordnetes Auslassventil 28 auf. Über die Ablaufleitung 26 und das Auslassventil 28 kann das Fluid aus der Zylinderkammer 18 ausgestoßen werden.In order to be able to fill the
In der hier gezeigten Ausführungsform hat die Pumpeneinheit 14 einen mit dem Hochdruckkolben 21 gekoppelten Rollenstößel 32. Der Rollenstößel 32 ist über eine zylinderförmige Rolle 30 in Wirkverbindung mit der Antriebswelle 16. In alternativen Ausführungsformen kann die Pumpeneinheit 14 beispielsweise auch mit einem Exzenterring und einem mit dem Hochdruckkolben gekoppelten Gleitschuh ausgebildet sein.In the embodiment shown here, the
Radial zwischen dem Achselement 15 und der Antriebswelle 16 sind ein Gleitlager 36 sowie ein weiteres Gleitlager 38 angeordnet. In weiteren Ausführungsformen können auch mehr als zwei Gleitlager zwischen dem Achselement 15 und der Antriebswelle 16 angeordnet sein. Die Gleitlager 36, 38 ermöglichen, dass nur eine geringe Reibung zwischen dem Achselement 15 und der Antriebswelle 16 auftritt, auch wenn die zwischen dem Achselement 15 und der Antriebswelle 16 auftretenden Kräfte groß sind.Radial between the
Die Hochdruckpumpe 10 hat ferner ein Antriebselement 40. Das Antriebselement 40 ist fest mit der Antriebswelle 16 gekoppelt. Das Antriebselement 40 ist vorzugsweise als Riemenrad oder als Kettenrad ausgebildet.The high-
An der Antriebswelle 16 ist insbesondere eine Mutter 42 mit einem Gewinde 44 angeordnet. Mittels der Mutter 42 kann das Antriebselement 40 fest mit der Antriebswelle 16 gekoppelt sein. Damit kann insbesondere ein Verschieben oder ein Verkippen des Antriebselements 40 gegenüber dem Achselement 15 und der Antriebswelle 16 vermieden werden.On the
Die Hochdruckpumpe 10 weist weiterhin ein Lagerelement 46 auf. Das Lagerelement 46 ist fest mit dem Pumpengehäuse 12 gekoppelt. In einer alternativen Ausführungsform kann das Lagerelement 46 auch einstückig mit dem Pumpengehäuse ausgebildet sein. Das Lagerelement 46 weist eine Ausnehmung 48 auf. Besonders bevorzugt ist das Lagerelement 46 als Bügel ausgebildet. Das als Bügel ausgebildete Lagerelement 46 hat einen ersten Bügelabschnitt 50. Der erste Bügelabschnitt 50 ist fest mit dem Pumpengehäuse 12 gekoppelt. Das als Bügel ausgebildete Lagerelement 46 hat einen bezüglich des ersten Bügelabschnitts 50 distalen zweiten Bügelabschnitt 52. In dem zweiten Bügelabschnitt 52 ist die Ausnehmung 48 angeordnet. Das Lagerelement 46 hat weiter einen Zwischenabschnitt 54, der den ersten Bügelabschnitt 50 mit dem zweiten Bügelabschnitt 52 verbindet. Vorzugsweise ist das Lagerelement 46 aus dem ersten Bügelabschnitt 50, dem zweiten Bügelabschnitt 52 und dem Zwischenabschnitt 54 einstückig ausgebildet.The high-
Das Achselement 15 ist in der Ausnehmung 48 des Lagerelements 46 gelagert. Das Antriebselement 40 ist axial zwischen der Ausnehmung 48 und der Gehäuseausnehmung 13 angeordnet. Dies hat den Vorteil, dass eine sehr präzise Ausrichtung des Achselements 15 erreicht werden kann. Werden insbesondere von dem Antriebselement 40 große Kräfte über die Antriebswelle 16 auf das Achselement 15 übertragen, so kann eine sichere Lagerung des Achselements 15 in dem Pumpengehäuse 12 und in dem Lagerelement 46 erreicht werden. Damit kann ein geringer Verschleiß an dem Achselement 15 und an der Antriebswelle 16 erreicht werden. Damit kann auch erreicht werden, dass die für die Überwindung der Reibungskräfte erforderliche Antriebsleistung für die Hochdruckpumpe 10 klein sein kann.The
Das Antriebselement 40 erstreckt sich im Wesentlichen in einer Ebene E1, die senkrecht zu der Längsachse z ist. Damit kann auch bei großen in Richtung der Ebene E1 wirkenden Kräften des Antriebselements 40 eine stabile Lagerung des Achselements 15 und der Antriebswelle 16 erreicht werden. Mittels des Gleitlagers 36 kann des Weiteren erreicht werden, dass eine geringe Reibung zwischen dem Achselement 15 und der Antriebswelle 16 auftritt, auch dann, wenn die von dem Antriebselement 40 ausgehenden Kräfte auf die Antriebswelle 16 und das Achselement 15 groß sind.The
Die Pumpeneinheit 14 erstreckt sich im Wesentlichen in einer weiteren Ebene E2 senkrecht zu der Längsachse Z. Das weitere Gleitlager 38 ist radial zwischen dem Achselement 15 und der Antriebswelle 16 in der weiteren Ebene E2 angeordnet. Das weitere Gleitlager 38 liegt also in der weiteren Ebene E2, in der auch die Kräfte der Pumpeneinheit 14, insbesondere des Hochdruckkolbens 21 wirken. Es ist so möglich, zu erreichen, dass das weitere Gleitlager 38 nur zu einer geringen Reibung zwischen dem Achselement 15 und der Antriebswelle 16 führt. Dies gilt auch dann, wenn die Kräfte zwischen der Antriebswelle 16 und dem Achselement 15 groß sind.The
In der Antriebswelle 16 ist ein Schmiermittelzulaufkanal 56 ausgebildet, mittels dem es möglich ist, insbesondere einen Raum zwischen dem Achselement 15 und der Antriebswelle 16, in dem die Gleitlager 36, 38 angeordnet sind, mit einem Schmiermittel zu spülen. Durch die Spülung des Raums zwischen dem Achselement 15 und der Antriebswelle 16 kann eine Kühlung und Schmierung der Hochdruckpumpe 10 bewirkt werden. Das Schmiermittel kann anschließend von dem Zwischenraum zwischen dem Achselement 15 und der Antriebswelle 16 vorzugsweise über die Antriebswelle 16 und das Pumpengehäuse 12 über einen Schmiermittelrücklaufkanal 58 aus der Hochdruckpumpe 10 abgeführt werden.In the
In
Im Folgenden soll die Funktion der Hochdruckpumpe 10 anhand der
Durch eine Drehbewegung der Antriebswelle 16 wird zunächst ein Saughub durchgeführt, das heißt eine Bewegung des Hochdruckkolbens 21 in Richtung auf die Längsachse z des Achselements 15 hin. Dabei wird Fluid aus der Zulaufleitung 22 über das Einlassventil 24 in die Zylinderkammer 18 gefördert, wobei das Auslassventil 28 geschlossen ist. Durch eine weitere Drehung der Antriebswelle 16 wird dann ein Pumphub durchgeführt, das heißt eine Bewegung des Hochdruckkolbens 21 von der Längsachse Z des Achselements 15 weg. Dabei wird das in der Zylinderkammer 18 befindliche Fluid komprimiert beziehungsweise über das Auslassventil 28 unter hohem Druck abgegeben, wobei das Einlassventil 24 geschlossen ist. Handelt es sich bei der Hochdruckpumpe 10 beispielsweise um eine Kraftstoffhochdruckpumpe einer Einspritzanlage einer Brennkraftmaschine, so kann das mit hohem Druck beaufschlagte Fluid zu einem Hochdruckkraftstoffspeicher, dem so genannten Common-Rail gelangen.By a rotational movement of the
Über das Transmissionselement 60 werden in der Ebene E1 Spannkräfte FS, die in einer Querkraft FQ resultieren, auf das Antriebselement 40 ausgeübt. Durch die Lagerung des Achselements 15 in der Ausnehmung 48 des Lagerelements 46 und der Gehäuseausnehmung 13 kann erreicht werden, dass die Querkraft FQ insbesondere auch von dem Lagerelement 46 aufgenommen wird, und so eine präzise Lagerung des Achselements 15 und der Antriebswelle 16 erreicht wird. Dies gilt in entsprechender Weise für die von dem Hochdruckkolben 21 auf die Antriebswelle 16 und das Achselement 15 ausgehenden Kräfte quer zu der Längsachse z in der weiteren Ebene E2.Clamping forces F S , which result in a transverse force F Q , are exerted on the
Durch die Anordnung der Gleitlager 36, 38 in den Ebenen E1, E2 radial zwischen dem Achselement 15 und der Antriebswelle 16 kann des Weiteren vermieden werden, dass die Gleitlager 36, 38 gegenüber dem Achselement 15 beziehungsweise der Antriebswelle 16 verkanten. Damit kann der Verschleiß an dem Achselement 15 und der Antriebswelle 16 gering gehalten werden. Damit kann eine geringe Reibleistung zwischen dem Achselement 15 und der Antriebswelle 16 erreicht werden.The arrangement of the
Des Weiteren kann durch den Aufbau der Hochdruckpumpe 10 mit dem Lagerelement 46, in dessen Ausnehmung 48 das Achselement 15 gelagert ist, die Hochdruckpumpe 10 als kompakte Einheit ausgebildet werden. An der Hochdruckpumpe 10 kann so eine definierte Schnittstelle für den Kunden bereitgestellt werden kann.Furthermore, by constructing the high-
- 1010
- Hochdruckpumpehigh pressure pump
- 1212
- Pumpengehäusepump housing
- 12a, 12b12a, 12b
- Teile von 12Parts of 12
- 1313
- Gehäuseausnehmunghousing recess
- 1414
- Pumpeneinheitpump unit
- 1515
- Achselementaxle
- 1616
- Antriebswelledrive shaft
- 1717
- Zylindergehäusecylinder housing
- 1818
- Zylinderkammercylinder chamber
- 2020
- Federfeather
- 2121
- HochdruckkolbenHigh pressure piston
- 2222
- Zulaufleitungsupply line
- 2424
- Einlassventilintake valve
- 2626
- Ablaufleitungdrain line
- 2828
- Auslassventiloutlet valve
- 3030
- Rollerole
- 3232
- Rollenstößelroller plunger
- 3636
- Gleitlagerbearings
- 3838
- weiteres Gleitlageranother plain bearing
- 4040
- Antriebselementdriving element
- 4242
- Muttermother
- 4444
- Gewindethread
- 4646
- Lagerelementbearing element
- 4848
- Ausnehmung von 46Recess of 46
- 5050
- 1. Bügelabschnitt1st bracket section
- 5252
- 2. Bügelabschnitt2nd bracket section
- 5454
- Zwischenabschnittintermediate section
- 5656
- SchmiermittelzulaufkanalLubricant supply channel
- 5858
- SchmiermittelrücklaufkanalLubricant return channel
- 6060
- Transmissionselement (Riemen/Kette)Transmission element (belt / chain)
- 6262
- Befestigungselementfastener
- E1, E2E1, E2
- Ebenenlevels
- ZZ
- Längsachselongitudinal axis
- FS F S
- Spannkräfteclamping forces
- FQ F Q
- Querkraftlateral force
Claims (5)
- High-pressure pump (10) for delivering a fluid, comprising- a pump housing (12),- a drive shaft (16) which is rotatably mounted in a housing aperture (13) of the pump housing (12),- a drive element (40) which is fixedly coupled with the drive shaft (16) and which is designed to drive the drive shaft (16),wherein the high-pressure pump (10) has a bearing element (46) which is coupled fixedly with the pump housing (12) or formed integrally with the pump housing (12), and which has an aperture (48) which is arranged relative to the housing aperture (13) in such a way that the drive element (40) is arranged axially between the aperture (48) of the bearing element (46) and the housing aperture (13), characterized by a spindle element (15) which extends in the direction of a longitudinal axis (Z) and which is mounted in the housing aperture (13) of the pump housing (12) and in the aperture (48) of the bearing element (46), and on which the drive shaft (16) is rotatably mounted.
- High-pressure pump (10) according to Claim 1, wherein the drive element (40) extends substantially in a plane (E1) perpendicular to the longitudinal axis (Z), and a sliding bearing (36) is arranged in the plane (E1) radially between the spindle element (15) and the drive shaft (16).
- High-pressure pump (10) according to Claim 1 or 2, wherein the high-pressure pump (10) has at least one pump unit (14) which can be driven by the drive shaft (16) and which extends substantially in a further plane (E2) perpendicular to the longitudinal axis (Z), wherein the further plane (E2) is arranged axially between the aperture (48) of the bearing element (46) and the housing aperture (13).
- High-pressure pump (10) according to Claim 3, wherein at least one further sliding bearing (38) is arranged in the further plane (E2) radially between the spindle element (15) and the drive shaft (16).
- High-pressure pump (10) according to one of the preceding claims, wherein the bearing element (46) takes the form of a bracket which is fixedly coupled with the pump housing (12) at a first bracket portion (50), and the bearing element (46) has the aperture (48) of the bearing element (46) at a second bracket portion (52) which is distal with respect to the first bracket portion (50).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201210211976 DE102012211976B3 (en) | 2012-07-10 | 2012-07-10 | high pressure pump |
PCT/EP2013/064061 WO2014009224A1 (en) | 2012-07-10 | 2013-07-03 | High-pressure pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2872778A1 EP2872778A1 (en) | 2015-05-20 |
EP2872778B1 true EP2872778B1 (en) | 2016-09-14 |
Family
ID=48790399
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13736844.5A Active EP2872778B1 (en) | 2012-07-10 | 2013-07-03 | High-pressure pump |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2872778B1 (en) |
DE (1) | DE102012211976B3 (en) |
WO (1) | WO2014009224A1 (en) |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2263837A1 (en) * | 1972-12-28 | 1974-07-04 | Teves Gmbh Alfred | RADIAL PISTON PUMP |
DE4332324A1 (en) * | 1993-09-23 | 1994-10-20 | Bosch Gmbh Robert | Radial piston machine |
DE19605781B4 (en) * | 1996-02-16 | 2005-04-28 | Zahnradfabrik Friedrichshafen | Radial piston pump |
DE19920168A1 (en) * | 1998-05-16 | 1999-11-18 | Luk Automobiltech Gmbh & Co Kg | Radial piston pump of camshaft and cylinders for vehicle media |
DE102006006555B4 (en) * | 2006-02-13 | 2008-03-06 | Siemens Ag | high pressure pump |
DE102006027773A1 (en) * | 2006-06-16 | 2007-12-20 | Robert Bosch Gmbh | Vehicle brake piston pump |
DE102010001882A1 (en) * | 2010-02-12 | 2011-08-18 | Robert Bosch GmbH, 70469 | High-pressure fuel pump |
-
2012
- 2012-07-10 DE DE201210211976 patent/DE102012211976B3/en not_active Expired - Fee Related
-
2013
- 2013-07-03 EP EP13736844.5A patent/EP2872778B1/en active Active
- 2013-07-03 WO PCT/EP2013/064061 patent/WO2014009224A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
EP2872778A1 (en) | 2015-05-20 |
DE102012211976B3 (en) | 2013-11-07 |
WO2014009224A1 (en) | 2014-01-16 |
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