EP4013958A1 - High-pressure fuel pump - Google Patents
High-pressure fuel pumpInfo
- Publication number
- EP4013958A1 EP4013958A1 EP20753329.0A EP20753329A EP4013958A1 EP 4013958 A1 EP4013958 A1 EP 4013958A1 EP 20753329 A EP20753329 A EP 20753329A EP 4013958 A1 EP4013958 A1 EP 4013958A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- blind hole
- valve
- fuel pump
- pressure
- 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.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/001—Pumps with means for preventing erosion on fuel discharge
-
- 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
- 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
- F02M59/46—Valves
- F02M59/462—Delivery 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
Definitions
- a high-pressure fuel pump according to the preamble of claim 1 was already presented by the applicant in DE 10 2004 013 307 A1.
- High-pressure fuel pumps designed in this way have the functional advantage that the pressure relief valve does not open during the delivery stroke and therefore pressure peaks occurring briefly during the delivery stroke of the high-pressure fuel pump do not impair the degree of delivery of the high-pressure fuel pump.
- high-pressure fuel pumps designed in this way are comparatively easy to manufacture.
- the present invention is based on the inventors' observation that the valve seat surface arranged on the inner contour of the valve body of the pressure limiting valve is subject to wear during operation of the high-pressure fuel pump.
- the inventors identified a mechanism of action of this wear and tear that during a suction phase of the high-pressure fuel pump, i.e. when the pump piston moves in the direction enlarging the delivery chamber, the pressure of the fuel in the delivery chamber occasionally falls below the vapor pressure of this fuel, so that it vapor bubbles can form in the conveying space.
- these vapor bubbles collapse like an implosion, which is also known as cavitation.
- the cavitation basically leads to erosion phenomena in the delivery chamber and in the areas of the high-pressure fuel pump that communicate fluidly with the delivery chamber, including in the valve seat area of the pressure limiting valve.
- the cavitation erosion phenomena in the valve seat area of the pressure relief valve become noticeable as wear, which can be associated with a leak in the pressure relief valve and impaired function of the high-pressure fuel pump.
- cavitation and the associated erosion phenomena in the pumping space or in the area of the pump that fluidly communicates with the pumping space do not occur uniformly, but to a particularly high degree at locations where the propagation of pressure waves , which form in the context of cavitation, encounter a significant spatial limitation, i.e. a solid obstacle. Because the pressure waves hit a solid obstacle, there is a further increase in the local pressure and consequently erosion processes preferentially at these locations.
- the measure according to the invention that the essentially cylindrical blind hole is widened at the axial height of the valve seat surface by an additional recess in the housing compared to a cylindrical blind hole in the radial direction, so that the recess forms a damping volume arranged radially outside the valve seat surface, is achieved that the valve seat surface only represents such a solid obstacle to a far lesser extent. Instead, pressure waves can propagate past the valve seat surface into the recess of the housing. Cavitation erosion only occurs to a reduced extent on the valve seat surface. To the extent that cavitation erosion occurs within the recess, this is generally harmless to the functioning of the high-pressure fuel pump.
- the high-pressure fuel pump can in particular be a piston pump which is able to compress a liquid fuel, for example a fuel such as gasoline, to a pressure of, for example, 20 MPa or 35 MPa.
- the pressure limiting valve can in particular be a check valve, in particular with a conical or dome-shaped sealing seat surface and a spherical valve element.
- the blind hole in which the pressure relief valve is arranged according to the invention is essentially cylindrical, so that reference can be made to this in the context of the application to an axial and a radial direction.
- a blind hole is understood to mean in particular a hole which - apart from the recess according to the invention, see below - can be thought of as being introduced into the housing by a drill, for example a twist drill, which has penetrated the housing without penetrating it.
- the blind hole ends inside the housing, for example at a hole bottom.
- the essentially cylindrical shape of the blind hole can on the one hand deviate from the exact shape due to the recess; on the other hand, it is also possible that the blind hole intersects another hole in the housing, for example a piston hole, or that the blind hole is fluidically connected to the piston hole by a connection provided in the housing.
- the connection can in particular be coaxial with the piston bore and / or be tapered in diameter or cross section in comparison to this.
- the piston bore and / or the connection can in particular be formed at right angles to the blind hole, for example intersect it at right angles.
- an additional recess in the housing through which the essentially cylindrical blind hole is widened at the axial height of the valve seat surface, so that the recess forms a damping volume arranged radially outside the valve seat surface.
- the additional recess can in particular be thought of as a volume which, starting from an initially cylindrical blind hole in the interior of the cylindrical blind hole, is additionally removed from the housing.
- the provision of the additional recess in the housing as part of the blind hole is not to be understood as meaning that the blind hole degenerates into any outwardly open inner contour of the housing. Rather, the blind hole is still cylindrical in essence.
- the volume of the recess - and thus also the additional damping volume - can for example be smaller than the volume of the cylindrical part of the blind hole or even smaller than the volume of the part of the cylindrical part of the blind hole arranged on the high-pressure side of the pressure relief valve and / or smaller than the volume of the the delivery chamber side of the pressure relief valve arranged part of the cylindrical part of the blind hole.
- the additional recess - and thus also the additional damping volume - can have an extension in the axial direction which is less than a quarter of the extension in the axial direction of the essentially cylindrical blind hole.
- the additional recess - and thus also the additional damping volume - can have an extension in the axial direction which is less than the extension of the valve body in the axial direction.
- the additional recess - and thus also the additional damping volume - has an extension in the axial direction which is greater than the extension of the valve element in the axial direction.
- the additional recess - and thus also the additional damping volume - can have an extension in the radial direction which is at least 20% of the diameter of the cylindrical part of the blind hole.
- the radial extension of the blind hole is increased by at least 20% than in the area of the recess.
- the recess is an undercut in the blind hole. It is therefore in particular an annular volume removal from the housing in the interior of the blind hole which is coaxial with the cylindrical part of the blind hole.
- the diameter of the blind hole in the area of the undercut is increased by at least 20% and / or an axial extent of the undercut is greater than the axial extent of the valve element, but in particular is smaller than the axial extent of the valve body.
- the recess is a cutout in the blind hole.
- a volume removal from the housing in the interior of the blind hole which is asymmetrical to the cylindrical part of the blind hole and is directed only in a radial direction, as can be produced, for example, by a milling tool.
- the milling in this radial direction is at least 20% of the diameter of the blind hole and / or an axial extension of the milling is greater than the axial extension of the valve element, but in particular is smaller than the axial extension of the valve body.
- the blind hole is designed as a stepped bore, with an area with a larger diameter, which includes the first end area and the area in which the valve seat surface is arranged, and with an area with a smaller diameter, which includes the other end area includes.
- the recess is part of the area around which the blind hole is expanded in the area with a larger diameter. Its sub-area located fluidically on the delivery chamber side of the pressure relief valve is the damping volume formed by it.
- the diameter of the stepped bore in the area with a larger diameter is at least 10% larger than the diameter of the stepped bore in the area with a smaller diameter.
- the housing consists of a housing body and one on the housing body fixed housing cover, with a damper chamber of the high-pressure fuel pump being formed between the housing body and the housing cover and with a connecting bore in the housing which extends from the damper chamber to the blind hole and which is through a closure introduced into the connecting bore, for example through a ball pressed into the part of the bore facing the housing cover is closed in a fluid-tight manner.
- the recess is the connecting bore
- the damping volume formed by it is in this case the part of the connecting bore facing away from the housing cover when viewed from the ball.
- the connecting bore has an extension in the axial direction with respect to the blind hole which is larger than that of the valve element but smaller than that of the valve body.
- FIG. 1 shows a longitudinal section through a high-pressure pump known from the prior art with an enlarged representation of the pressure limiting valve
- FIG. 2 shows a first embodiment modified according to the invention
- FIG. 3 shows a second embodiment modified according to the invention
- FIG. 4 shows a third embodiment modified according to the invention
- FIG. 5 shows a fourth embodiment modified according to the invention.
- FIG. 1 shows a high-pressure fuel pump known from the prior art.
- a high-pressure fuel pump 30 with a housing 58 and a pumping chamber 60 arranged in the housing 58, a pump piston 62 that is displaceable in the housing 58 and delimiting the pumping chamber 60, an inlet valve 34 opening from a low pressure area 18 to the pumping chamber 60, a high pressure connected from the pumping chamber 60 to the housing 58 in a liquid-tight manner -Connection 63 opening outlet valve 44 and a pressure limiting valve 56 opening from the high pressure connection 63 to the delivery chamber 60.
- the pressure limiting valve 56 is arranged in a substantially cylindrical blind hole 69 of the housing 58, which at its first end region 201 of one of the High-pressure connection 63 and the space 68 bounded by the housing 58 starts out and communicates fluidically at its other end region 202 with the delivery chamber 60.
- the pressure limiting valve 56 has a sleeve-shaped valve body 102 fixed in the essentially cylindrical blind hole bore 69, on the inner contour of which a valve seat surface 72 is formed.
- the pressure relief valve 56 has a valve element 74 which, when the pressure relief valve 56 is closed, is pressed against the valve seat surface 72 by a valve spring 76 supported in the other end area 202 of the blind hole 69 on the housing 58.
- FIGS. 2 to 5 further developments according to the invention of the known high pressure fuel pump 30 are shown. What they have in common is that the essentially cylindrical blind hole 69 is widened in the radial direction at the axial height of the valve seat surface 72 by an additional recess 10 in the housing 58 compared to a cylindrical blind hole, so that the recess 10 has a damping volume arranged radially outside the valve seat surface 72 forms.
- the pump piston 62 can be displaced in a piston bore 64 of the housing 58, the piston bore 64 running at right angles to the blind bore 69.
- piston bore 64 and the blind bore 69 either intersect or are fluidically connected to one another by a connection 70b.
- the embodiment shown in Figure 2 is also distinguished characterized in that the recess 10 is an undercut 108 in the blind hole 69.
- the diameter of the blind hole D in the area of the undercut 108 is increased by at least 20% and an axial extent of the undercut AH is greater than the axial extent of the valve element AVE but is smaller than the axial extent of the valve body AVK.
- the exemplary embodiment shown in FIG. 3 is also characterized in that the recess 10 is a milled recess 107 in the blind hole 69.
- the milled recess 107 is a recess 10 which is asymmetrical only in the upper direction in FIG.
- the cutout 107 in the radial direction is at least 20% of the diameter of the blind hole D and an axial extent of the cutout AA is greater than the axial extent of the valve element AVE but is smaller than the axial extent of the valve body AVK-
- the exemplary embodiment shown in FIG. 4 is characterized in that the blind hole 69 is designed as a stepped bore 106, with an area with a larger diameter 106a, which comprises the first end area 201 and the area in which the valve seat surface 72 is arranged, and having a smaller diameter portion 106b that includes the other end portion 202.
- the recess 10 or the damping volume can be seen in the spatial area of the blind hole 69 by which the area with the larger diameter 106a protrudes radially beyond the area with the smaller diameter 106b and which is on the side of the valve body 102 facing away from the high pressure connection 63 .
- the exemplary embodiment shown in FIG. 5 is characterized, on the other hand, in that the housing 58 consists of a housing body 58a and a housing cover 58b fixed on the housing body 58a, with a damper chamber 32 of the high-pressure fuel pump 30 being formed between the housing body 58a and the housing cover 58b is and wherein in the housing 58 is a connecting bore 105, which extends from the Damper chamber 32 extends to the blind hole 69 and which is closed in a fluid-tight manner by a closure introduced into the connecting bore 105, for example by a part of the ball 105a pressed into the connecting bore 105 facing the housing cover 58b.
- the connecting bore 105 has an extension in the axial direction AVB with respect to the blind hole 69, which is larger than that of the valve element AVE but smaller than that of the valve body AVK.
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
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019212247.7A DE102019212247A1 (en) | 2019-08-15 | 2019-08-15 | High pressure fuel pump |
PCT/EP2020/071958 WO2021028282A1 (en) | 2019-08-15 | 2020-08-05 | High-pressure fuel pump |
Publications (1)
Publication Number | Publication Date |
---|---|
EP4013958A1 true EP4013958A1 (en) | 2022-06-22 |
Family
ID=71994498
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20753329.0A Withdrawn EP4013958A1 (en) | 2019-08-15 | 2020-08-05 | High-pressure fuel pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP4013958A1 (en) |
CN (1) | CN114599874A (en) |
DE (1) | DE102019212247A1 (en) |
WO (1) | WO2021028282A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPWO2023032253A1 (en) * | 2021-09-03 | 2023-03-09 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10327411B4 (en) * | 2002-10-15 | 2015-12-17 | Robert Bosch Gmbh | Pressure relief valve and fuel system with such a pressure relief valve |
DE102004013307B4 (en) * | 2004-03-17 | 2012-12-06 | Robert Bosch Gmbh | High-pressure fuel pump with a pressure relief valve |
DE102007016134A1 (en) * | 2006-04-25 | 2007-11-08 | Robert Bosch Gmbh | High pressure fuel pump, has throttle arrangement provided at high pressure side of valve seat of pressure limiting valve, where cross section of arrangement is approximately equal to desired maximum opening cross section of valve |
DE102013216817A1 (en) * | 2013-08-23 | 2015-02-26 | Continental Automotive Gmbh | Pump arrangement and system for a motor vehicle |
DE102013220816A1 (en) * | 2013-10-15 | 2015-04-16 | Continental Automotive Gmbh | Pressure relief valve for a fuel injection system and fuel injection system |
JP6432440B2 (en) * | 2015-05-15 | 2018-12-05 | 株式会社デンソー | High pressure pump |
DE102018200612B4 (en) * | 2018-01-16 | 2019-11-28 | Continental Automotive Gmbh | High-pressure connection for a high-pressure fuel pump and high-pressure fuel pump |
-
2019
- 2019-08-15 DE DE102019212247.7A patent/DE102019212247A1/en not_active Withdrawn
-
2020
- 2020-08-05 CN CN202080072234.0A patent/CN114599874A/en active Pending
- 2020-08-05 EP EP20753329.0A patent/EP4013958A1/en not_active Withdrawn
- 2020-08-05 WO PCT/EP2020/071958 patent/WO2021028282A1/en unknown
Also Published As
Publication number | Publication date |
---|---|
DE102019212247A1 (en) | 2021-02-18 |
WO2021028282A1 (en) | 2021-02-18 |
CN114599874A (en) | 2022-06-07 |
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Legal Events
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