EP2867520A1 - Kraftstoffhochdruck-kolbenpumpe - Google Patents
Kraftstoffhochdruck-kolbenpumpeInfo
- Publication number
- EP2867520A1 EP2867520A1 EP13730210.5A EP13730210A EP2867520A1 EP 2867520 A1 EP2867520 A1 EP 2867520A1 EP 13730210 A EP13730210 A EP 13730210A EP 2867520 A1 EP2867520 A1 EP 2867520A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve seat
- valve
- piston pump
- pressure fuel
- fuel piston
- 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.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 70
- 238000002485 combustion reaction Methods 0.000 claims description 7
- 230000000295 complement effect Effects 0.000 claims description 2
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000005086 pumping Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 241000219793 Trifolium Species 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
-
- 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
- F02M59/464—Inlet valves of the check valve type
-
- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0077—Valve seat details
-
- 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
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
Definitions
- the invention relates to a high-pressure fuel piston pump after
- Internal combustion engines are used with a common rail fuel system.
- the fuel is compressed by the high-pressure fuel piston pump to a very high pressure and conveyed into a fuel rail, from where the fuel is injected directly into combustion chambers of the internal combustion engine.
- the high-pressure fuel piston pump has this
- Check valve is formed. Downstream of the delivery chamber, an outlet valve, which is likewise designed as a check valve, is arranged. To control the amount of fuel delivered by the high-pressure fuel piston pump into the fuel rail, the known high-pressure fuel piston pump has a quantity control valve. This is usually the inlet valve, which can be temporarily forced into its open position by an actuator, for example electromagnetically actuated. Does this happen during a funding period of
- High-pressure fuel piston pump the fuel from the delivery chamber is not promoted to the fuel rail, but through the forced open inlet valve back into the upstream of the high-pressure fuel piston pump arranged region (low pressure region) of the fuel system.
- the intake valve various embodiments are known.
- EP 2 236 809 A2 describes an inlet valve having a disk-like valve seat body which cooperates with a membrane-like valve element.
- the valve seat body can be a
- the movable valve member may consist of a plurality of membranous circular individual elements which are movably supported by spring arms.
- DE 40 23 044 discloses in another context a valve seat body with two arcuate
- Object of the present invention is to provide a high-pressure fuel piston pump having a high efficiency.
- the fuel In the operation of the high-pressure fuel piston pump, there are essentially two cases to be distinguished: In the suction phase, the fuel has to pass from the region located upstream of the inlet valve (low-pressure region) into the downstream region, the delivery chamber of the high-pressure fuel piston pump. To avoid vapor formation, the pressure drop at the valve seat of the inlet valve should be as low as possible. If steam is formed, the delivery rate of the pump may decrease. The largest possible flow area in the valve seat area reduces the pressure drop. The area flowed through in turn is calculated from the valve seat length and the valve lift. The latter should be small for reasons of dynamism.
- the valve seat of the inlet valve is significantly longer than in the conventional
- Valve seat results in the same stroke of the valve element, a smaller pressure drop across the inlet valve away. This is beneficial for the
- the extended valve seat line reduces the velocity of the fuel as it flows through the inlet valve, reducing the pressure drop during suction and thereby reducing the pressure
- Piston pump is characterized in that it comprises a plunger guided by the valve body, with which the valve element can be forcibly acted upon in an open position, and that the plunger with a closed inlet valve by a circumferential and with the valve element cooperating valve seat line against a downstream
- valve seat line is at least partially formed by a raised web.
- this creates a defined sealing contour, by means of which the areas of the valve element in which the inlet valve is closed on the one side and on the other side on the high pressure prevail, are kept small. As a result, the dynamics of the intake valve is further improved.
- Valve seat line which is formed on a valve seat body, the valve seat body in a directly adjacent to the valve seat line downstream region has a flow channel.
- the flow channel comprises a depression in the valve seat body. This depression, for example, the entire between two adjacent waves or meanders or
- Clovers cover existing area. This is easy to produce and leads to an optimal outflow of the fuel.
- valve seat extends along a first radial inner valve seat line and a second radially outer valve seat line
- valve element has at least one passage opening radially inwardly from the radially inner valve seat line. This also makes the outflow and, in forced open inlet valve, the backflow of the fuel is facilitated again.
- valve element has a circular shape. This is particularly easy and therefore inexpensive to produce, and a backup against rotation of the valve element is not required.
- valve element is complementary to the valve seat line, so also wavy meandering or
- Figure 1 is a schematic representation of a fuel system of a
- FIG. 2 is a schematic detail of the high-pressure fuel piston pump with an inlet valve
- Figure 3 is a perspective view of a first variant of
- Figure 4 is a perspective view of a second variant of
- Figure 5 is a perspective view of a third variant of
- a fuel system of an internal combustion engine bears the reference numeral 10 as a whole. It comprises a fuel tank 12, from which a prefeed pump 14 conveys fuel into a low-pressure line 16. This leads to a fuel high-pressure piston pump 18, designated overall by 18. This first comprises an inlet valve 20, which is designed as a check valve and can be acted upon by an electromagnetic actuator 22 forcibly in the open direction.
- the inlet valve 20 is designed as a check valve and can be acted upon by an electromagnetic actuator 22 forcibly in the open direction.
- Actuator 22 is also referred to as a quantity control valve, as a result, the flow rate of the high-pressure fuel piston pump 18 can be adjusted.
- the inlet valve 20 and its configuration are presently of particular interest. This will therefore be dealt with in more detail below.
- a pump piston 24 which can be offset by an eccentric drive, not shown in Figure 1 in a reciprocating motion.
- a delivery chamber 27 is present between this and a housing 26.
- a high-pressure line 30 leads to a fuel rail 32, to which a plurality of fuel injectors 34 are connected via an exhaust valve 28 which is likewise designed as a check valve. These inject the fuel directly into each associated combustion chambers (not shown).
- FIG. 2 A portion of the high-pressure fuel piston pump 18 is shown in more detail in Figure 2. It can be seen that the inlet valve 20 comprises a plate-shaped valve element 36, which cooperates with a valve seat body 38. When the inlet valve 20 is closed, the valve element 36 is located on
- Valve seat body 38 at. When the inlet valve 20 is open, as shown in FIG. 2, the valve element 36 is lifted off the valve seat body 38.
- the valve seat body 38 is a disk-shaped member which is press-fit into the housing 26 of the high-pressure fuel piston pump 18.
- passage openings 40th In the valve seat body 38 are passage openings 40th
- a central opening 42 is provided, through which a plunger 44 of the electromagnetic actuator 22 extends therethrough.
- the plunger 44 has a stop shoulder 46 which cooperates with housing-side stops 48 and 50.
- an armature 52 is attached to this, which cooperates with an electromagnetic coil (not shown).
- Anchor spring 54 is forcibly acted upon in the open position. If the electromagnetic actuator 22 is energized, however, the plunger 44 is pulled away from the valve member 36 so that it can come into contact with the valve seat body 38 and close within the normal function of a check valve.
- the inlet valve 20 and here in particular the embodiment of the valve seat body 38 with reference to Figure 3 explained in more detail.
- the inlet valve 20 is shown in perspective from the direction of the delivery chamber 27.
- Valve seat body 38 four circular arc segment-shaped recesses are present, which form the passage openings 40. Between
- Passage openings 40 extend in the radial direction webs 56, which hold a central ring 58, in which the central opening 42 for the plunger 44 is present.
- the valve member 36 facing the end of the plunger 44 is shown.
- Valve seat body 38 is at the edge of the passage openings 40 and the central opening 42 to the valve member 36 axially projecting circumferential ridge 60 present, the valve element 36 facing edge is formed as a flattened edge and the extent forms a valve seat for the valve element 36. It can therefore be clearly seen from FIG. 3 that the valve seat 60 in the present case extends along a cloverleaf-shaped valve seat line. Between two adjacent passage openings 40, there is a recess 62 in the side of the valve seat body 38 facing the valve element 36, which recess extends further in the radial direction than the valve seat 60.
- Recess 62 forms, as will be explained below, a
- Valve element 36 facing side of the valve seat body 38 thus three discrete planes are present: A center plane 64, which is present in that area where neither a valve seat 60 nor a recess 62 are present. A second plane which is offset from this median plane 64 away from the valve member 36 and in which the recesses 62 are located. And a third level, the opposite the median plane 64 to the valve member 36 is raised and in which the flattened edge of the valve seat 60 is located.
- the intake valve 20 operates as follows: fuel from the
- Low-pressure line 16 flow into the delivery chamber 27, the fuel passes through the passage openings 40 therethrough. However, it then flows not only in the radial direction through the gap between the radially outer regions (in FIG. 3, one of them is provided by the reference numeral 60a) of the valve seat 60 and the valve element 36, but also in the circumferential direction through the radially extending sections the valve seat 60 (in Fig. 3, one is designated by reference numeral 60b). In comparison to previous inlet valves, therefore, the area through which flowed through in the region of the sealing seat 60 is significantly increased, as a result of which the pressure drop occurring there is markedly reduced. This means less, or maybe not at all
- the central opening 42 which guides the tappet 44 with a small clearance, moreover, to allow its axial movement, is located within the circumferential cloverleaf-shaped valve seat 60, whereby the guidance of the plunger 44 in the central opening 42nd always facing the low-pressure region, so that when the inlet valve 20 is closed and the plunger 44 is withdrawn behind the valve seat 60, no leakage occurs across the inlet valve 20.
- the recesses 62 is a flow channel for the over the radially extending portions 60 b of
- Valve seat 60 outflowing fluid created so that even with low lift of the valve element 36, a sufficient cross section for the outflow of the fuel is available.
- forced open inlet valve 20 and a return flow from the pumping chamber 27 in the low pressure line 16 also results from the comparatively long valve seat 60, a lower pressure drop and thus a lower force exerted by the valve element 36 on the plunger 44.
- a full-surface circular valve element 36 does not require any rotation prevention.
- the valve element 36 in the region of the recesses 62, ie between the passage openings 40, also recesses, as indicated in Figure 3 by dashed lines. In this case, however, the valve element 36 must be secured against rotation.
- FIG. 4 An alternative embodiment of the inlet valve 20 is shown in FIG 4.
- the intake valve 20 shown in FIG. 4 there is a radially inner valve seat 60c and a radially outer annular valve seat 60d.
- the passage openings 40 are provided between these two annular valve seats 60c and 60d.
- openings 66 are provided radially inwardly of the valve seat 60c in the valve element 36, which allow an axial flow of fuel.
- the central opening 42 is sealed by a valve seat 60e.
- openings 66 in the valve element 36 serve to allow a flow of fuel in the radially inward region of the inlet valve 20.
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 |
---|---|---|---|
DE102012211106.9A DE102012211106A1 (de) | 2012-06-28 | 2012-06-28 | Kraftstoffhochdruck-Kolbenpumpe |
PCT/EP2013/062514 WO2014001122A1 (de) | 2012-06-28 | 2013-06-17 | Kraftstoffhochdruck-kolbenpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2867520A1 true EP2867520A1 (de) | 2015-05-06 |
EP2867520B1 EP2867520B1 (de) | 2019-04-03 |
Family
ID=48669936
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13730210.5A Not-in-force EP2867520B1 (de) | 2012-06-28 | 2013-06-17 | Kraftstoffhochdruck-kolbenpumpe |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2867520B1 (de) |
KR (1) | KR20150027127A (de) |
DE (1) | DE102012211106A1 (de) |
WO (1) | WO2014001122A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014223198A1 (de) * | 2014-11-13 | 2016-05-19 | Robert Bosch Gmbh | Kraftstoffpumpe mit verbessertem Förderverhalten |
DE102018200612B4 (de) | 2018-01-16 | 2019-11-28 | Continental Automotive Gmbh | Hochdruckanschluss für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1355285A (en) * | 1919-02-20 | 1920-10-12 | W N Matthews And Brother Inc | Pump-valve |
DE3404520C2 (de) * | 1984-02-09 | 1997-01-09 | Uraca Pumpen | Pumpe oder Hydraulikanlage |
DE4023044A1 (de) | 1990-07-20 | 1992-01-23 | Bosch Gmbh Robert | Ventil zum dosierten zumischen von verfluechtigtem kraftstoff zum kraftstoffluftgemisch einer brennkraftmaschine |
US7124966B2 (en) * | 2004-06-01 | 2006-10-24 | Haynes Corporation | Fuel injector check valve |
EP1724467B1 (de) | 2005-05-20 | 2016-07-13 | Magneti Marelli S.p.A. | Kraftstoffpumpe für Brennkraftmaschinen |
EP1895218B1 (de) * | 2006-09-04 | 2010-11-10 | Magneti Marelli S.p.A. | Absperrventil zur Steuerung des Durchflusses einer Kraftstoffpumpe für eine Brennkraftmaschine |
US20080203347A1 (en) * | 2007-02-28 | 2008-08-28 | Santos Burrola | Control valve for a gas direct injection fuel system |
IT1396473B1 (it) | 2009-03-30 | 2012-12-14 | Magneti Marelli Spa | Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta |
DE102010044119A1 (de) * | 2010-11-18 | 2012-05-24 | Robert Bosch Gmbh | Mengensteuerventil eines Kraftstoffsystems |
-
2012
- 2012-06-28 DE DE102012211106.9A patent/DE102012211106A1/de not_active Withdrawn
-
2013
- 2013-06-17 WO PCT/EP2013/062514 patent/WO2014001122A1/de active Application Filing
- 2013-06-17 KR KR20147036474A patent/KR20150027127A/ko active IP Right Grant
- 2013-06-17 EP EP13730210.5A patent/EP2867520B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2014001122A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102012211106A1 (de) | 2014-01-02 |
EP2867520B1 (de) | 2019-04-03 |
WO2014001122A1 (de) | 2014-01-03 |
KR20150027127A (ko) | 2015-03-11 |
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