EP3482060A1 - Pompe à carburant haute pression - Google Patents

Pompe à carburant haute pression

Info

Publication number
EP3482060A1
EP3482060A1 EP17722771.7A EP17722771A EP3482060A1 EP 3482060 A1 EP3482060 A1 EP 3482060A1 EP 17722771 A EP17722771 A EP 17722771A EP 3482060 A1 EP3482060 A1 EP 3482060A1
Authority
EP
European Patent Office
Prior art keywords
wall
pressure fuel
fuel pump
cover element
pump housing
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
EP17722771.7A
Other languages
German (de)
English (en)
Other versions
EP3482060B1 (fr
Inventor
Jan Herrmann
Sebastian Bauer
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 EP3482060A1 publication Critical patent/EP3482060A1/fr
Application granted granted Critical
Publication of EP3482060B1 publication Critical patent/EP3482060B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F02M59/44—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
    • 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 high-pressure fuel pump according to the preamble of claim 1.
  • Fuel systems for internal combustion engines are known from the market, in which fuel from a fuel tank is conveyed under high pressure into a high-pressure accumulator ("rail") by means of a pre-demand pump and a mechanically driven high-pressure fuel pump.
  • a high-pressure accumulator (“rail")
  • a damper device When a high-pressure fuel pump is usually arranged a damper device.
  • a damper device usually comprises a cover element and a between cover element and
  • Pump housing arranged diaphragm damper which is usually designed as a gas-filled diaphragm box and a holding element on
  • the damper device is fluidic with a
  • the damper device serves to damp pressure pulsations in the low-pressure region of the fuel system, which are caused, for example, by opening and closing operations of valves, for example an intake valve, in the high-pressure fuel pump.
  • the object of the present invention is to provide a fuel-high return pump whose operation is perceived as little disturbing for vehicle occupants. This object is achieved by a high-pressure fuel pump according to claim 1.
  • the fuel return pump according to the invention ensures that vibrations of the cover element, which during operation of the
  • Fuel high-pressure pump for example, due to the development of sound at attacks of a plunger, which operates a quantity control valve, occur, only a small
  • a stiffening of a wall of the cover element is also formed in that curved regions of the wall, which extend at least also in the radial direction, have a respective center of curvature on the side of the damping volume.
  • a section of the wall which generally runs substantially or at least also in the radial direction, is of the damping volume (or, if the section of FIG
  • a center of curvature on the side of the damping volume means that the center of a local circle of curvature (also referred to as a circle or circle) ) lies on the side of the damping volume
  • the circle of curvature in a particular point of the wall is the circle that best approximates the course of the wall at this point, which thus conforms locally to the course of the wall.
  • a tangent of the circle of curvature at this point coincides with the tangent of the wall.
  • a point on the wall depending on the cutting plane have different curvature circles
  • the thus curved wall has a self-stabilizing effect, whereby the cover element with low material thickness and thus low weight, small size and compact dimensions high rigidity and thus resistance to
  • stiffening can also be produced in a very different way, for example by the formation of stiffening ribs, by an appropriate selection of
  • the membrane damper which is arranged between the cover element and the pump housing, preferably a holding element, supported by the diaphragm damper on the pump housing and in a vertical direction to
  • Pump housing is arranged spaced, and preferably a
  • Spring element via which the diaphragm damper is supported on the cover element and arranged in the vertical direction spaced therefrom comprises. Due to the design of the cover element as part of the just described
  • Damper device may cause pressure fluctuations during operation of the
  • inventive high-pressure fuel pump be damped in an advantageous manner.
  • the cover element has a first section which extends overall axially, and a second section which extends in the radial direction. This will in a simple way the
  • Damping capacity occur during operation of the high-pressure fuel pump.
  • extending in the radial direction with respect to the second section is meant that it has in its course a component which points in the radial direction, that is, the second section does not have to run completely in the radial direction.
  • This feature also includes a second section that extends obliquely in the radial and axial directions.
  • Lid member facing away from the second portion at its end a radially inner tapered portion for attachment to the
  • Manner be attached to the pump housing and, for example by means of a capacitor discharge press-fitting welding operation on the
  • the second section - ie that section of the wall which runs overall or at least also in the radial direction and which is concave as a whole from the damping volume (or if the section of the wall is a lens - from the focal point)
  • Transition region having a cross section with a first inner radius of curvature between 2 mm to 10 mm, preferably between 5 mm to 9 mm, preferably between 6 mm to 8 mm, in particular between 6.5 mm to 7.5 mm, in particular of 7 mm, and a main region having a cross section with a second inner radius of curvature between 40 mm to 54 mm, preferably between 42 mm to 52 mm, preferably between 44 mm to 50 mm, in particular between 46 mm to 48 mm, in particular of 47 mm, comprising, wherein the second portion preferably from the transition region and the
  • Main area consists. This is achieved in a particularly simple and easy to produce way that vibration modes or
  • Resonant frequencies of the lid are such that during operation of the pump, an advantageous spectrum of noise emissions or noise emission occurs, which by the user of a vehicle in which the
  • High-pressure fuel pump is installed, not or is not perceived as unpleasant.
  • the overall axially extending first section of the cover element has an axial extent of at least 5 mm, preferably at least 6 mm, preferably at least 7 mm, in particular at least 8 mm and / or at most 12 mm, preferably at most 1 1 mm, preferably of at most 10 mm, in particular of at most 9 mm.
  • a lid member provides sufficient space to accommodate other parts of the damper device between the cover element and the pump housing, for example, the above-mentioned membrane damper. Nevertheless, the overall height is relatively low, and the resonance behavior is such that undesirable noise emissions are effectively suppressed.
  • the overall substantially radially extending second portion of the wall of the cover element seen in the axial direction an extension of at least 7 mm, preferably at least 8 mm, preferably at least 9 mm, in particular at least 9.5 mm and / / or not more than 13 mm, preferably not more than 12 mm, preferably not more than 1 1 mm, in particular not more than 10,5 mm, having.
  • the above-mentioned areas provide an advantageous compromise solution
  • a wall thickness of the cover element in a radially inner region is at least 1.5 mm, preferably at least 1.6 mm, preferably at least 1.65 mm, the inner region being arranged around a central axis of the cover element and in the radial direction a diameter of at least 41 mm, preferably 41, 7 mm, preferably 43 mm, in particular 45 mm.
  • the said minimum cover thickness in the radially inner region leads to a sufficient degree of suppression of
  • Wall thickness allow a cost-effective production of the lid with a small installation size and reasonable weight of the high-pressure fuel pump but at the same time sufficient suppression of noise emissions.
  • the cover element has an axial extension of at least 15 mm, preferably of at least 16 mm, preferably of at least 17 mm, in particular of at least 18 mm, and / or an axial extent of at most 22 mm, preferably of at most 21 mm, preferably not more than 20 mm, in particular not more than 19 mm.
  • the described lower limits represent advantageous values which make it possible, for example, to arrange the diaphragm damper, the retaining element and / or the spring element between the cover element and the pump housing as described above, the maximum values specified ensuring an advantageously low profile of the high-pressure fuel pump.
  • Figure 1 is a simplified schematic representation of a fuel system for an internal combustion engine
  • Figure 2 is a sectional view of an inventive
  • FIG 3 is a single enlarged view of a lid member of
  • FIG. 4 shows a diagram in which the resonance frequency of the cover element from FIG. 2 and FIG. 3 is shown in detail and in comparison with the resonance frequency of a conventional fuel-boost pump.
  • FIG. 1 shows a fuel system 10 for a further not shown
  • an inlet valve 24 is arranged, via which a piston chamber 26 with a
  • Low pressure region 28 which includes the feed pump 16, the suction line 14, and the fuel tank 12, is fluidically connectable. Pressure pulsations in the
  • Low-pressure region 28 can be damped by means of a pressure damper device 29.
  • the inlet valve 24 can via a
  • Actuator 30 are forcibly opened.
  • Actuator 30 and thus the inlet valve 24 are connected via a
  • Control unit 32 controlled.
  • a piston 34 of the high-pressure fuel pump 22 can be moved up and down along a piston longitudinal axis 38 by means of a drive 36 which is designed as a cam disk, which is schematically represented by an arrow with the reference numeral 40.
  • Hydraulically between the piston chamber 26 and an outlet 42 of the high-pressure fuel pump 22 is an exhaust valve 44, which may open to a high-pressure accumulator 46 ("rail").
  • a pressure relief valve 48 which opens when a limit pressure in the high-pressure accumulator 46 is exceeded, the high-pressure accumulator 46 and the piston chamber 26 are fluidically connectable.
  • the pressure limiting valve 48 is designed as a spring-loaded check valve and can open to the piston chamber 26 out.
  • the fuel high pressure pump 22 is shown in a sectional view in FIG. In the illustration of Figure 2 it can be seen that the
  • Actuator 30 comprises a spring-loaded plunger 49.
  • the plunger 49 is movable via a magnetic coil 50 and can also one
  • the pressure damper device 29 comprises a pot-like cover element 54, which is connected to the pump housing 52 in a connection region 56, in the present case via a KEEP weld seam (capacitor discharge press-in weld).
  • the connecting portion 56 runs around the pump housing 52 in a circumferential direction.
  • the pump housing 52 and the cover member 54 define an interior 58 of the pressure damper device 29.
  • the interior 58 of the pressure damper device 29 In the interior 58 of the
  • Pressure damper device 29 is a diaphragm damper 60 is arranged. This comprises a first and in the figures upper membrane 62 and a second and in the figures lower membrane 64, which are welded together at the edges. The upper membrane 62 and the lower membrane 64 enclose
  • Damping volume 66 which is filled with gas and compressible, since the two membranes 62 and 64 are each flexible walls for the damping volume 66.
  • the diaphragm damper 60 is at the edge via a support element 68 on
  • Pump housing 52 supported and arranged in an axial or in the figures vertical direction along the piston longitudinal axis 38 spaced therefrom.
  • a spring element 70 is disposed opposite the support element 68 between the diaphragm damper 60 and the cover element 54.
  • the diaphragm damper 60 is supported on the cover member 54 and arranged in the axial direction 38 spaced therefrom. Overall, the diaphragm damper 60 is braced on the support element 68 and the spring element 70 at the edge between the cover element 54 and the pump housing 52.
  • the fuel is in
  • the cover element 54 will be explained in more detail below with reference to FIG.
  • the piston longitudinal axis 38 shown in FIG. 2 corresponds in FIG. 3 to a central axis 38 of the cover element 54.
  • the cover element 54 has a wall 72.
  • the wall 72 of the lid member 54 has a first one
  • Section 74 which runs completely vertically in Figure 3, so that its course is completely in the direction of the piston longitudinal axis 38.
  • Lid member 54 also has a second portion 76 which adjoins first portion 74 and which extends generally and substantially in a radial direction 78.
  • the second portion 76 is not only in a radial direction (arrow 78 in Figure 3) but also somewhat in the axial direction.
  • the second section 76 is away from the interior 58
  • Interior 58 is located, whereby a stiffening of the cover member 54 and its wall 72 is formed.
  • the radial portion 74 has a radially tapered portion 80, which serves for attachment to the pump housing 52.
  • the second section 76 has, for the first section 74, a transition area 82 with a first one inner radius of curvature 84, which in the present case is 7 mm.
  • the second portion 76 also has a main portion 86 which connects radially inwardly to the transition region 82 and which has a cross-section with a second inner radius of curvature 88, the second inner radius of curvature 88 being presently 47 mm.
  • the second section 76 consists of the transition area 78 and the main area 86.
  • An inner area of the cover element is provided with the reference number 90 in FIG.
  • the wall 72 of the cover element 54 has a wall thickness 92, which in the present case is 1.65 mm.
  • the inner region 90 in the present case has a diameter around the
  • An axial extension of the first section carries the reference numeral 94 in FIG. 3 and in the present case is 8.2 mm.
  • a vertical extension of the second section carries the reference numeral 94 in FIG. 3 and in the present case is 8.2 mm.
  • Section 76 bears the reference numeral 96 in FIG. 3 and in the present case amounts to 9.9 mm. Consequently, a total vertical extent 98 of the
  • Lid element 54 present 18.1 mm.
  • the second portion 76 are formed concave with respect to the interior 58.
  • the inlet valve 24 During operation of the inlet valve 24, this is partially forced open by the plunger 49 or prevented from closing. Thereby, the amount of fuel that is conveyed by the high-pressure fuel pump 22 can be adjusted. If the plunger 49 abuts the valve body 51 of the inlet valve 24, this causes a noise. This propagates through the pump housing 52 and through the fuel to the cover element 54, whereby it can be excited to vibrate. The lid member 54 then radiates these sounds. If the oscillation modes of the cover element 54 were, for example, in the region of 8000 Hz, unfavorable amplification of the noise emission could occur. Due to the just described geometry of the cover element 54, the vibration modes of the cover element 54 are close to the non-audible range or in the non-audible range, in particular in the range of 12000Hz-13000hz. This has an advantageous effect on the
  • FIG. 4 shows the noise emission 100 as a function of the excitation frequency 102.
  • the resonance behavior of the invention is
  • High-pressure fuel pump 22 is designated by the reference numeral 104 and plotted as a dashed line, and the resonance behavior of a known from the prior art high-pressure fuel pump 22 is provided with the reference numeral 106 and plotted as a solid line.
  • Resonant frequencies 107 of the high-pressure fuel pump 22 according to the invention are shifted in relation to the resonance frequencies 108 of the prior art to the inaudible range 110. Also the total height
  • Noise emission 100 (volume) in the resonant frequencies 107 is lower than at the resonant frequencies 108 of the prior art high-pressure fuel pump 22.

Landscapes

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

Abstract

L'invention concerne une pompe à carburant haute pression (22) qui comprend un carter de pompe (52) et un élément formant couvercle (54) assemblé au carter de pompe (52), qui présente une paroi (72). Un volume d'amortissement (66) est formé entre l'élément formant couvercle (54) et le carter de pompe (52), et la paroi (72) présente un renforcement configuré de telle sorte que la fréquence de résonance de l'élément formant couvercle (54) se situe au-dessus de 9 kHz, de préférence au-dessus de 11 kHz, en particulier au-dessus de 12 kHz.
EP17722771.7A 2016-07-08 2017-05-10 Pompe à carburant haute pression Active EP3482060B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016212458.7A DE102016212458A1 (de) 2016-07-08 2016-07-08 Kraftstoffhochdruckpumpe
PCT/EP2017/061214 WO2018007055A1 (fr) 2016-07-08 2017-05-10 Pompe à carburant haute pression

Publications (2)

Publication Number Publication Date
EP3482060A1 true EP3482060A1 (fr) 2019-05-15
EP3482060B1 EP3482060B1 (fr) 2022-01-05

Family

ID=58699136

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17722771.7A Active EP3482060B1 (fr) 2016-07-08 2017-05-10 Pompe à carburant haute pression

Country Status (8)

Country Link
US (1) US10865751B2 (fr)
EP (1) EP3482060B1 (fr)
JP (1) JP2019520519A (fr)
KR (2) KR20190026745A (fr)
CN (1) CN109416009B (fr)
DE (1) DE102016212458A1 (fr)
ES (1) ES2909470T3 (fr)
WO (1) WO2018007055A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW201945639A (zh) * 2018-03-14 2019-12-01 新加坡商祕方能源私人有限公司 用於內燃機之泵及形成此泵之方法
CN115398091A (zh) * 2020-05-21 2022-11-25 日立安斯泰莫株式会社 燃料泵
GB2600765B (en) * 2020-11-10 2023-04-05 Delphi Tech Ip Ltd Fuel pump assembly
DE102021214628A1 (de) 2021-12-17 2023-06-22 Robert Bosch Gesellschaft mit beschränkter Haftung Hochdruckpumpe für ein Kraftstoffsystem einer Brennkraftmaschine

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10362411B3 (de) * 2002-10-19 2017-09-07 Robert Bosch Gmbh Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine
EP1411236B1 (fr) * 2002-10-19 2012-10-10 Robert Bosch Gmbh Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
DE102004002489B4 (de) * 2004-01-17 2013-01-31 Robert Bosch Gmbh Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe
JP4686501B2 (ja) * 2007-05-21 2011-05-25 日立オートモティブシステムズ株式会社 液体脈動ダンパ機構、および液体脈動ダンパ機構を備えた高圧燃料供給ポンプ
DE102007038984A1 (de) * 2007-08-17 2009-02-19 Robert Bosch Gmbh Kraftstoffpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
JP2010180727A (ja) * 2009-02-03 2010-08-19 Toyota Motor Corp デリバリパイプ
JP4736142B2 (ja) 2009-02-18 2011-07-27 株式会社デンソー 高圧ポンプ
IT1396142B1 (it) * 2009-11-03 2012-11-16 Magneti Marelli Spa Pompa carburante con dispositivo smorzatore perfezionato per un sistema di iniezione diretta
JP5316956B2 (ja) 2010-01-12 2013-10-16 株式会社デンソー 高圧ポンプ
JP5668438B2 (ja) 2010-12-02 2015-02-12 株式会社デンソー 高圧ポンプ
JP5382551B2 (ja) 2011-03-31 2014-01-08 株式会社デンソー 高圧ポンプ
DE112011105490B4 (de) * 2011-08-01 2018-02-22 Toyota Jidosha Kabushiki Kaisha Kraftstoffpumpe
JP6219672B2 (ja) 2013-10-28 2017-10-25 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
JP2015232283A (ja) 2014-06-09 2015-12-24 トヨタ自動車株式会社 ダンパー装置
JP6324282B2 (ja) 2014-09-19 2018-05-16 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
JP6012785B2 (ja) 2015-01-30 2016-10-25 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
JP6039787B2 (ja) 2015-12-17 2016-12-07 株式会社デンソー 高圧ポンプ
DE102016201082B4 (de) * 2016-01-26 2017-10-05 Continental Automotive Gmbh Kraftstoffhochdruckpumpe
DE102017213891B3 (de) * 2017-08-09 2019-02-14 Continental Automotive Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
TW201945639A (zh) * 2018-03-14 2019-12-01 新加坡商祕方能源私人有限公司 用於內燃機之泵及形成此泵之方法

Also Published As

Publication number Publication date
KR102466601B1 (ko) 2022-11-16
KR20220005630A (ko) 2022-01-13
US20190301415A1 (en) 2019-10-03
KR20190026745A (ko) 2019-03-13
US10865751B2 (en) 2020-12-15
CN109416009A (zh) 2019-03-01
EP3482060B1 (fr) 2022-01-05
DE102016212458A1 (de) 2018-01-11
CN109416009B (zh) 2022-03-08
JP2019520519A (ja) 2019-07-18
WO2018007055A1 (fr) 2018-01-11
ES2909470T3 (es) 2022-05-06

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