WO2009013175A1 - Pump, particularly high-pressure fuel pump - Google Patents

Pump, particularly high-pressure fuel pump Download PDF

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Publication number
WO2009013175A1
WO2009013175A1 PCT/EP2008/059209 EP2008059209W WO2009013175A1 WO 2009013175 A1 WO2009013175 A1 WO 2009013175A1 EP 2008059209 W EP2008059209 W EP 2008059209W WO 2009013175 A1 WO2009013175 A1 WO 2009013175A1
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WO
WIPO (PCT)
Prior art keywords
pump
drive shaft
axis
rotation
pair
Prior art date
Application number
PCT/EP2008/059209
Other languages
German (de)
French (fr)
Inventor
Friedrich Boecking
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2009013175A1 publication Critical patent/WO2009013175A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being 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
    • F04B1/0413—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
    • F04B1/053—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
    • F04B1/0536—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 with two or more serially arranged radial piston-cylinder units
    • F04B1/0538—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 with two or more serially arranged radial piston-cylinder units located side-by-side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
    • 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

Definitions

  • the invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.
  • Such a pump in the form of a high-pressure fuel pump is known from DE 199 07 311 Al.
  • This pump has a drive shaft which is provided with a double cam whose cam is about 180 ° about the axis of rotation of
  • the pump also has a pair of pumping elements, each driven at least indirectly by the double cam in a reciprocating motion.
  • the pump pistons are arranged rotated by about 90 ° about the axis of rotation of the drive shaft to each other.
  • the pump pistons are supported by one roller tappet on the double cam.
  • FIG. 1 shows a pump in one
  • FIG. 1 Longitudinal section according to a first embodiment
  • Figure 2 the pump in a cross section along line II-II in Figure 1
  • Figure 3 shows the pump in a longitudinal section according to a second embodiment
  • Figure 4 shows the pump in a cross section along line IV-IV in Figure 3.
  • a pump is shown, in particular a high-pressure fuel pump for a
  • the pump has a housing 10, which may be designed in several parts and in which a rotationally driven drive shaft 12 is arranged.
  • the drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings 14 and 15.
  • the bearings 14,15 can be arranged in different parts 16,17 of the housing 10.
  • the drive shaft 12 In a region lying between the two bearing points 14, 15, the drive shaft 12 has two double cams 18, 20 arranged next to one another in the direction of its axis of rotation 13. Between the two double cams 18,20, a further bearing point of the drive shaft 12 may be provided.
  • the cams of the double cams 18, 20 are in each case rotated through approximately 180 ° about the axis of rotation 13 of the drive shaft 12 relative to each other and thus each arranged approximately diametrically opposite one another.
  • the two double cams 18 and 20 are mutually rotated by an angle ß of about 45 ° about the rotational axis 13 of the drive shaft 12 is arranged.
  • the pump has associated with each one of the double cam 18,20 a first pair of pump elements 22,23 and a second pair of pump elements 24,25.
  • Each of the pump elements 22 to 25 each have a pump piston 28 which is driven by the double cam 18 and 20 of the drive shaft 12 at least indirectly in a lifting movement in at least approximately radial direction to the rotation axis 13 of the drive shaft 12.
  • the pump elements 22 and 23 are designed such that their pump pistons 28 are arranged rotated by an angle ⁇ of about 90 ° about the rotational axis 13 of the drive shaft 12 to each other.
  • the pump elements 24,25 designed so that their
  • Pump piston 28 are also arranged rotated by about 90 ° about the axis of rotation 13 of the drive shaft 12 to each other.
  • the pump piston 28 is supported, for example, via a plunger 30 and a roller 32 rotatably mounted in this or in a roller shoe 31 arranged in the plunger 30 on the double cam 18 or 20.
  • the pump piston 28 and the plunger 30 are acted upon by a prestressed spring 34 to the double cam 18 and 20 out.
  • the pump piston 28 is guided in a cylinder bore 36 in a housing part 38 tightly displaceable and limited with his Drive shaft 12 facing away from the end face in the cylinder bore 36 a pump working space 40.
  • the pump working chamber 40 has a running in the housing of the pump fuel inlet passage 42 with a connection to a fuel inlet, for example a feed pump.
  • an inlet check valve 44 opening into the pump working chamber 40 is arranged.
  • the pump working chamber 40 furthermore has a connection with an outlet, which is connected to a high-pressure accumulator 110, for example, via a fuel outlet channel 46 running in a housing part of the pump.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • an outlet check valve 48 which opens out of the pump working chamber 40 is arranged.
  • the pump elements 22,23,24,25 with pump piston 28, plunger 30, roller 32, spring 34 and housing part 38 are preferably formed identically, so that the production cost is kept low.
  • the pump piston 28 of the second pair of pump elements 24,25 with respect to the pump piston 28 of the first pair of pump elements 22,23 about the rotational axis 13 of the drive shaft 12 is rotated by about 180 °.
  • For the pump thus results in a uniform low drive torque, since the delivery strokes of the pump piston 28 of the pump elements 22 to 25 evenly over a revolution of the drive shaft 12th are distributed.
  • the pump pistons 28 are driven according to the profile of the double cam 18,20 in a lifting movement.
  • the respective pump working chamber 40 is filled with fuel through the fuel inlet channel 42 when the inlet valve 44 is open, the outlet valve 48 being closed.
  • the respective pump piston 28 is held in its suction stroke by the spring 34 via the plunger 30 and the roller 32 in contact with the double cam 18 and 20 respectively.
  • fuel is pumped under high pressure through the fuel discharge passage 46 with the exhaust valve 48 open to the high-pressure accumulator 110, wherein the inlet valve 44 is closed.
  • FIGS. 3 and 4 the pump according to a second exemplary embodiment is shown, in which the basic construction is the same as in the first embodiment, but the arrangement of the second pair of pump elements 24, 25 is modified.
  • the drive shaft 12 has the two adjacent to each other in the direction of the rotational axis 13 arranged double cams 18 and 20, which are mutually rotated about the rotational axis 13 by an angle ß of about 45 °.
  • Pump elements 24,25 are each rotated by a Winekl ⁇ of about 90 ° about the rotational axis 13 of the drive shaft 12 to each other.
  • the pump pistons 28 of the second pair of pump elements 24, 25 are at least approximately in the same with respect to the axis of rotation 13 of the drive shaft 12
  • Conveying strokes of the pump piston 28 of the pump elements 22 to 25 are uniformly distributed over one revolution of the drive shaft 12.
  • the pump pistons 28 of the second pair of pump elements 24, 25 can also be arranged in any other rotational positions with respect to the axis of rotation 13 of the drive shaft 12 in which these are about 90 ° or an integer multiple of 90 ° with respect to the pump piston 28 of the first pair of pump elements 22,23 are arranged twisted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to a pump, particularly a high-pressure fuel pump, having a drive shaft (12) which is provided with a first double lobe (18), wherein the two lobes are arranged at a rotational displacement to each other of approximately 180° about the axis of rotation (13) of the drive shaft (12). The invention comprises a first pair of pump elements (22, 23) which each have a pump piston which is at least indirectly driven by the lifting motion of the first double lobe (18), wherein the pump pistons are arranged at a rotational displacement to each other of approximately 90° about the axis of rotation (13) of the drive shaft (12). The drive shaft has a second double lobe (20) which is next to the first double lobe (18) in the direction of the drive shaft rotational axis (13), wherein the lobes of the second double lobe (20) are arranged at a rotational displacement to each other of approximately 180° about the axis of rotation (13) of the drive shaft (12). The second double lobe (20) is arranged on the drive shaft at a rotational displacement with respect to the first double lobe (18) of approximately 45°. A second pair of pump elements (24, 25) is provided, each having a pump piston (28) which is at least indirectly driven by the lifting motion of the second double lobe (20), and which are arranged at a rotational displacement to each other of approximately 90° about the axis of rotation (13) of the drive shaft (12)

Description

Beschreibungdescription
Titeltitle
Pumpe, insbesondere KraftstoffhochdruckpumpePump, in particular high-pressure fuel pump
Stand der TechnikState of the art
Die Erfindung geht aus von einer Pumpe, insbesondere Kraftstoffhochdruckpumpe nach der Gattung des Anspruchs 1.The invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.
Eine solche Pumpe in Form einer Kraftstoffhochdruckpumpe ist durch die DE 199 07 311 Al bekannt. Diese Pumpe weist eine Antriebswelle auf, die mit einem Doppelnocken versehen ist, dessen Nocken um etwa 180° um die Drehachse derSuch a pump in the form of a high-pressure fuel pump is known from DE 199 07 311 Al. This pump has a drive shaft which is provided with a double cam whose cam is about 180 ° about the axis of rotation of
Antriebswelle zueinander verdreht angeordnet sind. Die Pumpe weist außerdem ein Paar von Pumpenelementen auf, die jeweils einen zumindest mittelbar durch den Doppelnocken in einer Hubbewegung angetrieben werden. Die Pumpenkolben sind dabei um etwa 90° um die Drehachse der Antriebswelle zueinander verdreht angeordnet. Die Pumpenkolben stützen sich dabei über jeweils einen Rollenstößel am Doppelnocken ab. Für Brennkraftmaschinen mit Bedarf großer Kraftstoffeinspritzmengen ist die durch diese Kraftstoffhochdruckpumpe mit zwei Pumpenelementen geförderte Kraftstoffmenge unter Umständen nicht ausreichend.Drive shaft are arranged rotated to each other. The pump also has a pair of pumping elements, each driven at least indirectly by the double cam in a reciprocating motion. The pump pistons are arranged rotated by about 90 ° about the axis of rotation of the drive shaft to each other. The pump pistons are supported by one roller tappet on the double cam. For internal combustion engines requiring large quantities of fuel, the amount of fuel delivered by this high-pressure fuel pump with two pump elements may not be sufficient.
Offenbarung der ErfindungDisclosure of the invention
Vorteile der Erfindung Die erfindungsgemäße Pumpe mit den Merkmalen gemäß AnspruchAdvantages of the invention The pump according to the invention with the features of claim
1 hat den Vorteil, dass diese durch das zweite Paar von Pumpenelementen eine hohe Kraftstoffmenge fördern kann, wobei ein geringes Antriebsmoment für die Pumpe erforderlich ist und deren Förderung gleichmäßig ist.1 has the advantage that it can promote a high fuel quantity by the second pair of pump elements, with a low drive torque for the pump is required and their promotion is uniform.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpe angegeben.In the dependent claims advantageous refinements and developments of the pump according to the invention are given.
Zeichnungdrawing
Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Pumpe in einemSeveral embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. FIG. 1 shows a pump in one
Längsschnitt gemäß einem ersten Ausführungsbeispiel, FigurLongitudinal section according to a first embodiment, FIG
2 die Pumpe in einem Querschnitt entlang Linie II-II in Figur 1, Figur 3 die Pumpe in einem Längsschnitt gemäß einem zweiten Ausführungsbeispiel und Figur 4 die Pumpe in einem Querschnitt entlang Linie IV-IV in Figur 3.2 the pump in a cross section along line II-II in Figure 1, Figure 3 shows the pump in a longitudinal section according to a second embodiment and Figure 4 shows the pump in a cross section along line IV-IV in Figure 3.
Beschreibung der AusführungsbeispieleDescription of the embodiments
In den Figuren 1 bis 4 ist eine Pumpe dargestellt, die insbesondere eine Kraftstoffhochdruckpumpe für eineIn Figures 1 to 4, a pump is shown, in particular a high-pressure fuel pump for a
Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Pumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet sein kann und in dem eine rotierend angetriebene Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist im Gehäuse 10 über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen 14 und 15 drehbar gelagert. Die Lagerstellen 14,15 können in verschiedenen Teilen 16,17 des Gehäuses 10 angeordnet sein. In einem zwischen den beiden Lagerstellen 14,15 liegenden Bereich weist die Antriebswelle 12 zwei in Richtung ihrer Drehachse 13 nebeneinander angeordnete Doppelnocken 18,20 auf. Zwischen den beiden Doppelnocken 18,20 kann eine weitere Lagerstelle der Antriebswelle 12 vorgesehen sein. Die Nocken der Doppelnocken 18,20 sind dabei jeweils um etwa 180° um die Drehachse 13 der Antriebswelle 12 zueinander verdreht und somit jeweils etwa einander diametral gegenüberliegend angeordnet. Die beiden Doppelnocken 18 und 20 sind zueinander um einen Winkel ß von etwa 45° um die Drehachse 13 der Antriebswelle 12 verdreht angeordnet.Fuel injection device of an internal combustion engine is. The pump has a housing 10, which may be designed in several parts and in which a rotationally driven drive shaft 12 is arranged. The drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings 14 and 15. The bearings 14,15 can be arranged in different parts 16,17 of the housing 10. In a region lying between the two bearing points 14, 15, the drive shaft 12 has two double cams 18, 20 arranged next to one another in the direction of its axis of rotation 13. Between the two double cams 18,20, a further bearing point of the drive shaft 12 may be provided. The cams of the double cams 18, 20 are in each case rotated through approximately 180 ° about the axis of rotation 13 of the drive shaft 12 relative to each other and thus each arranged approximately diametrically opposite one another. The two double cams 18 and 20 are mutually rotated by an angle ß of about 45 ° about the rotational axis 13 of the drive shaft 12 is arranged.
Die Pumpe weist zu jeweils einem der Doppelnocken 18,20 zugeordnet ein erstes Paar von Pumpenelementen 22,23 und ein zweites Paar von Pumpenelementen 24,25 auf. Jedes der Pumpenelemente 22 bis 25 weist jeweils einen Pumpenkolben 28 auf, der durch den Doppelnocken 18 bzw. 20 der Antriebswelle 12 zumindest mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebswelle 12 angetrieben wird. Die Pumpenelemente 22 und 23 sind so ausgebildet, dass deren Pumpenkolben 28 um einen Winkel α von etwa 90° um die Drehachse 13 der Antriebswelle 12 zueinander verdreht angeordnet sind. Die Pumpenelemente 24,25 so ausgebildet, dass derenThe pump has associated with each one of the double cam 18,20 a first pair of pump elements 22,23 and a second pair of pump elements 24,25. Each of the pump elements 22 to 25 each have a pump piston 28 which is driven by the double cam 18 and 20 of the drive shaft 12 at least indirectly in a lifting movement in at least approximately radial direction to the rotation axis 13 of the drive shaft 12. The pump elements 22 and 23 are designed such that their pump pistons 28 are arranged rotated by an angle α of about 90 ° about the rotational axis 13 of the drive shaft 12 to each other. The pump elements 24,25 designed so that their
Pumpenkolben 28 ebenfalls um etwa 90° um die Drehachse 13 der Antriebswelle 12 zueinander verdreht angeordnet sind.Pump piston 28 are also arranged rotated by about 90 ° about the axis of rotation 13 of the drive shaft 12 to each other.
Der Pumpenkolben 28 stützt sich beispielsweise über einen Stößel 30 und eine in diesem oder in einem im Stößel 30 angeordneten Rollenschuh 31 drehbar gelagerte Rolle 32 am Doppelnocken 18 bzw. 20 ab. Der Pumpenkolben 28 und der Stößel 30 werden durch eine vorgespannte Feder 34 zum Doppelnocken 18 bzw. 20 hin beaufschlagt. Der Pumpenkolben 28 ist in einer Zylinderbohrung 36 in einem Gehäuseteil 38 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 36 einen Pumpenarbeitsraum 40. Der Pumpenarbeitsraum 40 weist über einen im Gehäuse der Pumpe verlaufenden Kraftstoffzulaufkanal 42 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung des Kraftstoffzulaufkanals 42 in den Pumpenarbeitsraum 40 ist ein in den Pumpenarbeitsraum 40 öffnendes Einlassrückschlagventil 44 angeordnet. Der Pumpenarbeitsraum 40 weist ausserdem über einen in einem Gehäuseteil der Pumpe verlaufenden Kraftstoffablaufkanal 46 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. Mit dem Hochdruckspeicher 110 sind ein oder vorzugsweise mehrere an den Zylindern der Brennkraftmaschine angeordnete Injektoren 120 verbunden, durch die Kraftstoff in die Zylinder der Brennkraftmaschine eingespritzt wird. An der Mündung des Kraftstoffablaufkanals 46 in den Pumpenarbeitsraum 40 ist ein aus dem Pumpenarbeitsraum 40 öffnendes Auslassrückschlagventil 48 angeordnet. Die Pumpenelemente 22,23,24,25 mit Pumpenkolben 28, Stößel 30, Rolle 32, Feder 34 und Gehäuseteil 38 sind vorzugsweise identisch ausgebildet, so dass des Fertigungsaufwand gering gehalten ist.The pump piston 28 is supported, for example, via a plunger 30 and a roller 32 rotatably mounted in this or in a roller shoe 31 arranged in the plunger 30 on the double cam 18 or 20. The pump piston 28 and the plunger 30 are acted upon by a prestressed spring 34 to the double cam 18 and 20 out. The pump piston 28 is guided in a cylinder bore 36 in a housing part 38 tightly displaceable and limited with his Drive shaft 12 facing away from the end face in the cylinder bore 36 a pump working space 40. The pump working chamber 40 has a running in the housing of the pump fuel inlet passage 42 with a connection to a fuel inlet, for example a feed pump. At the mouth of the fuel inlet channel 42 into the pump working chamber 40, an inlet check valve 44 opening into the pump working chamber 40 is arranged. The pump working chamber 40 furthermore has a connection with an outlet, which is connected to a high-pressure accumulator 110, for example, via a fuel outlet channel 46 running in a housing part of the pump. One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine. At the mouth of the fuel discharge channel 46 into the pump working chamber 40, an outlet check valve 48 which opens out of the pump working chamber 40 is arranged. The pump elements 22,23,24,25 with pump piston 28, plunger 30, roller 32, spring 34 and housing part 38 are preferably formed identically, so that the production cost is kept low.
Bei einem in den Figuren 1 und 2 dargestellten erstenIn a first shown in Figures 1 and 2
Ausführungsbeispiel sind die Pumpenkolben 28 des zweiten Paars der Pumpenelemente 24,25 bezüglich den Pumpenkolben 28 des ersten Paars der Pumpenelemente 22,23 um die Drehachse 13 der Antriebswelle 12 um etwa 180° verdreht angeordnet. Insgesamt ergibt sich somit bei der Pumpe eine gleichmäßige Anordnung der Pumpenelemente 22 bis 25 mit jeweils etwa 90° Winkelabständen um die Drehachse 13 der Antriebswelle 12 verteilt. Für die Pumpe ergibt sich somit ein gleichmäßiges geringes Antriebsmoment, da die Förderhübe der Pumpenkolben 28 der Pumpenelemente 22 bis 25 gleichmäßig über eine Umdrehung der Antriebswelle 12 verteilt sind. Außerdem ergibt sich eine gleichmäßige Förderung der Pumpe.Embodiment, the pump piston 28 of the second pair of pump elements 24,25 with respect to the pump piston 28 of the first pair of pump elements 22,23 about the rotational axis 13 of the drive shaft 12 is rotated by about 180 °. Overall, therefore, results in the pump, a uniform arrangement of the pump elements 22 to 25, each with approximately 90 ° angular intervals around the axis of rotation 13 of the drive shaft 12 distributed. For the pump thus results in a uniform low drive torque, since the delivery strokes of the pump piston 28 of the pump elements 22 to 25 evenly over a revolution of the drive shaft 12th are distributed. In addition, there is a uniform delivery of the pump.
Bei der Drehbewegung der Antriebswelle 12 werden die Pumpenkolben 28 entsprechend dem Profil der Doppelnocken 18,20 in einer Hubbewegung angetrieben. Beim Saughub des jeweiligen Pumpenkolbens 28, bei dem sich dieser radial nach innen bewegt, wird der jeweilige Pumpenarbeitsraum 40 durch den Kraftstoffzulaufkanal 42 bei geöffnetem Einlassventil 44 mit Kraftstoff befüllt, wobei das Auslassventil 48 geschlossen ist. Der jeweilige Pumpenkolben 28 wird bei dessen Saughub durch die Feder 34 über den Stößel 30 und die Rolle 32 in Anlage am Doppelnocken 18 bzw. 20 gehalten. Beim Förderhub des Pumpenkolbens 28, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 28 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 46 bei geöffnetem Auslassventil 48 zum Hochdruckspeicher 110 gefördert, wobei das Einlassventil 44 geschlossen ist.During the rotational movement of the drive shaft 12, the pump pistons 28 are driven according to the profile of the double cam 18,20 in a lifting movement. During the intake stroke of the respective pump piston 28, in which the latter moves radially inwards, the respective pump working chamber 40 is filled with fuel through the fuel inlet channel 42 when the inlet valve 44 is open, the outlet valve 48 being closed. The respective pump piston 28 is held in its suction stroke by the spring 34 via the plunger 30 and the roller 32 in contact with the double cam 18 and 20 respectively. During the delivery stroke of the pump piston 28, in which this moves radially outward, fuel is pumped under high pressure through the fuel discharge passage 46 with the exhaust valve 48 open to the high-pressure accumulator 110, wherein the inlet valve 44 is closed.
In den Figuren 3 und 4 ist die Pumpe gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau gleich ist wie beim ersten Ausführungsbeispiel jedoch die Anordnung des zweiten Paars der Pumpenelemente 24,25 modifiziert ist. Die Antriebswelle 12 weist die beiden in Richtung von deren Drehachse 13 nebeneinander angeordneten Doppelnocken 18 und 20, die zueinander um die Drehachse 13 um einen Winkel ß von etwa 45° verdreht angeordnet sind. Die Pumpenkolben 28 des ersten Paars der Pumpenelemente 22,23 und des zweiten Paars derIn FIGS. 3 and 4, the pump according to a second exemplary embodiment is shown, in which the basic construction is the same as in the first embodiment, but the arrangement of the second pair of pump elements 24, 25 is modified. The drive shaft 12 has the two adjacent to each other in the direction of the rotational axis 13 arranged double cams 18 and 20, which are mutually rotated about the rotational axis 13 by an angle ß of about 45 °. The pump pistons 28 of the first pair of pump elements 22,23 and the second pair of
Pumpenelemente 24,25 sind zueinander jeweils um einen Winekl α von etwa 90° um die Drehachse 13 der Antriebswelle 12 verdreht angeordnet. Die Pumpenkolben 28 des zweiten Paars der Pumpenelemente 24,25 sind bezüglich der Drehachse 13 der Antriebswelle 12 zumindest annähernd in derselbenPump elements 24,25 are each rotated by a Winekl α of about 90 ° about the rotational axis 13 of the drive shaft 12 to each other. The pump pistons 28 of the second pair of pump elements 24, 25 are at least approximately in the same with respect to the axis of rotation 13 of the drive shaft 12
Drehstellung angeordnet wie die Pumpenkolben 28 des ersten Paars der Pumpenelemente 22,23. Infolge der Verdrehung des zweiten Doppelnockens 20 bezüglich des ersten Doppelnockens 18 ergibt sich auch bei dieser Anordnung der Pumpenkolben 28 des zweiten Paars der Pumpenelemente 24,25 für die Pumpe ein gleichmäßiges geringes Antriebsmoment, da dieRotary position arranged as the pump piston 28 of the first Pair of pump elements 22, 23. As a result of the rotation of the second double cam 20 with respect to the first double cam 18 results in this arrangement, the pump piston 28 of the second pair of pump elements 24,25 for the pump a uniform low drive torque, as the
Förderhübe der Pumpenkolben 28 der Pumpenelemente 22 bis 25 gleichmäßig über eine Umdrehung der Antriebswelle 12 verteilt sind. Außerdem ergibt sich eine gleichmäßige Förderung der Pumpe. Die Pumpenkolben 28 des zweiten Paars der Pumpenelemente 24,25 können auch in beliebigen anderen Drehstellungen bezüglich der Drehachse 13 der Antriebswelle 12 angeordnet sein, in denen diese um etwa 90° oder ein ganzzahliges Vielfaches von 90° bezüglich den Pumpenkolben 28 des ersten Paars der Pumpenelemente 22,23 verdreht angeordnet sind. Conveying strokes of the pump piston 28 of the pump elements 22 to 25 are uniformly distributed over one revolution of the drive shaft 12. In addition, there is a uniform delivery of the pump. The pump pistons 28 of the second pair of pump elements 24, 25 can also be arranged in any other rotational positions with respect to the axis of rotation 13 of the drive shaft 12 in which these are about 90 ° or an integer multiple of 90 ° with respect to the pump piston 28 of the first pair of pump elements 22,23 are arranged twisted.

Claims

Ansprüche claims
1. Pumpe, insbesondere Kraftstoffhochdruckpumpe, mit einer Antriebswelle (12), durch wenigstens einen ersten Doppelnocken (18) aufweist, dessen Nocken um etwa 180° um die Drehachse (13) der Antriebswelle (12) zueinander verdreht angeordnet sind, mit wenigstens einem ersten Paar von Pumpenelementen (22,23), die jeweils einen zumindest mittelbar durch den ersten Doppelnocken (18) in einer Hubbewegung angetriebenen Pumpenkolben (28) aufweisen, die um etwa 90° um die Drehachse (13) der Antriebswelle (12) zueinander verdreht angeordnet sind, dadurch gekennzeichnet, dass die Antriebswelle (12) in Richtung ihrer Drehachse (13) neben dem ersten Doppelnocken (18) einen zweiten Doppelnocken (20) aufweist, dessen Nocken um etwa 180° um die Drehachse (13) der Antriebswelle (12) zueinander verdreht angeordnet sind, dass der zweite1. Pump, in particular high-pressure fuel pump, with a drive shaft (12), by at least a first double cam (18) whose cams are arranged rotated by about 180 ° about the axis of rotation (13) of the drive shaft (12) to each other, with at least a first A pair of pump elements (22,23), each having an at least indirectly by the first double cam (18) driven in a reciprocating pump piston (28), which is rotated by about 90 ° about the axis of rotation (13) of the drive shaft (12) to each other characterized in that the drive shaft (12) in the direction of its axis of rotation (13) next to the first double cam (18) has a second double cam (20) whose cam about 180 ° about the axis of rotation (13) of the drive shaft (12) are arranged twisted to each other that the second
Doppelnocken (20) bezüglich dem ersten Doppelnocken (18) um die Drehachse (13) der Antriebswelle (12) um etwa 45° verdreht angeordnet ist und dass ein zweites Paar von Pumpenelementen (24,25) vorgesehen ist mit jeweils einem Pumpenkolben (28), der zumindest mittelbar durch den zweiten Doppelnocken (20) in einer Hubbewegung angetrieben wird und die um etwa 90° um die Drehachse (13) der Antriebswelle (12) zueinander verdreht angeordnet sind.Double cam (20) with respect to the first double cam (18) about the rotational axis (13) of the drive shaft (12) is rotated by about 45 ° and that a second pair of pump elements (24,25) is provided with one pump piston (28) which is at least indirectly driven by the second double cam (20) in a lifting movement and which are arranged rotated by about 90 ° about the axis of rotation (13) of the drive shaft (12) to each other.
2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Pumpenkolben (28) des zweiten Paars der Pumpenelemente (24,25) in zumindest annähernd derselben Drehstellung bezüglich der Drehachse (13) der Antriebswelle (12) angeordnet sind wie die Pumpenkolben (28) des ersten Paars der Pumpenelemente (22,23) . 2. Pump according to claim 1, characterized in that the pump pistons (28) of the second pair of pump elements (24,25) are arranged in at least approximately the same rotational position with respect to the axis of rotation (13) of the drive shaft (12) as the pump piston (28). the first pair of pump elements (22,23).
3. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Pumpenkolben (28) des zweiten Paars der Pumpenelemente (24,25) bezüglich der Pumpenkolben (28) des ersten Paars der Pumpenelemente (22,23) um etwa 90° oder ein ganzzahliges Vielfaches von 90° um die Drehachse (13) der Antriebswelle (12) verdreht angeordnet sind.3. Pump according to claim 1, characterized in that the pump piston (28) of the second pair of pump elements (24,25) with respect to the pump piston (28) of the first pair of pump elements (22,23) by about 90 ° or an integer multiple are arranged rotated by 90 ° about the axis of rotation (13) of the drive shaft (12).
4. Pumpe nach Anspruch 3, dadurch gekennzeichnet, dass die Pumpenkolben (28) des zweiten Paars der Pumpenelemente (24,25) bezüglich der Pumpenkolben (28) des ersten Paars der Pumpenelemente (22,23) um etwa 180° um die Drehachse (13) der Antriebswelle (12) verdreht angeordnet sind, so dass die Pumpenkolben (28) der Pumpenelemente (22,23,24,25) zumindest annähernd gleichmäßig um die Drehachse (13) der Antriebswelle (12) verteilt angeordnet sind. 4. Pump according to claim 3, characterized in that the pump piston (28) of the second pair of pump elements (24,25) with respect to the pump piston (28) of the first pair of pump elements (22,23) by about 180 ° about the axis of rotation ( 13) of the drive shaft (12) are arranged rotated, so that the pump piston (28) of the pump elements (22,23,24,25) at least approximately uniformly around the axis of rotation (13) of the drive shaft (12) are arranged distributed.
PCT/EP2008/059209 2007-07-26 2008-07-15 Pump, particularly high-pressure fuel pump WO2009013175A1 (en)

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CN107076125A (en) * 2014-09-11 2017-08-18 赫梅蒂克水力公司 Gearshift

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Publication number Priority date Publication date Assignee Title
DE102009027312A1 (en) * 2009-06-30 2011-01-05 Robert Bosch Gmbh Multi-piston pump

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US2697403A (en) * 1949-06-06 1954-12-21 Melba L Benedek Hydraulic pump or motor
DE19907311A1 (en) * 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulic pump unit
DE102005055057A1 (en) * 2005-11-18 2007-05-24 Robert Bosch Gmbh Multi-piston pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2697403A (en) * 1949-06-06 1954-12-21 Melba L Benedek Hydraulic pump or motor
DE19907311A1 (en) * 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulic pump unit
DE102005055057A1 (en) * 2005-11-18 2007-05-24 Robert Bosch Gmbh Multi-piston pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107076125A (en) * 2014-09-11 2017-08-18 赫梅蒂克水力公司 Gearshift

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