WO2010127899A1 - Circuit de lubrification d'une pompe de rampe commune haute pression et pompe de rampe commune haute pression - Google Patents

Circuit de lubrification d'une pompe de rampe commune haute pression et pompe de rampe commune haute pression Download PDF

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Publication number
WO2010127899A1
WO2010127899A1 PCT/EP2010/053531 EP2010053531W WO2010127899A1 WO 2010127899 A1 WO2010127899 A1 WO 2010127899A1 EP 2010053531 W EP2010053531 W EP 2010053531W WO 2010127899 A1 WO2010127899 A1 WO 2010127899A1
Authority
WO
WIPO (PCT)
Prior art keywords
support seat
pump
common rail
pressure common
shaft
Prior art date
Application number
PCT/EP2010/053531
Other languages
English (en)
Inventor
Ruggiero Gissi
Antonio Mercurio
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 WO2010127899A1 publication Critical patent/WO2010127899A1/fr

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
    • F02M59/38—Pumps characterised by adaptations to special uses or conditions
    • F02M59/42—Pumps characterised by adaptations to special uses or conditions for starting of engines
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0531—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with cam-actuated distribution members

Definitions

  • the present invention relates to a lubricating circuit of a high-pressure common rail pump, to a method for lubricating a high-pressure common rail pump and to a high-pressure common rail pump.
  • High-pressure common rail pumps are used for feeding pressurized fuel in common-rail internal combustion engines.
  • High-pressure common rail pumps comprise a number of pump units (generally three) which are driven by an actuating mechanism.
  • Each of the pump units comprises a piston which slides axially in a seat and is coupled to the actuating mechanism, which imparts a reciprocating motion to said piston.
  • the actuating mechanism comprises a shaft provided with an eccentric.
  • a prismatic ring with, on the outside, a number of planar faces which equals the number of pump units is fitted on said eccentric in an idle manner.
  • Each face of the prismatic ring is coupled to the base of a respective piston.
  • the rotation of the eccentric by means of an engine causes pivoting of the faces of the prismatic ring and, as a result, reciprocating motion of the pistons.
  • the prismatic ring is housed in a driving chamber of the pump body.
  • the shaft has a first end and a second end, which are at opposite ends from each other.
  • the first end protrudes from the pump body and can be connected to engine members in order to initiate motion.
  • the second end is housed in a blind support seat of the pump body and can be provided with a reinforcing sleeve, fitted with interference.
  • the second end of the shaft, or possibly the sleeve, is coupled to the support seat via an annular plain bearing.
  • the high rotational speed of the shaft means that correct functioning always requires the provision of adequate lubrication, both of the support seat of the second end of the shaft (the clearance between the shaft and the plain bearing) and of the driving chamber (the coupling between the prismatic ring and the shaft and, in particular, between the prismatic ring and the bases of the pistons of the pump units).
  • a lubricating circuit feeds a certain quantity of lubricating fluid to the support seat of the shaft, which is connected to the driving chamber by a flui- die passage.
  • the lubricating fluid is normally the same fuel supplied to the engine
  • the present invention provides a lubricating circuit of a high-pressure common rail pump comprising:
  • a driving chamber formed in the pump body and fluidly connected to the support seat;
  • an inlet branch for supplying a lubricating fluid to the support seat
  • an inlet passage for fluidly connecting the inlet branch to the support seat
  • the concentrated load-drop element prevents or else drastically limits the flow of the fuel out through the fluidic passage when the high-pressure common rail pump is started up.
  • the passage of fuel through the clearance is promoted, and therefore the coupling members of the shaft and of the support seat 24 are adequately lubricated immediately on start-up.
  • the lubricating circuit comprises retention means for preventing leakage of the lubricating fluid from the support seat through the inlet passage.
  • the retention means prevent the fuel from flowing back towards the inlet branch, and this contributes to an improvement in the lubrication, particularly during the start-up phase.
  • the retention means comprise a backflow valve arranged so as to prevent leakage of the lubricating fluid from the support seat towards the inlet branch through the inlet passage.
  • the present invention also provides a high-pressure common rail pump compri- sing: a shaft;
  • a pump body having a support seat, for supporting a portion of the shaft, and a driving chamber, fluidly connected to the support seat;
  • FIG. 1 schematically shows a portion of a common rail engine feed- system, which contains a high-pressure common rail pump and a lubricating circuit according to a first embodiment of the present invention
  • FIG. 2 shows a side view, in longitudinal section and with parts removed for ease of understanding, of the pump and of part of the lubricating circuit shown in Figure 1;
  • Figure 3 shows a side view, in longitudinal section and with parts re- moved for ease of understanding, of a high-pressure common rail pump and of part of an associated lubricating circuit, according to a second embodiment of the present invention.
  • the reference numeral 1 denotes a fuel feed system for an internal combustion engine (not shown).
  • the feed system 1 comprises a fuel tank 2, a high-pressure common rail pump 3, a low-pressure feed circuit 4, which connects the fuel tank 2 to the high-pressure common rail pump 3, a high-pressure delivery circuit 5, which connects the high-pressure pump 3 to a common rail 6, and a lubricating circuit 8.
  • the high-pressure common rail pump 3 comprises a pump body 9 (not shown in Figure 1 and partially visible in Figure 2), three pump units 10 housed in the pump body 9, and an actuating mechanism 11.
  • the three pump units 10 are arranged radially at 120° around the actuating mechanism 11 and each comprise a piston 13 which slides axially in a respective seat 15. That portion of each seat 15 which is not occupied by the respective piston 13 defines a variable-volume pump chamber and is coupled to the feed circuit 4 via a respective feed valve 17 and to the delivery circuit 5 via a respecti- ve delivery valve 18.
  • the actuating mechanism comprises a shaft 20, which is provided with an eccentric 21, and a prismatic ring 23, which is fitted on the eccentric 21.
  • the shaft 20 extends along an axis A, has a drive portion 20a, which protrudes from the pump body 9 and can be connected to a drive member (not shown here), and a supporting portion 20b.
  • the supporting portion 20b is housed in a support seat 24 of the pump body 9 and supports the shaft 20 and the prismatic ring 23 for rotation around the axis A.
  • the supporting portion 20b of the shaft 20 is provided with a reinforcing sleeve 25, fitted with interference, and is coupled to the support seat 24 by means of an annular plain bearing 27.
  • the support seat 24 defines an annular chamber 28 around a part of the shaft 20 which protrudes from the plain bearing 27.
  • the prismatic ring 23, fitted on the eccentric 21 in an idle manner, is housed in a driving chamber 28 of the pump body 9.
  • the low-pressure feed circuit 4 comprises a prefilter 30, a prefeed pump 31, a fuel filter 32 and a metering valve 34.
  • the prefeed pump 31 is preferably provided with a bypass valve 35 and with a pressure-relief valve 37, which limits the pressure downstream of the prefeed pump 31 to a gaugeable value.
  • the metering valve 34 controls the flow of fuel towards the high-pressure com- mon rail pump 3.
  • the feed circuit is divided into branches downstream of the metering valve 34, and each of these branches is connected to the pump chamber by a respective pump unit 10.
  • the lubricating circuit 8 comprises an inlet branch 40, a return branch 41, an annular chamber 42, the driving chamber 28 which houses the eccentric 21, an inlet passage 44 and a fluidic passage 45.
  • the inlet branch 40 taps a flow of fuel from the feed circuit 4 between the fuel filter 32 and the metering valve 34.
  • the quantity of tapped fuel which is used as lubricating fluid, is supplied to parts of the high-pressure common rail pump 3 which are to be lubricated.
  • a control device 46 controls the pressure of the fuel in the inlet branch 40 towards the high-pressure common rail pump 3, and returns a fraction of excess fuel to the feed circuit 4, in this case upstream of the prefeed pump 31.
  • the return branch 41 recovers the fuel used as lubricating fluid for the high- pressure common rail pump 3 and returns it into the tank 2 at low pressure.
  • the annular chamber 42 is defined in the support seat 24 around the supporting portion 20b of the shaft 20 and receives a flow of fuel from the inlet branch 40 through the inlet passage 44. More precisely, the annular chamber 42 is delimi- ted axially on the one hand by an end wall of the support seat 24 and, on the other hand, by the sleeve 25, by an annular protrusion of the shaft 20 and by the plain bearing 27.
  • a backflow valve 48 is arranged along the inlet passage 44 to prevent the fuel from flowing back from the annular chamber 42 towards the inlet branch 40. In the embodiment shown in Figure 2, the backflow valve 48 is carried by the pump body 9 and is positioned at the start of the inlet passage 44.
  • a clearance 49 is radially defined between the coupling members of the shaft and of the support seat 24.
  • these coupling members are the reinforcing sleeve 25 of the shaft 20 and the plain bearing 27.
  • the clearance 49 also extends axially between the annular chamber 42 and the driving chamber 28. Consequently, the clearance 49 is also accessible to the fuel and forms part of the lubricating circuit 8, in particular for the lubrication between the sleeve 25 and the plain bearing 27.
  • the clearance 49 fluidly connects the annular chamber 42 and the driving chamber 28.
  • the fluidic passage 45 connects the annular chamber 42 and the driving chamber 28, in practice in parallel to the clearance 49.
  • a concentrated load-drop element is positioned along the fluidic passage 45 and, in the embodiment descri- bed, this element is a calibrated throttling 50.
  • a transverse section 20 of the throttling 50 is roughly equal to a transverse section of the clearance 49.
  • the concentrated load-drop element is a counterpressure valve 55 which is normally closed and opens in the event of a pressure drop between its inlet and its outlet which is higher than a gaugeable pressure threshold.
  • the concentrated load-drop element prevents or else drastically limits the flow of the fuel out through the fluidic passage 45.
  • the passage of fuel through the clearance 49 is promoted, and therefore the coupling between the reinforcing sleeve 25 and the side wall of the support seat 24 is adequately lubricated immediately the high-pressure common rail pump 3 starts.
  • the backflow valve 48 which prevents the fuel from flowing back towards the inlet branch 40, also contributes to an improvement in the lubrication, particularly during the startup phase.
  • the supporting portion of the shaft can be coupled directly to the support seat, without the interposition of the reinforcing sleeve and/or of the plain bearing.
  • the coupling members between the supporting portion of the shaft and the support seat comprise a lateral surface of the shaft (instead of the reinforcing sleeve) and/or a lateral surface of the support seat (instead of the plain bearing).

Landscapes

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

Abstract

L'invention porte sur un circuit de lubrification d'une pompe de rampe commune haute pression (3), lequel circuit comprend : un siège de support (24) pour une partie (20b) d'un arbre (20) d'une pompe de rampe commune haute pression (3), formé dans un corps de pompe (9) de la pompe de rampe commune haute pression (3); une chambre d'entraînement (28), formée dans le corps de pompe (9) et reliée fluidiquement au siège de support (24); un dégagement (49), défini entre des éléments d'accouplement (25, 27) de l'arbre (20) et du siège de support (24) et communiquant avec la chambre d'entraînement (28); une ramification d'entrée (40), pour distribuer un fluide de lubrification au siège de support (24); un passage d'entrée (44), pour relier fluidiquement la ramification d'entrée (40) au siège de support (24); et un passage de fluide (45) entre le passage d'entrée (44) et la chambre d'entraînement (28), parallèle au dégagement (49). Le circuit comprend également un élément de baisse de charge concentrée (50; 55) disposé le long du passage de fluide (45).
PCT/EP2010/053531 2009-04-17 2010-03-18 Circuit de lubrification d'une pompe de rampe commune haute pression et pompe de rampe commune haute pression WO2010127899A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI2009A000638 2009-04-17
ITMI2009A000638A IT1398728B1 (it) 2009-04-17 2009-04-17 Circuito di lubrificazione di una pompa common rail di alta pressione e pompa common rail di alta pressione

Publications (1)

Publication Number Publication Date
WO2010127899A1 true WO2010127899A1 (fr) 2010-11-11

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ID=41316212

Family Applications (1)

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PCT/EP2010/053531 WO2010127899A1 (fr) 2009-04-17 2010-03-18 Circuit de lubrification d'une pompe de rampe commune haute pression et pompe de rampe commune haute pression

Country Status (2)

Country Link
IT (1) IT1398728B1 (fr)
WO (1) WO2010127899A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014220750A1 (de) * 2014-10-14 2016-04-14 Continental Automotive Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine und Anordnung aus Hochdruckpumpe und Motorblock
WO2017067856A1 (fr) * 2015-10-20 2017-04-27 Delphi International Operations Luxembourg S.À R.L. Machine hydraulique ayant un piège centrifuge à particules
CN108915919A (zh) * 2018-08-28 2018-11-30 河南柴油机重工有限责任公司 一种高压共轨柴油机共轨泵驱动装置
IT202100010568A1 (it) * 2021-04-27 2022-10-27 Bosch Gmbh Robert Gruppo pompa per alimentare carburante ad un motore a combustione interna

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030101970A1 (en) * 2001-12-04 2003-06-05 Yasutaka Utsumi Fuel injection pump having feed pump assembly
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump
WO2003048564A1 (fr) * 2001-12-01 2003-06-12 Robert Bosch Gmbh Pompe a piston radiaux a graissage force
EP1394403A2 (fr) * 2002-08-31 2004-03-03 Robert Bosch Gmbh Système de combustible pour un moteur à combustion interne
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003048564A1 (fr) * 2001-12-01 2003-06-12 Robert Bosch Gmbh Pompe a piston radiaux a graissage force
US20030101970A1 (en) * 2001-12-04 2003-06-05 Yasutaka Utsumi Fuel injection pump having feed pump assembly
US20030108443A1 (en) * 2001-12-12 2003-06-12 Masashi Suzuki Fuel injection pump
EP1394403A2 (fr) * 2002-08-31 2004-03-03 Robert Bosch Gmbh Système de combustible pour un moteur à combustion interne
EP1544462A2 (fr) * 2003-12-15 2005-06-22 Denso Corporation Pompe à carburant avec rainure de lubrification

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014220750A1 (de) * 2014-10-14 2016-04-14 Continental Automotive Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine und Anordnung aus Hochdruckpumpe und Motorblock
WO2017067856A1 (fr) * 2015-10-20 2017-04-27 Delphi International Operations Luxembourg S.À R.L. Machine hydraulique ayant un piège centrifuge à particules
CN108915919A (zh) * 2018-08-28 2018-11-30 河南柴油机重工有限责任公司 一种高压共轨柴油机共轨泵驱动装置
CN108915919B (zh) * 2018-08-28 2023-10-20 河南柴油机重工有限责任公司 一种高压共轨柴油机共轨泵驱动装置
IT202100010568A1 (it) * 2021-04-27 2022-10-27 Bosch Gmbh Robert Gruppo pompa per alimentare carburante ad un motore a combustione interna
WO2022228818A1 (fr) * 2021-04-27 2022-11-03 Robert Bosch Gmbh Unité de pompe pour la fourniture de carburant à un moteur à combustion interne

Also Published As

Publication number Publication date
ITMI20090638A1 (it) 2010-10-18
IT1398728B1 (it) 2013-03-18

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