EP0925443A1 - Pompe a piston pour l'alimentation haute pression en carburant - Google Patents

Pompe a piston pour l'alimentation haute pression en carburant

Info

Publication number
EP0925443A1
EP0925443A1 EP98936263A EP98936263A EP0925443A1 EP 0925443 A1 EP0925443 A1 EP 0925443A1 EP 98936263 A EP98936263 A EP 98936263A EP 98936263 A EP98936263 A EP 98936263A EP 0925443 A1 EP0925443 A1 EP 0925443A1
Authority
EP
European Patent Office
Prior art keywords
piston pump
pump according
roller
bolt
tappet
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
EP98936263A
Other languages
German (de)
English (en)
Other versions
EP0925443B1 (fr
Inventor
Horst Klinger
Uwe Kuhn
Bernd Rosenau
Peter Traub
Thomas GÖTTEL
Gerd LÖSCH
Sandro Soccol
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 EP0925443A1 publication Critical patent/EP0925443A1/fr
Application granted granted Critical
Publication of EP0925443B1 publication Critical patent/EP0925443B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M59/02—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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2307/00—Preventing the rotation of tappets

Definitions

  • the invention relates to a piston pump, in particular a radial piston pump of the roller tappet type
  • High-pressure fuel supply in fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft which has a plurality of cam-like elevations in the circumferential direction, and with at least one plunger which is arranged radially with respect to the drive shaft and which has a rotatable roller at its radially inner end region, which unrollable against the drive shaft in the region of the elevations is supported unrollable in the circumferential direction.
  • a piston pump of this type preferably has a plurality of radially arranged plungers which either abut pistons delimiting a high-pressure side on their side facing away from the drive shaft or even delimit the high-pressure side and thus directly displace or Perform compressor function.
  • the drive shaft of the piston pump has several elevations in the circumferential direction, which successively cause a stroke movement in a radial piston or tappet during a drive shaft revolution (multiple cam system).
  • the present invention is therefore based on the object of reducing the wear in generic piston pumps without having to reduce the tappet load (piston force, piston or tappet stroke, relative speed of the roller relative to its mounting).
  • a piston pump of the type mentioned which is characterized according to the invention by a lubricant supply opening which emanates from the jacket of the tappet and which opens into the radially inner end region of the tappet which supports the roller and at least during part of the stroke with a lubricant supply line opening into the cylinder chamber of the housing communicates.
  • the lubricant feed opening which is preferably connected to a lubricating oil circuit of the engine, either opens directly in the area of the sliding surfaces or in the so-called roller space, which is delimited by the end region of the tappet that receives the roller and the roller axis.
  • the piston pump can be designed in a particularly simple manner in terms of production technology in such a way that a respective tappet has a roller with rigidly attached bearing journals with which the roller is rotatably mounted in the end region of the tappet.
  • the roller can also be rotated relative to a pin extending parallel to the axis of rotation of the drive shaft and can be mounted on this pin on the end region of the tappet.
  • the lubricant supply opening in the end region of the tappet opens into at least one hub of the tappet for mounting the bearing journal or the bearing pin of the roller. It would also be conceivable that the bearing pin or the pin in the hub area are formed with an annular groove which coincides with the lubricant supply opening.
  • the Bolt is fixed with respect to the tappet and has a lubricant guiding device which overlaps or communicates with the lubricant supply opening to the surfaces of the bolt / roller pair sliding against one another.
  • the lubricant guide device therefore serves to transport the lubricant, which is conveyed via the lubricant feed opening into the hubs or into the roller chamber, to the surfaces of the roller and bolt sliding against one another.
  • the lubricant device is formed by a transverse bore in the bolt and a further bore in the bolt which extends obliquely to the longitudinal direction of the bolt, the latter opening in the region of the sliding surfaces.
  • the lubricant thus passes through the lubricant supply opening into the transverse bore, which runs essentially in the radial direction, into the interior of the bolt and from there via the further bore, which runs obliquely to the longitudinal direction of the bolt, into the region of the sliding surfaces.
  • the lubricant guide device could also be formed in a technically simple and thus advantageous manner by a surface groove running in the longitudinal direction of the bolt, which extends into the area of the sliding surfaces.
  • the surface groove can have any shape in cross-section exhibit; it has proven to be advantageous if it is convexly rounded in cross-section in the longitudinal direction of the bolt. Furthermore, it has proven to be advantageous if the surface groove is closed in the longitudinal direction of the bolt, ie if it does not open on the end faces of the bolt, in order to prevent the lubricant from escaping in this undesired direction.
  • the lubricant guiding device could furthermore be formed by a flattening on the bolt jacket running in the longitudinal direction of the bolt, which is particularly easy to accomplish in terms of production technology.
  • a groove running in the stroke direction is provided in the lateral surface of the tappet and / or in the cylinder inner surface. The groove ensures that the plunger moves back and forth
  • Lubricant feed opening of the tappet communicates with the lubricant feed line of the housing, which opens into the inner surface of the cylinder, at each stroke height.
  • the bolt and / or the roller is made of ceramic material and is therefore distinguished from metallic sliding pairings with regard to the temperature resistance and wearability.
  • the bolt has a structured outer surface, which preferably has groove-shaped recesses which extend along the bolt in any desired shape, or lubrication pockets can be provided.
  • a structured outer surface which preferably has groove-shaped recesses which extend along the bolt in any desired shape, or lubrication pockets can be provided.
  • Figure 1 is a partial sectional view through a piston pump according to the invention
  • FIG. 2 shows a sectional view with a detailed representation along the line II-II in FIG. 1;
  • Figure 3 shows two sectional views of a plunger according to Figure 1;
  • FIG. 4 shows a sectional view and a side view of a tappet designed according to the invention with a lubricant feed opening
  • Figure 5 shows two further sectional views of another
  • FIG. 6 shows a sectional view of the tappet according to FIG. 4 with an anti-rotation device for the bolt
  • FIG. 7 shows two sectional views of a tappet with a lubricating oil supply directly into the roller chamber
  • Figure 8 different surface structures of plunger pins and Figure 9 shows two sectional views of a plunger with an additional intermediate bush between the pin and roller.
  • Figures 1 and 2 show a piston pump with a pump housing 2, in which a drive shaft 4 and a plurality of roller tappet compression units 6 are arranged in a radial direction or in a star shape relative to one another.
  • the drive shaft 4 comprises three cam-like elevations 8 in the circumferential direction, the radially outermost points of which are each offset by 120 ° in the circumferential direction and form the apex of a uniform rounding.
  • a corresponding cam-like design 10 of the drive shaft 4 is provided in a plane running parallel to the plane of the figure, but is rotated by 60 ° to the former and cooperates with a further roller tappet compressor unit 6 '(FIG. 2).
  • the roller tappet compressor unit 6 comprises a tappet 12 which is provided in a cylinder space 16 of the pump housing 2 and can be moved back and forth in the radial direction 14.
  • a roller 20 is rotatably mounted on its end section 18 facing the drive shaft 4.
  • the end section 18 forms a pin chair 22 (FIG. 3), in which hubs 24 are provided in order to receive a pin 26 for the rotatable mounting of the roller 20.
  • the roller 20 rolls against the cam-like elevations 8 of the drive shaft 4 in the circumferential direction and thereby causes the plunger 12 to move back and forth.
  • the plunger 12 On its side facing away from the drive shaft 4, the plunger 12 is biased inward in the radial direction 14 toward the drive shaft 4 by a spring 28.
  • the spring 28 is supported on the plunger side against a spring plate 30 which is pressed with its outer region 32 against the plunger 12.
  • a central opening 36 is provided in the inner region 34, through which a piston 38 is guided.
  • the piston 38 is supported on the tappet side against a central shoulder 40 of the tappet 12 and projects with its opposite free end 42 into a cylinder chamber 44 on the high-pressure side, which is formed by a flange-shaped section 46 of the pump housing 2.
  • the piston 38 is moved back and forth in the high-pressure cylinder space 44 in the compression direction or suction direction.
  • the cylinder chamber 44 on the high-pressure side is connected in a manner not shown to an intake line and to a high-pressure line leading to a common rail accumulator.
  • the end section 18 on the drive axle side and the bolt chair 22 of the plunger 12 form a roller chamber 50 above the longitudinal axis 48 of the bolt.
  • This roller chamber 50 is connected via a ventilation opening 52 to the side of the plunger 12 remote from the drive shaft, on which the spring 28 is supported, for the back and forth Going of the plunger 12 not to be hampered by pressure / vacuum formation.
  • a lubricant supply channel 54 is also provided, which is connected to a Lubricant supply of a motor vehicle engine interacts From the lubricant supply channel 54, a spur line 56 (not shown in FIG. 1) leads away with a throttle device 55 (FIG. 2) and opens into the inner cylinder surface of the cylinder space 16. At the appropriate point is in the outer lateral surface 56 of the tappet 12 a groove 58 (FIG. 3) extending in the stroke direction is provided. A lubricant supply opening 60 extends from this groove 58 into the tappet and opens out in the region of the hub 24, that is to say in the region of the bearing point of the bolt 26.
  • FIG. 4 shows a further embodiment of a tappet 70 with a roller 72 which is mounted in the hubs 76 of the pin chair 78 of the tappet 70 via a pin 74.
  • a lubricant feed opening 82 is again provided, which is designed in the form of a straight bore and opens into the apex of the hub 76.
  • the bolt 74 is designed as a fixed bolt and is oriented in the hub 76 such that a bore 84 provided in the radial direction of the bolt 74 communicates with the mouth of the lubricant supply opening 82 in the hub 76.
  • the radial bore 84 in the bolt 74 extends approximately to the center of the bolt.
  • a further bore 86 extends obliquely to the bolt axis, which opens in the region of the sliding surfaces of the bolt 74 and the roller 72 in the bolt surface 88.
  • lubricant can be supplied via the lubricant feed opening 82 in the tappet and the transverse bore 84 and the subsequent additional bore 86 be brought into the area of the opposing surfaces of roller 72 and bolt 74.
  • the bores 84 and 86 thus form a lubricant guide device 89.
  • no groove is provided on the tappet casing 80 in the stroke direction.
  • Such a groove could, however, in the inner cylinder surface can be provided in order to ensure a connection to the lubricant circuit in a particularly advantageous manner over the entire stroke.
  • FIG. 5 shows a tappet 90 with a roller 92 and a fixed bolt 94.
  • the tappet 90 in turn has a longitudinal groove 96 in the stroke direction on its outer lateral surface 98, from which a lubricant supply opening 100 leads and opens in the area of the hub 102.
  • the bolt 94 has a lubricant guide device 104 in the form of a groove 106 extending in the longitudinal direction of the bolt on the bolt surface 108. Via the lubricant guide device 104, the lubricant conveyed into the hub area via the lubricant supply opening 100 is brought in the axial direction (arrow 110) into the area of the mutually sliding surfaces of the roller 92 and the pin 94.
  • FIG. 6 shows a plunger 110 corresponding to FIG. 5, in which an anti-rotation device 112 of the bolt 114 is provided in relation to the hub 116.
  • the anti-rotation device 112 is formed by a pin 118 inserted radially to the longitudinal direction of the bolt through the plunger 110.
  • FIG. 7 shows a further embodiment, according to which a plunger 120 is formed with lubricant supply openings 124 opening into the roller chamber 122. Lubrication takes place here via the roller chamber 122.
  • This embodiment proves to be advantageous in connection with a loose bolt. As a result, at least an increased supply of lubricating oil is achieved with a relatively low processing and assembly outlay in terms of production technology.
  • FIG. 8 shows a bolt 130 with a groove-shaped structuring 134 which extends helically on its outer lateral surface 132.
  • Surface structures 136 (waffle pattern) and 138 shown in the form of separate lubrication pockets. Furthermore, a cross section of a V-shaped groove profile 140 is shown, which has a depth of preferably 40 ⁇ m and a width in the region of the lateral surface of preferably 70 ⁇ m. It is pointed out that lubrication pockets can also be provided for a structure such as 136 in order to achieve a combined effect.
  • Figure 9 shows a plunger, in which between the Roller 154 and the bolt 156 an intermediate bush 158 running relative to the bolt 156 and relative to the roller 154 is provided to reduce the relative speed of the friction partners.

Landscapes

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

Abstract

L'invention concerne une pompe à piston de type poussoir à galets pour l'alimentation haute pression en carburant de systèmes d'injection de carburant de moteurs à combustion interne, en particulier d'un système d'injection pour rampe d'alimentation. La pompe comporte un arbre moteur (4) logé dans un carter de pompe (2) et présentant plusieurs bossages (8) en forme de cames dans le sens périphérique, ainsi qu'au moins un poussoir (12) disposé radialement par rapport à l'arbre moteur (4) dans une chambre de cylindre (16). Le poussoir présente, à son extrémité interne radiale (18), un galet rotatif (20) qui s'appuie, de façon à pouvoir rouler, contre l'arbre moteur (4) dans la zone des bossages (8) de ce dernier dans le sens périphérique. Afin de réduire l'usure dans la zone du logement de galet, la pompe est réalisée de telle façon qu'une ouverture d'amenée de lubrifiant (60, 82, 100) partant de la gaine du poussoir (12, 70, 90) débouche dans la zone d'extrémité interne radiale (18) du poussoir où loge le galet (20, 72, 92), et communique, au moins pendant une partie de la course, avec une conduite d'amenée de lubrifiant (54, 56) du carter (2) débouchant dans la chambre de cylindre (16).
EP98936263A 1997-07-11 1998-06-30 Pompe a piston pour l'alimentation haute pression en carburant Expired - Lifetime EP0925443B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19729793 1997-07-11
DE19729793A DE19729793A1 (de) 1997-07-11 1997-07-11 Kolbenpumpe zur Kraftstoffhochdruckversorgung
PCT/DE1998/001791 WO1999002852A1 (fr) 1997-07-11 1998-06-30 Pompe a piston pour l'alimentation haute pression en carburant

Publications (2)

Publication Number Publication Date
EP0925443A1 true EP0925443A1 (fr) 1999-06-30
EP0925443B1 EP0925443B1 (fr) 2003-10-15

Family

ID=7835428

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98936263A Expired - Lifetime EP0925443B1 (fr) 1997-07-11 1998-06-30 Pompe a piston pour l'alimentation haute pression en carburant

Country Status (5)

Country Link
US (1) US6216583B1 (fr)
EP (1) EP0925443B1 (fr)
JP (1) JP2001500221A (fr)
DE (2) DE19729793A1 (fr)
WO (1) WO1999002852A1 (fr)

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JP5706850B2 (ja) * 2012-05-21 2015-04-22 株式会社丸山製作所 往復動ポンプ
KR101371897B1 (ko) * 2012-09-05 2014-03-07 현대자동차주식회사 윤활성능이 개선된 고압연료펌프
DE102012223413A1 (de) 2012-12-17 2014-06-18 Robert Bosch Gmbh Rollenstößel für eine Pumpe, insbesondere Kraftstoffhochdruckpumpe, und Pumpe mit Rollenstößel
FR3013774B1 (fr) * 2013-11-22 2019-08-23 Renault S.A.S Pompe d'injection de carburant a lubrification integree a l'axe de rotation du galet
EP2960446A1 (fr) * 2014-06-24 2015-12-30 Aktiebolaget SKF Système mécanique formant un suiveur de came ou un culbuteur
JP6380132B2 (ja) * 2015-01-29 2018-08-29 株式会社デンソー 駆動機構搭載部品
DE202015003039U1 (de) * 2015-04-24 2016-07-27 GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) Verbrennungsmotor mit einer Düse zur Schmierung des Eingriffs zwischen Kraftstoffeinspritzpumpe und Antriebsnocke
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EP3173592B1 (fr) * 2015-11-24 2021-01-06 Aktiebolaget SKF Dispositif de levier à galet ou à came suiveur avec trous d'alimentation en lubrifiant et procédé de lubrification
DE102016219712A1 (de) * 2016-10-11 2018-04-12 Robert Bosch Gmbh Rollenstößel für eine Kolbenpumpe, Kolbenpumpe
DE102016219718A1 (de) * 2016-10-11 2018-04-12 Robert Bosch Gmbh Rollenstößel für eine Kolbenpumpe, Kolbenpumpe
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JP2021032100A (ja) * 2019-08-21 2021-03-01 株式会社デンソー 燃料噴射ポンプ

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DE19729793A1 (de) 1999-01-14
EP0925443B1 (fr) 2003-10-15
WO1999002852A1 (fr) 1999-01-21
US6216583B1 (en) 2001-04-17
JP2001500221A (ja) 2001-01-09
DE59809920D1 (de) 2003-11-20

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