EP3482060B1 - Pompe à carburant haute pression - Google Patents

Pompe à carburant haute pression Download PDF

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Publication number
EP3482060B1
EP3482060B1 EP17722771.7A EP17722771A EP3482060B1 EP 3482060 B1 EP3482060 B1 EP 3482060B1 EP 17722771 A EP17722771 A EP 17722771A EP 3482060 B1 EP3482060 B1 EP 3482060B1
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EP
European Patent Office
Prior art keywords
section
cover element
pressure fuel
fuel pump
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.)
Active
Application number
EP17722771.7A
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German (de)
English (en)
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EP3482060A1 (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
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Robert Bosch GmbH
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Publication of EP3482060A1 publication Critical patent/EP3482060A1/fr
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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
    • 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
    • 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
    • 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.
  • a damper device is usually arranged on or in a pump housing of such a high-pressure fuel pump.
  • Such a damper device usually comprises a cover element and a diaphragm damper arranged between the cover element and the pump housing, which is usually designed as a gas-filled diaphragm can and is supported on the pump housing via a retaining element and is arranged at a distance from it in a vertical direction.
  • the damper device is fluidically connected to a low-pressure area.
  • the damper device serves to dampen pressure pulsations in the low-pressure region of the fuel system, which are caused, for example, by opening and closing processes of valves, for example an inlet valve, in the high-pressure fuel pump.
  • a damper device is for example from document WO 2016/042 853 A1 known.
  • the high-pressure fuel pump according to the invention ensures that vibrations of the cover element, which occur during operation of the high-pressure fuel pump, for example due to the generation of noise when a plunger that actuates a quantity control valve strikes, only cause a low level of noise, or that the noise emitted by the cover element of are not perceived as annoying by the vehicle occupants.
  • a stiffening of a wall of the cover element is in any case also formed in that curved regions of the wall, which also run at least in the radial direction, have a respective center of curvature on the side of the damping volume.
  • a section of the wall which as a whole runs essentially or at least also in the radial direction, is concavely curved from the damping volume (or - if the section of the wall were a lens - viewed from the "focal point").
  • This curved course of the wall forms the stiffener.
  • a center of curvature on the side of the damping volume means that the center of a local curvature circle (also called osculating circle or osculating circle) lies on the side of the damping volume.
  • the circle of curvature at a respective point on the wall is the circle that best approximates the course of the wall at this point, that is to say that it hugs the course of the wall locally.
  • a tangent of the circle of curvature at this point coincides with the tangent of the wall.
  • a point on the wall can have different circles of curvature depending on the cutting plane (the cutting planes to be considered are each arranged parallel to a piston longitudinal axis).
  • the wall curved in this way has a self-stabilizing effect, as a result of which the cover element has high rigidity and thus resistance to vibrations with a low material thickness and thus low weight, small size and compact dimensions.
  • stiffening can also be produced in a completely different way, for example by forming stiffening ribs, by selecting the material thickness and / or selecting the material mass of the wall accordingly.
  • the cover element is part of a damper device which has a diaphragm damper which is arranged between the cover element and the pump housing, preferably a holding element via which the diaphragm damper is supported on the pump housing and is arranged at a distance from the pump housing in a vertical direction, and preferably a spring element, via which the membrane damper is supported on the cover element and arranged at a distance from it in the vertical direction.
  • the cover element has a first section, which runs axially as a whole, and a second section, which runs in the radial direction.
  • the vibration behavior of the cover element is influenced in an advantageous manner when the high-pressure fuel pump is in operation, so that particularly low noise emissions occur with a high damping capacity when the high-pressure fuel pump is in operation.
  • “Running in the radial direction” with regard to the second section means that the latter has a component in its course which points in the radial direction, so the second section does not have to run completely in the radial direction.
  • This feature also includes a second section which runs obliquely in the radial and axial directions.
  • the cover element has, at its end facing away from the second section, a radially inner beveled area for joining to the pump housing.
  • the cover element can advantageously be attached to the pump housing and fastened to the pump housing, for example, by means of a capacitor discharge press-fit welding process.
  • the radially inner beveled region of the cover element encloses part of the pump housing in the radial direction. This allows the cover element to be attached to the pump housing in a simple manner.
  • the second section - that is, that section of the wall which runs as a whole or at least also in the radial direction and which is generally concave from the damping volume (or - if the section of the wall were a lens - viewed from the focal point) - is one Transition area which has 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 7 mm, and a main area which has 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 47 mm, comprises, wherein the second section preferably consists of the transition area and the main area.
  • the vibration modes or resonance frequencies of the cover are such that an advantageous spectrum of noise emissions or noise radiation occurs during operation of the pump, which the user of a vehicle in which the high-pressure fuel pump is installed, is not perceived or is not perceived as unpleasant.
  • the overall axially extending first section of the cover element has an axial extension of at least 5 mm, preferably of at least 6 mm, preferably of at least 7 mm, in particular of at least 8 mm and / or of at most 12 mm, preferably of at most 11 mm, preferably of at most 10 mm, in particular of at most 9 mm.
  • Such a cover element offers sufficient space to accommodate further parts of the damper device between the cover element and the pump housing, for example the membrane damper mentioned above. Nevertheless, the overall height is comparatively low, and the resonance behavior is such that undesired noise emissions are effectively suppressed.
  • the generally radially extending second section of the wall of the cover element has an extension of at least 7 mm, preferably of at least 8 mm, preferably of at least 9 mm, in particular of at least 9.5 mm and / or of a maximum of 13 mm, preferably of a maximum of 12 mm, preferably of a maximum of 11 mm, in particular of a maximum of 10.5 mm, having.
  • the areas just mentioned represent an advantageous compromise between noise suppression and space-saving overall height of the high-pressure fuel pump according to the invention.
  • a wall thickness of the cover element in a radially inner area is at least 1.5 mm, preferably at least 1.6 mm, preferably at least 1.65 mm, the inner area being arranged around a central axis of the cover element and in the radial direction has a diameter of at least 41 mm, preferably 41.7 mm, preferably 43 mm, in particular 45 mm.
  • the mentioned minimum cover thickness in the radially inner area leads to a sufficient degree of suppression of vibrations of the cover element, which cause noises during operation of the high-pressure fuel pump.
  • the specified values for the wall thickness allow the cover to be manufactured inexpensively with a small installation size and reasonable weight of the high-pressure fuel pump while at the same time providing adequate 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 extension of at most 22 mm, preferably at most 21 mm, preferably of at most 20 mm, in particular of at most 19 mm.
  • the lower limits described represent advantageous values that make it possible, for example, to arrange the diaphragm damper, the retaining element and / or the spring element, as described above, between the cover element and the pump housing, the specified maximum values ensuring an advantageously low overall height of the high-pressure fuel pump.
  • FIG. 1 shows a fuel system 10 for an internal combustion engine, not shown further, in a simplified schematic illustration.
  • fuel is supplied from a fuel tank 12 via a suction line 14, by means of a prefeed pump 16 and a low-pressure line 18 via an inlet 20 to a high-pressure fuel pump 22 designed as a piston pump.
  • an inlet valve 24 is arranged, via which a piston chamber 26 can be fluidically connected to a low-pressure region 28, which comprises the prefeed pump 16, the suction line 14, and the fuel tank 12. Pressure pulsations in the low-pressure region 28 can be dampened by means of a pressure damper device 29.
  • the inlet valve 24 can be forcibly opened via an actuating device 30.
  • the actuation device 30 and thus the inlet valve 24 can be controlled via a control unit 32.
  • 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 embodied here as a cam disk, which is shown schematically by an arrow with the reference number 40.
  • An outlet valve is located hydraulically between the piston chamber 26 and an outlet connection 42 of the high-pressure fuel pump 22 44 arranged, which can open to a high pressure accumulator 46 ("rail").
  • the high-pressure accumulator 46 and the piston chamber 26 can be fluidically connected via a pressure-limiting 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 can be fluidically connected via a pressure limiting valve 48, which opens when a limit pressure in the high-pressure accumulator 46 is exceeded.
  • the pressure limiting valve 48 is designed as a spring-loaded check valve and can open towards the piston chamber 26.
  • the high pressure fuel pump 22 is in Figure 2 shown in a sectional view.
  • the actuating device 30 comprises a spring-loaded plunger 49.
  • the tappet 49 can be moved via a solenoid 50 and can forcibly open a likewise spring-loaded valve body 51 of the inlet valve 24.
  • the pressure damper device 29 is arranged in the upper region of the high-pressure fuel pump 22.
  • the pressure damper device 29 comprises a pot-like cover element 54, which is connected to the pump housing 52 in a connection area 56, in the present case via a KEEP weld seam (capacitor discharge press-fit weld seam).
  • the connection region 56 runs around the pump housing 52 in a circumferential direction.
  • the pump housing 52 and the cover element 54 delimit an interior space 58 of the pressure damper device 29.
  • a membrane damper 60 is arranged in the interior space 58 of the pressure damper device 29. This comprises a first and, in the figures, upper membrane 62 and a second and, in the figures, lower membrane 64, which are edge-welded to one another.
  • the upper membrane 62 and the lower membrane 64 enclose a damping volume 66 which is filled with gas and compressible, since the two membranes 62 and 64 each represent flexible walls for the damping volume 66.
  • the diaphragm damper 60 is supported on the edge side via a support element 68 on the pump housing 52 and is arranged at a distance from it in an axial direction or, in the figures, a vertical direction along the piston longitudinal axis 38.
  • a spring element 70 is arranged opposite the support element 68 between membrane damper 60 and cover element 54.
  • the diaphragm damper 60 is supported on the cover element 54 via the spring element 70 and is arranged at a distance therefrom in the axial direction 38.
  • the membrane damper 60 is braced on the edge between the cover element 54 and the pump housing 52 via the support element 68 and the spring element 70.
  • the cover element 54 is described below with reference to FIG Figure 3 further explained in detail.
  • the drawn piston longitudinal axis 38 corresponds to FIG Figure 3 a central axis 38 of the cover element 54.
  • the cover element 54 has a wall 72.
  • the wall 72 of the cover element 54 has a first section 74, which in FIG Figure 3 runs completely vertically, the course of which therefore lies completely in the direction of the piston longitudinal axis 38.
  • the wall 72 of the cover element 54 also has a second section 76 which adjoins the first section 74 and which runs as a whole and essentially in a radial direction 78. This means that the second section 76 is not only in a radial direction (arrow 78 in Figure 3 ) but also runs somewhat in the axial direction.
  • the second section 76 is bulged away from the interior 58, as concave from the interior 58 (or - if the second section 26 were a lens - viewed from the focal point) and is thus curved in such a way that a center of curvature of the local curvature on the side of the interior 58 lies, whereby a stiffening of the cover element 54 or its wall 72 is formed.
  • the radial section 74 has a radially beveled region 80 which is used for joining to the pump housing 52.
  • the second section 76 has a transition region 82 with a first one towards the first section 74 inner radius of curvature 84, which in the present case is 7 mm.
  • the second section 76 also has a main area 86 which adjoins the transition area 82 radially inward and which has a cross section with a second inner radius of curvature 88, the second inner radius of curvature 88 being 47 mm in the present case.
  • the second section 76 consists of the transition area 78 and the main area 86.
  • An inner area of the cover element is shown in FIG Figure 3 provided with the reference number 90.
  • 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 piston longitudinal axis 38 of 41.7 mm.
  • An axial extension of the first section contributes to Figure 3 the reference number 94 and in the present case is 8.2 mm.
  • a vertical extension of the second section 76 carries in Figure 3 the reference numeral 96 and in the present case is 9.9 mm. Consequently, a total vertical extension 98 of the cover element 54 is 18.1 mm in the present case.
  • Sections of the wall 72 running in the radial direction, that is to say in the present case the second section 76, are designed to be concave with respect to the interior 58.
  • the inlet valve 24 When the inlet valve 24 is in operation, it is partially forcibly opened by the plunger 49 or prevented from closing. In this way, the amount of fuel that is delivered by the high-pressure fuel pump 22 can be adjusted. If the tappet 49 strikes the valve body 51 of the inlet valve 24, this causes a noise. This propagates through the pump housing 52 or through the fuel to the cover element 54, whereby this can be excited to vibrate. The cover element 54 then emits these noises. If the oscillation modes of the cover element 54 were, for example, in the range around 8000 Hz, an unfavorable amplification of the noise emission could result.
  • the vibration modes of the cover element 54 are close to the inaudible range or in the inaudible range, in particular in the range from 12000 Hz to 13000 Hz. This has an advantageous effect on the noise emissions during the operation of the high-pressure fuel pump 22 according to the invention, since these are either high-frequency or directly in the inaudible range.
  • the noise emission 100 is shown as a function of the excitation frequency 102.
  • the resonance behavior of the high-pressure fuel pump 22 according to the invention is denoted by the reference number 104 and plotted as a dashed line, and the resonance behavior of a high-pressure fuel pump 22 known from the prior art is given the reference numeral 106 and plotted as a solid line.
  • the resonance frequencies 107 of the high-pressure fuel pump 22 according to the invention are shifted towards the inaudible region 110 compared to the resonance frequencies 108 of the prior art.
  • the total level of noise emission 100 (volume) in the resonance frequencies 107 is also lower than in the case of the resonance frequencies 108 of the high-pressure fuel pump 22 known from the prior art.

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

Claims (8)

  1. Pompe à carburant haute pression (22) dotée d'un corps de pompe (52) et d'un élément couvercle (54) présentant un axe médian (38), lequel élément couvercle est relié au corps de pompe (52) et présente une paroi (72), un volume d'amortissement (66) étant disposé entre l'élément couvercle (54) et le corps de pompe (52), la paroi (72) présentant un renforcement qui est réalisé de telle sorte qu'une fréquence de résonance de l'élément couvercle (54) se situe au-dessus de 9 kHz, de préférence au-dessus de 11 kHz, en particulier au-dessus de 12 kHz, caractérisée en ce que le renforcement de la paroi (72) est en tout cas également formé par le fait que l'élément couvercle (54) est constitué d'une première partie (74), qui s'étend dans la direction axiale, et une deuxième partie (76), qui se raccorde à la première partie (74) et s'étend dans la direction radiale, la deuxième partie (76) étant incurvée de manière continue de telle sorte qu'un centre de la courbure locale se situe sur le côté du volume d'amortissement (66).
  2. Pompe à carburant haute pression selon la revendication 1, caractérisée en ce que l'élément couvercle (54) fait partie d'un dispositif amortisseur (29) qui comporte un amortisseur à membrane (60), qui est disposé entre l'élément couvercle (54) et le corps de pompe (52), de préférence un élément de support (68), par le biais duquel l'amortisseur à membrane (60) est supporté sur le corps de pompe (52) et est disposé de manière espacée dans une direction verticale par rapport au corps de pompe (52), et de préférence un élément ressort (70), par le biais duquel l'amortisseur à membrane (60) est supporté sur l'élément couvercle (54) et est disposé de manière espacée par rapport à celui-ci dans la direction verticale.
  3. Pompe à carburant haute pression selon la revendication 1 ou 2, caractérisée en ce que la première partie (74) présente, à son extrémité opposée à la deuxième partie (76), une région (80) biseautée située radialement à l'intérieur pour joindre l'élément couvercle (54) au corps de pompe (52).
  4. Pompe à carburant haute pression selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la première partie (74) présente une étendue axiale (94) d'au moins 5 mm, de préférence d'au moins 6 mm, de préférence d'au moins 7 mm, en particulier d'au moins 8 mm, et/ou d'au maximum 12 mm, de préférence d'au maximum 11 mm, de préférence d'au maximum 10 mm, en particulier d'au maximum 9 mm.
  5. Pompe à carburant haute pression selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la deuxième partie (76) s'étendant dans l'ensemble sensiblement dans la direction radiale (70) comporte une région de transition (82) radialement extérieure, laquelle présente une section transversale dotée d'un premier rayon de courbure intérieur (84) compris entre 4 mm et 10 mm, de préférence entre 5 mm et 9 mm, de préférence entre 6 mm et 8 mm, en particulier entre 6,5 mm et 7,5 mm, en particulier de 7 mm, et comporte une région principale (86) radialement intérieure, qui présente une section transversale dotée d'un deuxième rayon de courbure intérieur (88) entre 40 mm et 54 mm, de préférence entre 42 mm et 52 mm, de préférence entre 44 mm et 50 mm, en particulier entre 46 mm et 48 mm, en particulier de 47mm, la deuxième partie (72) s'étendant dans l'ensemble sensiblement dans la direction radiale (78) étant constituée de préférence de la région de transition (82) et de la région principale (86) .
  6. Pompe à carburant haute pression selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la deuxième partie (76) s'étendant dans l'ensemble sensiblement radialement présente une étendue (96) dans la direction axiale d'au moins 7 mm, de préférence d'au moins 8 mm, de préférence d'au moins 9 mm, en particulier d'au moins 9,5 mm, et/ou d'au maximum 13 mm, de préférence d'au maximum 12 mm, de préférence d'au maximum 11 mm, en particulier d'au maximum 10,5 mm.
  7. Pompe à carburant haute pression selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'une épaisseur (92) de la paroi (72) dans une région (90) radialement intérieure de la deuxième partie (76) s'étendant dans l'ensemble sensiblement dans la direction radiale (78) vaut au moins 1,5mm, de préférence au moins 1,6 mm, de préférence au moins 1,65 mm, la région (90) radialement intérieure étant disposée autour d'un axe médian (38) de l'élément couvercle (54) et présentant dans la direction radiale (78) un diamètre d'au moins 41 mm, de préférence d'au moins 41,7 mm, de préférence de 43 mm, en particulier de 45 mm.
  8. Pompe à carburant haute pression selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que l'élément couvercle (54) présente dans l'ensemble une étendue (98) dans la direction axiale d'au moins 15 mm, de préférence d'au moins 16 mm, de préférence d'au moins 17 mm, en particulier d'au moins 18 mm, et/ou une étendue verticale d'au maximum 22 mm, de préférence d'au maximum 21 mm, de préférence d'au maximum 20 mm, en particulier d'au maximum 19 mm.
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 EP3482060A1 (fr) 2019-05-15
EP3482060B1 true EP3482060B1 (fr) 2022-01-05

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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)

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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

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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

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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
DE102016212458A1 (de) 2018-01-11
CN109416009B (zh) 2022-03-08
EP3482060A1 (fr) 2019-05-15
JP2019520519A (ja) 2019-07-18
WO2018007055A1 (fr) 2018-01-11
ES2909470T3 (es) 2022-05-06

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