EP2399031A1 - Fuel pump - Google Patents
Fuel pumpInfo
- Publication number
- EP2399031A1 EP2399031A1 EP09801210A EP09801210A EP2399031A1 EP 2399031 A1 EP2399031 A1 EP 2399031A1 EP 09801210 A EP09801210 A EP 09801210A EP 09801210 A EP09801210 A EP 09801210A EP 2399031 A1 EP2399031 A1 EP 2399031A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- connecting channel
- throttle
- inlet channel
- fuel 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.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 59
- 238000002347 injection Methods 0.000 claims abstract description 8
- 239000007924 injection Substances 0.000 claims abstract description 8
- 238000002485 combustion reaction Methods 0.000 claims abstract description 6
- 230000001154 acute effect Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 abstract description 12
- 230000007704 transition Effects 0.000 description 8
- 230000002349 favourable effect Effects 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 230000001419 dependent effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000010354 integration 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
- F02M59/44—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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/103—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being a radial piston pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
Definitions
- the invention relates to a fuel pump, in particular a low-pressure pump of a pump arrangement with a low-pressure pump and a high-pressure pump. Specifically, the invention relates to the field of fuel injection systems of air compressing, self-igniting internal combustion engines.
- the known pump arrangement is particularly suitable for a common rail injection system.
- the known pump arrangement comprises a radial piston pump with a drive shaft mounted in a pump housing and a low pressure pump upstream of the radial piston pump.
- the intake is located on the pump housing.
- the fuel pump according to the invention with the features of claim 1 and the fuel pump according to the invention with the features of claim 12 have the advantage that an operation is improved. Specifically, a fuel pump can be created, which has a throttle for limiting flow, with an advantageous mode of operation of the throttle and at the same time a deflection for a fuel is realized.
- a throttle may be designed as a diaphragm or nozzle.
- the length is much larger than a throttle diameter.
- the throttle is not configured as such a laminar throttle.
- a ratio of a length of the throttle to a diameter of the throttle is less than about 1.5.
- the ratio of the length of the throttle to the diameter of the throttle may also be greater than 1.5, in particular slightly greater than 1.5.
- the throttle may be arranged in the extension of the inlet channel. This allows the design of the inlet channel together with the throttle by means of a step tool.
- a configuration can be realized in which a flow separation in the region of the throttle is prevented or at least reduced, whereby the full throttle diameter is effective. Together with a subsequent large connection channel or the like. This can be achieved a good throttle effect.
- the connecting channel is designed as a blind bore and that the throttle opens laterally into a cylindrical portion of the connecting channel.
- a cross section of the connecting channel is greater than a cross section of the throttle, so that a nearly ideal throttle behavior can be achieved.
- the inlet channel has a conical end section and that the throttle adjoins the conical end section.
- the throttle is at least approximately aligned with an axis of the inlet channel.
- the throttle is designed as a throttle bore.
- an advantageous positioning of the throttle is given.
- a simple configuration by means of a step tool is possible.
- the direction of the inlet channel and the direction of the connecting channel form an angle of approximately 90 °.
- a deflection of the fuel is realized, wherein an advantageous intersection between the throttle and the connecting channel is realized, in particular, the throttle length is defined defined.
- the Connecting channel is designed as at least substantially unthrottled connection channel, so that the throttling effect of the inlet to the inlet channel, the connecting channel and the throttle is determined at least substantially by the throttle.
- the inlet channel can be configured in an advantageous manner as an inlet bore, which extends at least in sections through an inlet connection.
- the inlet channel can be configured in a housing part of the high-pressure pump, wherein the inlet nozzle can be an integral part of the housing part.
- the throttle and the connecting channel can be integrated in an advantageous manner in a housing part of an external gear pump.
- the inlet channel has a conical end portion and that an inner angle of the conical end portion is at least approximately equal to twice the acute angle included by the direction of the inflow channel with the direction of the connection channel.
- an advantageous transition between the inlet channel and the connecting channel is made possible.
- flow separation can be prevented or at least reduced.
- the connecting channel opens at the conical end portion of the inlet channel into the inlet channel and that the connecting channel is designed as throttling connecting channel.
- a suction chamber is provided, that the connecting channel opens into the suction chamber and that a cross section of the suction chamber in an opening region in which the connecting channel opens into the suction chamber, is substantially larger than a cross section of the connecting channel.
- the suction chamber can be designed in particular in a low-pressure pump, in particular an external gear pump. This results in the advantage that a good throttle effect can be achieved.
- Fig. 1 is a side view of a fuel pump according to an embodiment of the invention
- FIG. 2 shows a partial section through the fuel pump shown in FIG. 1 along the section line designated II according to a conventional embodiment
- Fig. 3 shows the section shown in Fig. 2 by the fuel pump according to the embodiment of the invention
- Fig. 4 shows the section shown in Fig. 2 by the fuel pump according to a further embodiment of the invention.
- Fig. 1 shows a fuel pump 1 in a side view according to an embodiment of the invention.
- the fuel pump 1 can in particular be configured as a pump arrangement with a low-pressure pump, for example an external gear pump 2, and a high-pressure pump 3 for fuel injection systems of air-compressing, self-igniting internal combustion engines.
- the fuel pump 1 can also be designed as another gear pump, in particular internal gear pump, or as a vane pump.
- a preferred use of the fuel pump 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure.
- the fuel pump 1 according to the invention is also suitable for other applications.
- the fuel pump 1 of the exemplary embodiment has a first pump part 2, which is designed as an external gear pump 2, and a second pump part 3, which is designed as a high-pressure pump 3, on.
- the second pump part 3 lies behind the first pump part 2 and is partially covered by the first pump part 2.
- a feed or intake 4 is provided, can be supplied via the fuel from a tank or the like. From the inlet nozzle 4, the fuel passes through the housing of the second pump part 3 to the gear pump forming the first pump part 2, that of the second pump part 3 forming high-pressure pump is connected upstream.
- the first pump part 2 therefore has the function of a low-pressure pump, while the second pump part 3 has the function of a high-pressure pump.
- the high-pressure pump of the second pump part 3 can be designed in particular as a radial piston pump.
- the first pump part 2 has gears 5, 6, the position of which is shown in FIG. 1 by broken lines.
- the gears 5, 6 are covered by a housing part 7 of the external gear pump 2, which is designed as a housing 7 of the external gear pump 2.
- the housing part 7 is connected to fixed points 8A, 8B, 8C, 8D with a housing part 9 of the second pump part 3.
- the housing part 9 is designed as a high-pressure pump housing 9.
- the inlet nozzle 4 is part of the housing part 9.
- the housing part 7 at four fixed points 8 A, 8 B, 8 C, 8 D is connected to the housing part 9 of the second pump part 3.
- different arrangements for the fixed points 8A, 8B, 8C, 8D are possible.
- a different number of fixed points may be provided, in particular, three fixed points may be provided to connect the housing parts 7, 9 with each other.
- FIG. 2 shows a partial cut through the housing part 9 of the fuel pump 1 shown in FIG. 1 along the section line designated II according to a conventional embodiment.
- an inlet channel 15 is formed, which is designed as a blind hole.
- the inlet channel 15 extends in sections through the inlet nozzle 4, wherein the inlet channel 15, in particular in the region of the inlet nozzle 4, can be configured as a stepped bore.
- the inlet channel 15 extends in a direction 16 through the housing part 9.
- the inlet channel 15 has an axis 17 along which the inlet channel 15 extends in the direction 16.
- the inlet channel 15 has a bore bottom 18, on which the inlet channel 15 designed as a blind hole ends.
- the bore bottom 18 is designed conical.
- a connecting channel 19 is also formed, which is configured by a bore.
- the connecting channel 19 opens into the inlet channel 15 at the bore bottom 18.
- the connecting channel 19 has an axis 21 along which the connecting channel 19 extends in one direction 22.
- fuel is fed via the inlet channel 15 and the connecting channel 19 to the external gear pump 2.
- the fuel flows in the direction 16 through the inlet channel 15 and in the direction 22 through the connecting channel 19.
- the direction 16 of the inlet channel 15 includes with the direction 22 of the connecting channel 19 an angle 23 of about 90 °. That is, the axis 17 of the inlet channel 15 closes with the axis 21 of the connecting channel 19, the angle 23 of about 90 °.
- the external gear pump 2 is preferably operated in suction-throttled operation in order to limit a flow rate.
- the throttle effect required for this purpose is achieved through the connecting channel 19.
- a cross section of the connecting channel 19 is set relatively small, so that the connecting channel 19 as a throttle acts. This means that acting as a throttle connection channel 19 is seated at an angle of approximately 90 ° to the inlet channel 15.
- the flow from the wall of the connecting channel 19 comes off in a region 24 of the connecting channel 19. In this way, the full cross section of the connecting channel 19 no longer acts as a throttle.
- the effect of the throttle is thereby changed and possibly undetermined.
- the throttling action of the connecting channel 19 is dependent on the transition of the inlet channel 15 in the connecting channel 19 at the bottom of the hole 18.
- the transition depending on the configuration of the intersection between the channels 15, 19 vary. Possible reasons for varying transitions between the inlet channel 15 and the connecting channel 19 are, for example:
- the connecting channel 19 meets in the bore bottom 18 or in a cylindrical part 25 of the inlet channel 15.
- the angle 23 between the inlet channel 15 and the connecting channel 19 may vary, for example due to interference contours.
- the diameter or cross section of the inlet channel 15 at the transition to the connecting channel 19 may vary due to interference contours.
- the throttle effect of the throttle formed by the connecting channel 19 can vary. As a result, the throttle behavior of the connection channel 19 is not determined, so that no ideal throttle behavior is present.
- the above points may also result in that for each variant of the high-pressure pump, in particular for legal and Linksmoortagen, a separate throttle diameter for the connecting channel 19 must be specified and votes are required.
- Fig. 3 shows the detail shown in Fig. 2 of the housing part 9 of the fuel pump 1 according to the embodiment of the invention.
- the connecting channel 19 extends in a direction 22 which deviates from a direction 16 of the inlet channel 15. However, adjoining the inlet channel 15 in the direction 16, a throttle 30, which is aligned in this embodiment on the axis 17 of the inlet channel 15.
- the connecting channel 19 is designed in this case in the form of a blind bore having a bore bottom 31.
- the connecting channel 19 has a cylindrical portion 32.
- the throttle 30 opens laterally into the connecting channel 19 and indeed into the cylindrical portion 32 of the connecting channel 19.
- the inlet channel 15 has a conical end portion 33.
- the conical end portion 33 connects in the direction 16 to the cylindrical part 25 of the inlet channel 15.
- the throttle 30 connects.
- a transition from the cylindrical part 25 of the inlet channel 15 is formed in the throttle 30.
- the connecting channel 19 has a diameter or cross section which is relatively large compared to a diameter or cross section of the throttle 30. This results in a favorable intersection between the throttle 30 and the connecting channel 19, wherein a reproducible in the production of the intersection line 34, which preferably deviates only slightly from a circular intersection line.
- Both the Inlet channel 15 and the connecting channel 19 have essentially no throttle effect.
- a specific throttle effect of the throttle 30 is predetermined.
- the effective length of the throttle 30 is therefore obtained uniformly along the circumference of the throttle 30. Thereby, a defined throttle effect of the throttle 30 is given.
- the effect of the throttle 30 can be specified in a simple manner.
- the diameter or cross section of the throttle 30 can be specified. Since the throttle 30 directly adjoins the inlet channel 15 in the direction 16, the inlet channel 15 can be produced together with the throttle 30 by means of a stepping tool.
- the throttle 30 can also be integrated into the housing part 7 of the external gear pump 2. In this case, defined ratios for the throttle 30 can also be created.
- the angle 23 between the inlet channel 15 and the connecting channel 19 is preferably equal to 90 °. This is production technology advantageous. However, a beneficial throttling effect can also be applied to other angles 23 not equal to 90 ° are reached. It is particularly advantageous if the angle 23 is equal to or greater than 90 °, for example equal to 110 °. This is fluidly advantageous.
- Fig. 4 shows the section shown in Fig. 2 by a fuel pump 1 according to another
- the inlet channel 15 has the cylindrical part 25 and the conical end section 33.
- the conical end portion 33 in this case has an internal angle 40.
- the conical end portion 33 is formed symmetrically to the axis 17 of the inlet channel 15. With respect to the axis 17 of the inlet channel 15, an angle 41 of the conical end portion 33 is determined as a half of the inner angle 40.
- the angle 41 represents an angle of inclination of the conical end portion 33 with respect to the axis 17 of the inlet channel 15.
- the connecting channel 19 opens in this embodiment at the conical end portion 33 in the inlet channel 15.
- the connecting channel 19 is preferably designed as throttling connecting channel 19.
- the connecting channel 19 can have along its axis 21 a constant cross section 42. This has a favorable effect on the flow conditions in the connecting channel 19, whereby a detachment of the flow is prevented.
- the cross-section 42 of the connecting channel 19 may also vary if necessary.
- the first pump part 2 which may be configured as a low-pressure pump 2, has a suction chamber 43.
- the connecting channel 19 opens into an outlet region 43 in the suction chamber 43.
- the suction chamber 43 has in the mouth region 44 has a cross section 45 which is substantially larger than the cross section 42 of the connecting channel 19.
- the connecting channel 19 is arranged obliquely to the inlet channel 15.
- the direction 16 of the inlet channel 15 with the direction 22 of the inlet channel 15 includes an angle 45, which is between 0 ° and 90 °.
- the angle 45 is an acute angle 45.
- the acute angle 45 between the direction 16 of the inlet channel 15 and the direction 22 of the connecting channel 19 at least approximately the same size as the angle 41 between the axis 17 of the inlet channel 15 and the conical end portion 33rd
- the inner angle 40 is at least approximately equal to twice the acute angle 45.
- the suction chamber 43 is significantly larger than the cross section 42 of the connecting channel 19. This can be a good Throttling action of the connecting channel 19 can be achieved. Specifically, flow separation can be prevented or at least reduced.
- the suction chamber 43 may be configured, for example, as part of an interior of the low-pressure pump 2.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009000945A DE102009000945A1 (en) | 2009-02-18 | 2009-02-18 | fuel pump |
PCT/EP2009/067745 WO2010094366A1 (en) | 2009-02-18 | 2009-12-22 | Fuel pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2399031A1 true EP2399031A1 (en) | 2011-12-28 |
EP2399031B1 EP2399031B1 (en) | 2015-08-05 |
Family
ID=41632302
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09801210.7A Active EP2399031B1 (en) | 2009-02-18 | 2009-12-22 | Fuel pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2399031B1 (en) |
CN (1) | CN102325997B (en) |
DE (1) | DE102009000945A1 (en) |
WO (1) | WO2010094366A1 (en) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19719265A1 (en) * | 1997-05-07 | 1998-11-12 | Deutz Ag | Internal combustion engine with fuel pump in the crankcase |
DE19736160A1 (en) | 1997-08-20 | 1999-02-25 | Bosch Gmbh Robert | High pressure fuel pump for IC engine in common rail systems |
JP2001214829A (en) * | 2000-01-31 | 2001-08-10 | Bosch Automotive Systems Corp | Fuel injection pump |
JP3861835B2 (en) * | 2003-03-31 | 2006-12-27 | 株式会社デンソー | Fuel injection pump |
DE10357612A1 (en) * | 2003-12-10 | 2005-07-07 | Robert Bosch Gmbh | Valve arrangement, in particular inlet valve of a high-pressure fuel pump |
DE102004037132A1 (en) * | 2004-07-30 | 2006-03-23 | Robert Bosch Gmbh | High-pressure line inside fuel injectors and suchlike has sections in which flow direction is reversed and in these sections has recirculation areas connected to flow restriction of determined width |
-
2009
- 2009-02-18 DE DE102009000945A patent/DE102009000945A1/en not_active Withdrawn
- 2009-12-22 EP EP09801210.7A patent/EP2399031B1/en active Active
- 2009-12-22 WO PCT/EP2009/067745 patent/WO2010094366A1/en active Application Filing
- 2009-12-22 CN CN200980157065.4A patent/CN102325997B/en active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2010094366A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN102325997A (en) | 2012-01-18 |
WO2010094366A1 (en) | 2010-08-26 |
DE102009000945A1 (en) | 2010-08-19 |
EP2399031B1 (en) | 2015-08-05 |
CN102325997B (en) | 2015-05-20 |
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