EP3482060B1 - High-pressure fuel pump - Google Patents
High-pressure fuel pump Download PDFInfo
- 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
- Authority
- 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
Links
- 239000000446 fuel Substances 0.000 title claims description 51
- 239000012528 membrane Substances 0.000 claims description 13
- 238000013016 damping Methods 0.000 claims description 11
- 230000007704 transition Effects 0.000 claims description 7
- 230000010349 pulsation Effects 0.000 description 4
- 230000001629 suppression Effects 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000002828 fuel tank Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 239000003990 capacitor Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 239000003351 stiffener Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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)
Description
Die Erfindung betrifft eine Kraftstoffhochdruckpumpe nach dem Oberbegriff des Anspruchs 1.The invention relates to a high-pressure fuel pump according to the preamble of claim 1.
Vom Markt her bekannt sind Kraftstoffsysteme für Brennkraftmaschinen, bei denen Kraftstoff aus einem Kraftstofftank mittels einer Vorförderpumpe und einer mechanisch angetriebenen Kraftstoffhochdruckpumpe unter hohem Druck in einen Hochdruckspeicher ("Rail") gefördert wird. An oder in einem Pumpengehäuse einer solchen Kraftstoffhochdruckpumpe ist üblicherweise eine Dämpfervorrichtung angeordnet. Eine derartige Dämpfervorrichtung umfasst meist ein Deckelelement und einen zwischen Deckelelement und Pumpengehäuse angeordneten Membrandämpfer, der üblicherweise als gasgefüllte Membrandose ausgeführt ist und über ein Halteelement am Pumpengehäuse abgestützt und in einer vertikalen Richtung zu diesem beabstandet angeordnet ist. Die Dämpfervorrichtung ist dabei fluidisch mit einem Niederdruckbereich verbunden. Die Dämpfervorrichtung dient zum Dämpfen von Druckpulsationen in dem Niederdruckbereich des Kraftstoffsystems, die beispielsweise durch Öffnungs- und Schließvorgänge von Ventilen, bspw. eines Einlassventils, in der Kraftstoffhochdruckpumpe hervorgerufen werden. Eine solche Dämpfervorrichtung ist zum Beispiel aus Dokument
Aufgabe der vorliegenden Erfindung ist es, eine Kraftstoffhochdruckpumpe bereitzustellen, deren Betrieb für Fahrzeuginsassen als wenig störend empfunden wird.It is the object of the present invention to provide a high-pressure fuel pump, the operation of which is perceived as less disruptive for vehicle occupants.
Diese Aufgabe wird durch eine Kraftstoffhochdruckpumpe nach Anspruch 1 gelöst. Durch die erfindungsgemäße Kraftstoffhochdruckpumpe ist gewährleistet, dass Schwingungen des Deckelelements, die im Betrieb der Kraftstoffhochdruckpumpe bspw. aufgrund von Schallentwicklung bei Anschlägen eines Stößels, der ein Mengensteuerventil betätigt, auftreten, nur eine geringe Geräuschemission hervorrufen, bzw. dass die von dem Deckelelement abgestrahlten Geräuschemissionen von den Fahrzeuginsassen nicht als störend wahrgenommen werden.This object is achieved by a high-pressure fuel pump according to claim 1. 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.
Erfindungsgemäss ist, eine Versteifung einer Wand des Deckelelements jedenfalls auch dadurch gebildet, dass gekrümmte Bereiche der Wand, die wenigstens auch in radialer Richtung verlaufen, ein jeweiliges Krümmungszentrum auf Seiten des Dämpfungsvolumens aufweisen. Anders ausgedrückt: ein solcher Abschnitt der Wand, der insgesamt im Wesentlichen oder zumindest auch in radialer Richtung verläuft, ist vom Dämpfungsvolumen (bzw. - wäre der Abschnitt der Wand eine Linse - vom "Brennpunkt") aus gesehen konkav gekrümmt. Dabei bildet dieser gekrümmte Verlauf der Wand die Versteifung. Mit einem Krümmungszentrum auf Seiten des Dämpfungsvolumens ist gemeint, dass der Mittelpunkt eines lokalen Krümmungskreises (auch Schmiegekreis oder Schmiegkreis genannt) auf Seiten des Dämpfungsvolumens liegt. Der Krümmungskreis in einem jeweiligen Punkt der Wand ist dabei der Kreis, der den Verlauf der Wand in diesem Punkt am besten annähert, der sich also lokal an den Verlauf der Wand anschmiegt. Eine Tangente des Krümmungskreises in diesem Punkt stimmt mit der Tangente der Wand überein. Dabei kann ein Punkt auf der Wand je nach Schnittebene verschiedene Krümmungskreise aufweisen (die zu betrachtenden Schnittebenen sind jeweils parallel zu einer Kolbenlängsachse angeordnet). Die derartig gekrümmte Wand weist einen selbststabilisierenden Effekt auf, wodurch das Deckelelement bei geringer Materialstärke und damit geringem Gewicht, geringer Baugröße und kompakten Abmessungen eine hohe Steifigkeit und damit Widerstand gegenüber Schwingungen aufweist.According to the invention, 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. In other words, such 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.
Es sei an dieser Stelle aber auch darauf hingewiesen, dass die Versteifung auch auf ganz andere Art und Weise hergestellt werden kann, beispielsweise durch das Ausformen von Versteifungsrippen, durch eine entsprechende Auswahl der Materialstärke und/oder eine entsprechende Auswahl der Materialmasse der Wand.It should be noted at this point, however, that the 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.
Bevorzugt ist, wenn das Deckelelement Teil einer Dämpfervorrichtung ist, die einen Membrandämpfer, der zwischen Deckelelement und Pumpengehäuse angeordnet ist, vorzugsweise ein Halteelement, über das der Membrandämpfer am Pumpengehäuse abgestützt und in einer vertikalen Richtung zum Pumpengehäuse beabstandet angeordnet ist, und vorzugsweise ein Federelement, über das der Membrandämpfer am Deckelelement abgestützt und in der vertikalen Richtung zu diesem beabstandet angeordnet ist, umfasst. Durch die Ausbildung des Deckelelements als Teil der eben beschriebenen Dämpfervorrichtung können Druckschwankungen im Betrieb der erfindungsgemäßen Kraftstoffhochdruckpumpe in vorteilhafter Weise gedämpft werden.It is preferred if 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. By designing the cover element as part of the damper device just described, pressure fluctuations during operation of the high-pressure fuel pump according to the invention can be dampened in an advantageous manner.
Erfindungsgemäss, weist das Deckelelement einen ersten Abschnitt, der insgesamt axial verläuft, und einen zweiten Abschnitt, der in radialer Richtung verläuft, auf. Hierdurch wird auf einfache Art und Weise das Dämpfungsvolumen geschaffen. Dabei wird das Schwingungsverhalten des Deckelelements im Betrieb der Kraftstoffhochdruckpumpe in vorteilhafter Weise beeinflusst, so dass besonders geringe Geräuschemissionen bei hoher Dämpfungskapazität im Betrieb der Kraftstoffhochdruckpumpe auftreten. Mit "in radialer Richtung verlaufend" ist in Bezug auf den zweiten Abschnitt gemeint, dass dieser in seinem Verlauf eine Komponente aufweist, die in radiale Richtung zeigt, der zweite Abschnitt also nicht vollständig in radialer Richtung verlaufen muss. Von diesem Merkmal umfasst ist also auch ein zweiter Abschnitt, der schräg in radialer und axialer Richtung verläuft.According to the invention, the cover element has a first section, which runs axially as a whole, and a second section, which runs in the radial direction. This creates the damping volume in a simple manner. 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.
Von Vorteil ist dabei, wenn der axial verlaufende erste Abschnitt des Deckelelements an seinem dem zweiten Abschnitt abgewandten Ende einen radial innenliegenden abgeschrägten Bereich zum Anfügen an das Pumpengehäuse aufweist. Hierdurch kann das Deckelelement in vorteilhafter Weise an das Pumpengehäuse angefügt werden und beispielsweise mittels eines Kondensator-Entladungs-Einpress-Schweißvorgangs an dem Pumpengehäuse befestigt werden. Dabei ist es bevorzugt, wenn der radial innenliegend abgeschrägte Bereich des Deckelelements einen Teil des Pumpengehäuses in radialer Richtung umschließt. Hierdurch kann das Deckelelement in einfacher Weise am Pumpengehäuse befestigt werden.It is advantageous here if the axially extending first section of the cover element has, at its end facing away from the second section, a radially inner beveled area for joining to the pump housing. In this way, 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. It is preferred here if 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.
Bevorzugt ist auch, wenn der zweite Abschnitt - also jener Abschnitt der Wand, der insgesamt oder wenigstens auch in radialer Richtung verläuft und der vom Dämpfungsvolumen (bzw. - wäre der Abschnitt der Wand eine Linse - vom Brennpunkt) aus gesehen insgesamt konkav ist - einen Übergangsbereich, der einen Querschnitt mit einem ersten inneren Krümmungsradius zwischen 2 mm bis 10 mm, vorzugsweise zwischen 5 mm bis 9 mm, vorzugsweise zwischen 6 mm bis 8 mm, insbesondere zwischen 6,5 mm bis 7,5 mm, insbesondere von 7 mm, aufweist und einen Hauptbereich, der einen Querschnitt mit einem zweiten inneren Krümmungsradius zwischen 40 mm bis 54 mm, vorzugsweise zwischen 42 mm bis 52 mm, vorzugsweise zwischen 44 mm bis 50 mm, insbesondere zwischen 46 mm bis 48 mm, insbesondere von 47 mm aufweist, umfasst, wobei der zweite Abschnitt vorzugsweise aus dem Übergangsbereich und dem Hauptbereich besteht. Hierdurch wird auf besonders einfache und leicht herstellbare Art und Weise erreicht, dass Schwingungsmoden oder Resonanzfrequenzen des Deckels derart liegen, dass im Betrieb der Pumpe ein vorteilhaftes Spektrum an Geräuschemissionen bzw. Geräuschabstrahlung auftritt, welche vom Nutzer eines Fahrzeugs, in dem die Kraftstoffhochdruckpumpe verbaut ist, nicht bzw. als nicht unangenehm wahrgenommen wird.It is also preferred if 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. In this way, it is achieved in a particularly simple and easily producible manner that 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.
Von Vorteil ist auch, wenn der insgesamt axial verlaufende erste Abschnitt des Deckelelements eine axiale Erstreckung von wenigstens 5 mm, vorzugsweise von wenigstens 6 mm, vorzugsweise von wenigstens 7 mm, insbesondere von wenigstens 8 mm und/oder von höchstens 12 mm, vorzugsweise von höchstens 11 mm, vorzugsweise von höchstens 10 mm, insbesondere von höchstens 9 mm, aufweist. Ein solches Deckelelement bietet ausreichend Platz, um weitere Teile der Dämpfervorrichtung zwischen Deckelelement und Pumpengehäuse aufzunehmen, beispielsweise den oben genannten Membrandämpfer. Dennoch ist die Bauhöhe insgesamt vergleichsweise gering, und das Resonanzverhalten ist so, dass unerwünschte Geräuschemissionen wirksam unterdrückt werden.It is also advantageous if 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.
Von Vorteil ist auch, wenn der insgesamt im Wesentlichen radial verlaufende zweite Abschnitt der Wand des Deckelelements in axialer Richtung gesehen eine Erstreckung von wenigstens 7 mm, vorzugsweise von wenigstens 8 mm, vorzugsweise von wenigstens 9 mm, insbesondere von wenigstens 9,5 mm und/oder von höchstens 13 mm, vorzugsweise von höchstens 12 mm, vorzugsweise von höchstens 11 mm, insbesondere von höchstens 10,5 mm, aufweist. Je höher die axiale Erstreckung des zweiten Abschnitts desto stärker gekrümmt kann der zweite Abschnitt ausgeführt werden, was zu einer besonders wirksamen Unterdrückung von Geräuschemissionen führt, sich jedoch negativ auf die benötigte Bauhöhe der Kraftstoffhochdruckpumpe auswirkt. Die eben genannten Bereiche stellen eine vorteilhafte Kompromisslösung zwischen Geräuschunterdrückung und platzsparender Bauhöhe der erfindungsgemäßen Kraftstoffhochdruckpumpe dar.It is also advantageous if the generally radially extending second section of the wall of the cover element, viewed in the axial direction, 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 higher the axial extent of the second section, the more curved the second section can be, which leads to a particularly effective suppression of noise emissions, but has a negative effect on the required overall height of the high-pressure fuel pump. 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.
Vorteilhaft ist auch, wenn eine Wandstärke des Deckelelements in einem radial inneren Bereich mindestens 1,5 mm, vorzugsweise mindestens 1,6 mm, vorzugsweise mindestens 1,65 mm beträgt, wobei der innere Bereich um eine Mittelachse des Deckelelements angeordnet ist und in radialer Richtung einen Durchmesser von mindestens 41 mm, vorzugsweise 41,7 mm, vorzugsweise 43 mm, insbesondere 45 mm, aufweist. Die genannte Mindestdeckelstärke im radial inneren Bereich führt zu einem ausreichenden Maß an Unterdrückung von Schwingungen des Deckelelements, die Geräusche im Betrieb der Kraftstoffhochdruckpumpe verursachen. Die angegebenen Werte für die Wandstärke erlauben eine kostengünstige Herstellung des Deckels bei geringer Einbaugröße und vertretbarem Gewicht der Kraftstoffhochdruckpumpe bei jedoch gleichzeitig ausreichender Unterdrückung von Geräuschemissionen.It is also advantageous if 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.
Vorteilhaft ist auch, wenn das Deckelelement eine axiale Erstreckung von wenigstens 15 mm, vorzugsweise von wenigstens 16 mm, vorzugsweise von wenigstens 17 mm, insbesondere von wenigstens 18 mm, und/oder eine axiale Erstreckung von höchstens 22 mm, vorzugsweise von höchstens 21 mm, vorzugsweise von höchstens 20 mm, insbesondere von höchstens 19 mm, aufweist. Die beschriebenen unteren Grenzen stellen vorteilhafte Werte dar, die es ermöglichen, beispielsweise den Membrandämpfer, das Halteelement und/oder das Federelement, wie oben beschrieben, zwischen Deckelelement und Pumpengehäuse anzuordnen, wobei die angegebenen Höchstwerte eine vorteilhafte geringe Bauhöhe der Kraftstoffhochdruckpumpe gewährleisten.It is also advantageous if 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.
Weitere Merkmale, Anwendungsmöglichkeiten und Vorteile der Erfindung ergeben sich aus der nachfolgenden Ansprüche, wobei die Merkmale sowohl in Alleinstellung als auch in unterschiedlicher Kombination für die Erfindung wichtig sein können, ohne dass hierauf nochmals explizit hingewiesen wird. Es zeigen:
- Figur 1
- eine vereinfachte schematisierte Darstellung eines Kraftstoffsystems für eine Brennkraftmaschine;
- Figur 2
- eine Schnittdarstellung einer erfindungsgemäßen Kraftstoffhochdruckpumpe;
- Figur 3
- eine einzelne vergrößerte Darstellung eines Deckelelements der Kraftstoffhochdruckpumpe aus
Figur 2 im Detail; und - Figur 4
- ein Diagramm, in dem die Resonanzfrequenz des Deckelelements aus
Figur 2 undFigur 3 im Detail und Vergleich mit der Resonanzfrequenz einer herkömmlichen Kraftstoffhochdruckpumpe dargestellt ist.
- Figure 1
- a simplified schematic representation of a fuel system for an internal combustion engine;
- Figure 2
- a sectional view of a high-pressure fuel pump according to the invention;
- Figure 3
- a single enlarged illustration of a cover element of the high-pressure fuel pump
Figure 2 in detail; and - Figure 4
- a diagram showing the resonance frequency of the cover element
Figure 2 andFigure 3 is shown in detail and in comparison with the resonance frequency of a conventional high-pressure fuel pump.
Ein Kolben 34 der Kraftstoffhochdruckpumpe 22 kann mittels eines vorliegend als Nockenscheibe ausgeführten Antriebs 36 entlang einer Kolbenlängsachse 38 auf- und abbewegt werden, was durch einen Pfeil mit dem Bezugszeichen 40 schematisch dargestellt ist. Hydraulisch zwischen dem Kolbenraum 26 und einem Auslassstutzen 42 der Kraftstoffhochdruckpumpe 22 ist ein Auslassventil 44 angeordnet, das zu einem Hochdruckspeicher 46 ("Rail") hin öffnen kann. Über ein Druckbegrenzungsventil 48, das bei Überschreiten eines Grenzdrucks im Hochdruckspeicher 46 öffnet, sind der Hochdruckspeicher 46 und der Kolbenraum 26 fluidisch verbindbar.A
Über ein Druckbegrenzungsventil 48, das bei Überschreiten eines Grenzdrucks im Hochdruckspeicher 46 öffnet, sind der Hochdruckspeicher 46 und der Kolbenraum 26 fluidisch verbindbar. Das Druckbegrenzungsventil 48 ist als federbelastetes Rückschlagventil ausgebildet und kann zum Kolbenraum 26 hin öffnen.The high-
Die Kraftstoffhochdruckpumpe 22 ist in
In der Darstellung von
Das Pumpengehäuse 52 und das Deckelelement 54 begrenzen einen Innenraum 58 der Druckdämpfervorrichtung 29. In dem Innenraum 58 der Druckdämpfervorrichtung 29 ist ein Membrandämpfer 60 angeordnet. Dieser umfasst eine erste und in den Figuren obere Membran 62 und eine zweite und in den Figuren untere Membran 64, die randseitig miteinander verschweißt sind. Die obere Membran 62 und die untere Membran 64 umschließen ein Dämpfungsvolumen 66, das mit Gas gefüllt und kompressibel ist, da die beiden Membranen 62 und 64 jeweils flexible Wände für das Dämpfungsvolumen 66 darstellen.The
Der Membrandämpfer 60 ist randseitig über ein Abstützelement 68 am Pumpengehäuse 52 abgestützt und in einer axialen bzw. in den Figuren vertikalen Richtung entlang der Kolbenlängsachse 38 zu diesem beabstandet angeordnet. Ein Federelement 70 ist dem Abstützelement 68 gegenüberliegend zwischen Membrandämpfer 60 und Deckelelement 54 angeordnet. Über das Federelement 70 ist der Membrandämpfer 60 am Deckelelement 54 abgestützt und in der axialen Richtung 38 zu diesem beabstandet angeordnet. Insgesamt ist der Membrandämpfer 60 über das Abstützelement 68 und das Federelement 70 randseitig zwischen dem Deckelelement 54 und dem Pumpengehäuse 52 verspannt.The
Im Betrieb der Kraftstoffhochdruckpumpe 22 wird der Kraftstoff im Niederdruckbereich 28 zu Druckpulsationen angeregt. Diese Druckpulsationen können durch Kompression bzw. Dekompression des Membrandämpfers 60 ausgeglichen werden.When the high-
Das Deckelelement 54 wird im Folgenden unter Bezug auf
An seinem vom zweiten Abschnitt 76 abgewandten Ende des ersten Abschnitts 74 weist der radiale Abschnitt 74 einen radial abgeschrägten Bereich 80 auf, der zum Anfügen an das Pumpengehäuse 52 dient. Der zweite Abschnitt 76 weist zum ersten Abschnitt 74 hin einen Übergangsbereich 82 mit einem ersten inneren Krümmungsradius 84 auf, der vorliegend 7 mm beträgt. Der zweite Abschnitt 76 weist außerdem einen Hauptbereich 86 auf, der sich nach radial einwärts an den Übergangsbereich 82 anschließt und der einen Querschnitt mit einem zweiten inneren Krümmungsradius 88 aufweist, wobei der zweite innere Krümmungsradius 88 vorliegend 47 mm beträgt.At its end of the
Vorliegend besteht der zweite Abschnitt 76 aus dem Übergangsbereich 78 und dem Hauptbereich 86. Ein innerer Bereich des Deckelelements ist in
Eine axiale Erstreckung des ersten Abschnitts trägt in
Im Betrieb des Einlassventils 24 wird dieses teilweise zwangsweise durch den Stößel 49 geöffnet bzw. am Schließen gehindert. Hierdurch kann die Menge an Kraftstoff, die durch die Kraftstoffhochdruckpumpe 22 gefördert wird, eingestellt werden. Schlägt der Stößel 49 an den Ventilkörper 51 des Einlassventils 24 an, so verursacht dies ein Geräusch. Dieses pflanzt sich durch das Pumpengehäuse 52 bzw. durch den Kraftstoff bis zum Deckelelement 54 fort, wodurch dieses zum Schwingen angeregt werden kann. Das Deckelelement 54 strahlt dann diese Geräusche ab. Würden die Schwingungsmoden des Deckelelements 54 bspw. im Bereich um 8000Hz liegen, so könnte es zu einer unvorteilhaften Verstärkung der Geräuschemission kommen. Durch die eben beschriebene Geometrie des Deckelelements 54 sind die Schwingungsmoden des Deckelelements 54 nahe dem nicht-hörbaren Bereich bzw. im nicht-hörbaren Bereich, insbesondere im Bereich von 12000Hz - 13000hz. Dies wirkt sich vorteilhaft auf die Geräuschemissionen im Betrieb der erfindungsgemäßen Kraftstoffhochdruckpumpe 22 aus, da diese entweder hochfrequent oder direkt im nicht-hörbaren Bereich sind.When the
In
Claims (8)
- High-pressure fuel pump (22) having a pump housing (52) and a cover element (54) which has a central axis (38), which is connected to the pump housing (52) and which has a wall (72), wherein a damping volume (66) is arranged between cover element (54) and pump housing (52), wherein the wall (72) has a stiffening means which is designed such that a resonance frequency of the cover element (54) lies above 9 kHz, preferably above 11 kHz, in particular above 12 kHz, characterized in that the stiffening of the wall (72) is at any rate also formed by virtue of the cover element (54) being composed of a first section (74), which runs in an axial direction, and a second section (76), which adjoins the first section (74) and which runs in a radial direction, wherein the second section (76) is curved in a continuous manner such that a centre of curvature of the local curvature is situated on the side of the damping volume (66).
- High-pressure fuel pump according to Claim 1, characterized in that the cover element (54) is part of a damper device (29) which comprises a membrane damper (60), which is arranged between cover element (54) and pump housing (52), preferably a support element (68), by means of which the membrane damper (60) is supported on the pump housing (52) and is arranged spaced apart in a vertical direction from the pump housing (52), and preferably a spring element (70), by means of which the membrane damper (60) is supported on the cover element (54) and is arranged spaced apart in the vertical direction from said cover element.
- High-pressure fuel pump according to Claim 1 or 2, characterized in that the first section (74) has, at its end averted from the second section (76), a radially internally situated bevelled region (80) for the joining of the cover element (54) to the pump housing (52).
- High-pressure fuel pump according to one or more of the preceding claims, characterized in that the first section (74) has an axial extent (94) 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.
- High-pressure fuel pump according to one or more of the preceding claims, characterized in that the second section (76), which runs overall substantially in the radial direction (70), comprises a radially outer transition region (82) which has a cross section with a first inner curvature radius (84) between 4 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 comprises a radially inner main region (86), which has a cross section with a second inner curvature radius (88) 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, wherein the second section (72), which runs overall substantially in the radial direction (78), is composed preferably of the transition region (82) and the main region (86).
- High-pressure fuel pump according to one or more of the preceding claims, characterized in that the second section (76), which runs overall substantially radially, has an extent (96) in the axial direction 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 at most 13 mm, preferably of at most 12 mm, preferably of at most 11 mm, in particular of at most 10.5 mm.
- High-pressure fuel pump according to one or more of the preceding claims, characterized in that a wall thickness (92) of the wall (72) in a radially inner region (90) of the second section (76), which extends overall substantially in the radial direction (78), amounts to at least 1.5 mm, preferably at least 1.6 mm, preferably at least 1.65 mm, wherein the radially inner region (90) is arranged around a central axis (38) of the cover element (54) and, in the radial direction (78), has a diameter of at least 41 mm, preferably 41.7 mm, preferably 43 mm, in particular 45 mm.
- High-pressure fuel pump according to one or more of the preceding claims, characterized in that the cover element (54) has overall an extent (98) in the axial direction 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 a vertical extent of at most 22 mm, preferably of at most 21 mm, preferably of at most 20 mm, in particular of at most 19 mm.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016212458.7A DE102016212458A1 (en) | 2016-07-08 | 2016-07-08 | High-pressure fuel pump |
PCT/EP2017/061214 WO2018007055A1 (en) | 2016-07-08 | 2017-05-10 | High-pressure fuel pump |
Publications (2)
Publication Number | Publication Date |
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EP3482060A1 EP3482060A1 (en) | 2019-05-15 |
EP3482060B1 true EP3482060B1 (en) | 2022-01-05 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP17722771.7A Active EP3482060B1 (en) | 2016-07-08 | 2017-05-10 | High-pressure fuel pump |
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US (1) | US10865751B2 (en) |
EP (1) | EP3482060B1 (en) |
JP (1) | JP2019520519A (en) |
KR (2) | KR20190026745A (en) |
CN (1) | CN109416009B (en) |
DE (1) | DE102016212458A1 (en) |
ES (1) | ES2909470T3 (en) |
WO (1) | WO2018007055A1 (en) |
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TW201945639A (en) * | 2018-03-14 | 2019-12-01 | 新加坡商祕方能源私人有限公司 | Pump for internal combustion engine and method of forming the same |
CN115398091A (en) * | 2020-05-21 | 2022-11-25 | 日立安斯泰莫株式会社 | Fuel pump |
GB2600765B (en) * | 2020-11-10 | 2023-04-05 | Delphi Tech Ip Ltd | Fuel pump assembly |
DE102021214628A1 (en) | 2021-12-17 | 2023-06-22 | Robert Bosch Gesellschaft mit beschränkter Haftung | High pressure pump for a fuel system of an internal combustion engine |
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DE10327408A1 (en) * | 2002-10-19 | 2004-04-29 | Robert Bosch Gmbh | Device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine |
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EP1411236B1 (en) * | 2002-10-19 | 2012-10-10 | Robert Bosch Gmbh | Device for damping of pressure pulsations in a fluid system, especially in a fuel system of an internal combustion engine |
DE102004002489B4 (en) * | 2004-01-17 | 2013-01-31 | Robert Bosch Gmbh | Fluid pump, in particular high-pressure fuel pump |
JP4686501B2 (en) * | 2007-05-21 | 2011-05-25 | 日立オートモティブシステムズ株式会社 | Liquid pulsation damper mechanism and high-pressure fuel supply pump having liquid pulsation damper mechanism |
DE102007038984A1 (en) * | 2007-08-17 | 2009-02-19 | Robert Bosch Gmbh | Fuel pump for a fuel system of an internal combustion engine |
JP2010180727A (en) * | 2009-02-03 | 2010-08-19 | Toyota Motor Corp | Delivery pipe |
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IT1396142B1 (en) * | 2009-11-03 | 2012-11-16 | Magneti Marelli Spa | FUEL PUMP WITH DAMPENER PERFECTED FOR A DIRECT INJECTION SYSTEM |
JP5316956B2 (en) | 2010-01-12 | 2013-10-16 | 株式会社デンソー | High pressure pump |
JP5668438B2 (en) | 2010-12-02 | 2015-02-12 | 株式会社デンソー | High pressure pump |
JP5382551B2 (en) | 2011-03-31 | 2014-01-08 | 株式会社デンソー | High pressure pump |
DE112011105490B4 (en) * | 2011-08-01 | 2018-02-22 | Toyota Jidosha Kabushiki Kaisha | Fuel pump |
JP6219672B2 (en) | 2013-10-28 | 2017-10-25 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
JP2015232283A (en) | 2014-06-09 | 2015-12-24 | トヨタ自動車株式会社 | Damper device |
JP6324282B2 (en) | 2014-09-19 | 2018-05-16 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
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JP6039787B2 (en) | 2015-12-17 | 2016-12-07 | 株式会社デンソー | High pressure pump |
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2016
- 2016-07-08 DE DE102016212458.7A patent/DE102016212458A1/en not_active Withdrawn
-
2017
- 2017-05-10 KR KR1020197000455A patent/KR20190026745A/en not_active IP Right Cessation
- 2017-05-10 KR KR1020227000132A patent/KR102466601B1/en active IP Right Grant
- 2017-05-10 US US16/315,329 patent/US10865751B2/en active Active
- 2017-05-10 EP EP17722771.7A patent/EP3482060B1/en active Active
- 2017-05-10 JP JP2019500441A patent/JP2019520519A/en active Pending
- 2017-05-10 WO PCT/EP2017/061214 patent/WO2018007055A1/en unknown
- 2017-05-10 CN CN201780042474.4A patent/CN109416009B/en active Active
- 2017-05-10 ES ES17722771T patent/ES2909470T3/en active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10327408A1 (en) * | 2002-10-19 | 2004-04-29 | Robert Bosch Gmbh | Device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine |
Also Published As
Publication number | Publication date |
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KR102466601B1 (en) | 2022-11-16 |
KR20220005630A (en) | 2022-01-13 |
US20190301415A1 (en) | 2019-10-03 |
KR20190026745A (en) | 2019-03-13 |
US10865751B2 (en) | 2020-12-15 |
CN109416009A (en) | 2019-03-01 |
DE102016212458A1 (en) | 2018-01-11 |
CN109416009B (en) | 2022-03-08 |
EP3482060A1 (en) | 2019-05-15 |
JP2019520519A (en) | 2019-07-18 |
WO2018007055A1 (en) | 2018-01-11 |
ES2909470T3 (en) | 2022-05-06 |
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