EP2315930A1 - Pump for a fuel injection system of an internal combustion engine with an improved delivery valve - Google Patents
Pump for a fuel injection system of an internal combustion engine with an improved delivery valveInfo
- Publication number
- EP2315930A1 EP2315930A1 EP09753752A EP09753752A EP2315930A1 EP 2315930 A1 EP2315930 A1 EP 2315930A1 EP 09753752 A EP09753752 A EP 09753752A EP 09753752 A EP09753752 A EP 09753752A EP 2315930 A1 EP2315930 A1 EP 2315930A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shut
- seat
- pump according
- spring
- opening
- 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
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
- F02M59/462—Delivery valves
Definitions
- the present invention relates to a pump comprising an improved delivery valve, and preferably to a high-pressure pump for a fuel injection system of an internal combustion engine.
- a high-pressure pump is generally used in a fuel injection system which comprises a low-pressure branch, a pre-feed pump which draws the fuel from a tank and conveys it to a high-pressure pump via the low-pressure branch and a high-pressure branch which connects a delivery of the high-pressure pump to a group of injectors via an accumulator, commonly called a "common rail".
- the high-pressure pump comprises a plurality of pumping cylinders operated by a driving shaft via a lobed body or via a cam.
- the pumping cylinders slide in a reciprocating manner inside respective compression chambers, each of which is connected in flow terms to an intake valve and a delivery or high-pressure valve.
- the high-pressure or delivery valve is a non-return valve.
- a high-pressure valve comprises a ball shut-off member biased by means of a coil spring against a conical seat. Upstream the conical seat is connected in flow to the compression chamber and downstream the high-pressure valve is connected in flow to the common rail.
- the fuel flow which passes through the high-pressure valve exerts a complex hydrodynamic action on the shut-off member which results in wear and a delay in the dynamic response.
- the hydraulic forces acting on the shut-off member are such as to generate a torque which causes the shut-off member to rotate about the axis of the spring and thus produces both friction of the latter against the spring and a delay in the closing action.
- the object of the present invention is to provide a feed pump for a fuel injection circuit which does not have the abovementioned drawbacks.
- a pump for a fuel injection system of an internal combustion engine comprising a seat connected in flow terms to the delivery of a compression chamber, an outlet duct for connecting the seat to a plurality of injectors, a shut-off member housed inside the seat, a spring for biasing the shut-off member against a first contact surface of the seat in a closed position, the seat being provided with a first through-opening in the axial direction, arranged downstream of the shut-off member, and fuel flow deviation means being provided upstream of the outlet duct and configured so that the speed of the fuel flow is greater between the shut-off member and the opening than upstream of the shut-off member.
- the fuel flow deviation means are configured so as to direct the flow towards the opening so that the speed of the fuel increases immediately downstream of the shut-off member and a negative pressure is therefore created. This negative pressure pushes the shut-off member against the spring and reduces rotation of the shut-off member. Moreover, when the fluid tends to change direction during the intake phase of the pumping member, the pressure is localized along the axis of the spring and is applied effectively to the shut-off member so as to favour a closing action.
- FIG. 1 is a prospective view of a component according to Figure 1.
- 1 denotes generically the head of a reciprocating fuel feed pump.
- the head defines a compression chamber 2 housing a pumping member 3 and a delivery valve 4 connected to the delivery of the chamber 2.
- the delivery valve 4 is a non-return valve.
- the compression chamber 2 has an axis A and is closed axially by a threaded member 5 screwed into the head 1.
- the valve 4 is connected to the delivery of the compression chamber 2 via a duct 6 having an axis B perpendicular to the axis A.
- the duct 6 emerges inside a seat 7 of the valve 4 defined by a cylindrical wall 8 coaxial with the duct 6 and by a frustoconical contact surface 9 axially arranged between the duct 6 and the cylindrical wall 8.
- the seat 7 is also connected to a duct 10 having an axis C parallel to the axis A and connected to the injectors preferably via a common rail, both not shown.
- the valve 4 comprises a ball shut-off member 11 designed to cooperate selectively with the contact surface 9; a coil spring 12 for keeping the shut-off member 11 pressed against the contact surface 9 in a closed position; and a closing member 13 for pre-stressing the spring 12.
- the closing member 13 is connected rigidly to the head 1 preferably by means of a threaded connection and comprises, for example in the form of a single body, a closing head-piece 14 screwed into the head 1 in a fluid-type manner and a cylindrical body 15 housed inside the seat 7.
- the cylindrical body 5 defines preferably a radial through-hole 16 coaxial during use with the axis C and an axial cavity 17 communicating with the hole 16 via an opening 18 and open towards the contact wall 9.
- the axial cavity 17 houses the spring 12 and is cylindrical with an internal diameter smaller than that of the shut- off member 11.
- the opening 18 is situated on the opposite side to the shut-off member 11 relative to the spring 12 and is situated in an axial position lying between the axis C and the cavity 17.
- the cylindrical body 15 Towards the contact wall 9, the cylindrical body 15 comprises an annular end portion 19 which defines a flaring 20 and at least one radial through-groove 21.
- the spring 12 is housed inside the axial cavity 17 so as to be coaxial with the axis B and the shut-off member 11 makes contact with the contact surface 9 when the valve 4 is closed.
- the valve 4 opens when the shut-off member 11 separates from the contact surface 9 and is able to reach the fully open condition when the shut-off member 11 makes contact with the flaring 20.
- the cylindrical body 15 is mounted with radial play of its diameter inside the seat 7 so that the hydraulic resistance defined by the aperture 22 between the cylindrical body 15 and the cylindrical wall 8 is greater than that defined by the groove 21, the coils of the spring 12, the opening 18 and the hole 16.
- the diameter of the duct 6 and the dimensions of the groove 21 are such as to ensure that the speed of the fuel inside the cavity 17 is greater than that inside the duct 6.
- the flow of fuel pumped by the member 3 opens the shut-off member 11 when the pressure upstream of the valve 4 is greater than the sum of the pressure downstream of the shut-off member and the equivalent, in terms of pressure, of the pre-stressing force of the spring 12.
- shut-off member 11 makes contact against the flaring 20 and most of the flow is directed along a path which leads from the groove 21 to the hole 16 through the coils of the spring 12 and the opening 18 since the hydraulic resistance of this path is less than that defined by the aperture 22 between the annular end portion 19 and the duct 10.
- the speed of rotation of the shut-off member 11 about the axis B is so high that the shut-off member continues to rotate even when the pumping member 3 reverses its movement and starts the intake phase, preventing closure of the valve also - in the worst of cases - for the entire duration of the intake phase.
- the number of grooves 21 may be more than one, for example up to five, so as to ensure that the speed of the fuel flow inside the cavity 17 is greater than that inside the duct 6.
- the aperture 22 may also be completely closed in the case where the part 15 engages precisely with the cylindrical surface 8 of the seat 7. In this case, the hydraulic resistance is practically infinite and the entire flow of fuel which passes through the valve 4 flows through the coils of the spring 12 and the opening 18.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITMI20081008 ITMI20081008A1 (en) | 2008-05-30 | 2008-05-30 | PUMP FOR A FUEL INJECTION SYSTEM WITH A PERFORMED DELIVERY VALVE |
PCT/EP2009/054639 WO2009144097A1 (en) | 2008-05-30 | 2009-04-20 | Pump for a fuel injection system of an internal combustion engine with an improved delivery valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2315930A1 true EP2315930A1 (en) | 2011-05-04 |
EP2315930B1 EP2315930B1 (en) | 2012-06-20 |
Family
ID=40302854
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09753752A Not-in-force EP2315930B1 (en) | 2008-05-30 | 2009-04-20 | Pump for a fuel injection system of an internal combustion engine with an improved delivery valve |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2315930B1 (en) |
IT (1) | ITMI20081008A1 (en) |
WO (1) | WO2009144097A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2688406B1 (en) | 2011-03-25 | 2015-04-22 | Bayer Intellectual Property GmbH | Use of n-(tetrazol-4-yl)- or n-(triazol-3-yl)arylcarboxamides or their salts for controlling unwanted plants in areas of transgenic crop plants being tolerant to hppd inhibitor herbicides |
WO2012130684A1 (en) | 2011-03-25 | 2012-10-04 | Bayer Cropscience Ag | Use of n-(1,2,5-oxadiazol-3-yl)benzamides for controlling unwanted plants in areas of transgenic crop plants being tolerant to hppd inhibitor herbicides |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB513349A (en) * | 1938-07-25 | 1939-10-10 | Bryce Ltd | Improvements relating to fuel injection pumps |
JP4237560B2 (en) * | 2003-07-03 | 2009-03-11 | カヤバ工業株式会社 | Fluid pressure control valve |
DE102004027825A1 (en) * | 2004-02-11 | 2005-09-01 | Robert Bosch Gmbh | High-pressure pump, especially for fuel injection device for internal combustion engine, has smallest throughflow cross-section region downstream of sealing surface when valve element in open position |
DE102005061886A1 (en) * | 2005-12-23 | 2007-07-05 | Robert Bosch Gmbh | High pressure pump for fuel injection device in internal combustion engine having valve which when open releases first, then second through-flow cross sections in flow direction and lastly third cross-section larger than preceding two |
EP1813845A1 (en) * | 2006-01-31 | 2007-08-01 | Centro Studi Componenti per Veicoli S.P.A. | High-pressure pump for feeding fuel to an internal combustion engine |
-
2008
- 2008-05-30 IT ITMI20081008 patent/ITMI20081008A1/en unknown
-
2009
- 2009-04-20 WO PCT/EP2009/054639 patent/WO2009144097A1/en active Application Filing
- 2009-04-20 EP EP09753752A patent/EP2315930B1/en not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2009144097A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP2315930B1 (en) | 2012-06-20 |
WO2009144097A1 (en) | 2009-12-03 |
ITMI20081008A1 (en) | 2009-11-30 |
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