EP2561213B1 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
EP2561213B1
EP2561213B1 EP11712557.5A EP11712557A EP2561213B1 EP 2561213 B1 EP2561213 B1 EP 2561213B1 EP 11712557 A EP11712557 A EP 11712557A EP 2561213 B1 EP2561213 B1 EP 2561213B1
Authority
EP
European Patent Office
Prior art keywords
cylinder head
head part
pump
pressure pump
housing
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.)
Not-in-force
Application number
EP11712557.5A
Other languages
German (de)
French (fr)
Other versions
EP2561213A1 (en
Inventor
Friedrich Boecking
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2561213A1 publication Critical patent/EP2561213A1/en
Application granted granted Critical
Publication of EP2561213B1 publication Critical patent/EP2561213B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F02M59/44—Details, 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • 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
    • 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
    • F02M59/44—Details, 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
    • 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
    • F02M59/44—Details, 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
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F02M59/44—Details, 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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • 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
    • 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
    • F02M59/44—Details, 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
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • a fuel pump with a housing and a drive shaft mounted in the housing is known.
  • two oppositely arranged cylinder heads are provided, which are fixed to the housing.
  • an intake valve and an exhaust valve is integrated.
  • high pressure ports are provided, which are screwed into the respective cylinder head.
  • Fuel pumps in particular plug-in pumps, with multi-part pump housings for attachment to a housing of an internal combustion engine known.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that the manufacturing cost is reduced. Specifically, the material and processing costs for the design of the cylinder head is reduced. This advantage is multiplied by the number of cylinder heads provided on the high-pressure pump.
  • an outlet valve is arranged on the first cylinder head part and that in the first cylinder head part a fuel channel is formed which leads from the pump working chamber to the outlet valve.
  • the fuel channel is configured by a stepped bore formed in the first cylinder head part and that the outlet valve is formed in the stepped bore.
  • the exhaust valve can be integrated in an advantageous manner in the first cylinder head part.
  • the outlet valve can be designed as a check valve.
  • the first cylinder head part may be designed as a forged part, so that there are considerable advantages in terms of the strength of the first cylinder head part.
  • the second cylinder head part may be formed from a favorable material, in particular from a non-hardened material, so that in this respect a cost reduction with respect to the assembled cylinder head results.
  • the high pressure pump comprises a housing to which the cylinder head is mounted.
  • a plurality of cylinder heads may be provided, which are mounted on the housing.
  • the housing of the high pressure pump can be configured in one or more parts.
  • the pump assembly has a cylinder bore configured in the first cylinder head part and a pump piston guided in the cylinder bore, that the pump piston in the cylinder bore limits the pump working space and that the pump piston can be driven by the drive shaft.
  • a high stability of the first cylinder head part can advantageously be utilized in order to form the cylinder bore with the pump working space.
  • an inlet valve is arranged on the second cylinder head part and that the inlet valve limits the pump working space.
  • one or more components of the inlet valve can limit the pump working space.
  • the inlet valve may be suitably placed on an end face of the first cylinder head part. An attachment of the intake valve to the first cylinder head part can take place via the second cylinder head part.
  • the second cylinder head part may have a suitable receptacle in which the inlet valve is arranged.
  • the second cylinder head part is configured as a flange and that the second cylinder head part can be screwed to the housing in at least two different screw-on positions. Specifically, four screw-on positions can be provided.
  • the Anschraubpositionen differ by rotation of the cylinder head about an axis of the pump assembly from each other. For example, by rotating the cylinder head by 90 ° or by integer multiples of 90 ° a certain variability can be achieved with four possible Anschraubpositionen.
  • a suitable alignment of the cylinder head with respect to the housing of the high-pressure pump can then take place. Specifically, this makes it possible to align the outlet valve or a high-pressure connection of the high-pressure pump provided behind the outlet valve with respect to the respective application.
  • the second cylinder head part has a lateral recess, which serves for receiving a lateral neck of the first cylinder head part.
  • a lateral recess which serves for receiving a lateral neck of the first cylinder head part.
  • the first cylinder head part is formed from a high pressure resistant material and that the second cylinder head part is formed from a low pressure resistant material.
  • the first cylinder head portion may be made of a high grade steel, such as 100CR6.
  • the second cylinder head part may be formed from a low-cost material. The second cylinder head part can in this case fix the first cylinder head part and thus the cylinder head and carry the low-pressure circuit.
  • the cylinder head may be formed as a two-part cylinder head, which is composed of the first cylinder head part and the second cylinder head part.
  • sealing rings and the like may be integrated into the cylinder head, which allow the required tightness at the interfaces in the assembled state.
  • Fig. 1 shows a high pressure pump 1 in a partial, schematic, axial sectional view according to an embodiment of the invention.
  • the high pressure pump 1 can be configured in particular as a radial or inline piston pump.
  • the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high-pressure pump 1 is for a fuel injection system with a common rail that stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a housing 2, which may be configured in one or more parts. Further, a drive shaft 3 is provided, which is mounted in a suitable manner in the housing 2.
  • the drive shaft 3 has a cam 4. In operation, the drive shaft 3 rotates about its axis of rotation 5. Here, the cam 4 rotates with the drive shaft 3.
  • the cam 4 can be configured as a single or multiple cam. Further, the cam 4 may also be formed by an eccentric portion of the drive shaft 3. Depending on the configuration of the high-pressure pump 1, further cams may be provided on the drive shaft 3.
  • the housing 2 may also be a housing of an internal combustion engine, for example, the cylinder head, and the drive shaft 3 may be a camshaft of the internal combustion engine, are actuated by the gas exchange valves and the cam or the cam 4 for the high pressure pump 1.
  • the high-pressure pump 1 also has a cylinder head 6.
  • the cylinder head 6 is composed of a first cylinder head part 7 and a second cylinder head part 8.
  • the first cylinder head part 7 is formed of a high pressure resistant material.
  • the first cylinder head part 7 may be made of a high-grade steel, in particular 100CR6.
  • the second cylinder head part 8 is designed as a flange 8.
  • the second cylinder head part 8 may be formed of a low-cost material.
  • the second cylinder head part 8 is formed of a low pressure resistant material.
  • the housing 2 has a plunger bore 10.
  • the first cylinder head part 7 of the cylinder head 6 has a projection 11 which extends into the plunger bore 10.
  • the first cylinder head part 7 has a cylinder bore 12 in which a pump piston 13 is guided.
  • the pump piston 13 is in this case part of a pump assembly 14, which is arranged in the region of the plunger bore 10 and the the Cam 4 is assigned.
  • the cam 4 acts in a suitable manner on the pump piston 13, as illustrated by the double arrow 15. For example, via a plunger body, a roller shoe inserted into the plunger body and a roller mounted in the roller shoe, which runs on a running surface of the cam 4, an operative connection between the cam 4 and the pump piston 13 for driving the pump assembly 14 may be provided.
  • a provision of such a plunger body can in this case take place via a plunger spring 16, which surrounds the projection 11 in sections. This results during the rotation of the drive shaft 3 about its axis of rotation 5 to a reciprocating motion of the pump piston 13 in the cylinder bore 12th
  • pump working chamber 18 At the end of the cylinder bore 12 a limited by an end face 17 pump working chamber 18 is formed.
  • the pump working space 18 is configured in the first cylinder head part 7.
  • the pump piston 13 is guided in operation along an axis 19 of the pump assembly 14, wherein the axis 19 is determined by the cylinder bore 12.
  • the housing 2 of the high-pressure pump 1 has an end face 25.
  • the cylinder head 6 is placed on the end face 25 of the housing 2.
  • the first cylinder head part 7 has a circumferential collar 26 in the region of its projection 11. With the encircling collar 26, the first cylinder head part 7 is supported on the end face 25 of the housing 2.
  • the second cylinder head part 8 has a contact surface 27 which rests against the front side 25 of the housing 2.
  • the second cylinder head part 8 is fixed to the housing 2.
  • the second cylinder head part 8 also fixes the first cylinder head part 7 on the housing 2.
  • the entire cylinder head 6 is fastened to the housing 2.
  • the first cylinder head part 7 has a connecting piece 28, which is oriented at least approximately perpendicular to the axis 19. At the nozzle 28, a high-pressure port 29 is formed. Further, a stepped bore 30 is formed on the nozzle 28, which forms a fuel channel 31.
  • a valve ball 33 of the outlet valve 32 is arranged in the region of a conical step of the stepped bore 30.
  • the second cylinder head part 8 has a recess 34 with a threaded portion 35.
  • a valve piece 36 is inserted in the recess 34.
  • Via a screw ring 37 which is screwed into the threaded portion 35, the valve piece 36 is acted upon against an end face 38 of the first cylinder head part 7.
  • a Sealing ring 39 is provided in the area of the end face 38 , which ensures a seal.
  • a valve stem 40 is provided, which is acted upon by a valve spring 41. Between the valve stem 40 and a valve seat surface 42, a sealing seat is formed.
  • a fuel passage 43 is configured, which in this embodiment is connected to a further passage section 44.
  • the channel section 44 is configured here in the housing 2.
  • a sealing ring 45 is arranged to seal the transition from the channel portion 44 of the housing 2 to the fuel channel 43 of the second cylinder head part 8.
  • inlet valve 46 Via the fuel channel 43, low-pressure fuel is led to an inlet valve 46, which is configured by the valve piece 36, the screw ring 37, the valve stem 40 and the valve spring 41.
  • the intake valve 46 can be integrated into the second cylinder head part 8 in this way.
  • a high pressure line may be mounted to guide the high pressure fuel to a common rail or the like.
  • the second cylinder head part 8 of the cylinder head 6 is only loaded by the low pressure of the fuel under low pressure.
  • the first cylinder head part 7 is loaded by the high pressure of the high pressure fuel delivered by the pump piston 13.
  • the first cylinder head part 7 is made of a high-pressure-resistant material, in particular a high-grade steel.
  • the second cylinder head part 8 can be made of a cost-effective material, which only has to be low-pressure resistant.
  • the configuration of the high pressure pump 1 of the embodiment is hereinafter also with reference to the Fig. 2 described in further detail.
  • Fig. 2 shows the in Fig. 1 illustrated high-pressure pump 1 in an excerpt, schematic representation of the designated II viewing direction.
  • the second cylinder head part 8 of the cylinder head 6 has an edge 50.
  • four holes 51, 52, 53, 54 are configured on the edge 50.
  • the Holes 51 to 54 are distributed uniformly with respect to the axis 19 in the circumferential direction at the edge 50. Between adjacent holes 51 to 54 is given with respect to the axis 19, a distance of 90 °.
  • Through the bores 51 to 54 extend screws 51 ', 52', 53 ', 54', which are screwed into suitable threaded holes of the housing 2.
  • the cylinder head 6 is bolted to the housing 2.
  • the high pressure port 29 on the nozzle 28 of the first cylinder head part 7 is disposed between the bores 51, 54.
  • the cylinder head 6 can also be screwed in a different position to the housing 2.
  • the position of the high-pressure port 29 can be changed.
  • the high-pressure port 29 can be pivoted with respect to the axis 19 by 90 ° or by multiples of 90 °.
  • the bore 51 is offset relative to the axis 55 of the nozzle 28 by an angle 56 of 45 °.
  • the second cylinder head part 8 has a lateral recess 57, which serves to receive the lateral neck 28 of the first cylinder head part 7.
  • a simple assembly of the cylinder head 6 from the two cylinder head parts 7, 8 is possible.
  • the flange 8 can be designed to be open, so that joining of the first cylinder head part 7 into the second cylinder head part 8 is possible.
  • the second cylinder head part 8 is open and closed by the inlet valve 46.
  • the inlet valve 46 is designed here as a suction valve.
  • the one-piece design of the first cylinder head part 7 with the integrated outlet valve 32 has the advantage that a high strength can be achieved.
  • four different positions for the exhaust valve 32 and the downstream high-pressure portion 29 can be realized.
  • a different number of positions is possible. This can be realized by a suitable design of holes on the edge 50 of the second cylinder head part 8.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Hochdruckpumpe, insbesondere eine Radial- oder Reihenkolbenpumpe. Speziell betrifft die Erfindung das Gebiet der Brennstoffpumpen für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.

Aus der EP 1 013 921 A2 ist eine Brennstoffpumpe mit einem Gehäuse und einer in dem Gehäuse gelagerten Antriebswelle bekannt. Hierbei sind zwei gegenüberliegend zueinander angeordnete Zylinderköpfe vorgesehen, die an dem Gehäuse befestigt sind. In die Zylinderköpfe ist hierbei jeweils ein Einlassventil und ein Auslassventil integriert. Ferner sind nach den Auslassventilen der Zylinderköpfe Hochdruckanschlüsse vorgesehen, die in den jeweiligen Zylinderkopf eingeschraubt sind.From the EP 1 013 921 A2 For example, a fuel pump with a housing and a drive shaft mounted in the housing is known. Here, two oppositely arranged cylinder heads are provided, which are fixed to the housing. In the cylinder heads in each case an intake valve and an exhaust valve is integrated. Further, after the exhaust valves of the cylinder heads, high pressure ports are provided, which are screwed into the respective cylinder head.

Die aus der EP 1 013 921 A2 bekannte Brennstoffpumpe hat den Nachteil, dass die Herstellungskosten relativ hoch sind. Speziell müssen zur Ausgestaltung der Zylinderköpfe hochdruckfeste Werkstoffe zum Einsatz kommen und es ist eine Bearbeitung dieser hochdruckfesten Werkstoffe erforderlich.The from the EP 1 013 921 A2 known fuel pump has the disadvantage that the production costs are relatively high. Specifically, high pressure resistant materials must be used for the design of the cylinder heads and it is a processing of these high pressure resistant materials required.

Ferner sind aus der EP 2 112 368 A2 , der DE 197 19 265 A1 und der WO 87/00582 A1 Kraftstoffpumpen, insbesondere Steckpumpen, mit mehrteiligen Pumpengehäusen zur Befestigung an einem Gehäuse einer Brennkraftmaschine bekannt.Furthermore, from the EP 2 112 368 A2 , of the DE 197 19 265 A1 and the WO 87/00582 A1 Fuel pumps, in particular plug-in pumps, with multi-part pump housings for attachment to a housing of an internal combustion engine known.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass die Herstellungskosten verringert sind. Speziell ist der Material- und Bearbeitungsaufwand zur Ausgestaltung des Zylinderkopfes verringert. Dieser Vorteil vervielfacht sich mit der Anzahl der an der Hochdruckpumpe vorgesehenen Zylinderköpfe.The high pressure pump according to the invention with the features of claim 1 has the advantage that the manufacturing cost is reduced. Specifically, the material and processing costs for the design of the cylinder head is reduced. This advantage is multiplied by the number of cylinder heads provided on the high-pressure pump.

Vorteilhaft ist es auch, dass an dem ersten Zylinderkopfteil ein Auslassventil angeordnet ist und dass in dem ersten Zylinderkopfteil ein Brennstoffkanal ausgebildet ist, der von dem Pumpenarbeitsraum zu dem Auslassventil führt. Hierbei ist es ferner von Vorteil, dass erfindungsgemäß der Brennstoffkanal durch eine in dem ersten Zylinderkopfteil ausgebildete Stufenbohrung ausgestaltet ist und dass das Auslassventil in der Stufenbohrung ausgebildet ist. Hierdurch kann das Auslassventil in vorteilhafter Weise in das erste Zylinderkopfteil integriert werden. Das Auslassventil kann hierbei als Rückschlagventil ausgestaltet sein. Beispielsweise kann das erste Zylinderkopfteil als Schmiedeteil ausgestaltet sein, so dass sich erhebliche Vorteile bezüglich der Festigkeit des ersten Zylinderkopfteils ergeben. Das zweite Zylinderkopfteil kann hingegen aus einem günstigen Material gebildet sein, insbesondere aus einem nicht gehärteten Material, so dass sich diesbezüglich eine Kostenreduktion in Bezug auf den zusammengesetzten Zylinderkopf ergibt.It is also advantageous that an outlet valve is arranged on the first cylinder head part and that in the first cylinder head part a fuel channel is formed which leads from the pump working chamber to the outlet valve. In this case, it is also advantageous that according to the invention the fuel channel is configured by a stepped bore formed in the first cylinder head part and that the outlet valve is formed in the stepped bore. As a result, the exhaust valve can be integrated in an advantageous manner in the first cylinder head part. The outlet valve can be designed as a check valve. For example, the first cylinder head part may be designed as a forged part, so that there are considerable advantages in terms of the strength of the first cylinder head part. On the other hand, the second cylinder head part may be formed from a favorable material, in particular from a non-hardened material, so that in this respect a cost reduction with respect to the assembled cylinder head results.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der im Anspruch 1 angegebenen Hochdruckpumpe möglich.The measures listed in the dependent claims advantageous refinements of the claim 1 high-pressure pump are possible.

In vorteilhafter Weise umfasst die Hochdruckpumpe ein Gehäuse, an das der Zylinderkopf montiert ist. Hierbei können auch mehrere Zylinderköpfe vorgesehen sein, die an das Gehäuse montiert sind. Hierbei kann der Vorteil einer Ausgestaltung des Zylinderkopfes aus einem ersten Zylinderkopfteil und zumindest einem zweiten Zylinderkopfteil mehrfach ausgenutzt werden. Das Gehäuse der Hochdruckpumpe kann ein oder mehrteilig ausgestaltet sein.Advantageously, the high pressure pump comprises a housing to which the cylinder head is mounted. In this case, a plurality of cylinder heads may be provided, which are mounted on the housing. Here, the advantage of an embodiment of the cylinder head from a first cylinder head part and at least one second cylinder head part can be exploited several times. The housing of the high pressure pump can be configured in one or more parts.

Vorteilhaft ist es, dass die Pumpenbaugruppe eine in dem ersten Zylinderkopfteil ausgestaltete Zylinderbohrung und einen in der Zylinderbohrung geführten Pumpenkolben aufweist, dass der Pumpenkolben in der Zylinderbohrung den Pumpenarbeitsraum begrenzt und dass der Pumpenkolben von der Antriebswelle antreibbar ist. Hierdurch kann in vorteilhafter Weise eine hohe Stabilität des ersten Zylinderkopfteils ausgenutzt werden, um die Zylinderbohrung mit dem Pumpenarbeitsraum zu bilden. Ferner ist es vorteilhaft, dass an dem zweiten Zylinderkopfteil ein Einlassventil angeordnet ist und dass das Einlassventil den Pumpenarbeitsraum begrenzt. Hierbei können ein oder mehrere Bauteile des Einlassventils den Pumpenarbeitsraum begrenzen. Beispielsweise kann das Einlassventil in geeigneter Weise auf eine Stirnseite des ersten Zylinderkopfteils aufgesetzt sein. Eine Befestigung des Einlassventils an dem ersten Zylinderkopfteil kann über das zweite Zylinderkopfteil erfolgen.It is advantageous that the pump assembly has a cylinder bore configured in the first cylinder head part and a pump piston guided in the cylinder bore, that the pump piston in the cylinder bore limits the pump working space and that the pump piston can be driven by the drive shaft. As a result, a high stability of the first cylinder head part can advantageously be utilized in order to form the cylinder bore with the pump working space. Furthermore, it is advantageous that an inlet valve is arranged on the second cylinder head part and that the inlet valve limits the pump working space. In this case, one or more components of the inlet valve can limit the pump working space. For example, the inlet valve may be suitably placed on an end face of the first cylinder head part. An attachment of the intake valve to the first cylinder head part can take place via the second cylinder head part.

Hierfür kann das zweite Zylinderkopfteil eine geeignete Aufnahme aufweisen, in der das Einlassventil angeordnet ist.For this purpose, the second cylinder head part may have a suitable receptacle in which the inlet valve is arranged.

Vorteilhaft ist es auch, dass das zweite Zylinderkopfteil als Flansch ausgestaltet ist und dass das zweite Zylinderkopfteil an dem Gehäuse in zumindest zwei verschiedenen Anschraubpositionen anschraubbar ist. Speziell können vier Anschraubpositionen vorgesehen sein. Hierbei ist es ferner vorteilhaft, dass sich die Anschraubpositionen durch eine Drehung des Zylinderkopfes um eine Achse der Pumpenbaugruppe voneinander unterscheiden. Beispielsweise kann durch Drehen des Zylinderkopfes um 90° oder um ganzzahlige Vielfache von 90° eine gewisse Variabilität mit vier möglichen Anschraubpositionen erzielt werden. In Bezug auf den jeweiligen Anwendungsfall kann dann eine geeignete Ausrichtung des Zylinderkopfes bezüglich des Gehäuses der Hochdruckpumpe erfolgen, Speziell kann dadurch das Auslassventil beziehungsweise ein hinter dem Auslassventil vorgesehener Hochdruckanschluss der Hochdruckpumpe in Bezug auf den jeweiligen Anwendungsfall ausgerichtet werden.It is also advantageous that the second cylinder head part is configured as a flange and that the second cylinder head part can be screwed to the housing in at least two different screw-on positions. Specifically, four screw-on positions can be provided. Here, it is also advantageous that the Anschraubpositionen differ by rotation of the cylinder head about an axis of the pump assembly from each other. For example, by rotating the cylinder head by 90 ° or by integer multiples of 90 ° a certain variability can be achieved with four possible Anschraubpositionen. In relation to the particular application, a suitable alignment of the cylinder head with respect to the housing of the high-pressure pump can then take place. Specifically, this makes it possible to align the outlet valve or a high-pressure connection of the high-pressure pump provided behind the outlet valve with respect to the respective application.

Vorteilhaft ist es auch, dass das zweite Zylinderkopfteil eine seitliche Ausnehmung aufweist, die zum Aufnehmen eines seitlichen Stutzens des ersten Zylinderkopfteils dient. An dem seitlichen Stutzen des ersten Zylinderkopfteils kann der Hochdruckanschluss vorgesehen sein. Hierdurch kann der Zylinderkopf in einfacher Weise zusammengesetzt werden.It is also advantageous that the second cylinder head part has a lateral recess, which serves for receiving a lateral neck of the first cylinder head part. At the lateral neck of the first cylinder head part of the high pressure port can be provided. As a result, the cylinder head can be assembled in a simple manner.

Vorteilhaft ist es auch, dass das erste Zylinderkopfteil aus einem hochdruckfesten Werkstoff gebildet ist und dass das zweite Zylinderkopfteil aus einem niederdruckfesten Werkstoff gebildet ist. Speziell kann das erste Zylinderkopfteil aus einem hochwertigen Stahl, beispielsweise 100CR6 hergestellt sein. Das zweite Zylinderkopfteil kann aus einem kostengünstigen Werkstoff gebildet sein. Das zweite Zylinderkopfteil kann hierbei das erste Zylinderkopfteil und somit den Zylinderkopf fixieren und den Niederdruckkreislauf tragen.It is also advantageous that the first cylinder head part is formed from a high pressure resistant material and that the second cylinder head part is formed from a low pressure resistant material. Specifically, the first cylinder head portion may be made of a high grade steel, such as 100CR6. The second cylinder head part may be formed from a low-cost material. The second cylinder head part can in this case fix the first cylinder head part and thus the cylinder head and carry the low-pressure circuit.

Speziell kann der Zylinderkopf als zweiteiliger Zylinderkopf ausgebildet sein, der aus dem ersten Zylinderkopfteil und dem zweiten Zylinderkopfteil zusammengesetzt ist. Hierbei können noch Dichtringe und dergleichen in den Zylinderkopf integriert sein, die im zusammengesetzten Zustand die erforderliche Dichtheit an den Schnittstellen ermöglichen. Kurze Beschreibung der ZeichnungenSpecifically, the cylinder head may be formed as a two-part cylinder head, which is composed of the first cylinder head part and the second cylinder head part. In this case, sealing rings and the like may be integrated into the cylinder head, which allow the required tightness at the interfaces in the assembled state. Brief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 eine Hochdruckpumpe in einer auszugsweisen, schematischen, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung und Fig. 2 die in Fig. 1 dargestellte Hochdruckpumpe in einer schematischen Darstellung aus der mit II bezeichneten Blickrichtung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a high pressure pump in a partial, schematic, axial sectional view according to an embodiment of the invention and Fig. 2 in the Fig. 1 shown high-pressure pump in a schematic representation of the designated II viewing direction.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine Hochdruckpumpe 1 in einer auszugsweisen, schematischen, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung. Die Hochdruckpumpe 1 kann insbesondere als Radial- oder Reihenkolbenpumpe ausgestaltet sein. Speziell eignet sich die Hochdruckpumpe 1 als Brennstoffpumpe für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen. Ein bevorzugter Einsatz der Hochdruckpumpe 1 besteht für eine Brennstoffeinspritzanlage mit einem Common-Rail, das Dieselbrennstoff unter hohem Druck speichert. Die erfindungsgemäße Hochdruckpumpe 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a high pressure pump 1 in a partial, schematic, axial sectional view according to an embodiment of the invention. The high pressure pump 1 can be configured in particular as a radial or inline piston pump. Specifically, the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the high-pressure pump 1 is for a fuel injection system with a common rail that stores diesel fuel under high pressure. However, the high-pressure pump 1 according to the invention is also suitable for other applications.

Die Hochdruckpumpe 1 weist ein Gehäuse 2 auf, das ein- oder mehrteilig ausgestaltet sein kann. Ferner ist eine Antriebswelle 3 vorgesehen, die auf geeignete Weise in dem Gehäuse 2 gelagert ist. Die Antriebswelle 3 weist einen Nocken 4 auf. Im Betrieb rotiert die Antriebswelle 3 um ihre Drehachse 5. Hierbei rotiert der Nocken 4 mit der Antriebswelle 3. Der Nocken 4 kann als Ein- oder Mehrfachnocken ausgestaltet sein. Ferner kann der Nocken 4 auch durch einen exzentrischen Abschnitt der Antriebswelle 3 gebildet sein. Je nach Ausgestaltung der Hochdruckpumpe 1 können auch weitere Nocken an der Antriebswelle 3 vorgesehen sein. Das Gehäuse 2 kann auch ein Gehäuse einer Brennkraftmaschine sein, beispielsweise deren Zylinderkopf, und die Antriebswelle 3 kann eine Nockenwelle der Brennkraftmaschine sein, durch die deren Gaswechselventile betätigt werden und die den oder die Nocken 4 für die Hochdruckpumpe 1 aufweist.The high-pressure pump 1 has a housing 2, which may be configured in one or more parts. Further, a drive shaft 3 is provided, which is mounted in a suitable manner in the housing 2. The drive shaft 3 has a cam 4. In operation, the drive shaft 3 rotates about its axis of rotation 5. Here, the cam 4 rotates with the drive shaft 3. The cam 4 can be configured as a single or multiple cam. Further, the cam 4 may also be formed by an eccentric portion of the drive shaft 3. Depending on the configuration of the high-pressure pump 1, further cams may be provided on the drive shaft 3. The housing 2 may also be a housing of an internal combustion engine, for example, the cylinder head, and the drive shaft 3 may be a camshaft of the internal combustion engine, are actuated by the gas exchange valves and the cam or the cam 4 for the high pressure pump 1.

Die Hochdruckpumpe 1 weist außerdem einen Zylinderkopf 6 auf. Der Zylinderkopf 6 ist aus einem ersten Zylinderkopfteil 7 und einem zweiten Zylinderkopfteil 8 zusammengesetzt. Hierbei ist das erste Zylinderkopfteil 7 aus einem hochdruckfesten Werkstoff gebildet. Beispielsweise kann das erste Zylinderkopfteil 7 aus einem hochwertigen Stahl, insbesondere 100CR6 hergestellt sein. Das zweite Zylinderkopfteil 8 ist als Flansch 8 ausgestaltet. Hierbei kann das zweite Zylinderkopfteil 8 aus einem günstigen Werkstoff gebildet sein. Speziell ist das zweite Zylinderkopfteil 8 aus einem niederdruckfesten Werkstoff gebildet.The high-pressure pump 1 also has a cylinder head 6. The cylinder head 6 is composed of a first cylinder head part 7 and a second cylinder head part 8. Here, the first cylinder head part 7 is formed of a high pressure resistant material. For example, the first cylinder head part 7 may be made of a high-grade steel, in particular 100CR6. The second cylinder head part 8 is designed as a flange 8. Here, the second cylinder head part 8 may be formed of a low-cost material. Specifically, the second cylinder head part 8 is formed of a low pressure resistant material.

Das Gehäuse 2 weist eine Stößelbohrung 10 auf. Das erste Zylinderkopfteil 7 des Zylinderkopfes 6 weist einen Ansatz 11 auf, der sich in die Stößelbohrung 10 erstreckt. Außerdem weist das erste Zylinderkopfteil 7 eine Zylinderbohrung 12 auf, in der ein Pumpenkolben 13 geführt ist. Der Pumpenkolben 13 ist hierbei Teil einer Pumpenbaugruppe 14, die im Bereich der Stößelbohrung 10 angeordnet ist und die dem Nocken 4 zugeordnet ist. Der Nocken 4 wirkt auf geeignete Weise auf den Pumpenkolben 13 ein, wie es durch den Doppelpfeil 15 veranschaulicht ist. Beispielsweise kann über einen Stößelkörper, einen in den Stößelkörper eingesetzten Rollenschuh und eine in dem Rollenschuh gelagerte Rolle, die auf einer Lauffläche des Nockens 4 läuft, eine Wirkverbindung zwischen dem Nocken 4 und dem Pumpenkolben 13 zum Antreiben der Pumpenbaugruppe 14 geschaffen sein. Eine Rückstellung solch eines Stößelkörpers kann hierbei über eine Stößelfeder 16 erfolgen, die den Ansatz 11 abschnittsweise umschließt. Hierdurch kommt es während der Rotation der Antriebswelle 3 um ihre Drehachse 5 zu einer Hin- und Herbewegung des Pumpenkolbens 13 in der Zylinderbohrung 12.The housing 2 has a plunger bore 10. The first cylinder head part 7 of the cylinder head 6 has a projection 11 which extends into the plunger bore 10. In addition, the first cylinder head part 7 has a cylinder bore 12 in which a pump piston 13 is guided. The pump piston 13 is in this case part of a pump assembly 14, which is arranged in the region of the plunger bore 10 and the the Cam 4 is assigned. The cam 4 acts in a suitable manner on the pump piston 13, as illustrated by the double arrow 15. For example, via a plunger body, a roller shoe inserted into the plunger body and a roller mounted in the roller shoe, which runs on a running surface of the cam 4, an operative connection between the cam 4 and the pump piston 13 for driving the pump assembly 14 may be provided. A provision of such a plunger body can in this case take place via a plunger spring 16, which surrounds the projection 11 in sections. This results during the rotation of the drive shaft 3 about its axis of rotation 5 to a reciprocating motion of the pump piston 13 in the cylinder bore 12th

Am Ende der Zylinderbohrung 12 ist ein durch eine Stirnfläche 17 begrenzter Pumpenarbeitsraum 18 ausgebildet. Der Pumpenarbeitsraum 18 ist in dem ersten Zylinderkopfteil 7 ausgestaltet. Der Pumpenkolben 13 ist im Betrieb entlang einer Achse 19 der Pumpenbaugruppe 14 geführt, wobei die Achse 19 durch die Zylinderbohrung 12 bestimmt ist.At the end of the cylinder bore 12 a limited by an end face 17 pump working chamber 18 is formed. The pump working space 18 is configured in the first cylinder head part 7. The pump piston 13 is guided in operation along an axis 19 of the pump assembly 14, wherein the axis 19 is determined by the cylinder bore 12.

Das Gehäuse 2 der Hochdruckpumpe 1 weist eine Stirnseite 25 auf. Der Zylinderkopf 6 ist auf die Stirnseite 25 des Gehäuses 2 aufgesetzt. Das erste Zylinderkopfteil 7 weist einen umlaufenden Bund 26 im Bereich seines Ansatzes 11 auf. Mit dem umlaufenden Bund 26 stützt sich das erste Zylinderkopfteil 7 an der Stirnseite 25 des Gehäuses 2 ab. Ferner weist das zweite Zylinderkopfteil 8 eine Anlagefläche 27 auf, die an der Stirnseite 25 des Gehäuses 2 anliegt. Das zweite Zylinderkopfteil 8 ist an dem Gehäuse 2 befestigt. Hierdurch fixiert das zweite Zylinderkopfteil 8 auch das erste Zylinderkopfteil 7 an dem Gehäuse 2. Dadurch ist der gesamte Zylinderkopf 6 an dem Gehäuse 2 befestigt.The housing 2 of the high-pressure pump 1 has an end face 25. The cylinder head 6 is placed on the end face 25 of the housing 2. The first cylinder head part 7 has a circumferential collar 26 in the region of its projection 11. With the encircling collar 26, the first cylinder head part 7 is supported on the end face 25 of the housing 2. Furthermore, the second cylinder head part 8 has a contact surface 27 which rests against the front side 25 of the housing 2. The second cylinder head part 8 is fixed to the housing 2. As a result, the second cylinder head part 8 also fixes the first cylinder head part 7 on the housing 2. As a result, the entire cylinder head 6 is fastened to the housing 2.

Das erste Zylinderkopfteil 7 weist einen Stutzen 28 auf, der zumindest näherungsweise senkrecht zu der Achse 19 orientiert ist. An dem Stutzen 28 ist ein Hochdruckanschluss 29 ausgebildet. Ferner ist an dem Stutzen 28 eine Stufenbohrung 30 ausgebildet, die einen Brennstoffkanal 31 bildet. Hierbei ist in dem Stutzen 28 des ersten Zylinderkopfteils 7 ein als Rückschlagventil ausgestaltetes Auslassventil 32 integriert. Hierbei ist im Bereich einer konischen Stufe der Stufenbohrung 30 eine Ventilkugel 33 des Auslassventils 32 angeordnet. Somit kann in vorteilhafter Weise das Auslassventil 32 in das erste Zylinderkopfteil 7 integriert werden.The first cylinder head part 7 has a connecting piece 28, which is oriented at least approximately perpendicular to the axis 19. At the nozzle 28, a high-pressure port 29 is formed. Further, a stepped bore 30 is formed on the nozzle 28, which forms a fuel channel 31. Here, in the neck 28 of the first cylinder head part 7 designed as a check valve outlet valve 32 is integrated. In this case, a valve ball 33 of the outlet valve 32 is arranged in the region of a conical step of the stepped bore 30. Thus, the exhaust valve 32 can be integrated into the first cylinder head part 7 in an advantageous manner.

Das zweite Zylinderkopfteil 8 weist eine Aussparung 34 mit einem Gewindeabschnitt 35 auf. In die Aussparung 34 ist ein Ventilstück 36 eingesetzt. Über einen Schraubring 37, der in den Gewindeabschnitt 35 eingeschraubt ist, wird das Ventilstück 36 gegen eine Stirnseite 38 des ersten Zylinderkopfteils 7 beaufschlagt. Hierbei ist im Bereich der Stirnseite 38 ein Dichtring 39 vorgesehen, der eine Abdichtung gewährleistet. Ferner ist ein Ventilstößel 40 vorgesehen, der von einer Ventilfeder 41 beaufschlagt ist. Zwischen dem Ventilstößel 40 und einer Ventilsitzfläche 42 ist ein Dichtsitz gebildet. Außerdem ist in dem zweiten Zylinderkopfteil 8 ein Brennstoffkanal 43 ausgestaltet, der in diesem Ausführungsbeispiel mit einem weiteren Kanalabschnitt 44 verbunden ist. Der Kanalabschnitt 44 ist hierbei in dem Gehäuse 2 ausgestaltet. Im Bereich der Stirnseite 25 ist ein Dichtring 45 angeordnet, um den Übergang von dem Kanalabschnitt 44 des Gehäuses 2 auf den Brennstoffkanal 43 des zweiten Zylinderkopfteils 8 abzudichten.The second cylinder head part 8 has a recess 34 with a threaded portion 35. In the recess 34, a valve piece 36 is inserted. Via a screw ring 37, which is screwed into the threaded portion 35, the valve piece 36 is acted upon against an end face 38 of the first cylinder head part 7. Here, in the area of the end face 38 a Sealing ring 39 is provided, which ensures a seal. Further, a valve stem 40 is provided, which is acted upon by a valve spring 41. Between the valve stem 40 and a valve seat surface 42, a sealing seat is formed. In addition, in the second cylinder head part 8, a fuel passage 43 is configured, which in this embodiment is connected to a further passage section 44. The channel section 44 is configured here in the housing 2. In the region of the front side 25, a sealing ring 45 is arranged to seal the transition from the channel portion 44 of the housing 2 to the fuel channel 43 of the second cylinder head part 8.

Über den Brennstoffkanal 43 wird unter niedrigem Druck stehender Brennstoff zu einem Einlassventil 46 geführt, das durch das Ventilstück 36, den Schraubring 37, den Ventilstößel 40 und die Ventilfeder 41 ausgestaltet ist. Das Einlassventil 46 kann auf diese Weise in das zweite Zylinderkopfteil 8 integriert werden.Via the fuel channel 43, low-pressure fuel is led to an inlet valve 46, which is configured by the valve piece 36, the screw ring 37, the valve stem 40 and the valve spring 41. The intake valve 46 can be integrated into the second cylinder head part 8 in this way.

Bei einem Saughub des Pumpenkolbens 13 wird Brennstoff aus dem Brennstoffkanal 43 über das Einlassventil 46 in den Pumpenarbeitsraum 18 geführt. Bei einem anschließenden Förderhub wird der Brennstoff aus dem Pumpenarbeitsraum 18 über den Brennstoffkanal 31 und das Auslassventil 32 zu dem Hochdruckanschluss 29 geführt. An dem Hochdruckanschluss 29 kann eine Hochdruckleitung angebracht sein, um den unter hohem Druck stehenden Brennstoff zu einem Common-Rail oder dergleichen zu führen.During a suction stroke of the pump piston 13, fuel is guided out of the fuel channel 43 via the inlet valve 46 into the pump working chamber 18. During a subsequent delivery stroke, the fuel is led out of the pump working chamber 18 via the fuel channel 31 and the outlet valve 32 to the high-pressure port 29. At the high pressure port 29, a high pressure line may be mounted to guide the high pressure fuel to a common rail or the like.

Im Betrieb der Hochdruckpumpe 1 wird das zweite Zylinderkopfteil 8 des Zylinderkopfes 6 lediglich von dem Niederdruck des unter niedrigen Druck stehenden Brennstoffs belastet. Das erste Zylinderkopfteil 7 wird hingegen von dem Hochdruck des von dem Pumpenkolben 13 geförderten, unter hohem Druck stehenden Brennstoffs belastet. Das erste Zylinderkopfteil 7 ist aus einem hochdruckbeständigen Werkstoff, insbesondere einem hochwertigen Stahl, gebildet. Das zweite Zylinderkopfteil 8 kann aus einem kostengünstigen Werkstoff hergestellt werden, der lediglich niederdruckbeständig sein muss. Somit ergibt sich durch die zweiteilige Ausgestaltung des Zylinderkopfes 6 eine Reduzierung des Herstellungsaufwands und der Herstellungskosten.During operation of the high pressure pump 1, the second cylinder head part 8 of the cylinder head 6 is only loaded by the low pressure of the fuel under low pressure. By contrast, the first cylinder head part 7 is loaded by the high pressure of the high pressure fuel delivered by the pump piston 13. The first cylinder head part 7 is made of a high-pressure-resistant material, in particular a high-grade steel. The second cylinder head part 8 can be made of a cost-effective material, which only has to be low-pressure resistant. Thus, due to the two-part design of the cylinder head 6, a reduction of the production costs and the manufacturing costs.

Die Ausgestaltung der Hochdruckpumpe 1 des Ausführungsbeispiels ist im Folgenden auch unter Bezugnahme auf die Fig. 2 im weiteren Detail beschrieben.The configuration of the high pressure pump 1 of the embodiment is hereinafter also with reference to the Fig. 2 described in further detail.

Fig. 2 zeigt die in Fig. 1 dargestellte Hochdruckpumpe 1 in einer auszugsweisen, schematischen Darstellung aus der mit II bezeichneten Blickrichtung. Das zweite Zylinderkopfteil 8 des Zylinderkopfs 6 weist einen Rand 50 auf. In diesem Ausführungsbeispiel sind an dem Rand 50 vier Bohrungen 51, 52, 53, 54 ausgestaltet. Die Bohrungen 51 bis 54 sind dabei bezüglich der Achse 19 in Umfangsrichtung gleichmäßig an dem Rand 50 verteilt. Zwischen benachbarten Bohrungen 51 bis 54 ist in Bezug auf die Achse 19 ein Abstand von 90° gegeben. Durch die Bohrungen 51 bis 54 erstrecken sich Schrauben 51', 52', 53', 54', die in geeignete Gewindebohrungen des Gehäuses 2 eingeschraubt sind. Somit ist der Zylinderkopf 6 mit dem Gehäuse 2 verschraubt. Fig. 2 shows the in Fig. 1 illustrated high-pressure pump 1 in an excerpt, schematic representation of the designated II viewing direction. The second cylinder head part 8 of the cylinder head 6 has an edge 50. In this embodiment, four holes 51, 52, 53, 54 are configured on the edge 50. The Holes 51 to 54 are distributed uniformly with respect to the axis 19 in the circumferential direction at the edge 50. Between adjacent holes 51 to 54 is given with respect to the axis 19, a distance of 90 °. Through the bores 51 to 54 extend screws 51 ', 52', 53 ', 54', which are screwed into suitable threaded holes of the housing 2. Thus, the cylinder head 6 is bolted to the housing 2.

Der Hochdruckanschluss 29 am Stutzen 28 des ersten Zylinderkopfteils 7 ist zwischen den Bohrungen 51, 54 angeordnet. Der Zylinderkopf 6 kann auch in einer anderen Position an das Gehäuse 2 angeschraubt werden. Hierdurch kann die Position des Hochdruckanschlusses 29 verändert werden. In diesem Ausführungsbeispiel kann der Hochdruckanschluss 29 in Bezug auf die Achse 19 um 90° oder um Vielfache von 90° verschwenkt angeordnet werden. Dies ist durch eine versetzte Verschraubung des zweiten Zylinderkopfteils 8 mit dem ersten Zylinderkopfteil 7 an dem Gehäuse 2 möglich. Vorzugsweise ist die Bohrung 51 gegenüber der Achse 55 des Stutzens 28 um einen Winkel 56 von 45° versetzt angeordnet. Außerdem weist das zweite Zylinderkopfteil 8 eine seitliche Ausnehmung 57 auf, die zum Aufnehmen des seitlichen Stutzens 28 des ersten Zylinderkopfteils 7 dient. Hierdurch ist ein einfaches Zusammensetzen des Zylinderkopfes 6 aus den beiden Zylinderkopfteilen 7, 8 möglich.The high pressure port 29 on the nozzle 28 of the first cylinder head part 7 is disposed between the bores 51, 54. The cylinder head 6 can also be screwed in a different position to the housing 2. As a result, the position of the high-pressure port 29 can be changed. In this embodiment, the high-pressure port 29 can be pivoted with respect to the axis 19 by 90 ° or by multiples of 90 °. This is possible by an offset screw connection of the second cylinder head part 8 with the first cylinder head part 7 on the housing 2. Preferably, the bore 51 is offset relative to the axis 55 of the nozzle 28 by an angle 56 of 45 °. In addition, the second cylinder head part 8 has a lateral recess 57, which serves to receive the lateral neck 28 of the first cylinder head part 7. As a result, a simple assembly of the cylinder head 6 from the two cylinder head parts 7, 8 is possible.

Somit kann im Bereich des Auslassventils 32 der Flansch 8 offen ausgestaltet sein, so dass ein Fügen des ersten Zylinderkopfteils 7 in das zweite Zylinderkopfteil 8 möglich ist. Nach oben ist das zweite Zylinderkopfteil 8 offen und durch das Einlassventil 46 geschlossen. Das Einlassventil 46 ist hierbei als Saugventil ausgestaltet.Thus, in the region of the outlet valve 32, the flange 8 can be designed to be open, so that joining of the first cylinder head part 7 into the second cylinder head part 8 is possible. Upwards, the second cylinder head part 8 is open and closed by the inlet valve 46. The inlet valve 46 is designed here as a suction valve.

Die einstückige Ausgestaltung des ersten Zylinderkopfteils 7 mit dem integrierten Auslassventil 32, beispielsweise als Schmiedeteil, hat den Vorteil, dass eine hohe Festigkeit erzielbar ist. In diesem Ausführungsbeispiel können vier verschiedene Positionen für das Auslassventil 32 und den nachgeordneten Hochdruckanteil 29 realisiert werden. Hierbei ist auch eine andere Anzahl an Positionen möglich. Dies kann durch eine geeignete Ausgestaltung von Bohrungen an dem Rand 50 des zweiten Zylinderkopfteils 8 realisiert werden.The one-piece design of the first cylinder head part 7 with the integrated outlet valve 32, for example, as a forged part, has the advantage that a high strength can be achieved. In this embodiment, four different positions for the exhaust valve 32 and the downstream high-pressure portion 29 can be realized. Here also a different number of positions is possible. This can be realized by a suitable design of holes on the edge 50 of the second cylinder head part 8.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (8)

  1. High-pressure pump, in particular radial or in-line piston pump for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a housing (2), having a drive shaft (3) mounted in the housing (2), having at least one cylinder head (6) which is connected to the housing (2), and having at least one pump assembly (14) which is arranged on the cylinder head (6) and which can be driven by the drive shaft (3), wherein the cylinder head (6) has a first cylinder head part (7) and at least one second cylinder head part (8), wherein the pump assembly (14) has a pump working chamber (18) which is formed in the first cylinder head part (7), wherein an outlet valve (32) is arranged on the first cylinder head part (7), and a fuel duct (31) is formed in the first cylinder head part (7), which fuel duct leads from the pump working chamber (18) to the outlet valve (32), and wherein the cylinder head (6) is connected by way of the second cylinder head part (8) to the housing (2), characterized in that the fuel duct (31) is formed by a stepped bore (30) formed in the first cylinder head part (7), and in that the outlet valve (32) is formed in the stepped bore (30).
  2. High-pressure pump according to Claim 1,
    characterized
    in that the pump assembly (14) has a cylinder bore (12) formed in the first cylinder head part (7) and has a pump piston (13) guided in the cylinder bore (12), in that the pump piston (13) delimits, in the cylinder bore (12), the pump working chamber (18), and in that the pump piston (13) can be driven by the drive shaft (3) .
  3. High-pressure pump according to Claim 1 or 2,
    characterized
    in that an inlet valve (46) is arranged on the second cylinder head part (8), and in that the inlet valve (46) delimits the pump working chamber (18).
  4. High-pressure pump according to one of Claims 1 to 3,
    characterized
    in that the second cylinder head part (8) is formed as a flange, and in that the second cylinder head part (8) can be screwed onto the housing (2) in at least two different screw-on positions.
  5. High-pressure pump according to Claim 4,
    characterized
    in that the screw-on positions differ from one another by a rotation of the cylinder head (6) about an axis (19) of the pump assembly (14).
  6. High-pressure pump according to one of Claims 1 to 5,
    characterized
    in that the second cylinder head part (8) has a lateral recess (57) which serves for receiving a lateral connector (28) of the first cylinder head part (7).
  7. High-pressure pump according to one of Claims 1 to 6,
    characterized
    in that the first cylinder head part (7) is formed from a material which is resistant to high pressures, and in that the second cylinder head part (8) is formed from a material which is resistant to low pressures.
  8. High-pressure pump according to one of Claims 1 to 7,
    characterized
    in that the cylinder head (6) is formed as a two-part cylinder head (6) which is made up of the first cylinder head part (7) and the second cylinder head part (8).
EP11712557.5A 2010-04-21 2011-04-06 High pressure pump Not-in-force EP2561213B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010028036 DE102010028036A1 (en) 2010-04-21 2010-04-21 high pressure pump
PCT/EP2011/055328 WO2011131481A1 (en) 2010-04-21 2011-04-06 High-pressure pump

Publications (2)

Publication Number Publication Date
EP2561213A1 EP2561213A1 (en) 2013-02-27
EP2561213B1 true EP2561213B1 (en) 2016-01-20

Family

ID=44187859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11712557.5A Not-in-force EP2561213B1 (en) 2010-04-21 2011-04-06 High pressure pump

Country Status (4)

Country Link
EP (1) EP2561213B1 (en)
CN (1) CN102844559B (en)
DE (1) DE102010028036A1 (en)
WO (1) WO2011131481A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011089953A1 (en) 2011-12-27 2013-06-27 Robert Bosch Gmbh Suction valve for high pressure fuel pump for fuel injection system of internal combustion engine, has chamber provided in valve housing such that valve shaft is inserted in chamber, and housing that is provided with polygonal socket
DE102013204327A1 (en) * 2013-03-13 2014-09-18 Robert Bosch Gmbh Cylinder head blank, cylinder head and high-pressure pump for fuel injection systems
DE102013210036A1 (en) * 2013-05-29 2014-12-04 Robert Bosch Gmbh High pressure pump for a fuel injection system
DE102013212261A1 (en) * 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
WO2015169621A1 (en) * 2014-05-05 2015-11-12 Robert Bosch Gmbh High-pressure pump for feeding fuel to an internal combustion engine
GB201516704D0 (en) * 2015-09-21 2015-11-04 Delphi Int Operations Lux Srl Fuel pump assembly

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2170558B (en) * 1985-02-02 1988-05-25 Lucas Ind Plc Liquid fuel injection pump
IT1188325B (en) * 1985-02-02 1988-01-07 Lucas Ind Plc LIQUID FUEL INJECTION PUMP
DE3622633A1 (en) * 1985-07-20 1987-01-22 Bosch Gmbh Robert METHOD FOR ATTACHING AN INJECTION PUMP TO AN INTERNAL COMBUSTION ENGINE, AND RELATED COMBUSTION ENGINE
DE19719265A1 (en) * 1997-05-07 1998-11-12 Deutz Ag Internal combustion engine with fuel pump in the crankcase
JP4088738B2 (en) 1998-12-25 2008-05-21 株式会社デンソー Fuel injection pump
ITMI20071202A1 (en) * 2007-06-14 2008-12-15 Bosch Gmbh Robert HIGH PRESSURE PUMP FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE AND HAVING A DRIVE SHAFT
JP5002523B2 (en) * 2008-04-25 2012-08-15 日立オートモティブシステムズ株式会社 Fuel pressure pulsation reduction mechanism and high-pressure fuel supply pump for internal combustion engine equipped with the same
DE102008001572A1 (en) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Spring retaining sleeve

Also Published As

Publication number Publication date
CN102844559B (en) 2016-04-27
WO2011131481A1 (en) 2011-10-27
DE102010028036A1 (en) 2011-10-27
CN102844559A (en) 2012-12-26
EP2561213A1 (en) 2013-02-27

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