WO2020094278A1 - Pompe à carburant à haute pression - Google Patents

Pompe à carburant à haute pression Download PDF

Info

Publication number
WO2020094278A1
WO2020094278A1 PCT/EP2019/074624 EP2019074624W WO2020094278A1 WO 2020094278 A1 WO2020094278 A1 WO 2020094278A1 EP 2019074624 W EP2019074624 W EP 2019074624W WO 2020094278 A1 WO2020094278 A1 WO 2020094278A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve body
valve
fuel pump
pressure fuel
pump according
Prior art date
Application number
PCT/EP2019/074624
Other languages
German (de)
English (en)
Inventor
Stephan Wehr
Sebastian Vietze
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
Priority to CN201980088061.9A priority Critical patent/CN113302394B/zh
Publication of WO2020094278A1 publication Critical patent/WO2020094278A1/fr

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
    • 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
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves

Definitions

  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1.
  • a high-pressure fuel pump with a pressure-limiting valve for a fuel system of an internal combustion engine for direct petrol injection is known, for example, from DE102004013307 A1.
  • the pressure relief valve prevents pressure in one
  • High pressure accumulator of the fuel system rises too much. If the pressure in the high-pressure accumulator is too high, the valve opens in the suction stroke
  • High pressure pump the pressure relief valve to a delivery chamber of the high pressure pump of the fuel system and the pressure in the high pressure accumulator is not further increased, but fuel is released from the high pressure accumulator into the delivery chamber.
  • the pressure relief valve opens when the pressure in the high pressure accumulator is so high that a pressure difference that occurs between the high pressure accumulator and the delivery chamber in the suction stroke of the high pressure pump exceeds an opening pressure of the pressure relief valve.
  • the invention is based on the observation that hydraulic vibrations can occur in the operation of the high-pressure fuel pump in the region of the delivery chamber and in the downstream region of the pressure relief valve fluidically connected to the delivery chamber, and the invention is also based on the observation that these hydraulic vibrations
  • Wear mechanism ultimately means that the high-pressure fuel pump can no longer compress fuel with the originally intended pressure.
  • valve body in a cylindrical channel, whose diameter is D, over a length L of the
  • valve body can be displaced in a closely guided manner on its outer circumference, and that L is larger than D / 2, so that hydraulic vibrations in the downstream region of the pressure relief valve fluidically connected to the delivery chamber hardly any relative movements in the radial direction between the valve body and the valve element and barely
  • the valve body can be displaced in a narrow manner in the cylindrical channel over a length L of the valve body on its outer circumference. This is expressed quantitatively in particular by the fact that the
  • Valve body in the cylindrical channel along the whole in
  • Length L measured in the direction of displacement, into which the outer circumference of the valve body extends, has no more than 0.4 millimeters of play in the radial direction and / or can tilt by no more than 3 °. It can even be guided so closely that the valve body in the cylindrical channel has no more than 0.2 millimeters of play in the radial direction along the entire length L measured in the direction of displacement and / or can tilt by no more than 1.5 °.
  • L is greater than D / 2
  • it is further achieved that the valve body in the cylindrical channel can hardly tilt anymore and thus there can hardly be any friction between the valve element and the valve body and hardly any friction between the valve element and the valve seat can occur.
  • valve body has in particular a shape, so that one or more guide surfaces on its outer circumference
  • L is greater than 0.6D or even greater than 0.7D.
  • valve body only touches the valve element at one point.
  • Valve element to be a ball that rests on a flat surface of the valve body.
  • touching the valve body with the valve element in only one point means that the valve body would touch the valve element in only one mathematical point, if the surface roughness and the elastic deformability of the valve body and the valve element were disregarded.
  • the valve body and the valve element always have a certain roughness and a certain elastic deformability, so that an actual contact takes place in several points or along a contact surface that has a surface area that is different from zero.
  • it can also be realized what is meant by touching only one point in the context of the application.
  • the valve body can, for example, have a recess with a flat base on the side facing the valve element. For this reason, the valve element can rest, in particular, in only one point.
  • the fact that the valve body bears against the valve element in only one point has the effect that practically no torque can be transmitted from the valve body and valve element, and therefore there is little or no wear even if there are still relative movements between the valve body and the valve element occur in the radial direction.
  • valve body has an annular shoulder pointing away from the valve element, on which a spiral spring comes to bear, which presses the valve body against the valve element.
  • Hydraulic vibrations can range from
  • Coil spring occur. These measures, which further develop the invention, can effectively prevent the transmission of these vibrations to the valve body and to the valve element.
  • valve body In order to allow fuel to flow over the valve body within the cylindrical channel from the side facing the valve element to the side facing away from the valve element, provision can be made for the valve body to be tightly guided in the cylindrical channel not along the entire outer circumference of the valve body, but rather that on
  • At least one overflow channel is provided on the outer circumference of the valve body.
  • Several overflow channels can also be provided.
  • the geometry and the arrangement of the overflow channel or the overflow channels are selected in particular so that the tight guidance of the valve body in the cylindrical channel remains guaranteed.
  • the overflow channel can be, for example, a flat or a recess on the outer circumference of the valve body.
  • valve body is designed in an axially central region with a reduced diameter, so that it is in particular not closely guided in this area in the cylindrical channel, but in particular is closely guided only in the axial direction in front of and behind this central area.
  • the length L is understood in the context of the application in such a way that it is not changed by this, that is, it extends over the central region along the entire length
  • valve body has an axial bore which starts from the side of the valve body facing away from the valve element.
  • valve body has a further bore which is perpendicular to the axial bore and intersects the axial bore.
  • the further bores start, for example, from the axially central region of the valve body with a reduced diameter.
  • downstream area of the pressure relief valve are damped, which leads to a reduction in wear.
  • the valve body can have the shape of a cross section, for example
  • n-corners for example a regular triangle or a regular square or so on
  • Valve body which run in the overflow direction and on which the valve body is guided closely in the cylindrical channel, appear in the cross section as corners of the regular n-corner.
  • the corners of the regular n-corner can, for example, be rounded or chamfered (according to DIN ISO 13715: 2000-12). Further features, possible applications and advantages of the invention result from the following description of exemplary embodiments of the invention, which are explained with reference to the drawing.
  • FIG. 1 shows a longitudinal section through a first embodiment of a high-pressure fuel pump according to the invention
  • FIG. 2 is an enlarged detail view of the pressure relief valve of Figure 1;
  • Figure 3 is a perspective view of the valve body of the
  • FIGa, 4b two views of an alternative pressure relief valve or an alternative valve body
  • Figure 5 is an illustration of a known from the prior art
  • a high-pressure fuel pump for an internal combustion engine (not shown in detail) bears the reference number 10 overall.
  • the high-pressure fuel pump 10 has an essentially cylindrical overall
  • the high-pressure fuel pump 10 has an inlet and quantity control valve 14, a delivery piston 18 arranged in a delivery chamber 16, which can be reciprocated by a drive shaft (not shown), an outlet valve 20 and a pressure relief valve 22.
  • first, cylindrical channel 24 which extends coaxially to the delivery chamber 16 and to the delivery piston 18 and which leads from the delivery chamber 16 to a second cylindrical channel 26 which is arranged at an angle of 90 ° to the first channel 24 and in that Pressure relief valve 22 is added.
  • Pump housing 12 bears the reference numeral 28 in FIG. 1, a longitudinal axis of the cylindrical channel 26 bears the reference number 29.
  • a pressure damper 30 is arranged in the pump housing 12.
  • the delivery piston 18 sucks a fuel, for example a fuel such as gasoline, via the inlet and outlet valves during a suction stroke
  • Quantity control valve 14 in the delivery chamber 16 During a delivery stroke, the fuel located in the delivery space 16 is compressed and discharged via the outlet valve 20, for example into a high-pressure area 32, for example to a fuel collecting line (“rail”), where the fuel is stored under high pressure.
  • the high-pressure region 32 is connected to the high-pressure fuel pump 10 via an outlet 34 designed as an outlet connection.
  • the amount of fuel that is expelled during a delivery stroke is adjusted by the electromagnetically actuated inlet and amount control valve 14. This opens when there is an impermissible overpressure in the high pressure area
  • Pressure relief valve 22 whereby fuel can flow from the high pressure area 32 into the delivery chamber 16.
  • the pressure-limiting valve 22 connects the high-pressure region 32 to the delivery chamber 16 of the high-pressure fuel pump 10 in an open state.
  • the pressure-limiting valve 22 opens when there is a pressure difference between the outlet side
  • High pressure area 32 and the delivery chamber 16 of the fuel high pressure pump 10 exceeds a limit.
  • the pressure limiting valve 22 thus prevents the pressure in the high pressure region 32 on the outlet side from being inadmissibly high.
  • Pressure-limiting valve 22 first of all includes a sleeve-like valve seat body 38, which is pressed into the cylindrical channel 26.
  • a valve seat body 38 On the right side of the valve seat body 38 in FIG. 2, a, for example, planar (ie conical) valve seat 42 is formed, which cooperates in a sealing manner with a valve element 44, which for example has the shape of a valve ball.
  • valve seat 42 and valve element 44 can alternatively can also be designed differently than in the example, for example concave-convex or plane-plan with a seat angle difference.
  • the contact point can be designed in particular with these wear-reducing preferred forms.
  • the pressure limiting valve 22 also includes a spiral spring 52, which is supported on the pump housing 12 and presses the valve body 46 against the valve element 44.
  • the valve body 46 has an annular shoulder 464 on the side facing away from the valve element 44, on which the spiral spring 52 rests, and the valve body 46 also has a pin 465 pointing away from the valve element on the side facing away from the valve element to the valve element 44 facing turns 521 of the coil spring 52 is received.
  • valve body 46 On the side facing the valve element 44, the valve body 46 has a recess 462 with a flat base 463, on which the valve element 44 rests in only one point 50.
  • the valve body 46 can have a cross section, the shape of which corresponds to a square with rounded corners.
  • four edges 469 are thus formed on the valve body 46, along which the valve body 46 is closely guided in the cylindrical channel 26.
  • An overflow of the valve body 46 can take place along the flat side surfaces of the valve body 46, which are designed as flats 468.
  • the diameter of the channel 26 has the value D and that the length along which the valve body 46 is guided closely in the cylindrical channel 26 has the value L.
  • L is greater than 0.7D.
  • valve body 46 in an axially central region 104 with a reduced
  • cylindrical channel 26 is possibly not closely guided, but is only closely guided in the axial direction in front of and behind this central region 104.
  • the length L is not changed by this, that is, it extends over the middle region 104 along the entire extent of the
  • Valve body 46 in which it is guided closely in the cylindrical channel 26.
  • valve body 46 in this example has an axial bore 103 which starts from the side of the valve body 46 facing away from the valve element 44.
  • valve body 46 has two further bores 101, 102 which are perpendicular to one another and to the axial bore 103 and intersect one another and the axial bore.
  • the further bores 101, 102 start from the axially central region 104 of the valve body 46 with a reduced diameter.
  • Pressure relief valve 122 generate radial vibrations 300 in the area of the spiral spring 152. Relative movements in the radial direction result between the valve body 146 and the valve element 144 and the valve seat 142. These relative movements are indicated by the small arrows 200 and lead to wear.

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

Pompe à carburant haute pression comprenant un piston d'alimentation (18) monté coulissant dans un corps de pompe (12) et une chambre d'alimentation (16) délimitée par le piston d'alimentation (18), une entrée et une sortie pour le carburant, une soupape d'admission (14) s'ouvrant vers la chambre d'alimentation (16) étant prévue entre l'entrée et la chambre d'alimentation (16), et une soupape de sortie (20) s'ouvrant vers la sortie (34) étant disposée entre la chambre d'alimentation (16) et la sortie (34), et en outre une soupape de limitation de pression (22) s'ouvrant vers la chambre d'alimentation (16) étant disposée entre la chambre d'alimentation (16) et la sortie (34), la soupape de limitation de pression (22) comprenant un élément soupape (44) et un corps de soupape (46) qui pousse l'élément soupape (44) à l'encontre de la direction d'ouverture de la soupape de limitation de pression (22) en direction d'un siège de soupape (42) de la soupape de limitation de pression (22). Cette pompe à carburant haute pression est caractérisée en ce que le corps de soupape (46) peut coulisser en étant guidé étroitement sur sa périphérie externe (461) dans un canal cylindrique (26) dont le diamètre est D, sur une longueur L du corps de soupape (46), L étant supérieur à D/2.
PCT/EP2019/074624 2018-11-06 2019-09-16 Pompe à carburant à haute pression WO2020094278A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201980088061.9A CN113302394B (zh) 2018-11-06 2019-09-16 燃料高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018218919.6 2018-11-06
DE102018218919.6A DE102018218919A1 (de) 2018-11-06 2018-11-06 Kraftstoff-Hochdruckpumpe

Publications (1)

Publication Number Publication Date
WO2020094278A1 true WO2020094278A1 (fr) 2020-05-14

Family

ID=67997594

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/074624 WO2020094278A1 (fr) 2018-11-06 2019-09-16 Pompe à carburant à haute pression

Country Status (3)

Country Link
CN (1) CN113302394B (fr)
DE (1) DE102018218919A1 (fr)
WO (1) WO2020094278A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021203663A1 (de) 2021-04-14 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002250258A (ja) * 2001-02-22 2002-09-06 Denso Corp 燃料噴射装置用定残圧弁
DE102004013307A1 (de) 2004-03-17 2005-09-29 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
JP2010169083A (ja) * 2008-12-26 2010-08-05 Denso Corp 高圧ポンプ
JP2012158987A (ja) * 2011-01-28 2012-08-23 Denso Corp 高圧ポンプ
WO2017198371A1 (fr) * 2016-05-19 2017-11-23 Robert Bosch Gmbh Pompe à carburant haute pression

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002250258A (ja) * 2001-02-22 2002-09-06 Denso Corp 燃料噴射装置用定残圧弁
DE102004013307A1 (de) 2004-03-17 2005-09-29 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
JP2010169083A (ja) * 2008-12-26 2010-08-05 Denso Corp 高圧ポンプ
JP2012158987A (ja) * 2011-01-28 2012-08-23 Denso Corp 高圧ポンプ
WO2017198371A1 (fr) * 2016-05-19 2017-11-23 Robert Bosch Gmbh Pompe à carburant haute pression

Also Published As

Publication number Publication date
CN113302394B (zh) 2023-11-10
CN113302394A (zh) 2021-08-24
DE102018218919A1 (de) 2020-05-07

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