CN1711417A - High-pressure fuel pump comprising a ball valve in the low-pressure inlet - Google Patents
High-pressure fuel pump comprising a ball valve in the low-pressure inlet Download PDFInfo
- Publication number
- CN1711417A CN1711417A CN 200380102691 CN200380102691A CN1711417A CN 1711417 A CN1711417 A CN 1711417A CN 200380102691 CN200380102691 CN 200380102691 CN 200380102691 A CN200380102691 A CN 200380102691A CN 1711417 A CN1711417 A CN 1711417A
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- CN
- China
- Prior art keywords
- pressure
- fuel pump
- fuel
- ball
- pressure fuel
- 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 81
- 238000007789 sealing Methods 0.000 claims description 33
- 238000002347 injection Methods 0.000 claims description 11
- 239000007924 injection Substances 0.000 claims description 11
- 238000002485 combustion reaction Methods 0.000 claims description 9
- 238000010304 firing Methods 0.000 claims description 5
- 238000004519 manufacturing process Methods 0.000 abstract description 5
- 230000008092 positive effect Effects 0.000 abstract 1
- 230000008901 benefit Effects 0.000 description 5
- 238000005452 bending Methods 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000003534 oscillatory effect Effects 0.000 description 2
- 208000005189 Embolism Diseases 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 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
- 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
- F04B53/10—Valves; Arrangement of valves
- F04B53/1002—Ball 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
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- 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
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F04B1/0452—Distribution members, e.g. valves
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
The invention relates to a high-pressure fuel pump (10), in particular a radial-piston pump, in which the suction valves (35) are configured as ball valves. This has a positive effect on the efficiency of the high-pressure fuel pump (10). In addition, the use of ball valves simplifies the production and assembly of the inventive high-pressure fuel pump (10).
Description
Prior art
The present invention relates to by the German patent DE 101 17 600 disclosed high-pressure fuel pumps that are used for fuel injection system, it has: a housing, a low-pressure inlet, the conveying space of compressed fuel therein, suction valve between conveying space and low-pressure inlet, wherein the valve element of suction valve is bearing on the pressure spring that is arranged in the conveying space.
In this high-pressure fuel pump, the valve element of suction valve is configured to valve cone.
Advantage of the present invention
Have at the high-pressure fuel pump that is used for fuel injection system according to the present invention: a housing, a low-pressure inlet, the conveying space of compressed fuel therein, suction valve between conveying space and low-pressure inlet, wherein the valve element of suction valve is bearing on the pressure spring that is arranged in the conveying space, and the valve element of suction valve is configured balling-up.
Simplified the manufacturing of high-pressure fuel pump thus because the comparable example of ball as is known in the art, valve element with seal cones and an axle makes more cheaply.In addition, but efficient improved according to high-pressure fuel pump of the present invention, because a ball constitutes the circular seal line of accurately determining with sealing seat, although machining tolerance is that inevitably the sealing line can make valve seat seal well when making valve seat.When being circular, even when does not make with highi degree of accuracy the angle of valve seat or position, still can seal well according to suction valve of the present invention with the interactional valve seat of ball.
In addition, can guarantee: have much at one hydraulic characteristic with all suction valves of the high-pressure fuel pump made in batches, and simplified optimization thus with the high-pressure fuel pump of making in batches by suction valve according to the present invention.
In a modification according to the present invention, propose: between pressure spring and ball, be provided with a spring seat, make fixedly improving of the relative sealing seat of ball thus, and can avoid the transverse bending of pressure spring in addition.The use of spring seat can make that the diameter of pressure spring and ball is inequality in addition.Especially be proved advantageously, the diameter of ball is less than the diameter of pressure spring, because avoided the diameter of the transverse bending of pressure spring and ball can be fit to the hydraulic pressure requirement of high-pressure fuel pump best in this case effectively.
In another configuration of the present invention, in housing, be provided with one with the interactional valve seat of ball, the number that makes the number of the sealing surface that is loaded by high pressure and parts thus is than having been reduced by the known high-pressure fuel pump of prior art.This has just improved according to the reliability of high-pressure fuel pump of the present invention and has reduced its manufacturing and assembly cost.
Be proved advantageously, valve seat has the angle of valve seat between 30 ° and 150 °, and it is especially between 80 ° and 100 °.
Substitute sealing seat directly is set in housing, housing also can comprise a screw, and this screw outside relatively closes a conveying space hole, valve seat be formed in screw on the end face of conveying space.This scheme has its advantage, and promptly suction valve is easy to assembling or can be replaced under maintenance status, and need not the disintegration fully of high-pressure fuel pump, because suction valve can reach by screw from the outside.
Implement in another configuration of flexible program at this, screw has the zone that a diameter reduces, and zone that this diameter reduces and housing define an annular chamber, and this annular chamber is connected with low-pressure inlet formation hydraulic pressure.Guaranteed in simple mode thus: how deeply irrespectively to be screwed into housing with screw, formation all the time is connected with the hydraulic pressure of low-pressure inlet.
When high-pressure fuel pump constituted according to one in the above-mentioned embodiment, advantage of the present invention can work in a fuel system certainly, and this system has: a fuel container; An injection valve, it directly is ejected into fuel in the firing chamber of internal-combustion engine; A high pressure fuel pump; And a fuel manifold, on this fuel manifold, connect an injection valve at least.
Other advantage of the present invention and favourable configuration can obtain from following accompanying drawing, description of drawings and claims.
Description of drawings
Accompanying drawing is:
Fig. 1 is according to first embodiment of radial plunger pump of the present invention,
Fig. 2 is according to second embodiment of radial plunger pump of the present invention,
Fig. 3 reaches according to the zoomed-in view of suction valve of the present invention
Fig. 4 is equipped with the internal-combustion engine schematic representation according to high-pressure fuel pump of the present invention.
Embodiment
Fig. 1 represents the cross-sectional view according to first embodiment of high-pressure fuel pump 10 of the present invention.This high-pressure service pump 10 is configured to have the radial plunger pump of three pump unit 11.Pump unit 11 comprises a plunger 13, and this plunger is directed in a cylinder hole 15.This cylinder hole 15 is configured to blind hole in the housing 17 of high-pressure service pump 10.Can produce cylinder hole 15 by processing and pilot hole 19.After high-pressure fuel pump assembling according to the present invention, pilot hole 19 is by embolism 21 sealings.
Plunger 13 has the polygonal ring 23 that scabbles part 25 by the live axle with an eccentric section 22 by one and drives.A plunger base plate 27 rests on this and scabbles on the part 25, and when live axle is driven and polygonal ring 23 when carrying out circular movement thus, this plunger base plate makes plunger 13 produce oscillatory movements.In one of these pump unit 11, this oscillatory movement of plunger 13 indicates with double-head arrow 29.
For the sake of clarity, on all pump unit 11, all parts are not provided with label.But the structure of all three pump unit 11 is identical and have identical parts.
As mentioned above, cylinder hole 15 is configured blind hole.Be provided with suction valve 37 with a sealing seat 37 and one and ball 39 of sealing seat 37 cooperatings in the end in cylinder hole 15.This ball 39 is pressed on the valve seat 37 by pressure spring 43 by a spring seat 41, and the other end of this pressure spring is bearing on the plunger 13.
In the case, pressure spring 43 is determined parameter like this, and promptly fuel can not automatically be sucked when lower dead centre.When unshowned when one, as to be arranged on high-pressure fuel pump 10 suction sides metering unit sealed, high-pressure fuel pump 10 is transfer the fuel not.When metering unit is opened wholly or in part, set up the excess pressure that produces by prime transfer pump (not shown) in the front of suction valve 35, by this excess pressure, fuel renitency spring 43 is pressed into conveying space 31.The task of metering unit is, regulates the excess pressure of suction chamber front, so that carries required quantity delivered by high-pressure fuel pump 10.
When plunger 13 during towards the motion of the direction of its upper dead center, the bias voltage of pressure spring 33 increases so doughtily, also interrupts thus on the sealing seat 37 being connected between conveying space 31 and the low-pressure inlet 45 so that ball 39 is pressed in.This effect will strengthen significantly by the pressure that increases in the conveying space 31.
Conversion ground, this pressure spring 43 can be determined parameter in this wise, promptly ball 39 still gently is pressed on the sealing seat 37 when the lower dead centre (UT) of plunger 13.Only when the pressure in the relative conveying space 31 of low voltage side unshowned in Fig. 1, high-pressure fuel pump 10 had enough excess pressure, fuel just flowed in the conveying space 31.The pressure on the suction side on the low voltage side of high-pressure fuel pump 10 or at conveying space 31 and thus the quantity delivered of high-pressure fuel pump 10 will be by Fig. 1 in unshowned metering unit regulate according to the working state of internal-combustion engine by a control gear (not shown).
Guaranteed by these measures: though since unshowned metering unit make fuel stream by low-pressure inlet 45 throttlings when entering in the pump unit 11, each pump unit 11 almost can suck identical fuel quantity and make high-pressure fuel pump 10 acquire uniform torque requirement and power requirement thus.This has just improved the running stability of internal-combustion engine, especially when zero load.
Plunger 13 neither be directed in cylinder hole 15 by its whole length during the dead point thereon, makes boring grinding tool or similar cutter have enough " excess of stroke " by this measure.This excess of stroke makes the processing in the cylinder hole 15 that is configured to blind hole become easy.
Not shown high-pressure outlet and affiliated pressure valve in Fig. 1 are because high-pressure outlet and affiliated pressure valve are arranged on the back of pump unit 11 perpendicular to the drawing plane earth.The structure of these parts can be by obtaining among the DE-PS 101 17 600, and the document is hereby expressly incorporated by reference.
By between ball 39 and pressure spring 43, using a spring seat 41 to improve guiding to ball 39.In addition, because the improvement of the supporting surface of pressure spring 43 on spring seat 41 can be avoided the transverse bending of pressure spring 43.At last, the diameter of ball 39 can be irrespectively selected with the diameter of pressure spring 43, and this optimization for high-pressure fuel pump 10 is favourable.
But also directly can consider, also also can abandon using spring seat 41, so that pressure spring 43 directly rests on (not shown) on the ball 39.
High pressure sealing point, the especially sealing seat 37 that in first embodiment shown in Fig. 1, only has a number seldom and ball 39 according to high-pressure fuel pump 10 of the present invention be connected and plunger 13 and cylinder hole 15 between the annular space.These high pressure sealing points proof, when the cylinder hole was configured to blind hole, in many cases in the cylinder hole 15 when making, manufacture cost was higher.
Special benefits for the suction valve 35 that is configured ball valve studies in great detail in conjunction with Fig. 3 below.
In Fig. 2, also show second embodiment according to high-pressure service pump 10 of the present invention with sectional view.Identical parts are provided with identical label and corresponding with the configuration among Fig. 1.This embodiment and first embodiment's the main distinction is: cylinder hole 15 is not as blind hole but constitutes as open-work.In this embodiment, cylinder hole 15 is by 47 sealings of a screw.In this screw 47, offer the sealing seat 37 of suction valve 35.
Below will describe the function of suction valve 35 in more detail, the figure shows the local A of an amplification among the figure by Fig. 3.
On sealing seat 37, connecting an axial bore 48 and a transverse holes 49.As an alternative, a plurality of transverse holes 49 (not shown) also can be set.Transverse holes 49 is switched in the annular chamber 50, and this annular chamber 50 constitutes the border by the zone 50 that a diameter of housing 17 and screw 47 reduces.Structure has a joggle edges 53 on an end face 52 of screw 47, and its relative conveying space 31 is with annular chamber 51 sealings.
This annular chamber 51 forms being connected of hydraulic pressure with low-pressure inlet 45 that can not see in the figure, high-pressure fuel pump 10.Because annular chamber surrounds screw 47 on all sides, then can fuel be drawn in the conveying space 31 by transverse holes 49 and axial bore 48, and with screw 47 be screwed in the housing 17 the degree of depth what have nothing to do.
By the suction valve 35 that uses to constitute as ball valve, can improve the efficient of high-pressure fuel pump, because in a single day ball 39 rises from sealing seat 37, it can discharge big flow cross, so that fuel is not inhaled into with can promptly and having big flow loss.This favourable is also had: when suction valve 35 is opened, the annular cross section between sealing seat 37 and ball 39 approximately than the cross section of transverse holes 49 greatly to 20 times.
In addition because the good seal performance of the suction valve 35 that constitutes as ball valve, in the delivery stroke of plunger 13 no fuel from conveying space 31 by back pressure to low-pressure inlet 45.
Schematically show an internal-combustion engine 54 among Fig. 4.It comprises a fuel injection system 56.This system also has 58, one electronic low-pressure fuel pump 60 of a fuel container from this container transport fuel.
This electronic low-pressure fuel pump 60 is transported to high-pressure fuel pump 10 with fuel, and this high-pressure service pump constitutes shown in Fig. 1 and 2.The high-pressure outlet 18 of high-pressure fuel pump 10 is connected with a fuel manifold 62.This fuel manifold is also referred to as " rail altogether " usually.On fuel manifold 62, be connected with 4 injection valves 64 altogether.They directly are ejected into fuel in the firing chamber 66 of internal-combustion engine 54 respectively.
Claims (9)
1. the high-pressure fuel pump (10) that is used for fuel injection system (56), it has: a housing (17,47), a low-pressure inlet (45), the conveying space of compressed fuel (31) therein, suction valve (35) between conveying space (31) and low-pressure inlet (45), wherein a valve element of suction valve (35) is bearing on the plunger (13) by the pressure spring (43) that is arranged in the conveying space (31), and have a high-pressure outlet, it is characterized in that: the valve element of this suction valve (35) is constituted as ball (39).
2. according to the high-pressure fuel pump of claim 1, it is characterized in that: between pressure spring (43) and ball (39), be provided with a spring seat (41).
3. according to the high-pressure fuel pump of claim 1 or 2, it is characterized in that: the diameter of ball (39) is less than the diameter of pressure spring (43).
4. according to the high-pressure fuel pump (10) of one of above claim, it is characterized in that: in housing (17,47), have one and the interactional sealing seat of ball (39) (37).
5. according to the high-pressure fuel pump of claim 4, it is characterized in that: sealing seat (37) has the sealing seat angle (α) between 30 ° to 150 °, and it especially is 90 °.
6. according to the high-pressure fuel pump of one of above claim, it is characterized in that: housing (17,47) comprises a screw (47), the outside relatively sealing of this a screw cylinder hole (31); Sealing seat (37) is formed on the end face towards conveying space (31) (52) of screw (47).
7. according to the high-pressure fuel pump of claim 6, it is characterized in that: screw (47) has the zone (50) that a diameter reduces; Zone that this diameter reduces (50) and housing (17) have constituted the border of an annular chamber (51); This annular chamber (51) is connected with low-pressure inlet (45) hydraulic pressure.
8. fuel injection system (56), it has: a fuel container (58); At least one injection valve (64), it directly is ejected into fuel in the firing chamber (66) of internal-combustion engine (54); At least one high pressure fuel pump (10); And a fuel manifold (62), on this fuel manifold, connecting this at least one injection valve (64), it is characterized in that: high-pressure fuel pump (10) is configured (Fig. 4) according to one of claim 1 to 7.
9. have the internal-combustion engine (54) of at least one firing chamber (66), fuel is directly injected in this firing chamber, it is characterized in that: this internal-combustion engine has a fuel injection system (56) according to Claim 8 (Fig. 4).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10250661.2 | 2002-10-31 | ||
| DE10250661 | 2002-10-31 | ||
| DE10302043.8 | 2003-01-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1711417A true CN1711417A (en) | 2005-12-21 |
| CN100429395C CN100429395C (en) | 2008-10-29 |
Family
ID=32114989
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2003801026916A Expired - Fee Related CN100429395C (en) | 2002-10-31 | 2003-10-31 | High-pressure fuel pump comprising a ball valve in the low-pressure inlet |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN100429395C (en) |
| DE (2) | DE10302043A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101981316A (en) * | 2008-03-26 | 2011-02-23 | 罗伯特·博世有限公司 | Pump, particularly a high-pressure fuel pump |
| CN102762859A (en) * | 2010-02-16 | 2012-10-31 | 罗伯特·博世有限公司 | Cylinder head for a high-pressure fuel pump |
| WO2013010458A1 (en) * | 2011-07-14 | 2013-01-24 | Neo Mechanics Limited | Diesel engine fuel injection pump which pistons are sealed with all metal seal rings |
| CN103299065A (en) * | 2011-01-14 | 2013-09-11 | 罗伯特·博世有限公司 | High-pressure pump |
| CN105378279A (en) * | 2013-06-13 | 2016-03-02 | 麦格纳动力系巴德霍姆堡有限责任公司 | Radial piston compressor |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ATE434724T1 (en) * | 2006-07-14 | 2009-07-15 | Bosch Gmbh Robert | HIGH PRESSURE PISTON PUMP FOR FUEL INJECTION OF AN INTERNAL COMBUSTION ENGINE |
| CN104234897B (en) * | 2013-06-17 | 2016-05-25 | 北京亚新科天纬油泵油嘴股份有限公司 | The plunger assembly that high voltage common rail pump is used |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4307651C2 (en) * | 1993-03-11 | 1996-05-09 | Hatz Motoren | Internal combustion engine with fuel injection, in particular single-cylinder diesel engine |
| DE69920601T2 (en) * | 1998-02-27 | 2006-03-09 | Stanadyne Corp., Windsor | FUEL SUPPLY PUMP FOR FUEL INJECTION PUMP |
| JP3924999B2 (en) * | 1999-08-12 | 2007-06-06 | 株式会社日立製作所 | Fuel pump and in-cylinder injection engine using the same |
| DE10057244A1 (en) * | 2000-11-18 | 2002-06-06 | Bosch Gmbh Robert | Fuel injection system for internal combustion engines with improved starting behavior |
| DE10117600C1 (en) * | 2001-04-07 | 2002-08-22 | Bosch Gmbh Robert | High-pressure fuel pump for a fuel system of a direct-injection internal combustion engine, fuel system and internal combustion engine |
-
2003
- 2003-01-21 DE DE10302043A patent/DE10302043A1/en not_active Withdrawn
- 2003-10-31 DE DE50310206T patent/DE50310206D1/en not_active Expired - Lifetime
- 2003-10-31 CN CNB2003801026916A patent/CN100429395C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101981316A (en) * | 2008-03-26 | 2011-02-23 | 罗伯特·博世有限公司 | Pump, particularly a high-pressure fuel pump |
| CN101981316B (en) * | 2008-03-26 | 2013-07-24 | 罗伯特·博世有限公司 | Pump, particularly a high-pressure fuel pump |
| CN102762859A (en) * | 2010-02-16 | 2012-10-31 | 罗伯特·博世有限公司 | Cylinder head for a high-pressure fuel pump |
| CN102762859B (en) * | 2010-02-16 | 2015-11-25 | 罗伯特·博世有限公司 | For the cylinder cap of high pressure fuel pump |
| CN103299065A (en) * | 2011-01-14 | 2013-09-11 | 罗伯特·博世有限公司 | High-pressure pump |
| WO2013010458A1 (en) * | 2011-07-14 | 2013-01-24 | Neo Mechanics Limited | Diesel engine fuel injection pump which pistons are sealed with all metal seal rings |
| CN105378279A (en) * | 2013-06-13 | 2016-03-02 | 麦格纳动力系巴德霍姆堡有限责任公司 | Radial piston compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100429395C (en) | 2008-10-29 |
| DE10302043A1 (en) | 2004-05-19 |
| DE50310206D1 (en) | 2008-09-04 |
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