CN1729360A - The high-pressure service pump that is used for fuel indection device in internal combustion engine - Google Patents
The high-pressure service pump that is used for fuel indection device in internal combustion engine Download PDFInfo
- Publication number
- CN1729360A CN1729360A CN200380107002.0A CN200380107002A CN1729360A CN 1729360 A CN1729360 A CN 1729360A CN 200380107002 A CN200380107002 A CN 200380107002A CN 1729360 A CN1729360 A CN 1729360A
- Authority
- CN
- China
- Prior art keywords
- live axle
- pressure service
- housing
- 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.)
- Pending
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 42
- 238000002485 combustion reaction Methods 0.000 title claims description 9
- 230000005540 biological transmission Effects 0.000 claims abstract description 25
- 238000003860 storage Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
Images
Classifications
-
- 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
- F04B1/0413—Cams
-
- 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
Abstract
A kind of high-pressure service pump, has a housing (10), wherein be provided with at least one pump unit (32), this pump unit has one by at least one supporting position (14 in housing (10), 16) live axle that is supported rotationally on (12) is driven into the pump plunger (34) of linear reciprocating motion through a transmission part (28), wherein this live axle (12) has an eccentric section (26), and this transmission part (28) is rotatably supported on this off-centre section by a supporting position (30).By a channel system (54,55,57) that extends through this live axle (12) fuel that is used to lubricate is carried at the supporting position (30) of this transmission part (28) on this off-centre section (26) of described live axle.
Description
Prior art
The present invention relates to the high-pressure service pump that is used for fuel indection device in internal combustion engine according to the described type of claim 1.
This high-pressure service pump is disclosed by DE 198 48 035 A1.This high-pressure service pump has a housing, wherein be provided with at least one pump unit, this pump unit has a pump plunger, and this pump plunger is driven into linear reciprocating motion by a live axle that is supported on rotationally in the housing through the transmission part of a polygonal loop type.This live axle has an eccentric section, and described transmission part is supported on this off-centre section rotationally by a bearing sleeve.This live axle is supported in the housing by two supporting positions that respectively have a bearing sleeve.The lubricated fuel that exists by the inside at housing at the lubricated and supporting position of live axle in housing at the supporting position of transmission part on the eccentric section of live axle is realized.When by high-pressure service pump under very high pressure during transfer the fuel, especially produce corresponding high load for the supporting position of transmission part and for the supporting position of live axle, make the fuel that exists by inside thus at housing lubricated no longer fully and these supporting positions have high wearing and tearing.
Advantage of the present invention
By contrast, high-pressure service pump according to feature of the present invention, as to have claim 1 has its advantage, promptly transmission part lubricated on the supporting position on the eccentric section of live axle improves with little construction cost at least, thus under can wearing and tearing little situation at the supporting position by this high-pressure service pump under very high pressure transfer the fuel.
Favourable structure and further configuration have been provided in the dependent claims according to high-pressure service pump of the present invention.At least one supporting position by also can improving live axle according to the structure of claim 3 lubricated.Improvement by the fuel distribution on the supporting position can realize supporting the lubricated further improvement in position according to the structure of claim 4 and 5.Can realize simple manufacturing according to the structure of claim 6 to the channel system in the live axle.Structure according to claim 7 and 8 can realize that fuel is transported in the channel system of live axle with the supporting position of simple mode by live axle.
Description of drawings
Express embodiments of the invention in the accompanying drawings, and in the following description it is described in detail.Accompanying drawing is represented:
Fig. 1 has the fuel injection system of the internal-combustion engine of a high-pressure service pump,
The zoomed-in view of a longitudinal section of Fig. 2 high-pressure service pump,
The zoomed-in view of the part that indicates with III among Fig. 3 Fig. 2, it has a supporting position of high-pressure service pump, and
The zoomed-in view of the part that indicates with IV among Fig. 4 Fig. 2, it has a supporting position of high-pressure service pump.
Embodiment's description
Expression is used for a fuel injection system of internal-combustion engine among Fig. 1, and it is a self-igniting internal combustion engine.This fuel injection system has a high-pressure service pump 100, and by this high-pressure service pump, fuel is transported under the high pressure that can reach 2000bar in the storage 110.Draw the pipeline 120 that some lead to the sparger 130 on the cylinder that is arranged on internal-combustion engine from this storage 110, inject fuel into by these spargers in the firing chamber of cylinder.Fuel is transported to the suction side of high-pressure service pump 100 by a transfer pump 140 by a tank 150.Produce for example 2 to 10bar pressure by transfer pump 140.Between transfer pump 140 and high-pressure service pump 100, a fuel metering unit 160 can be set, can regulate the flow fuel that flows to high-pressure service pump 100 by transfer pump 140 changeably by this fuel metering unit.Go out a lubricated attachment portion 170 that is used for the drive area of high-pressure service pump 100 by transfer pump 140 with the top set that is connected between the high-pressure service pump 100, wherein will explain below high-pressure service pump 100 and drive area thereof.Be provided with a pressure valve 180 in this lubricated attachment portion 170, this pressure valve just discharges lubricated attachment portion 170 when surpassing predetermined pressure.Flow by lubricated attachment portion 170 preferably limits by a throttle point 190.
Express this high-pressure service pump 100 among Fig. 2 enlargedly.This high-pressure service pump has a housing 10, and is that this casing structure becomes multi-part type and be provided with a live axle 12 therein.This live axle 12 is supported in the housing 10 rotationally by two supporting positions 14 and 16 that separate each other on the direction of the spin axis 13 of this live axle 12.These supporting positions 14,16 can be set in the different parts of housing 10.In the zone at these supporting positions 14,16, described housing 10 always has a hole 18,20, and live axle 12 is supported by each bearing sleeve 22,24 in described hole.
In the zone between two supporting positions 14,16, this live axle 12 has an eccentric section 26, and on this off-centre section, the transmission part 28 of the form of a polygonal ring is supported on the supporting position 30 rotationally.This high-pressure service pump 100 have at least one, preferred a plurality of pump unit 32 that respectively have a pump plunger 34 that are arranged in the housing 10, this pump plunger is driven at the spin axis 13 of this live axle 12 relatively linear reciprocating motion on the direction of approximate radial at least by described transmission part 28.Described pump plunger 34 in housing 10 or a cylinder hole 36 in an inserts of housing 10 in be directed to and the end face of carrying described transmission part 28 with it forms the border in a pump work chamber 38 in this cylinder hole 36.This pump work chamber 38 has an attachment portion that is connected with described transfer pump 140 by the fuel input channel 40 of extending in housing 10.Be provided with an inlet valve 42 of opening towards pump work chamber 38 on the port in these fuel input channel 40 feeding pump work chambeies 38, this inlet valve has a spring-biased valve element 43.In addition, this pump work chamber 38 has an attachment portion that is connected with storage 110 by the fuel discharge route 44 that extends in housing 10.Be provided with an expulsion valve 46 of opening towards the direction of being discharged by pump work chamber 38 on the port in these fuel discharge route 44 feeding pump work chambeies 38, this expulsion valve also has a spring-biased valve element 47.
This pump plunger 34 is kept in touch with described transmission part 28 with its plunger base 50 by the spring 48 of preload by one.When described live axle 12 is rotated when motion, this transmission part does not rotate with this live axle, carries out and the perpendicular motion of the spin axis 13 of this live axle 12 and be based on described eccentric section 26, and this motion causes the linear reciprocating motion of pump plunger 34.In the suction stroke of pump plunger 34, wherein this pump plunger radially inwardly the motion, under the situation that described inlet valve 42 is opened by described fuel input channel 40 with fuel charge active chamber 38, at this moment described expulsion valve 46 cuts out.In the current drainage stroke of pump plunger 34, wherein this pump plunger radially outward motion under high pressure is transported to storage 110 through described fuel discharge route 44 by this pump plunger 34 with fuel under the situation that expulsion valve 46 is opened, and at this moment described inlet valve 42 cuts out.
Extend in the passage 52 of lubricated attachment portion 170 in housing 10 of being drawn by transfer pump 140, this passage leads on the outer surface of live axle 12.In this live axle 12, be configured with a channel system, passage 52 feeds this channel system, and by this channel system, fuel is drawn towards the supporting position 30 of transmission part 28 on the eccentric section 26 of live axle 12 under pressure, fuel flows out this channel system and lubricated this supporting position 30 at this.Channel system in live axle 12 has a first passage section 54, this channel section 54 for example spin axis 13 of relative drive shaft 12 approximate radial ground is extended and the outer surface that is configured to self-powered moving axis 12 is offered hole in this live axle at least, and this hole approximately reaches the center of this live axle 12.This first passage section 54 leads to the outer surface of described live axle 12 in a plane, the port of described passage 52 in housing 10 also is arranged in this plane.Connecting a second channel section 55 on this first passage section 54, this second channel section extends on the direction of the spin axis 13 of live axle 12, for example extends coaxially with this spin axis 13.The end face that this second channel section 55 is configured to a self-powered moving axis 12 is offered the vertical hole in this live axle, especially with the form of blind hole.This second channel section 55 seals by a packaged unit 56 that is placed in this second channel section towards the end face of this live axle 12.On this second channel section 55, connecting a third channel section 57, this third channel section for example spin axis 13 of relative drive shaft 12 approximate radial ground extends and the outer surface that is configured to a self-powered moving axis 12 is offered hole in this live axle at least, and this hole approximately reaches the center of this live axle 12 and leads in the described second channel section 55.This third channel section 57 leads to the outer surface of the eccentric section 26 of live axle 12, preferably lead at least approx described transmission part 28 supporting position 30 in the heart.The fuel of carrying by transfer pump 140 by the channel system in described lubricated attachment portion 170, passage 52 and the live axle 12 54,55,57 arrive described transmission part 28 on the eccentric section 26 of live axle 12 supporting position 30 and discharge therefrom and be used to lubricate.
Can consider that this transmission part 28 directly is supported on the described eccentric section 26.Scheme also can be considered as an alternative, and this transmission part 28 is supported on this off-centre section 26 by a bearing sleeve 58.In the case, this bearing sleeve 58 can be configured to single-piece as shown in Figure 3 or be configured to two-piece type as shown in Figure 2.In the case, this bearing sleeve 58 is divided into two parts disposed adjacent one another on the direction of the spin axis 13 of live axle 12, has a gap 59 between them.This gap 19 is preferably placed in the plane on the outer surface that a described therein third channel section 57 leads to eccentric section 26.The fuel that is flowed out by described third channel section 57 further improved the lubricated of supporting position 30 by this bearing sleeve that separates 58, because can be distributed in the supporting position 30 better.
Except the supporting position 30 of transmission part 28 on eccentric section 26, also can lubricate one or two supporting position 14,16 of the live axle 12 in the housing 10 by the described channel system in the live axle 12.In the case, described second channel section 55 continues to extend to supporting position 16 always on the direction of the spin axis 13 of live axle 12, at this, connecting a four-way section 60 on this second channel section.This four-way section 60 for example spin axis 13 of relative drive shaft 12 approximate radial ground extends and the outer surface that is configured to self-powered moving axis 12 is offered hole in this live axle at least, and this hole approximately reaches the center of this live axle 12 and leads in the described second channel section 55.This four-way section 60 leads on the outer surface of live axle 12, preferably lead at least approx live axle 12 supporting position 16 in the heart.The bearing sleeve 24 at this supporting position 16 can be configured to single-piece or as above for bearing sleeve 58 two-piece type that is configured to, and between these two part parts, have a gap 25.
In addition, the supporting position 14 that also can additionally lubricate the live axle 12 in the housing 10 by the fuel of carrying by transfer pump 140 described lubricated attachment portions 170 of process and passage 52.In the case, described first passage section 54 leads in the zone at the supporting position 14 on the outer surface of this live axle 12, preferably lead at least approx supporting position 14 in the heart.But must guarantee that in the case fuel is arrived in the first passage section 54 by the bearing sleeve 22 of passage 52 by supporting position 14.For this reason, reach as shown in Figure 2 as above-mentioned described for bearing sleeve 58, this bearing sleeve 22 can be a two-piece type, and wherein the gap 23 between bearing sleeve 22 these part parts is set at described first passage section 54 and leads in the plane on the outer surface of described live axle 12.
The embodiment of a conversion of expression bearing sleeve 22 among Fig. 4, wherein this bearing sleeve is configured single-piece.In the case, this bearing sleeve 22 has a circular groove 62 on the surface within it, and this circular groove constitutes by the incision recessing.This circular groove 62 is arranged at least approx to have described passage 52 and leads in the common plane of the port on the internal surface that port on the outer surface of bearing sleeve 22 and described first passage section 54 lead to bearing sleeve 22.In addition, this bearing sleeve 22 has at least one hole 64, and this hole makes described circular groove 62 be connected with the outer surface of this bearing sleeve 22.Fuel can be arrived in the described first passage section 54 of live axle 12 by this hole 64 and this circular groove 62 by described passage 52.
In the zone of supporting position 14,16 and 30, a current drainage channel 66 can respectively be set in housing 10, by these current drainage channels, fuel can go out from these support bit streams.
Claims (9)
1. the high-pressure service pump that is used for fuel indection device in internal combustion engine, has a housing (10), in this housing, be provided with at least one pump unit (32), this pump unit has one by at least one supporting position (14 in housing (10), 16) live axle that is supported rotationally on (12) is driven into the pump plunger (34) of linear reciprocating motion through a transmission part (28), wherein this live axle (12) has an eccentric section (26), this transmission part (28) is rotatably supported on this off-centre section by a supporting position (30), it is characterized in that: by a channel system (54 that extends through this live axle (12), 55,57) fuel that is used to lubricate is carried at the supporting position (30) of this transmission part (28) on this off-centre section (26) of described live axle (12).
2. according to the high-pressure service pump of claim 1, it is characterized in that: this transmission part (28) is bearing on this off-centre section (26) by a bearing sleeve (58).
3. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: at least one in housing (10) of this live axle (12) supported position (16) also by this channel system (54 in the live axle (12), 55,60) carry the fuel that is used to lubricate, wherein at least one supporting position (16) upward preferably is bearing in the housing (10) by a bearing sleeve (24) this live axle (12) at this.
4. according to the high-pressure service pump of claim 2 or 3, it is characterized in that: the described bearing sleeve (22 of this transmission part (28) and/or this live axle (12), 24,58) be divided into part disposed adjacent one another on the direction of two spin axiss (13) in this live axle (12), between these two-part, there is a gap (23,25,59).
5. according to the high-pressure service pump of claim 4, it is characterized in that: at described bearing sleeve (22,24,58) spin axis (13) that this gap between these parts (23,25,59) is set at described relatively live axle (12) is at least approx in diametrically the plane, in this plane, described channel system (54,55,57) leads on the outer surface of this live axle (12).
6. according to one high-pressure service pump in the claim 1 to 5, it is characterized in that: this channel system has: the first passage section (54) on outer surface that leads to described live axle (12) is transported to fuel in this first passage section by a passage (52) that extends in housing (10); One be connected on the first passage section (54), at least basically at the upwardly extending second channel section in side (55) of the spin axis (13) of described live axle (12); At least one be connected on this second channel section, at the third channel section (57) that leads on the outer surface of described live axle (12) on the supporting position (30) of described transmission part (28).
7. according to the high-pressure service pump of claim 6, it is characterized in that: the described passage (52) that extends in housing (10) leads on the supporting position (14) of described live axle (12), on this supporting position, this live axle (12) is bearing in the housing (10) by a bearing sleeve (22); Described first passage section (54) leads on the outer surface of this live axle (12) in this bearing sleeve (22); This first passage section passes bearing sleeve (22) with being connected of the passage (52) that extends and realizes in housing (10).
8. according to the high-pressure service pump of claim 7, it is characterized in that: described bearing sleeve (22) has a circular groove (62) in the surface within it, this circular groove is set in the plane radially of spin axis (13) of described relatively live axle (12), in this plane, described channel system (54) leads on the outer surface of described live axle (12), and this circular groove preferably is connected with the outer surface of this bearing sleeve (22) by at least one hole (64) in this bearing sleeve (22).
9. have according to one the fuel indection device in internal combustion engine of high-pressure service pump in the above claim, it is characterized in that: fuel is flowed to high-pressure service pump (100) by transfer pump (140); The part of the fuel of being carried by transfer pump (140) flows to channel system (54,55,57,60) by a lubricated attachment portion (170); A pressure valve (180) and/or a throttle point (190) of opening to this channel system (54,55,57,60) preferably is set in this lubricated attachment portion (170).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10259178.4 | 2002-12-18 | ||
| DE10259178A DE10259178A1 (en) | 2002-12-18 | 2002-12-18 | High pressure pump for a fuel injection device of an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1729360A true CN1729360A (en) | 2006-02-01 |
Family
ID=32477745
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200380107002.0A Pending CN1729360A (en) | 2002-12-18 | 2003-12-16 | The high-pressure service pump that is used for fuel indection device in internal combustion engine |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20060239847A1 (en) |
| EP (1) | EP1576287A1 (en) |
| JP (1) | JP2006510835A (en) |
| CN (1) | CN1729360A (en) |
| DE (1) | DE10259178A1 (en) |
| WO (1) | WO2004055368A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102483017A (en) * | 2009-08-21 | 2012-05-30 | 罗伯特·博世有限公司 | High-pressure fuel pump |
| CN104822935A (en) * | 2012-12-04 | 2015-08-05 | 罗伯特·博世有限公司 | Pump, in particular, high-pressure fuel pump for internal combustion engine |
| CN114738154A (en) * | 2022-04-25 | 2022-07-12 | 广西玉柴机器股份有限公司 | Driving shaft structure of fuel injection pump |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1657429A1 (en) * | 2004-11-12 | 2006-05-17 | C.R.F. Società Consortile per Azioni | A high-pressure pump for an internal-combustion engine |
| WO2006053792A1 (en) * | 2004-11-17 | 2006-05-26 | Siemens Aktiengesellschaft | Pump assembly |
| EP1803933B1 (en) * | 2005-12-27 | 2010-05-19 | C.R.F. Societa Consortile per Azioni | High-pressure pump for a fuel, with sump in communication with the fuel inlet |
| IT1391518B1 (en) * | 2008-10-31 | 2011-12-30 | Bosch Gmbh Robert | METHOD AND PLANT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
| IT1397725B1 (en) * | 2009-12-22 | 2013-01-24 | Bosch Gmbh Robert | FUEL SUPPLY SYSTEM FROM A TANK TO AN INTERNAL COMBUSTION ENGINE. |
| DE102011089959A1 (en) * | 2011-12-27 | 2013-06-27 | Robert Bosch Gmbh | High-pressure fuel pump for a fuel injection system |
| GB201508464D0 (en) * | 2015-05-18 | 2015-07-01 | Delphi Int Operations Lux Srl | Pump assembly for a fuel injection system |
| JP6096255B2 (en) * | 2015-08-31 | 2017-03-15 | 中禾亞股▲ふん▼有限公司 | Output pressure lubrication structure of liquid pressurizing pump |
| CN110691904B (en) * | 2017-03-29 | 2021-08-03 | 瓦锡兰芬兰有限公司 | High-pressure fuel pump assembly for internal combustion piston engine |
| IT201700076837A1 (en) * | 2017-07-07 | 2019-01-07 | Bosch Gmbh Robert | PUMPING GROUP FOR FOOD FUEL, PREFERIBLY GASOIL, FROM A CONTAINMENT TANK TO AN INTERNAL COMBUSTION ENGINE |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4078529A (en) * | 1976-04-15 | 1978-03-14 | Douglas Warwick | Rotary engine |
| US4301777A (en) * | 1979-11-28 | 1981-11-24 | General Motors Corporation | Fuel injection pump |
| JPS58104326U (en) * | 1982-01-11 | 1983-07-15 | 株式会社デンソー | Fuel injection device for internal combustion engines |
| US5630708A (en) * | 1993-12-28 | 1997-05-20 | Zexel Corporation | Radial piston pump for low-viscosity fuel |
| DE19627757A1 (en) * | 1996-07-10 | 1998-01-15 | Bosch Gmbh Robert | Fuel pump |
| FI101999B (en) * | 1997-02-20 | 1998-09-30 | Waertsilae Nsd Oy Ab | Arrangement for internal combustion engine injection pump |
| BR9904868A (en) * | 1998-02-27 | 2000-09-26 | Stanadyne Automotive Corp | Fuel supply pump and process of operating a fuel injection system |
| DE19848035A1 (en) * | 1998-10-17 | 2000-04-20 | Bosch Gmbh Robert | Radial piston pump for high fuel pressure in IC engines with common-rail injection system has suction valve closure spring supported on pump piston and contained in long piston bore |
| US6694950B2 (en) * | 1999-02-17 | 2004-02-24 | Stanadyne Corporation | Hybrid control method for fuel pump using intermittent recirculation at low and high engine speeds |
| DE19924064B4 (en) * | 1999-05-26 | 2007-07-05 | Siemens Ag | displacement |
| DE10012306C2 (en) * | 2000-03-14 | 2003-12-24 | Bosch Gmbh Robert | Distributor injection pump |
| DE10129449A1 (en) * | 2001-06-19 | 2003-01-02 | Bosch Gmbh Robert | High-pressure fuel pump for internal combustion engines with improved part-load behavior |
| JP3849928B2 (en) * | 2001-09-03 | 2006-11-22 | 株式会社デンソー | Fuel injection pump |
| US6722864B2 (en) * | 2001-12-12 | 2004-04-20 | Denso Corporation | Fuel injection pump |
| US7134846B2 (en) * | 2004-05-28 | 2006-11-14 | Stanadyne Corporation | Radial piston pump with eccentrically driven rolling actuation ring |
-
2002
- 2002-12-18 DE DE10259178A patent/DE10259178A1/en not_active Withdrawn
-
2003
- 2003-12-16 CN CN200380107002.0A patent/CN1729360A/en active Pending
- 2003-12-16 EP EP03785577A patent/EP1576287A1/en not_active Withdrawn
- 2003-12-16 US US10/539,749 patent/US20060239847A1/en not_active Abandoned
- 2003-12-16 WO PCT/DE2003/004134 patent/WO2004055368A1/en active Application Filing
- 2003-12-16 JP JP2004559613A patent/JP2006510835A/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102483017A (en) * | 2009-08-21 | 2012-05-30 | 罗伯特·博世有限公司 | High-pressure fuel pump |
| CN104822935A (en) * | 2012-12-04 | 2015-08-05 | 罗伯特·博世有限公司 | Pump, in particular, high-pressure fuel pump for internal combustion engine |
| CN114738154A (en) * | 2022-04-25 | 2022-07-12 | 广西玉柴机器股份有限公司 | Driving shaft structure of fuel injection pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10259178A1 (en) | 2004-07-08 |
| JP2006510835A (en) | 2006-03-30 |
| WO2004055368A1 (en) | 2004-07-01 |
| EP1576287A1 (en) | 2005-09-21 |
| US20060239847A1 (en) | 2006-10-26 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |