EP1155238A1 - Ensemble pompe hydraulique - Google Patents

Ensemble pompe hydraulique

Info

Publication number
EP1155238A1
EP1155238A1 EP99964362A EP99964362A EP1155238A1 EP 1155238 A1 EP1155238 A1 EP 1155238A1 EP 99964362 A EP99964362 A EP 99964362A EP 99964362 A EP99964362 A EP 99964362A EP 1155238 A1 EP1155238 A1 EP 1155238A1
Authority
EP
European Patent Office
Prior art keywords
pump
hydraulic pump
elements
hydraulic
angular
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
EP99964362A
Other languages
German (de)
English (en)
Other versions
EP1155238B1 (fr
Inventor
Andreas Kellner
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 EP1155238A1 publication Critical patent/EP1155238A1/fr
Application granted granted Critical
Publication of EP1155238B1 publication Critical patent/EP1155238B1/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
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • 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
    • F04B1/0413—Cams
    • 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
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • F04B11/0066—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control with special shape of the actuating element

Definitions

  • the present invention relates to a
  • Hydraulic pump unit with several pump elements arranged in one plane, each having a pump cylinder and a longitudinally displaceable therein
  • the invention also relates to a high-pressure pump for generating an injection pressure for fuel-operated internal combustion engines.
  • the hydraulic pump units of the type mentioned at the outset are also referred to as radial piston pumps. They are mainly used as high-pressure pumps for generating an injection pressure for a fuel-operated internal combustion engine. However, other possible uses of the hydraulic pump units are also conceivable.
  • Hydraulic pump units of the type mentioned in various embodiments are known from the prior art.
  • Hydraulic pump units in which two pump elements are arranged at an angular distance of 180 degrees to one another.
  • the pump elements of this known hydraulic pump unit are actuated from the inside by a camshaft that is perpendicular to the plane of the
  • externally actuated hydraulic pump units with two or four pump elements, which are arranged at an angular distance of 180 angular degrees or 90 angular degrees to one another, are also known. These have, for example, a cam ring, on the inner circumference of which two cams arranged at an angular distance of 180 angular degrees or four at an angular distance of 90 angular degrees are formed. By rotating the cam ring relative to the pump element, the pump piston would be replaced by the cam with a Actuation movement applied. In these externally operated hydraulic pump units, the pump pistons are pressed radially outwards by spring elements and pressed inwards by the cams of the camshaft in opposition to the force of the spring element.
  • the pump pistons of all the pump elements are in a conveying movement or in a suction movement at the same time, and all pump pistons reach top dead center or bottom dead center at the same time. This results in a very uneven delivery characteristic even with these known hydraulic pump units.
  • FIG. 5 An embodiment of a hydraulic pump unit known from the prior art is mentioned, in which three pump elements are arranged at an angular distance of 120 angular degrees from one another.
  • the pump elements are actuated from the inside via a cam shaft, on the outer circumference of which two cams are arranged at an angular distance of 180 degrees from one another.
  • the delivery curves of the pump elements of this known hydraulic pump arrangement is shown in FIG. 5.
  • the pump pistons of the pump elements C, D, E are partly at the same time in a conveying movement (in the upper region 90) or in a suction movement (in the lower region 91), so that there is an overlap 92 of the conveying courses or an overlap 93 of the Suction curve of the individual pump elements C, D, E comes. Due to the overlaps 92, 93, this known hydraulic pump unit also results in an uneven one
  • the present invention is based on the object of a hydraulic pump unit of the type mentioned at the beginning to be designed and further developed in such a way that, particularly with partial filling, it enables the hydraulic fluid to be conveyed uniformly.
  • the invention proposes, starting from the hydraulic pump unit of the type mentioned above, that the number and the angular distance of the cams is matched to the number and the angular distance of the pump elements such that when a certain number of pump pistons are in the top dead center, is the same number of pump pistons at bottom dead center.
  • the hydraulic pump unit has a particularly uniform delivery characteristic when the
  • Hydraulic pumps unit has an even number of pump elements, so that an equal number of pump elements can be actuated in opposite directions and at that point in time the same number of pump pistons in opposite delivery or
  • the hydraulic pump unit according to the invention has O 00/50772
  • the hydraulic pump unit according to the invention can be realized with a large number of different embodiments without thereby abandoning the idea of the present invention.
  • the number and the angular spacing of the cams of the cam drive can be varied.
  • the number and the angular spacing of the individual pump elements can also be varied.
  • the number and the angular distance of the cams of the cam drive is matched to the number and the angular distance of the pump elements such that when the number of pump pistons is at top dead center, the same number of pump pistons in the bottom dead center. This is the only way to achieve an even delivery of all pump pistons with "partial filling".
  • the cams of the cam drive drive the pump pistons from the inside with a
  • the cam drive is designed as a cam, which runs perpendicular to the plane in which the pump elements lie, through the intersection and on the outer circumferential surface of which the cam is formed.
  • the cam drive have two cams arranged at an angular distance of 180 angular degrees from one another.
  • the hydraulic pump unit then advantageously has two pump elements which are at an angular distance of 90 degrees from one another.
  • the hydraulic pump unit have four pump elements which have an angular distance of 90 degrees to one another. This embodiment has the advantage that the actuating movement of each pump element of the hydraulic pump unit counteracts an opposite actuating movement of another pump element of the hydraulic pump unit as a compensation.
  • the hydraulic pump unit has a particularly high running smoothness, in particular when the cam drive has high numbers of wires.
  • the cam drive have three cams arranged at an angular distance of 120 degrees.
  • the hydraulic pump unit then advantageously has two pump elements which have an angular distance of 60 angular degrees from one another. It is further proposed that the hydraulic pump unit has four pump elements which are at an angular distance of 60 angular degrees from one another. Finally, it is proposed that the hydraulic pump unit six
  • the pump pistons deliver the hydraulic fluid to the radially outer end of the pump elements.
  • the conveyed hydraulic fluid can then be led out of the hydraulic pump unit from the radially outer ends of the pump elements and fed to a high-pressure accumulator via feed lines located outside the hydraulic pump unit.
  • the high pressure is shifted out of the housing of the hydraulic pump unit into the outer supply lines.
  • the housing only has to be designed for low pressure and can be manufactured cheaper.
  • the hydraulic pump unit as a high-pressure pump for generating an injection pressure for a fuel-driven internal combustion engine. Especially when used as
  • a further object of the present invention is to design and further develop a high-pressure pump of the type mentioned at the outset in such a way that it enables the hydraulic fluid to be conveyed uniformly.
  • the invention proposes, starting from the high-pressure pump of the type mentioned, that several of the hydraulic pump units according to one of claims 1 to 11 are arranged one behind the other in such a way that the pump elements of all hydraulic pump units are acted upon by the same cam drive with their actuating movement.
  • the number and the angular distance of the pump elements of the hydraulic pump units and the angular displacement of the hydraulic pump units from one another are matched to the number and the angular distance of the cams such that when a certain number of pump pistons of the high pressure pump are located in the upper one Dead center is the same number of pump pistons in the bottom dead center.
  • two hydraulic pump units according to claims 3 and 5 are arranged in such a way that the planes in which the pump units are located run parallel to one another and that the intersections of the
  • Pump units of the hydraulic pump units are on the same camshaft.
  • the hydraulic pump units are advantageously arranged congruently one behind the other.
  • the hydraulic pump units are arranged one behind the other rotated by an angular offset of 180 angular degrees.
  • FIG. 1 shows a hydraulic pump unit according to the invention in accordance with a preferred embodiment
  • FIG. 2 shows the hydraulic pump unit from FIG. 1 in cross section along the line A-A;
  • Fig. 3 is a circuit diagram for the generation of high pressure O 00/50772
  • Hydraulic pump unit from FIG. 1 and FIG. 2;
  • Fig. 5 delivery curves of the Pumpsn ⁇ lem ⁇ nte a hydraulic pump unit known from the prior art.
  • the hydraulic pump unit 1 is designed as a radial piston pump. It is used, for example, as a high-pressure pump 18 (cf. FIG. 3) for generating an injection pressure for fuel-operated internal combustion engines.
  • the hydraulic pump unit 1 has two pump elements 2, which are arranged in one plane. Each pump element 2 has a pump cylinder 3 and a longitudinally displaceable therein
  • the pump piston 4 delivers a hydraulic fluid, e.g. B. fuel to the radially outer end of the hydraulic fluid
  • the pump piston 4 is pressed radially inward in the direction of the intersection 6 by a spring element 7. In this position, a pump chamber 8 of the pump element 2 has its largest volume.
  • the pump chamber 8 is filled with fuel from a metering unit 14.
  • the pump chamber 8 leads out of the hydraulic pump 1 via a pressure valve 11 and a connecting piece 12.
  • the hydraulic pump unit 1 is actuated internally. It has a camshaft 9 which is perpendicular to the plane of the plane Pump elements 2 and through the intersection 6 of the longitudinal axes 5 of the pump elements 2. More precisely, the longitudinal axis 26 of the camshaft 9 runs through the intersection 6. On the outer circumferential surface of the camshaft 9, two cams 10 are formed, which act on the pump pistons 4 one after the other with a radially outward conveying movement when the camshaft 9 is relative to the Pump elements 2 presses.
  • the pump piston 4 in the pump element 2 is pressed radially outward from the bottom dead center (UT) to the top dead center (OT) against the force of the spring element 7.
  • the volume of the pump chamber 8 is reduced, the fuel therein is compressed and conveyed out of the hydraulic pump unit 1 under high pressure via the pressure valve 11 and the connecting piece 12.
  • a supply line 13 is connected to the connecting piece 12, via which the fuel delivered is directed into a high-pressure accumulator 15, for example of a common rail system.
  • TDC top dead center
  • UT bottom dead center
  • the pump elements 2 of the hydraulic pump unit 1 have an angular spacing of 90 angular degrees from one another. More precisely, the longitudinal axes 5 of the pumping elements 2 have an angular distance of 90 angular degrees from one another. At an angular distance of approximately 135 degrees to d ⁇ n Pump units 2 are arranged in an inlet 16 from the metering unit 14 and a return 17.
  • the cams 10 are arranged at an angular distance of 180 degrees from one another on the outer circumference of the camshaft 9.
  • the number and the angular distance of the cams 10 are matched to the number and the angular distance of the pump elements 2 such that when one pump piston 4 is at top dead center (TDC), the other pump piston 4 is at bottom dead center (UT) (cf. Fig. 4). This results in a uniform delivery characteristic and a high level of smoothness of the hydraulic pump unit 1 according to the invention, even at high numbers of cams of the camshaft 9.
  • FIG. 3 shows a circuit diagram for generating high pressure for a common rail system with a high pressure pump 18 according to the invention.
  • the high-pressure pump 18 is designed as a hydraulic pump unit 1 according to FIGS. 1 and 2 and is only shown symbolically in FIG. 3.
  • a feed pump 19 draws fuel from a fuel tank 20 through a filter 21 and conveys it in front of the metering unit 14 and a cascade overflow valve 24.
  • the metering unit 14 is designed as a proportional valve and forwards the fuel to the
  • High-pressure pump 18 When the metering unit 14 is closed, this leakage is sucked off by the metering unit 14 via a zero-feed throttle 22 from the feed pump 19.
  • a line branches off between the feed pump 19 and the metering unit 14, which conducts part of the fuel pumped by the feed pump 19 to a parallel circuit consisting of a vent throttle 23 and a series connection of the cascade valve flow valve 24 and lubricant throttle valve.
  • the fuel pressure can be regulated to a constant value by the cascade overflow valve 24.
  • the excess fuel is the Inlet of the pump 19 fed.
  • the fuel from the venting throttle 23 and the lubricating throttle 25 is fed to the bearing of the camshaft 9 for lubrication and cooling and then fed back into the fuel tank 20.
  • FIG. 4 shows the conveying profile of the two pump elements 2 of the hydraulic pump unit 1 according to the invention in accordance with the exemplary embodiment from FIGS. 1 and 2.
  • the delivery profiles of the individual pump elements are for

Landscapes

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

Abstract

L'invention concerne un ensemble pompe hydraulique (1) comprenant plusieurs éléments de pompe (2) placés dans un plan et présentant chacun un cylindre (3) et un piston (4) qui peut coulisser dans le sens longitudinal à l'intérieur de ce dernier. Les axes longitudinaux (5) desdits éléments de pompe se coupent en un point d'intersection commun (6). Cet ensemble pompe hydraulique comprend également un organe de commande à cames, comportant des cames (10) qui actionnent les pistons (4) lors d'une rotation de cet organe de commande par rapport aux éléments de pompe (2). L'invention vise à permettre un refoulement homogène du fluide hydraulique et un fonctionnement très silencieux de l'ensemble pompe hydraulique. A cet effet, le nombre et l'écart angulaire des cames (10) est adapté au nombre et à l'écart angulaire des éléments de pompe (2), de sorte que, lorsqu'un nombre déterminé de pistons (4) se trouve au point mort haut, un nombre identique de pistons (4) se trouve au point mort bas.
EP99964362A 1999-02-22 1999-11-23 Ensemble pompe hydraulique Expired - Lifetime EP1155238B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19907311A DE19907311A1 (de) 1999-02-22 1999-02-22 Hydraulikpumpeneinheit
DE19907311 1999-02-22
PCT/DE1999/003713 WO2000050772A1 (fr) 1999-02-22 1999-11-23 Ensemble pompe hydraulique

Publications (2)

Publication Number Publication Date
EP1155238A1 true EP1155238A1 (fr) 2001-11-21
EP1155238B1 EP1155238B1 (fr) 2005-08-17

Family

ID=7898266

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99964362A Expired - Lifetime EP1155238B1 (fr) 1999-02-22 1999-11-23 Ensemble pompe hydraulique

Country Status (5)

Country Link
US (1) US6764285B1 (fr)
EP (1) EP1155238B1 (fr)
JP (1) JP2002538360A (fr)
DE (2) DE19907311A1 (fr)
WO (1) WO2000050772A1 (fr)

Cited By (2)

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EP1484502A2 (fr) * 2003-06-03 2004-12-08 Nissin Kogyo Co., Ltd. Pompe à piston
CN100458150C (zh) * 2004-01-30 2009-02-04 罗伯特·博世有限公司 高压泵

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DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
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ITMI20062003A1 (it) * 2006-10-18 2008-04-19 Sunbird Invest Ltd Pompa ad alta pressione per lubrificante per acciaierie
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EP1484502A2 (fr) * 2003-06-03 2004-12-08 Nissin Kogyo Co., Ltd. Pompe à piston
EP1484502B1 (fr) * 2003-06-03 2012-05-09 Nissin Kogyo Co., Ltd. Pompe à piston
CN100458150C (zh) * 2004-01-30 2009-02-04 罗伯特·博世有限公司 高压泵

Also Published As

Publication number Publication date
EP1155238B1 (fr) 2005-08-17
JP2002538360A (ja) 2002-11-12
US6764285B1 (en) 2004-07-20
WO2000050772A1 (fr) 2000-08-31
DE19907311A1 (de) 2000-08-31
DE59912440D1 (de) 2005-09-22

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