EP1537334A1 - Pump, especially for a fuel injection device for an internal combustion engine - Google Patents

Pump, especially for a fuel injection device for an internal combustion engine

Info

Publication number
EP1537334A1
EP1537334A1 EP03739364A EP03739364A EP1537334A1 EP 1537334 A1 EP1537334 A1 EP 1537334A1 EP 03739364 A EP03739364 A EP 03739364A EP 03739364 A EP03739364 A EP 03739364A EP 1537334 A1 EP1537334 A1 EP 1537334A1
Authority
EP
European Patent Office
Prior art keywords
pump
bore
blind bore
housing part
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP03739364A
Other languages
German (de)
French (fr)
Other versions
EP1537334B1 (en
Inventor
Helmut Haberer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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 EP1537334A1 publication Critical patent/EP1537334A1/en
Application granted granted Critical
Publication of EP1537334B1 publication Critical patent/EP1537334B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004Joints; Sealings
    • F02M55/005Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404Details or component parts
    • F04B1/0452Distribution members, e.g. valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • the invention relates to a pump, in particular for a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a pump is known from DE 198 48 035 AI.
  • This pump has at least one pump element with a pump piston which is tightly guided in a cylinder bore of a housing part and which delimits a pump working space in the cylinder bore with its end face.
  • the pump piston is driven in one stroke.
  • the pump workspace has one in the
  • the inlet valve has a valve member which interacts with a valve seat and is acted upon by a valve spring towards the valve seat.
  • the part of the inlet channel which opens into the pump work space is formed by a separate component which is inserted into a bore in the housing part and on which the valve seat is also formed.
  • Housing part is ' closed with a screw plug. Because of the many individual parts, the manufacture and assembly of the known pump is complex and expensive. Advantages of the invention
  • the pump according to the invention with the features according to claim 1 has the advantage that it is simple and inexpensive to manufacture and assemble, since the number of its individual parts is reduced.
  • FIG. 1 shows a pump in a longitudinal section
  • FIG. 2 shows a section of the pump designated II in FIG. 1 in an enlarged representation.
  • FIG. 1 and 2 show a pump which is provided in particular for a fuel injection device for an internal combustion engine, for example of a motor vehicle.
  • the pump delivers fuel under high pressure of up to 2000 bar, for example into a storage tank.
  • the pump has a housing which has, for example, a housing part 10 and a flange part 11 connected to it.
  • a drive shaft 12 is arranged in the housing and drives one or more pump elements 14 arranged in the housing.
  • a plurality of pump elements 14 are preferably arranged distributed over the circumference of the drive shaft 12.
  • the drive shaft 12 is via a bearing 16 in the housing part 10 and a bearing 18 in the flange part 11 rotatably mounted about an axis 13 and is driven in a manner not shown by the internal combustion engine.
  • the drive shaft 12 has an eccentric section 20 on which a cam ring 22 is mounted.
  • the pump element 14 has a pump piston 24, which is displaceably and sealingly guided in a cylinder bore 26 of the housing part 10 which extends at least approximately radially to the drive shaft 12.
  • the pump piston 24 is supported with its piston foot 25 on the cam ring 22, the piston foot 25 being held in contact with the cam ring 22 by a spring 28 which is supported on the one hand on the housing part 10 and on the other hand on the piston foot 25.
  • a pump working space 30 is delimited by the pump piston 24 in the cylinder bore 26 with its end face.
  • the pump working space 30 is connectable to an inlet fuel valve 34 through an inlet valve 32 opening into the pump working space 30, in which low pressure prevails.
  • the pump working space 30 can also be connected to the accumulator by means of an outlet valve 36 opening towards the accumulator via a fuel drain channel 38 running in the housing part 10.
  • a first blind bore 42 adjoins the pump work chamber 30, which is arranged in the end region of the cylinder bore 26 that is radially remote from the drive shaft 12, as part of the fuel inlet channel 34.
  • the first blind bore 42 has a smaller diameter than the cylinder bore 26 and preferably runs at least approximately coaxially with the cylinder bore 26.
  • the first blind bore 42 ends within the housing part 10. The transition from the cylinder bore 26 to the first blind bore 42 is, for example, at least approximately conical and forms a valve seat 44 for the inlet valve 32.
  • the inlet valve 32 has a valve member 46, which is designed, for example, as a ball and which interacts with the valve seat 44 for controlling the connection of the pump work chamber 30 to the fuel inlet channel 34.
  • the valve member 46 is urged toward the valve seat 44 by a preloaded valve spring 48, for example in the form of a helical compression spring.
  • a support element in the form of a spring plate can be arranged between the valve spring 48 and the valve member 46.
  • the valve spring 48 can be supported in a stationary manner on the housing part 10 or, as shown in the figure, on the end face of the pump piston 24.
  • a second blind bore 50 which also is introduced into the housing part 10 and ends in the housing part 10, opens into the first blind hole 42.
  • the second blind hole 50 is inclined to the first blind hole 42, preferably at least approximately perpendicular to the first blind hole 42 and at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the second blind hole 50 is made from a side surface 52 of the housing part 10 facing the flange part 11. In the flange 11, the
  • a sealing element 58 can be clamped in at the transition of the fuel channel 34 between the flange part 11 and the housing part 10.
  • the mutually facing side surfaces 52 and 54 of the housing part 10 and the flange part 11 run, for example, at least approximately perpendicular to the axis of rotation 13 of the drive shaft 12 and can be flat.
  • the housing part 10 and the flange part 11 are connected to one another in a manner not shown, for example by means of several screws.
  • blind bores 42 and 50 can be introduced into the housing part 10 in a simple manner from the cylinder bore 26 or from the side surface 52.
  • the housing part 10 has no openings for the fuel channel 34 on its outside.
  • the inlet valve 32 only the valve member 46 and the valve spring 48 as well as the supporting element arranged between them are required as additional components. It can be provided that a common housing part 10 is provided for several pump elements 14, in which in a corresponding
  • Number of cylinder bores 26 and blind bores 42 and 50 are introduced.
  • a separate housing part 10 is provided for each pump element 14. in each of which only one cylinder bore 26 and one blind bore 42, 50 are introduced.
  • the housing parts 10 of the pump elements 14 are then connected to one another in a suitable manner.
  • a bore 60 opens into the pump working chamber 30 in the cylinder bore 26, said bore 60 being at least approximately perpendicular to the longitudinal axis of the Cylinder bore 26 runs.
  • the bore 60 has a stepped diameter, the end portion of which opens into the pump working space 30 has a small diameter.
  • a central section of the bore 60 adjoins the end section away from the pump work chamber 30, the transition between the end section and the central section being able to be approximately conical, for example, and forming a valve seat 62 for the outlet valve 36.
  • a valve member 64 of the outlet valve 36 for example in the form of a ball, cooperates with the valve seat 62 to control the connection of the pump working chamber 30 to the fuel drain channel 38.
  • a screw plug 66 is screwed into an outer section of the bore 60 which is further enlarged in diameter compared to the central section and is provided with an internal thread.
  • a prestressed valve spring 68 for example in the form of a helical compression spring, is clamped between the screw plug 66 and the valve member 64, through which the valve member 64 is urged toward the valve seat 62.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to a pump comprising at least one pump element (14) which comprises a pump piston (24) which is tightly guided in a cylinder bore (26) of a housing part (10) and which defines a pump working chamber (26) in the cylinder bore (26) and which is driven in a stroke movement. The pump working chamber (26) is provided with a connection to a feeder channel (34) controlled by an inlet valve which opens into the pump working chamber (26) and a connection to a discharge channel (38) controlled by an outlet valve (30) which opens out of the pump working chamber (26). The inlet valve comprises a valve member (46) which co-operates with a valve seat (44) and which is impinged upon by a valve spring (48) in a closing direction in relation to the valve seat (44). The feeder channel (34) comprises a part which is embodied in the form of a first blind bore (42) which has a smaller diameter than that of the cylinder bore (26) and which is adjacent to the pump working chamber (30) in the cylinder bore (26) in the housing part (10). The valve seat is formed in the transition from the cylinder bore (26) to the first blind bore (42) and a second blind bore (50) leads into the first blind bore (42) as another part of the feeder chamber (34).

Description

Pumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung für eine BrennkraftmaschinePump, in particular for a fuel injection device for an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Pumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a pump, in particular for a fuel injection device for an internal combustion engine according to the preamble of claim 1.
Eine, solche Pumpe ist durch die DE 198 48 035 AI bekannt. Diese Pumpe weist wenigstens ein Pumpenelement mit einem in einer Zylinderbohrung eines Gehäuseteils dicht geführten Pumpenkolben auf, der in der Zylinderbohrung mit seiner Stirnseite einen Pumpenarbeitsraum begrenzent . Der Pumpenkolben wird dabei in einer Hubbewegung angetrieben. Der Pumpenarbeitsraum weist eine durch ein in denSuch a pump is known from DE 198 48 035 AI. This pump has at least one pump element with a pump piston which is tightly guided in a cylinder bore of a housing part and which delimits a pump working space in the cylinder bore with its end face. The pump piston is driven in one stroke. The pump workspace has one in the
Pumpenarbeitsraum öffnendes Einlassventil gesteuerte Verbindung mit einem Zulaufkanal und eine durch ein aus dem Pumpenarbeitsraum öffnendes Auslassventil gesteuerte Verbindung mit einem Ablaufkanal auf. Das Einlassventil weist ein mit einem Ventilsitz zusammenwirkendes Ventilglied auf, das durch eine Ventilfeder zum Ventilsitz hin beaufschlagt ist. Der in den Pumpenarbeitsraum mündende Teil des Zulaufkanals, ist durch ein in eine Bohrung des Gehäuseteils eingesetztes separatea Bauteil gebildet, an dem auch der Ventilsitz ausgebildet ist. Die Bohrung desInlet valve opening pump work space controlled connection to an inlet channel and a connection to an outlet channel controlled by an outlet valve opening from the pump work space. The inlet valve has a valve member which interacts with a valve seat and is acted upon by a valve spring towards the valve seat. The part of the inlet channel which opens into the pump work space is formed by a separate component which is inserted into a bore in the housing part and on which the valve seat is also formed. The bore of the
Gehäuseteils ist' mit einer Verschlußschraube verschlossen. Aufgrund der vielen Einzelteile ist die Fertigung und Montage der bekannten Pumpe aufwendig und teuer. Vorteile der ErfindungHousing part is ' closed with a screw plug. Because of the many individual parts, the manufacture and assembly of the known pump is complex and expensive. Advantages of the invention
Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß diese einfach und kostengünstig herstellbar und montierbar ist, da die Anzahl von deren Einzelteilen reduziert ist.The pump according to the invention with the features according to claim 1 has the advantage that it is simple and inexpensive to manufacture and assemble, since the number of its individual parts is reduced.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpe angegeben.Advantageous refinements and developments of the pump according to the invention are specified in the dependent claims.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert . Es zeigen Figur 1 eine Pumpe in einem Längsschnitt und Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Pumpe in vergrößerter Darstellung .An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a pump in a longitudinal section and FIG. 2 shows a section of the pump designated II in FIG. 1 in an enlarged representation.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In den Figuren 1 und 2 ist eine Pumpe dargestellt, die insbesondere für eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs vorgesehen ist. Durch die Pumpe wird dabei Kraftstoff unter Hochdruck von bis zu 2000 bar gefördert, beispielsweise in einen Speicher. Die Pumpe weist ein Gehäuse auf, das beispielsweise ein Gehäuseteil 10 und ein mit diesem verbundenes Flanschteil 11 aufweist . Im Gehäuse ist eine Antriebswelle 12 angeordnet, durch die ein oder mehrere im Gehäuse angeordnete Pumpenelemente 14 angetrieben werden. Vorzugsweise sind mehrere Pumpenelemente 14 über den Umfang der Antriebswelle 12 verteilt angeordnet. Die Antriebswelle 12 ist über eine Lagerstelle 16 im Gehäuseteil 10 und über eine Lagerstelle 18 im Flanschteil 11 um eine Achse 13 drehbar gelagert und wird in nicht dargestellter Weise durch die Brennkraftmaschine angetrieben. Die Antriebswelle 12 weist einen Exzenterabschnitt 20 auf, auf dem ein Hubring 22 gelagert ist. Das Pumpenelement 14 weist einen Pumpenkolben 24 auf, der in einer zumindest annähernd radial zur Antriebswelle 12 verlaufenden Zylinderbohrung 26 des Gehäuseteils 10 verschiebbar dicht geführt ist. Der Pumpenkolben 24 stützt sich mit seinem Kolbenfuß 25 am Hubring 22 ab, wobei der Kolbenfuß 25 durch eine Feder 28, die sich einerseits am Gehäuseteil 10 und andererseits am Kolbenfuß 25 abstützt, in Anlage am Hubring 22 gehalten wird.1 and 2 show a pump which is provided in particular for a fuel injection device for an internal combustion engine, for example of a motor vehicle. The pump delivers fuel under high pressure of up to 2000 bar, for example into a storage tank. The pump has a housing which has, for example, a housing part 10 and a flange part 11 connected to it. A drive shaft 12 is arranged in the housing and drives one or more pump elements 14 arranged in the housing. A plurality of pump elements 14 are preferably arranged distributed over the circumference of the drive shaft 12. The drive shaft 12 is via a bearing 16 in the housing part 10 and a bearing 18 in the flange part 11 rotatably mounted about an axis 13 and is driven in a manner not shown by the internal combustion engine. The drive shaft 12 has an eccentric section 20 on which a cam ring 22 is mounted. The pump element 14 has a pump piston 24, which is displaceably and sealingly guided in a cylinder bore 26 of the housing part 10 which extends at least approximately radially to the drive shaft 12. The pump piston 24 is supported with its piston foot 25 on the cam ring 22, the piston foot 25 being held in contact with the cam ring 22 by a spring 28 which is supported on the one hand on the housing part 10 and on the other hand on the piston foot 25.
Durch den Pumpenkolben 24 wird in der Zylinderbohrung 26 mit seiner Stirnseite ein Pumpenarbeitsraum 30 begrenzt. Der Pumpenarbeitsraum 30 ist der durch ein in den Pumpenarbeitsraum 30 öffnendes Einlassventil 32 mit einem KraftstoffZulaufkanal 34 verbindbar ist, in dem Niederdruck herrscht. Der Pumpenarbeitsraum 30 ist außerdem durch ein zum Speicher hin öffnendes Auslassventil 36 über einen im Gehäuseteil 10 verlaufenden Kraftstoffablaufkanal 38 mit dem Speicher verbindbar. Bei der Rotation der Antriebswelle 12 wird der Pumpenkolben 24 über den Exzenterabschnitt 20 und den Hubring 22 in einer Hubbewegung angetrieben. Wenn der Pumpenkolben 24 sich radial nach innen bewegt, so führt dieser einen Saughub aus, wobei das Einlassventil 32 geöffnet ist, so dass Kraftstoff über den Kraftstoffzulaufkanal 34 in den Pumpenarbeitsraum 30 einströmt, während das Auslassventil 36 geschlossen ist.A pump working space 30 is delimited by the pump piston 24 in the cylinder bore 26 with its end face. The pump working space 30 is connectable to an inlet fuel valve 34 through an inlet valve 32 opening into the pump working space 30, in which low pressure prevails. The pump working space 30 can also be connected to the accumulator by means of an outlet valve 36 opening towards the accumulator via a fuel drain channel 38 running in the housing part 10. When the drive shaft 12 rotates, the pump piston 24 is driven in a lifting movement via the eccentric section 20 and the cam ring 22. When the pump piston 24 moves radially inward, it carries out a suction stroke, the inlet valve 32 being open, so that fuel flows into the pump working chamber 30 via the fuel inlet channel 34, while the outlet valve 36 is closed.
Wenn der Pumpenkolben 24 sich radial nach außen bewegt, so führt dieser einen Förderhub aus, wobei das Einlassventil 32 geschlossen ist und der vom Pumpenkolben 24 verdichtete Kraftstoff durch das geöffnete Auslassventil 36 unter hohem Druck über den Kraftstoffablaufkanal 36 in den Speicher gelangt . Im Gehäuseteil 12 schließt sich an den in dem der Antriebswelle 12 radial abgewandten Endbereich der Zylinderbohrung 26 angeordneten Pumpenarbeitsraum 30 als Teil des KraftstoffZulaufkanals 34 eine erste Sackbohrung 42 an. Die erste Sackbohrung 42 weist gegenüber der Zylinderbohrung 26 einen kleineren Durchmesser auf und verläuft vorzugsweise zumindest annähernd koaxial zur Zylinderbohrung 26. Die erste Sackbohrung 42 endet innerhalb des Gehäuseteils 10. Der Übergang von der Zylinderbohrung 26 zur ersten Sackbohrung 42 ist beispielsweise zumindest annähernd konisch ausgebildet und bildet einen Ventilsitz 44 für das Einlassventil 32. Das Einlassventil 32 weist ein Ventilglied 46 auf, das beispielsweise als Kugel ausgebildet ist, und das mit dem Ventilsitz 44 zur Steuerung der Verbindung des Pumpenarbeitsraums 30 mit dem Kraftstoffzulaufkanal 34 zusammenwirkt. Das Ventilglied 46 wird durch eine vorgespannte Ventilfeder 48, beispielsweise in Form einer Schraubendruckfeder, zum Ventilsitz 44 hin beaufschlagt. Zwischen der Ventilfeder 48 und dem Ventilglied 46 kann ein Stützelement in Form eines Federtellers angeordnet sein. Die Ventilfeder 48 kann sich ortsfest am Gehäuseteil 10 abstützen oder wie in der Figur dargestellt an der Stirnseite des Pumpenkolbens 24.When the pump piston 24 moves radially outward, it executes a delivery stroke, the inlet valve 32 being closed and the fuel compressed by the pump piston 24 passing through the opened outlet valve 36 under high pressure via the fuel outlet channel 36 into the reservoir. In the housing part 12, a first blind bore 42 adjoins the pump work chamber 30, which is arranged in the end region of the cylinder bore 26 that is radially remote from the drive shaft 12, as part of the fuel inlet channel 34. The first blind bore 42 has a smaller diameter than the cylinder bore 26 and preferably runs at least approximately coaxially with the cylinder bore 26. The first blind bore 42 ends within the housing part 10. The transition from the cylinder bore 26 to the first blind bore 42 is, for example, at least approximately conical and forms a valve seat 44 for the inlet valve 32. The inlet valve 32 has a valve member 46, which is designed, for example, as a ball and which interacts with the valve seat 44 for controlling the connection of the pump work chamber 30 to the fuel inlet channel 34. The valve member 46 is urged toward the valve seat 44 by a preloaded valve spring 48, for example in the form of a helical compression spring. A support element in the form of a spring plate can be arranged between the valve spring 48 and the valve member 46. The valve spring 48 can be supported in a stationary manner on the housing part 10 or, as shown in the figure, on the end face of the pump piston 24.
In die erste Sackbohrung 42 mündet als weiterer Teil des Kraftstoffzulaufkanals 34 eine im Gehäuseteil 10 eingebrachte zweite Sackbohrung 50, die ebenfalls im Gehäuseteil 10 endet. Die zweite Sackbohrung 50 verläuft geneigt zur ersten Sackbohrung 42, vorzugsweise zumindest annähernd senkrecht zur ersten Sackbohrung 42 und zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12. Die zweite Sackbohrung 50 ist von einer dem Flanschteil 11 zugewandten Seitenfläche 52 des Gehäuseteils 10 aus eingebracht. Im Flanschteil 11 setzt sich derAs a further part of the fuel inlet channel 34, a second blind bore 50, which also is introduced into the housing part 10 and ends in the housing part 10, opens into the first blind hole 42. The second blind hole 50 is inclined to the first blind hole 42, preferably at least approximately perpendicular to the first blind hole 42 and at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The second blind hole 50 is made from a side surface 52 of the housing part 10 facing the flange part 11. In the flange 11, the
Kraftstoffzulauf anal 34 ausgehend von einer Seitenfläche 54 des Flanschteils 11 fort, wobei am Flanschteil 11 ein Ansσhluss 56 für eine Zulaufleitung vorgesehen sein kann, über die beispielsweise durch eine Förderpumpe Kraftstoff aus einem Kraftstoffvorratsbehälter zugeführt wird. Am Übergang des Kraftstoffkanals 34 zwischen dem Flanschteil 11 und dem Gehäuseteil 10 kann ein Dichtelement 58 eingespannt sein. Die einander zugewandten Seitenflächen 52 und 54 des Gehäuseteils 10 und des Flanschteils 11 verlaufen beispielsweise zumindest annähernd senkrecht zur Drehachse 13 der Antriebswelle 12 und können eben ausgebildet sein. Das Gehäuseteil 10 und das Flanschteil 11 sind in nicht näher dargestellter Weise miteinander verbunden, beispielsweise mittels mehrerer Schrauben.Fuel supply anal 34 starting from a side surface 54 of the flange part 11, wherein a connection 56 for an inlet line can be provided on the flange part 11, via which fuel is supplied, for example, by a feed pump from a fuel reservoir. A sealing element 58 can be clamped in at the transition of the fuel channel 34 between the flange part 11 and the housing part 10. The mutually facing side surfaces 52 and 54 of the housing part 10 and the flange part 11 run, for example, at least approximately perpendicular to the axis of rotation 13 of the drive shaft 12 and can be flat. The housing part 10 and the flange part 11 are connected to one another in a manner not shown, for example by means of several screws.
Die den Kraftstoffkanal 34 im Gehäuseteil 10 bildendenThe forming the fuel channel 34 in the housing part 10
Sackbohrungen 42 und 50 können auf einfache Weise von der Zylinderbohrung 26 her bzw. von der Seitenfläche 52 her in das Gehäuseteil 10 eingebracht werden. Das Gehäuseteil 10 weist dabei für den Kraftstoffkanal 34 an seiner Außenseite keine Öffnungen auf. Für das Einlassventil 32 sind als zusätzliche Bauteile lediglich das Ventilglied 46 und die Ventilfeder 48 sowie gegebenenfalls das zwischen diesen angeordnete Stützelement erforderlich. Es kann vorgesehen sein, dass für mehrere Pumpenelemente 14 ein gemeinsames Gehäuseteil 10 vorgesehen ist, in dem in entsprechenderBlind bores 42 and 50 can be introduced into the housing part 10 in a simple manner from the cylinder bore 26 or from the side surface 52. The housing part 10 has no openings for the fuel channel 34 on its outside. For the inlet valve 32, only the valve member 46 and the valve spring 48 as well as the supporting element arranged between them are required as additional components. It can be provided that a common housing part 10 is provided for several pump elements 14, in which in a corresponding
Anzahl die Zylinderbohrungen 26 sowie die Sackbohrungen 42 und 50 eingebracht sind. Alternativ kann auch vorgesehen sein, dass für jedes Pumpenelement 14 ein separates Gehäuseteil 10 vorgesehen ist. in dem jeweils nur eine Zylinderbohrung 26 sowie eine Sackbohrung 42,50 eingebracht ist . Die Gehäuseteile 10 der Pumpenelemente 14 sind dann in geeigneter Weise miteinander verbunden.Number of cylinder bores 26 and blind bores 42 and 50 are introduced. Alternatively, it can also be provided that a separate housing part 10 is provided for each pump element 14. in each of which only one cylinder bore 26 and one blind bore 42, 50 are introduced. The housing parts 10 of the pump elements 14 are then connected to one another in a suitable manner.
Als Teil des Kraftstoffablaufkanals 38 mündet in den Pumpenarbeitsraum 30 in der Zylinderbohrung 26 eine Bohrung 60, die zumindest annähernd senkrecht zur Längsachse der Zylinderbohrung 26 verläuft. Die Bohrung 60 ist im Durchmesser mehrfach gestuft ausgebildet, wobei deren in den Pumpenarbeitsraum 30 mündender Endabschnitt einen kleinen Durchmessser aufweist. An den Endabschnitt schließt sich vom Pumpenarbeitsraum 30 weg ein mittlerer Abschnitt der Bohrung 60 an, wobei der Übergang zwischen dem Endabschnitt und dem mittleren Abschnitt beispielsweise etwa konisch ausgebildet sein kann und einen Ventilsitz 62 für das Auslassventil 36 bildet. Mit dem Ventilsitz 62 wirkt ein Ventilglied 64 des Auslassventils 36, beispielsweise in Form einer Kugel, zur Steuerung der Verbindung des Pumpenarbeitsrau s 30 mit dem Kraftstoffablaufkanal 38 zusammen. In einen im Durchmesser gegenüber dem mittleren Abschnitt weiter vergrößerten und mit einem Innengewinde versehenen äußeren Abschnitt der Bohrung 60 ist eine Verschlußschraube 66 eingeschraubt. Zwischen der Verschlußschraube 66 und dem Ventilglied 64 ist eine vorgespannte Ventilfeder 68, beispielsweise in Form einer Schraubendruckfeder, eingespannt, durch die das Ventilglied 64 zum Ventilsitz 62 hin beaufschlagt ist. As part of the fuel drain channel 38, a bore 60 opens into the pump working chamber 30 in the cylinder bore 26, said bore 60 being at least approximately perpendicular to the longitudinal axis of the Cylinder bore 26 runs. The bore 60 has a stepped diameter, the end portion of which opens into the pump working space 30 has a small diameter. A central section of the bore 60 adjoins the end section away from the pump work chamber 30, the transition between the end section and the central section being able to be approximately conical, for example, and forming a valve seat 62 for the outlet valve 36. A valve member 64 of the outlet valve 36, for example in the form of a ball, cooperates with the valve seat 62 to control the connection of the pump working chamber 30 to the fuel drain channel 38. A screw plug 66 is screwed into an outer section of the bore 60 which is further enlarged in diameter compared to the central section and is provided with an internal thread. A prestressed valve spring 68, for example in the form of a helical compression spring, is clamped between the screw plug 66 and the valve member 64, through which the valve member 64 is urged toward the valve seat 62.

Claims

Ansprüche Expectations
1. Pumpe, insbesondere für eine1. Pump, especially for one
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine, mit wenigstens einem Pumpenelement (14) , das einen in einer Zylinderbohrung (26) eines Gehäuseteils (10) dicht geführten Pumpenkolben (24) aufweist, der in der Zylinderbohrung (26) einen Pumpenarbeitsraum (26) begrenzt und der in einerFuel injection device for an internal combustion engine, with at least one pump element (14), which has a pump piston (24) tightly guided in a cylinder bore (26) of a housing part (10), which delimits a pump working chamber (26) in the cylinder bore (26) and which in one
Hubbewegung angetrieben wird, wobei der Pumpenarbeitsraum (26) eine durch ein in den Pumpenarbeitsraum (26) öffnendes Einlassventil (28) gesteuerte Verbindung mit einem Zulaufkanal (34) und eine durch ein aus dem Pumpenarbeitsraum (26) öffnendes Auslassventil (30) gesteuerte Verbindung mit einem Ablaufkanal (38) aufweist, wobei das Einlassventil (32) ein mit einem Ventilsitz (44) zusammenwirkendes Ventilglied (46) aufweist, das durch eine Ventilfeder (48) in einer Schließrichtung zum Ventilsitz (44) hin beaufschlagt ist, dadurch gekennzeichnet, dass der Zulaufkanal (34) im Gehäuseteil (10) einen sich an den Pumpenarbeitsraum (30) in der Zylinderbohrung (26) anschließenden Teil in Form einer ersten Sackbohrung (42) mit kleinerem Durchmesser als die Zylinderbohrung (26) aufweist, dass am Übergang von der Zylinderbohrung (26) zur ersten Sackbohrung (42) der Ventilsitz (44) gebildet ist und dass in die erste Sackbohrung (42) als weiterer Teil des Zulaufkanals (34) eine zweite Sackbohrung (50) mündet. Lifting movement is driven, the pump work chamber (26) having a connection with an inlet channel (34) controlled by an inlet valve (28) opening into the pump work chamber (26) and a connection controlled by an outlet valve (30) opening from the pump work chamber (26) has a drain channel (38), the inlet valve (32) having a valve member (46) which interacts with a valve seat (44) and is acted upon by a valve spring (48) in a closing direction towards the valve seat (44), characterized in that the inlet channel (34) in the housing part (10) has a part adjoining the pump working chamber (30) in the cylinder bore (26) in the form of a first blind bore (42) with a smaller diameter than the cylinder bore (26) that at the transition from the Cylinder bore (26) to the first blind bore (42) of the valve seat (44) is formed and that in the first blind bore (42) as a further part of the inlet channel (34) a second blind bore tion (50) opens.
2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, dass die erste Sackbohrung (42) zumindest annähernd koaxial zur Zylinderbohrung (26) verläuft.2. Pump according to claim 1, characterized in that the first blind bore (42) extends at least approximately coaxially to the cylinder bore (26).
3. Pumpe nach Anspruch 1 oder 2 , dadurch gekennzeichnet, dass die zweite Sackbohrung (50) geneigt zur ersten Sackbohrung (42) im Gehäuseteil (10) verläuft.3. Pump according to claim 1 or 2, characterized in that the second blind bore (50) inclined to the first blind bore (42) in the housing part (10).
4. Pumpe nach Anspruch 3, dadurch gekennzeichnet, dass die ) zweite Sackbohrung (50) zumindest annähernd senkrecht zur ersten Sackbohrung (42) verläuft.4. Pump according to claim 3, characterized in that the) second blind bore (50) extends at least approximately perpendicular to the first blind bore (42).
5. Pumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die zweite Sackbohrung (50) von einer Seitenfläche (52) des Gehäuseteils (10) ausgeht, an die sich ein weiteres Gehäuseteil (11) anschließt.5. Pump according to one of claims 1 to 4, characterized in that the second blind bore (50) extends from a side surface (52) of the housing part (10) to which a further housing part (11) connects.
6. Pumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass im Gehäuseteil (10) eine Antriebswelle (12) zum Antrieb des wenigstens einen Pumpenelements (14) drehbar gelagert ist, dass die Zylinderbohrung (26) und die erste Sackbohrung (42) zumindest annähernd radial zur Drehachse (13) der Antriebswelle (12) verlaufen und dass die zweite Sackbohrung (50) zumindest annähernd parallel zur Drehachse (13) der Antriebswelle (12) verläuft.6. Pump according to one of the preceding claims, characterized in that in the housing part (10) a drive shaft (12) for driving the at least one pump element (14) is rotatably mounted, that the cylinder bore (26) and the first blind bore (42) at least run approximately radially to the axis of rotation (13) of the drive shaft (12) and that the second blind bore (50) runs at least approximately parallel to the axis of rotation (13) of the drive shaft (12).
7. Pumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass für jeweils ein Pumpenelement (14) ein separates Gehäuseteil (10) vorgesehen ist, in dem die O Zylinderbohrung (26) , die erste Sackbohrung (46) , der7. Pump according to one of the preceding claims, characterized in that for each pump element (14) a separate housing part (10) is provided in which the O cylinder bore (26), the first blind bore (46), the
Ventilsitz (44) und die zweite Sackbohrung (50) für das Pumpenelement (14) eingebracht sind. Valve seat (44) and the second blind bore (50) for the pump element (14) are introduced.
EP03739364A 2002-08-29 2003-02-11 Pump, especially for a fuel injection device for an internal combustion engine Expired - Lifetime EP1537334B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10239728A DE10239728A1 (en) 2002-08-29 2002-08-29 Pump, in particular for a fuel injection device for an internal combustion engine
DE10239728 2002-08-29
PCT/DE2003/000383 WO2004022975A1 (en) 2002-08-29 2003-02-11 Pump, especially for a fuel injection device for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1537334A1 true EP1537334A1 (en) 2005-06-08
EP1537334B1 EP1537334B1 (en) 2010-10-13

Family

ID=31502103

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Application Number Title Priority Date Filing Date
EP03739364A Expired - Lifetime EP1537334B1 (en) 2002-08-29 2003-02-11 Pump, especially for a fuel injection device for an internal combustion engine

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US (1) US7210463B2 (en)
EP (1) EP1537334B1 (en)
JP (1) JP4309840B2 (en)
DE (2) DE10239728A1 (en)
WO (1) WO2004022975A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004028999A1 (en) * 2004-06-16 2006-01-05 Robert Bosch Gmbh High-pressure pump for a fuel injection device of an internal combustion engine
EP1813844A1 (en) * 2006-01-31 2007-08-01 Centro Studi Componenti per Veicoli S.P.A. High-pressure piston pump for delivering fuel to a common rail of an internal combustion engine
DE102008043217A1 (en) * 2008-10-28 2010-04-29 Robert Bosch Gmbh High-pressure fuel pump for an internal combustion engine
WO2013010458A1 (en) * 2011-07-14 2013-01-24 Neo Mechanics Limited Diesel engine fuel injection pump which pistons are sealed with all metal seal rings
ITMI20132109A1 (en) * 2013-12-17 2015-06-18 Bosch Gmbh Robert PUMP ASSEMBLY TO SUPPLY FUEL, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE
US10012228B2 (en) * 2014-04-17 2018-07-03 Danfoss Power Solutions Gmbh & Co. Ohg Variable fluid flow hydraulic pump
GB2555599A (en) * 2016-11-02 2018-05-09 Delphi Int Operations Luxembourg Sarl Fuel pump

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1218675B (en) * 1987-08-25 1990-04-19 Weber Srl RADIAL PUMP PUMP IN PARTICULAR PUMP FOR INJECTION OF FUEL IN DIESEL CYCLE ENGINES
IT239879Y1 (en) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat REFINEMENTS TO A PISTON PUMP, IN PARTICULAR TO A RADIAL APISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE.
DE19801353A1 (en) * 1998-01-16 1999-07-22 Bosch Gmbh Robert Radial piston pump providing HP fuel for fuel injection systems of internal combustion engines, especially with common rail injection system
DE19848035A1 (en) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radial piston pump for high fuel pressure in IC engines with common-rail injection system has suction valve closure spring supported on pump piston and contained in long piston bore
JP4088738B2 (en) 1998-12-25 2008-05-21 株式会社デンソー Fuel injection pump
IT1310755B1 (en) * 1999-11-30 2002-02-22 Elasis Sistema Ricerca Fiat HIGH PRESSURE HYDRAULIC PUMP, IN PARTICULAR RUBBER PISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE.
DE10117600C1 (en) 2001-04-07 2002-08-22 Bosch Gmbh Robert High-pressure fuel pump for a fuel system of a direct-injection internal combustion engine, fuel system and internal combustion engine
US20040022654A1 (en) * 2002-08-05 2004-02-05 Takashi Ishida Piston type small discharge pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004022975A1 *

Also Published As

Publication number Publication date
JP4309840B2 (en) 2009-08-05
DE50313186D1 (en) 2010-11-25
DE10239728A1 (en) 2004-03-11
US7210463B2 (en) 2007-05-01
EP1537334B1 (en) 2010-10-13
WO2004022975A1 (en) 2004-03-18
US20050031478A1 (en) 2005-02-10
JP2005537425A (en) 2005-12-08

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