EP4377565A1 - Pompe à carburant haute pression - Google Patents

Pompe à carburant haute pression

Info

Publication number
EP4377565A1
EP4377565A1 EP22732175.9A EP22732175A EP4377565A1 EP 4377565 A1 EP4377565 A1 EP 4377565A1 EP 22732175 A EP22732175 A EP 22732175A EP 4377565 A1 EP4377565 A1 EP 4377565A1
Authority
EP
European Patent Office
Prior art keywords
pressure
bore
valve
outlet
pump
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.)
Pending
Application number
EP22732175.9A
Other languages
German (de)
English (en)
Inventor
Thomas FROIHOFER
Rainer Kornhaas
Guido Bredenfeld
Stephan Wehr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP4377565A1 publication Critical patent/EP4377565A1/fr
Pending legal-status Critical Current

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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—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 is based on the inventors' observation that the solution known from the prior art leads to a potentially excessive mechanical load on the pressure damper.
  • the electromagnetic actuator can be designed, for example, in such a way that it only advances the tappet into a position that opens the intake valve when the electrical coil is energized.
  • the electromagnetic actuator can be designed, for example, in such a way that it only allows the tappet to retract, so that the inlet valve can optionally close when the electrical coil is energized. It can be provided that the outlet valve is fixed in an outlet valve bore of the pump housing and that the pressure relief valve is fixed in a pressure relief valve bore of the pump housing.
  • outlet valve bore and the pressure-limiting valve bore are also oriented geometrically parallel to one another, this has the advantage that machining, for example machining, of the pump housing to produce the pressure-limiting valve bore and the outlet valve bore is facilitated, since the machining is in the same direction and thus, for example, even with the same tool and/or, for example, at the same time.
  • the outlet socket space can consist of or comprise the part of the interior space of the socket pointing towards the pump housing.
  • the outlet connector space can also include a recess in the pump body that is covered by the outlet connector, and in particular can consist of these two partial spaces.
  • the outlet socket space can consist of the recess in the pump body covered by the outlet socket.
  • the reduction in the cross-section with which the outlet connector is attached to the pump body which is associated with the measure that only the outlet valve bore extends from the outlet connector space, but not the pressure-limiting valve bore, increases the ratio of the connection length along which the connector extends along its circumference can be attached to the pump housing, to the cross-section with which the outlet port is attached to the pump body.
  • the attachment of the outlet port is able to withstand higher pressures of the fuel being pumped.
  • the pressure-limiting valve bore is closed on the side of its outlet with a ball or a plug, the outlet valve bore being connected to the pressure-limiting valve bore by a high-pressure connection bore located in the high-pressure region.
  • the fluidic communication between the outlet and the pressure-limiting valve then takes place through the high-pressure connection hole only inside the pump housing.
  • a simple and reliable sealing point is realized by closing the pressure relief valve bore with a ball or a plug.
  • the pressure-limiting valve bore is connected to the inlet valve region by a low-pressure connecting bore located in the low-pressure region.
  • the cross section of the low-pressure connection bore can be smaller than the cross section of the pressure-limiting valve bore.
  • the low-pressure connection hole acts as a throttle and pressure pulsations from the high-pressure area only reach the inlet valve area to a weaker extent.
  • the low-pressure connection bore and the pressure-limiting valve bore are angled from one another at an angle different from 0° in a projection along the longitudinal direction and/or that the low-pressure connection bore and the pressure-limiting valve bore are in at least one projection perpendicular to the longitudinal direction are angled from each other at an angle different from 0°. In these cases, a more efficient use of the space available in the pump housing or pump body for inner contours is achieved.
  • the low-pressure connection hole is angled in the at least one projection perpendicular to the longitudinal direction at an angle different from 0° from the pressure-limiting valve hole such that the low-pressure connection hole with respect to the longitudinal direction and is directed toward the intake valve with respect to its direction pointing from the pressure relief valve bore to the intake valve area.
  • the low-pressure connection bore and the pressure-limiting valve bore are coaxial with one another.
  • the two bores can then be made in a single drilling process, for example with a step drill.
  • a bore in particular outlet valve bore, pressure relief valve bore, low-pressure connection bore, high-pressure connection bore, etc.
  • the bore has an axial symmetry whose axis of symmetry corresponds to the axis of rotation of the twist drill. This axis of symmetry then indicates the direction in which the hole is oriented.
  • the bore can basically be a through bore through the pump housing or the pump body or a blind bore which ends at a bore bottom arranged in the pump housing or in the pump body.
  • the exit of a bore is the side of the bore that is first produced by machining when the drill penetrates into the pump housing or the pump body. In the case of blind holes, this is always the side opposite the bottom of the hole.
  • the mouth of a bore is therefore the side of the bore opposite the outlet of a bore if the bore meets another inner contour of the pump housing or pump body there or emerges from the pump housing or pump body.
  • the bores of the present invention are free of undercuts, particularly when viewed from their exit.
  • the bore wall in a through bore is the inner contour represented by the through bore;
  • the wall of the hole is that part of the inner contour represented by the through hole that is not the bottom of the hole.
  • the high-pressure area is understood to be the entire space that communicates with the outlet easily, in particular without further interposed valves, so that a uniform pressure is established in the high-pressure area, for example 500 bar when the pump is in operation.
  • the low-pressure area is understood to mean the entire space that communicates with the inlet without further ado, in particular without further interposed valves, so that a uniform pressure is established in the low-pressure area during operation of the pump and when the pump is connected to the inlet Low pressure pump for example 5 bar.
  • the inner contours of the high-pressure fuel pump through which fuel flows finally consist of the low-pressure area, the pumping chamber and the high-pressure area. These areas are separated from each other by the inlet valve, the outlet valve and the pressure relief valve.
  • the fuel can be, for example, a fuel such as gasoline.
  • an angle different from 0° can be an angle that differs significantly from 0°, that is, for example, is at least 2° or at least 5°.
  • it can be an angle between 2° and 90°.
  • FIG. 1 shows a simplified schematic representation of a fuel system for an internal combustion engine.
  • FIG. 2 shows a first exemplary embodiment of the invention.
  • FIG. 3 shows a detailed example of a pressure-limiting valve, as can be used in the embodiments according to FIG. 2 or 4.
  • FIG. 3 shows a detailed example of a pressure-limiting valve, as can be used in the embodiments according to FIG. 2 or 4.
  • FIG. 4 shows a second exemplary embodiment of the invention.
  • FIG. 1 shows a fuel system 1 for an internal combustion engine (not shown further) in a simplified schematic representation.
  • fuel is supplied from a fuel tank 2 via a suction line 4 by means of a pre-supply pump 6 and a low-pressure line 8 via an inlet connection 20 to a high-pressure fuel pump 10 designed as a piston pump.
  • An inlet valve 14 is arranged fluidically downstream of the inlet connection piece 20 .
  • a low-pressure region 28 of the high-pressure fuel pump 10 is located fluidically between the inlet connection 20 and the inlet valve 14.
  • a delivery chamber 16 of the high-pressure fuel pump 10 is located downstream of the inlet valve 14. Pressure pulsations in the low-pressure region 28 can be damped by means of a pressure damper device.
  • the inlet valve 14 can be forced open via an actuating device designed here as an electromagnetic actuator 30 .
  • the actuating device and thus the intake valve 14 can be controlled via a control unit 32 .
  • a pump piston 18 of the high-pressure fuel pump 10 can be moved up and down along a longitudinal axis running in the longitudinal direction LA, to which the pump piston 18 is axially symmetrical, by means of a drive 36 embodied here as a cam disk, which is illustrated in Figure 1 by a double arrow 40 is.
  • An outlet valve 37 is arranged fluidically between the pumping chamber 16 and an outlet connection 35 of the high-pressure fuel pump 10 and can open towards the outlet connection 35 and a high-pressure accumulator 45 (“rail”) located further downstream.
  • a high-pressure region 29 of the high-pressure fuel pump 10 extends fluidically between the outlet valve 37 and the outlet connection piece 35 .
  • the high-pressure area 29 and the low-pressure area 28 are directly connected to one another via a pressure-limiting valve 22, which opens when a limit pressure is exceeded in the high-pressure area 29 of the high-pressure fuel pump 10 or in the high-pressure accumulator 45 communicating with it.
  • the pressure-limiting valve 22 is designed as a spring-loaded check valve and can open toward the low-pressure area 28 of the high-pressure fuel pump 10 . In this way, the pressure that can be generated by the high-pressure fuel pump 10 in the high-pressure accumulator 45 is limited.
  • FIG. 2 shows a sectional view of a high-pressure fuel pump 10 as a first exemplary embodiment of the invention.
  • the high-pressure fuel pump 10 has an inlet 11 designed as an inlet connection piece 20 .
  • the inlet 11 communicates with the entire low-pressure area 28 of the high-pressure fuel pump 10 without the interposition of valves.
  • the high-pressure fuel pump 10 has an outlet 34 designed as an outlet connector 35 .
  • the outlet 34 communicates with the entire high-pressure area 29 of the high-pressure fuel pump 10 without the interposition of valves.
  • the non-visible fluidic connection between the inlet 11 and the damper chamber 28a can, for example, comprise a filter bore in which a filter element is arranged, which frees a fuel flowing through the filter bore from entrained solid particles above a minimum size.
  • the inlet valve 14 can be forced open by a tappet 31 driven by the actuator 30 .
  • the actuator 30 has an actuator housing 30a which is fixed to the pump housing 12 and in which an electromagnetic coil 30b is arranged, which can be energized via an externally accessible electrical connection 30c of the high-pressure fuel pump 10 .
  • the high-pressure fuel pump 10 has a pressure-limiting valve 22, which fluidly connects the high-pressure area 29 to the low-pressure area 28 and opens towards the low-pressure area 28, so that fuel flows out of the high-pressure area 29 into the low-pressure area 28 when the pressure difference between fuel in the high-pressure area 29 and fuel in the low pressure region 28 exceeds a cracking pressure.
  • the arrangement of the pressure-limiting valve 22 in the high-pressure fuel pump 10 according to the invention will now be discussed further by way of example.
  • the pressure relief valve 22 fluidly connects the high-pressure area 29 to an inlet valve area 28c of the low-pressure area 28 and opens towards the inlet valve area 28c, so that fuel flows out of the high-pressure area 29 into the inlet valve area 28c when the pressure difference between fuel in the high-pressure area 29 and fuel in low-pressure region 28 exceeds an opening pressure, with inlet valve region 28c of low-pressure region 28 being located geometrically between inlet valve 14 and an electromagnetic actuator 30 of high-pressure fuel pump 10 that acts on inlet valve 14 via a tappet 31.
  • the outlet 34 is designed as an outlet connector 35 fixed to the pump housing 12, and an outlet connector space 35a is formed between the pump housing 12 and the outlet connector 35, from which both the outlet valve bore 37a and the pressure-limiting valve bore 22a emanate.
  • Pressure-limiting valve bore 22a and the outlet valve bore 37a communicate with one another via the outlet connection space 35a arranged between the pump housing 12 and the outlet connection 35 .
  • the low-pressure connection bore 28b and the pressure-limiting valve bore 22a are angled from one another in a projection along the longitudinal direction LA at an angle different from 0°, for example at least 20°. It can be provided that the low-pressure connection bore 28b and the pressure-limiting valve bore 22a are angled from one another in at least one projection perpendicular to the longitudinal direction LA at an angle different from 0°, for example at least 20°.
  • this can be done in such a way that the low-pressure connection bore 28b is angled in the at least one projection perpendicular to the longitudinal direction LA at an angle other than 0° from the pressure-limiting valve bore 22a such that the low-pressure connection bore 28b with respect to the longitudinal direction LA and with respect to its direction pointing from the pressure relief valve bore 22a to the inlet valve area 28c is directed towards the inlet valve 14 .
  • the pressure-limiting valve 22 from FIG. 2 (it can also be the pressure-limiting valve 22 shown in FIG. 4) is enlarged in FIG. 3 and shown as an example. It has a valve seat body 38 which is pressed into the pressure relief valve bore 22a or into a housing of the pressure relief valve 22 and on which a conical valve seat 42 is formed.
  • the pressure-limiting valve 22 also has a valve element 44 which has the shape of a sphere and which comes into sealing contact with the valve seat 42 .
  • the valve element 44 is pressed in the closing direction by a holding element 46 and the holding element 46 is pressed in the closing direction by a coil spring 52 .
  • the spiral spring 52 is supported on a housing of the pressure relief valve 22 or directly on the pump housing 12 .
  • the spiral spring 52 is in contact with a radially outer area 464 of the holding element 46 .
  • a radially inner area 465 of the holding element 46 is received by the spiral spring 52 .
  • the opening pressure of the pressure-limiting valve 22 is defined by the stiffness of the spiral spring 52 and by the area acting on the pressure-limiting valve at the same time the maximum pressure difference that the high-pressure fuel pump 10 is able to generate between its inlet 11 and its outlet 34 .
  • the spiral spring 52 is arranged on a pressure-limiting valve bore formed between the low-pressure connection bore 28b and the pressure-limiting valve bore 22a 22a pointing annular step 22.2 is supported.
  • FIG. 4 A second exemplary embodiment is shown in FIG. 4 in a sectional view. It differs from the first exemplary embodiment in that only the outlet valve bore 37a, but not the pressure-limiting valve bore 22a, emanates from the outlet connector space 35a. Instead, it is provided in this exemplary embodiment that the pressure relief valve bore 22a is closed on the side of its outlet 22aa with a ball 56 pressed particularly into the pressure relief valve bore 22a or a plug 57 pressed particularly into the pressure relief valve bore 22a, with the outlet valve bore 37a being connected to the pressure relief valve bore 22a by a in the high-pressure area 29 lying high-pressure connection bore 29a is connected.
  • the high-pressure connection bore 29a starts from the damping area 28a and is closed on its outlet side 29aa with a ball 56 pressed into it or a plug 57 pressed into it.
  • the outlet connector 34 can be made smaller than in the first exemplary embodiment, for example, an (outer) diameter with which the outlet connector 35 is fixed to the pump housing 12 in this arrangement can be smaller than the sum of the diameter of the pressure-limiting valve bore 22a and the diameter of the Outlet valve bore 37a, in particular even smaller than 0.9 times this sum.
  • the robustness of the connection of the outlet connector 35 to the pump housing 12 is increased in this way, because while the hydraulic forces acting on the outlet connector 35 are proportional to the cross-sectional area covered by it, the connection length with which the Outlet nozzle 35 is fixed to the pump housing 12, only proportional to the extent of the cross-sectional area covered by it, ie proportional to the square root of the cross-sectional area covered by it.
  • the pressure-limiting valve bore 22a, the outlet valve bore 37a and the low-pressure connection bore 28b and what has been said about the relations between these bores also applies to this second exemplary embodiment.
  • the high-pressure connection bore 29a can have a cross section that is smaller than the respective cross sections of the pressure-limiting valve bore 22a, the outlet valve bore 37a and the low-pressure connection bore 28b, for example each at most half as large.
  • the high-pressure communication bore 29a may have a cross section that is smaller than the respective cross sections of the pressure relief valve bore 22a and the outlet valve bore 37a but larger than that of the low-pressure communication bore 28b.

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 (10) comprenant une soupape d'admission (14) et une soupape de limitation de pression (22) qui relie fluidiquement une région à haute pression (29) à une région de soupape d'admission (28c) située, en termes de géométrie, entre la soupape d'admission (14) et un actionneur électromagnétique (30) de la pompe à carburant haute pression (10), qui agit sur la soupape d'admission (14) par l'intermédiaire d'un poussoir (31).
EP22732175.9A 2021-07-27 2022-06-08 Pompe à carburant haute pression Pending EP4377565A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021208052.9A DE102021208052A1 (de) 2021-07-27 2021-07-27 Kraftstoff-Hochdruckpumpe
PCT/EP2022/065458 WO2023006285A1 (fr) 2021-07-27 2022-06-08 Pompe à carburant haute pression

Publications (1)

Publication Number Publication Date
EP4377565A1 true EP4377565A1 (fr) 2024-06-05

Family

ID=82117290

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22732175.9A Pending EP4377565A1 (fr) 2021-07-27 2022-06-08 Pompe à carburant haute pression

Country Status (5)

Country Link
EP (1) EP4377565A1 (fr)
KR (1) KR20240033282A (fr)
CN (1) CN118103594A (fr)
DE (1) DE102021208052A1 (fr)
WO (1) WO2023006285A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004063074B4 (de) 2004-12-28 2013-03-07 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
JP4437552B2 (ja) * 2006-05-26 2010-03-24 株式会社デンソー 高圧燃料ポンプ
DE102008043217A1 (de) 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102017212498A1 (de) 2017-07-20 2019-01-24 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102018221702A1 (de) * 2018-12-13 2020-06-18 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe

Also Published As

Publication number Publication date
KR20240033282A (ko) 2024-03-12
DE102021208052A1 (de) 2023-02-02
WO2023006285A1 (fr) 2023-02-02
CN118103594A (zh) 2024-05-28

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