EP3047136B1 - Système de transport de fluide pour un fluide - Google Patents

Système de transport de fluide pour un fluide Download PDF

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Publication number
EP3047136B1
EP3047136B1 EP14761880.5A EP14761880A EP3047136B1 EP 3047136 B1 EP3047136 B1 EP 3047136B1 EP 14761880 A EP14761880 A EP 14761880A EP 3047136 B1 EP3047136 B1 EP 3047136B1
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EP
European Patent Office
Prior art keywords
pressure
damper
compression spring
delivery system
line
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
EP14761880.5A
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German (de)
English (en)
Other versions
EP3047136A1 (fr
Inventor
Achim Koehler
Andreas Dutt
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 EP3047136A1 publication Critical patent/EP3047136A1/fr
Application granted granted Critical
Publication of EP3047136B1 publication Critical patent/EP3047136B1/fr
Active legal-status Critical Current
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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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/54—Arrangement of fuel pressure regulators
    • 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
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • 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
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to a fluid delivery system for a fluid, comprising a low-pressure delivery system with a low-pressure pump and a high-pressure delivery system with a high-pressure pump, which are connected via a connecting line, and wherein the fluid delivery system comprises a pressure damper.
  • Such a fluid delivery system is known from US 2010/212639 A1 known.
  • This fluid delivery system is designed as a fuel delivery system of a common rail injection system for an internal combustion engine.
  • the fuel delivery system includes a low pressure delivery system with a low pressure pump and a high pressure delivery system with a high pressure pump.
  • the two systems are connected to each other via a connecting line.
  • the fluid delivery system has a hydraulic pressure damper disposed in the low pressure delivery system.
  • the pressure damper has a piston arranged in a cylinder and acted upon by a compression spring.
  • the compression spring is arranged in a compression spring chamber and the compression spring chamber is on the piston side a damper chamber opposite.
  • the damper chamber is connected via a damper supply line to the connecting line and the compression spring chamber is connected via a pressure spring chamber line to the connecting line.
  • a check valve opening to this space is arranged, which opens when a predetermined pressure in the connecting line is exceeded.
  • the piston When arranged in the damper supply check valve is open, the piston is moved against the force of the compression spring to the compression spring chamber.
  • the piston When pressure is reduced in the connecting line, the piston moves through the Pressure spring causes in the damper chamber wherein the pressure spring chamber is filled via the arranged in the pressure spring chamber line open check valve with fluid.
  • the pressure spring chamber is thus constantly filled with fluid.
  • the piston has through openings through which the compression spring chamber and the damper chamber are interconnected. As a result, the damping behavior of the hydraulic pressure damper is set.
  • the invention has for its object to provide a fluid delivery system with a hydraulic pressure damper with improved damping behavior.
  • the piston is displaced against the force of the compression spring in the direction of the pressure spring space by damping fluid flowing in the damper space, thereby damping the quantity wave or the pressure wave in the damper space and thus also in the connection line and in the connection line built-in components takes place.
  • the compression spring and the (fluid) pressure prevailing in the pressure spring chamber moves the piston in the direction of the damper space, while in the enlarging compression spring chamber the pressure is reduced to the constant vapor pressure, which can for example at least approximately correspond to the atmospheric pressure .
  • the compression spring is designed so that this (Together with the pressure prevailing in the compression spring chamber) pushes the piston faster in the direction of the damper chamber, as the next volume wave of the fluid reaches the damper chamber and presses the piston back in the direction of the compression spring chamber.
  • An outflow throttle can be used in particular when the return pressure is low and is very close to the vapor pressure of the fluid and when the pressure pulsations, ie the mass waves and / or the pressure waves, are very high-frequency.
  • the connecting line between the damper supply line and the pressure spring chamber line has a throttle. This throttle is optional and ensures that the aforementioned pressure difference ⁇ P is established.
  • the fluid delivery system is a fuel delivery system and the fluid fuel. While the subject matter of the present invention may be applied to any fluid delivery system, the preferred application is in a fuel delivery system.
  • This fuel delivery system is, for example, a common-rail injection system, in which the fuel supplied by the low-pressure delivery system to the high-pressure delivery system is delivered by the high-pressure pump into a high-pressure accumulator. From this high-pressure accumulator take fuel injectors stored there for taxed injection into associated combustion chambers of an internal combustion engine to which the fuel delivery system is installed.
  • FIG. 1 shows a designed as a fuel delivery system fluid delivery system for a common rail injection system.
  • the fuel delivery system has a low-pressure delivery system, which has a built-in a tank 1 low-pressure pump 2 with a pre-filter 3 and a check valve 5, a filter 4 and the above-mentioned components interconnecting connecting line in the form of a supply line 6. Furthermore, belongs to the low pressure conveyor system, a connecting line in the form of a return line 7, which opens into the tank 1 and also with not connected fuel injectors is connected to dissipate leakage fuel.
  • the return line 7 is connected to the high-pressure delivery system, in particular a high-pressure pump 8, to remove fuel and fuel not required by the high-pressure pump 8, which is conveyed through the high-pressure pump for lubrication purposes and cooling purposes.
  • the high pressure pump 8 has a schematically illustrated pump housing 9, in which a camshaft space 10 is formed.
  • the camshaft space 10 is connected to the feed line 6 and has a bearing 11a, 11b mounted in the camshaft 12, which is formed for example as a double camshaft.
  • At least one high-pressure pump element which essentially consists of a roller tappet, a pump piston 13 and a pump cylinder formed integrally with a pump cylinder head, which is a component of the pump housing or is installed in this, interacts with the camshaft 12.
  • the pump piston 13 is alternately moved up and down in the pump cylinder and promotes introduced into a pump working chamber 14 fuel via a high-pressure line 15 in a high-pressure accumulator 16, from which there stored under high pressure fuel from the fuel injectors for injection in associated combustion chambers of an internal combustion engine is removed.
  • the fuel fed into the camshaft space 10 is admitted into the pump working chamber 14 under the control of a metering unit 17, while fuel supplied by the metering unit 17, for example when the engine is idling, is not diverted to the pump working chamber 14 via a shut-off valve 18 into the return line 7. Also with the return line 7, the bearings 11a, 11b are connected, through which from the camshaft space 10 in particular for lubricating the bearings 11a, 11b, a constant amount of fuel is passed.
  • a hydraulic pressure damper 19 is installed in the supply line 6 and / or the return line 7, a hydraulic pressure damper 19 is installed.
  • the pressure damper 19 can be installed directly in the feed line 6 or the return line 7, or else be integrated into the pump housing 9 of the high pressure pump 8 in the region of the connection of the feed line 6 or the return line 7. It is expressly in the Within the scope of the invention, it is possible to install in each case an independent hydraulic pressure damper both in the feed line 6 and in the return line 7, or else to arrange either a hydraulic pressure damper 19 in the feed line 6 or the return line 7.
  • FIG. 2 shows a first embodiment of such a hydraulic pressure damper 19, which is connected here to a connecting line in the form of the feed line 6 or the return line 7.
  • the hydraulic pressure damper 19 has a damping housing in the form of a cylinder 20, in which a piston 21 is inserted.
  • the piston is subjected to force by a compression spring 23 arranged in a compression spring 23 and pressed in the direction of a damper chamber 24 which is opposite to the compression spring chamber 22 separated by the piston 21.
  • the damper chamber 24 is connected via a damper supply line 25 to the connecting line in the form of the feed line 6 or the return line 7 at a branch 26.
  • the pressure spring chamber 22 is opposite to the piston 21 bounded by a spring holder 27, on which the compression spring 23 is supported and in which a pressure spring chamber line 28 is inserted.
  • the pressure spring chamber line 28 is composed of different line sections and flows downstream of the branch 26 back into the connecting line in the form of the feed line 6 or the return line 7 a.
  • a check valve 29 is used, which shuts off the pressure spring chamber line 28 in the direction of the compression spring chamber 22.
  • At a predetermined pressure in the compression spring chamber 22 opens the check valve 29 and located in the pressure spring chamber 22 fluid is discharged via the continuing pressure spring chamber line 28 into the connecting line.
  • the pressure P1 via the damper supply line 25 in the damper chamber 24 and presses in the stationary state, the piston 21 against the compression spring 23.
  • periodic waves or pressure waves of fuel which are generated in particular by the high-pressure pump 8, on the Dämpferzutechnisch 25 in the damper chamber 24 and press the piston 21 in the direction of the compression spring chamber 22 against the force of the compression spring 23 and the pressure prevailing in the pressure spring chamber 22, which preferably at least approximately corresponds to the atmospheric pressure at rest.
  • the embodiment according to FIG. 2 differs from the embodiment according to FIG. 1 only in that a discharge throttle 31 is inserted into the pressure spring chamber line 18 instead of the check valve 29.
  • the outflow throttle 31 or the check valve 29 cause that in the pressure spring chamber 22 along the piston 21 penetrated leakage is dissipated continuously or discontinuously.

Landscapes

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

Claims (3)

  1. Système de transport de fluide pour un fluide, présentant un système de transport à basse pression comprenant une pompe à basse pression (2) et un système de transport à haute pression avec une pompe à haute pression (8), qui sont connectés par le biais d'une conduite de liaison et le système de transport de fluide présentant un amortisseur de pression (19), qui est disposé dans le système de transport à basse pression et un amortisseur de pression hydraulique (19), l'amortisseur de pression hydraulique (19) présentant un piston (21) disposé dans un cylindre (20) et sollicité par force par un ressort de pression (23), le ressort de pression (23) étant disposé dans un espace de ressort de pression (22) et un espace d'amortissement (24) étant disposé du côté du piston à l'opposé de l'espace de ressort de pression (22), caractérisé en ce que l'espace d'amortisseur (24) est connecté par le biais d'une conduite d'alimentation d'amortisseur (25) à la conduite de liaison, en ce que l'espace de ressort de pression (22) est connecté par le biais d'une conduite d'espace de ressort de pression (28) directement ou indirectement à la conduite de liaison en aval d'une dérivation (26) dans la conduite d'alimentation d'amortisseur (25) et en ce que la conduite d'espace de ressort de pression (28) présente un clapet antiretour (29) et/ou un étranglement (31) fermant l'espace de ressort de pression (22), de telle sorte qu'il se produise de la vapeur lors du déplacement du piston (21) dans la direction de l'espace d'amortisseur (24) par détente dans l'espace de ressort de pression (22) par séparation hors du fluide.
  2. Système de transport de fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que la conduite de liaison présente un étranglement (30) entre la conduite d'alimentation d'amortisseur (25) et la conduite d'espace de ressort de pression (28).
  3. Système de transport de fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que le système de transport de fluide est un système de transport de carburant et le fluide est du carburant.
EP14761880.5A 2013-09-19 2014-09-11 Système de transport de fluide pour un fluide Active EP3047136B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013218873.0A DE102013218873A1 (de) 2013-09-19 2013-09-19 Fluidfördersystem für ein Fluid
PCT/EP2014/069385 WO2015039948A1 (fr) 2013-09-19 2014-09-11 Système de transport de fluide pour un fluide

Publications (2)

Publication Number Publication Date
EP3047136A1 EP3047136A1 (fr) 2016-07-27
EP3047136B1 true EP3047136B1 (fr) 2018-11-14

Family

ID=51518786

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14761880.5A Active EP3047136B1 (fr) 2013-09-19 2014-09-11 Système de transport de fluide pour un fluide

Country Status (5)

Country Link
US (1) US10145345B2 (fr)
EP (1) EP3047136B1 (fr)
CN (1) CN105556111B (fr)
DE (1) DE102013218873A1 (fr)
WO (1) WO2015039948A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2600765B (en) * 2020-11-10 2023-04-05 Delphi Tech Ip Ltd Fuel pump assembly

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19900564C2 (de) 1999-01-09 2003-09-18 Bosch Gmbh Robert Common-Rail-System
GB2366336A (en) * 2000-08-31 2002-03-06 Delphi Tech Inc Fuel pump
DE10247210A1 (de) 2002-10-10 2004-04-22 Robert Bosch Gmbh Filteranordnung für Kraftstoffeinspritzsysteme
JP4165572B2 (ja) * 2006-04-12 2008-10-15 トヨタ自動車株式会社 内燃機関の燃料供給装置
DE102007038426A1 (de) 2007-08-14 2009-02-19 Robert Bosch Gmbh Kraftstoffeinspritzsystem
JP4803269B2 (ja) * 2009-02-24 2011-10-26 株式会社デンソー 脈動低減装置
DE102010031356A1 (de) 2010-07-15 2012-01-19 Robert Bosch Gmbh Hochdruck-Einspritzsystem für Kraftstoff-Verbrennungsmaschinen
DE102011087957A1 (de) 2011-12-08 2013-06-13 Robert Bosch Gmbh Verfahren zum Lokalisieren eines Fehlverhaltens eines Fördersystem einer Brennkraftmaschine und Fördersystem einer Brennkraftmaschine
DE102012224004A1 (de) 2012-12-20 2014-06-26 Robert Bosch Gmbh Hochdruckeinspritzsystem

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3047136A1 (fr) 2016-07-27
US10145345B2 (en) 2018-12-04
CN105556111B (zh) 2018-11-13
US20160230726A1 (en) 2016-08-11
WO2015039948A1 (fr) 2015-03-26
CN105556111A (zh) 2016-05-04
DE102013218873A1 (de) 2015-03-19

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