EP1658433B1 - High-pressure pump for a fuel-injection device of an internal combustion engine - Google Patents

High-pressure pump for a fuel-injection device of an internal combustion engine Download PDF

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Publication number
EP1658433B1
EP1658433B1 EP20040738752 EP04738752A EP1658433B1 EP 1658433 B1 EP1658433 B1 EP 1658433B1 EP 20040738752 EP20040738752 EP 20040738752 EP 04738752 A EP04738752 A EP 04738752A EP 1658433 B1 EP1658433 B1 EP 1658433B1
Authority
EP
European Patent Office
Prior art keywords
ring
high
pressure pump
coating
characterized
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.)
Active
Application number
EP20040738752
Other languages
German (de)
French (fr)
Other versions
EP1658433A1 (en
Inventor
Thomas Kleinbeck
Markus Koch
Wolfram Rittmannsberger
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
Priority to DE20313014U priority Critical patent/DE20313014U1/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PCT/DE2004/001303 priority patent/WO2005026541A1/en
Publication of EP1658433A1 publication Critical patent/EP1658433A1/en
Application granted granted Critical
Publication of EP1658433B1 publication Critical patent/EP1658433B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B1/053Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B1/0413Cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00Other material characteristics; Treatment of material
    • F05C2253/12Coating

Description

    State of the art
  • The invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 198 44 272 A1 known. This high-pressure pump has a rotationally driven drive shaft, which has an eccentric to its axis of rotation formed shaft portion. On the eccentric shaft portion a polygon ring is rotatably mounted. The high-pressure pump has at least one pump element with a pump piston driven at least indirectly by the drive shaft via the ring in a lifting movement. The ring has on its circumference corresponding to the number of pump elements on flats on which the pump piston at least indirectly, for example via a plunger abut. During operation of the high-pressure pump, high loads of the ring and of the pump pistons or tappets occur, in particular to high surface pressures. In addition, there may be sliding movements between the ring and the pump piston or rams. Lubrication of the contact area between the ring and the pump piston or tappets takes place through the fuel present in the interior of the housing of the high-pressure pump. However, especially at high fuel temperatures, the lubrication by the fuel is no longer sufficient, so that it comes to heavy wear of the ring and / or the pump piston or plunger, which can eventually lead to failure of the high-pressure pump.
  • By the US-A-5 642 988 is a high-pressure pump is known, which has a rotationally driven drive shaft with an eccentric to its axis of rotation shaft portion on which a ring is rotatably mounted. The high-pressure pump has at least one pump element which has a pump piston driven at least indirectly by the drive shaft via the ring in a stroke movement. The ring is generally hardened to improve the wear resistance. However, the sliding properties between the ring and the pump piston supporting it are not improved by the hardening of the ring.
  • Advantages of the invention
  • The high pressure pump according to the invention with the features of claim 1 has the advantage that the sliding properties of the ring sliding properties are improved and sufficient wear resistance of the contact area between the ring and at least indirectly the at least one pump piston is ensured.
  • In the dependent claims advantageous refinements and developments of the high pressure pump according to the invention are given. The combination of a nitrocarburised surface layer and the coating of bonded coating applied thereto allows a particularly good wear resistance. The coating of lubricating varnish is at the beginning of operation of the high-pressure pump an enema so that the microtopographies of the surfaces of the ring and at least indirectly of the pump piston can match each other. In addition, by the occurring during operation of the high-pressure pump pressure between the ring and at least indirectly the pump piston Gleitlackbestandteile pressed into the coarsely porous pore space of the nitrocarburierten surface layer of the ring. This creates lubricant reservoirs from Gleitlackbestandteilen, from which the high-pressure pump at high fuel temperatures continuously solid lubricant particles are discharged during the hot run, by which a lack of lubrication is prevented.
  • drawing
  • An embodiment of the invention is illustrated in the drawing and closer in the following description explained. Show it FIG. 1 a fuel injection device of an internal combustion engine with a high-pressure pump and FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1 ,
  • Description of the embodiment
  • In the FIGS. 1 and 2 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a housing 10, which is designed in several parts and in which a drive shaft 12 is arranged. The drive shaft 12 is rotatably supported in the housing 10 via two spaced apart in the direction of the axis of rotation 13 of the drive shaft 12 bearings 14 and 16. The bearings 14,16 can be arranged in different parts of the housing 10.
  • In a lying between the two bearing points 14,16 range, the drive shaft 12 has an eccentric to its axis of rotation 13 formed shaft portion 26 on which a transmission element 28 is rotatably mounted via a bearing 30 in the form of a polygon ring. The high-pressure pump has at least one, preferably a plurality of pump elements 32 arranged in the housing 10, each having a pump piston 34 which is driven by the polygon ring 28 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. The pump piston 34 is guided in a cylinder bore 36 in the housing 10 or an insert in the housing 10 and slidably limited with its the transmission element 28 facing away from the end face in the cylinder bore 36 a pump working chamber 38. The pump chamber 38 has a running in the housing 10 fuel inlet channel 40 a Connection with a fuel inlet, such as a feed pump. At the mouth of the fuel supply passage 40 in the pump working space 38 is an inlet valve 42 opening into the pump working space 38 is arranged, which has a spring-loaded valve member 43. The pump working chamber 38 also has, via a fuel drain passage 44 running in the housing 10, a connection to an outlet, which is connected, for example, to a reservoir. At the mouth of the fuel discharge channel 44 into the pump working chamber 38, an outlet valve 46 which opens out of the pump working chamber 38 is arranged, which likewise has a spring-loaded valve member 47.
  • The pump piston 34 is held by a prestressed spring 48 with its piston foot 50 directly or via a plunger 52 in contact with the polygon ring 28. During the rotational movement of the drive shaft 12 of the polygon ring 28 is not moved with this, but due to the Exzenterabschnitts 26 performs a movement perpendicular to the rotational axis 13 of the drive shaft 12, which causes the lifting movement of the pump piston 34. The polygon ring 28 has in its outer jacket for each pump element 32 a flattening 29, against which the piston foot 50 or the plunger 52 is applied. When the suction stroke of the pump piston 34, in which this moves radially inward, the pump chamber 38 is filled by the fuel inlet passage 40 with the inlet valve 42 open with fuel, the exhaust valve 46 is closed. During the delivery stroke of the pump piston 34, in which the latter moves radially outward, fuel is pumped under high pressure through the fuel discharge channel 44 with the outlet valve 46 open to the reservoir 110 by the pump piston 34, the inlet valve 42 being closed.
  • The polygon ring 28 is mounted on the Lagerstellte 30 directly, that is without a bushing, or on a bearing bushing on the shaft portion 26. The polygon ring 28 may on its the shaft portion 26 facing inner surface with a coating 54 made of a lubricating varnish. Alternatively or additionally, the shaft section 26 may be provided on its outer surface facing the polygon ring 28 with a coating 54 of a bonded coating. The coating 54 has a thickness between about 10 and 50 microns, preferably between about 15 and 30 microns. The coating 54 consists of a bonded coating with the required properties in terms of coefficient of friction, wear resistance and temperature resistance for use at the bearing 30. By the coating 54 is even with lubrication of the bearing 30 only by the present in the interior of the housing 10 fuel low friction and a sufficient wear resistance of the bearing 30 ensured. For a given size of the outer cross section of the polygon ring 28, this can be performed with a relatively large wall thickness because of the small thickness of the coating 54 and the thus possible small inner diameter.
  • The polygon ring 28 is provided on its side facing away from the shaft portion 26 outer surface at least in the region of the flats 29 with a coating 56 of a bonded coating. It can also be provided that the polygon ring 28 is provided on its entire surface with the coating 56 of lubricating varnish. The coating 56 of anti-friction varnish has a thickness of between about 10 and 50 μm, preferably between about 15 and 30 μm. The bonded coating for the coating 56 is applied in liquid or powder form to the polygon ring 28 and then cured at elevated temperature. The bonded coating consists at least substantially of a paint with embedded particles of solid lubricant.
  • The polygon ring 28 is preferably provided with a nitrocarburized surface layer 58 at least in the region of the flats 29. The ring 28 can also open have the nitrocarburized surface layer 58 over its entire surface. This surface layer 58 is produced by introducing the polygon ring 28 into a salt bath. The nitrocarburized surface layer 58 has a thickness of about 5 to 20 μm, preferably about 10 μm. The surface layer 58 has an outer area with pores and an inner, non-porous area, with a thickness of at least 5 μm.
  • The polygon ring 28 is made of steel, preferably of a 16MnCrS5 alloy. The polygon ring 28 is tempered, then introduced into the salt bath where the nitrocarburized surface layer 58 is formed, and finally the coating 56 of lubricating varnish is applied to this surface layer 58 and cured.
  • The coating 56 of anti-friction varnish constitutes an enema aid at the beginning of the operation of the high-pressure pump, so that the microtopographies of the abutting surfaces of the flats 29 of the polygon ring 28 and of the piston foot 50 or the tappet 52 can mutually adapt. In addition, by the pressure occurring in operation of the high-pressure pump between the polygon ring 28 and the piston base 50 and the plunger 52 Gleitlackbestandteile in the coarsely porous pore space, that is the outer region of the nitrocarburized surface layer 58, the polygon ring 28 is pressed. In this case, lubricant reservoirs of Gleitlackbestandteilen, from which during high-pressure pump running at high fuel temperatures continuously solid lubricant particles are discharged through which a lack of lubrication between the polygon ring 28 and the piston 50 and the plunger 52 is prevented.

Claims (6)

  1. High-pressure pump for a fuel injection device of an internal combustion engine, having a rotationally driven drive shaft (12) which has a shaft section (26) which is formed eccentrically with respect to its rotational axis (13) and on which a ring (28) is mounted rotatably, and having at least one pump element (32) which has a pump piston (34) which is driven in a reciprocating movement at least indirectly by the drive shaft (12) via the ring (28) and bears against the ring (28) at least indirectly, characterized in that the ring (28) is provided with a coating (56) made from a lubricating varnish at least on its outer side which faces away from the shaft section (26) at least in a region, in which the at least one pump piston (34) bears against the ring (28) at least indirectly, which lubricating varnish comprises at least substantially a varnish having incorporated solid lubricant particles.
  2. High-pressure pump according to Claim 1, characterized in that the ring (28) has at least one flattened portion (29) on its circumference, against which flattened portion (29) the pump piston (34) bears at least indirectly, and which flattened portion (29) is provided with the coating (56) made from lubricating varnish.
  3. High-pressure pump according to Claim 1 or 2, characterized in that the ring (28) has a carbonitrided surface layer (58) at least in the region, in which the coating (56) made from lubricating varnish is applied, onto which carbonitrided surface layer (58) the coating (56) made from lubricating varnish is applied.
  4. High-pressure pump according to Claim 3, characterized in that the carbonitrided surface layer (58) has a thickness of approximately from 5 to 20 µm, preferably of approximately 10 µm.
  5. High-pressure pump according to Claims 1 to 4, characterized in that the coating (56) made from lubricating varnish has a thickness of approximately from 10 to 50 µm, preferably of approximately from 15 to 30 µm.
  6. High-pressure pump according to one of the preceding claims, characterized in that the ring (28) comprises an alloy 16MnCrS5.
EP20040738752 2003-08-21 2004-06-22 High-pressure pump for a fuel-injection device of an internal combustion engine Active EP1658433B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE20313014U DE20313014U1 (en) 2003-08-21 2003-08-21 High pressure pump for a fuel injector of an internal combustion engine
PCT/DE2004/001303 WO2005026541A1 (en) 2003-08-21 2004-06-22 High-pressure pump for a fuel-injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1658433A1 EP1658433A1 (en) 2006-05-24
EP1658433B1 true EP1658433B1 (en) 2008-03-26

Family

ID=33547282

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040738752 Active EP1658433B1 (en) 2003-08-21 2004-06-22 High-pressure pump for a fuel-injection device of an internal combustion engine

Country Status (8)

Country Link
US (1) US7284537B2 (en)
EP (1) EP1658433B1 (en)
JP (1) JP2006514722A (en)
KR (1) KR101018957B1 (en)
CN (1) CN100523494C (en)
DE (2) DE20313014U1 (en)
RU (1) RU2347100C2 (en)
WO (1) WO2005026541A1 (en)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005035082A1 (en) * 2005-07-21 2007-02-01 Ks Gleitlager Gmbh Hubring for an injection pump
DE102006034768A1 (en) * 2006-07-27 2008-01-31 Siemens Ag Radial piston pump unit for high-pressure fuel supply in fuel injection systems
US8122811B2 (en) * 2007-11-12 2012-02-28 Denso Corporation Fuel injection pump and method for assembling the same
DE102007060772A1 (en) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
JP4941337B2 (en) * 2008-02-01 2012-05-30 株式会社デンソー Fuel supply pump
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
IT1392791B1 (en) * 2008-07-17 2012-03-23 Bosch Gmbh Robert High-pressure pump for feeding fuel to an internal combustion engine
ITMI20081470A1 (en) * 2008-08-05 2010-02-06 Bosch Gmbh Robert High-pressure pump for feeding fuel to an internal combustion engine
DE102008041751A1 (en) * 2008-09-02 2010-03-04 Robert Bosch Gmbh High-pressure radial piston pump
DE102008043993B3 (en) * 2008-11-21 2010-04-29 Thielert Aircraft Engines Gmbh Common-rail high-pressure pump
DE102010020578A1 (en) * 2010-05-14 2011-11-17 Bayerische Motoren Werke Aktiengesellschaft Device for driving an auxiliary unit
JP5633387B2 (en) * 2011-01-24 2014-12-03 株式会社デンソー Fuel supply pump
DE102013210036A1 (en) * 2013-05-29 2014-12-04 Robert Bosch Gmbh High pressure pump for a fuel injection system
CN103470416B (en) * 2013-09-26 2016-08-17 南岳电控(衡阳)工业技术股份有限公司 A kind of radial plunger oil feed pump being applied to high pressure common rail fuel injection system
CN106133313B (en) * 2014-02-03 2018-10-30 康明斯公司 The method of pump and group armored pump

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5642988A (en) * 1991-02-15 1997-07-01 Ina Walzlager Schaeffler Kg Radial piston pump
US5462362A (en) * 1993-04-30 1995-10-31 Nsk Ltd. Wear resisting slide member
JPH06280740A (en) * 1993-03-26 1994-10-04 Zexel Corp Radial piston pump for viscosity fuel oil
DE19635164A1 (en) * 1996-08-30 1998-03-05 Bosch Gmbh Robert Piston pump
WO1999047810A1 (en) * 1998-03-19 1999-09-23 Sumitomo Electric Industries, Ltd. Combination of shim and cam
JP2000257555A (en) 1999-03-08 2000-09-19 Toyota Autom Loom Works Ltd Compressor
JP3337071B2 (en) 1999-11-26 2002-10-21 大豊工業株式会社 Hemispherical shoe
JP2003148294A (en) * 2001-11-12 2003-05-21 Hitachi Ltd Fuel pump and cylinder injection engine
DE10212492B4 (en) * 2002-03-21 2012-02-02 Daimler Ag Piston pump
DE10256528A1 (en) * 2002-12-04 2004-06-24 Robert Bosch Gmbh High pressure pump for a fuel injector of an internal combustion engine

Also Published As

Publication number Publication date
EP1658433A1 (en) 2006-05-24
US20060280620A1 (en) 2006-12-14
RU2005120649A (en) 2007-09-27
CN1839260A (en) 2006-09-27
US7284537B2 (en) 2007-10-23
CN100523494C (en) 2009-08-05
KR20060067961A (en) 2006-06-20
JP2006514722A (en) 2006-05-11
RU2347100C2 (en) 2009-02-20
KR101018957B1 (en) 2011-03-02
DE502004006679D1 (en) 2008-05-08
DE20313014U1 (en) 2004-12-23
WO2005026541A1 (en) 2005-03-24

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