CN102939456B - High-pressure pump - Google Patents
High-pressure pump Download PDFInfo
- Publication number
- CN102939456B CN102939456B CN201180029004.7A CN201180029004A CN102939456B CN 102939456 B CN102939456 B CN 102939456B CN 201180029004 A CN201180029004 A CN 201180029004A CN 102939456 B CN102939456 B CN 102939456B
- Authority
- CN
- China
- Prior art keywords
- roller
- rolling surface
- descending branch
- cam
- pressure service
- 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.)
- Active
Links
- 239000000446 fuel Substances 0.000 claims abstract description 10
- 238000002347 injection Methods 0.000 claims abstract description 7
- 239000007924 injection Substances 0.000 claims abstract description 7
- 238000002485 combustion reaction Methods 0.000 claims abstract description 6
- 238000005096 rolling process Methods 0.000 claims description 44
- 230000002349 favourable effect Effects 0.000 description 13
- 239000012530 fluid Substances 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 4
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003028 elevating effect Effects 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000000034 method Methods 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
- F02M59/02—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
- F02M59/10—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 the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- 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
- F02M59/44—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
- 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
- F04B1/0439—Supporting or guiding means for the pistons
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
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 pump (1), which is used in particular as a radial or in-line piston pump for fuel injection systems of air-compressing, auto-igniting internal combustion engines, comprising a pump assembly (5) and a drive shaft (6), which comprises a cam (7) associated with the pump assembly (15). The pump assembly (15) has a roller shoe (30) and a roller (31) mounted in the roller shoe (30). The roller (31) rolls on a running face (34) of the cam (7). To this end, the cam (7) has eased areas (40, 41) on the running face (34) thereof. The eased areas (40, 41) ensure advantageous guidance of the roller (31) on the running face (34). The eased areas (40, 41) are needed in order to avoid edge loading. The fact that the eased areas are located on the camshaft and not on the roller (31) means that the hydrodynamics between the roller (31) and the roller shoe (30) can be perfected.
Description
Technical field
The present invention relates to high-pressure service pump, especially radial or inline plunger pump.The invention particularly relates to the field of the petrolift of the fuel injection system for pressurized air, self ignition formula internal-combustion engine.
Background technique
By the known a kind of high-pressure service pump of the fuel injection system for internal-combustion engine of DE10 2,005 046 670 A1.This known high-pressure service pump has a pump case, is provided with a pump part wherein, and this pump part comprises one is become elevating movement pump piston by drive shaft.Pump piston is directed to movably and in this hole, defines a pump working chamber in the cylindrical hole of a part for pump case.Pump piston indirectly by a cylinder side face shape push rod support on the driving shaft, wherein, push rod is directed to movably in a hole of a part for pump case on the direction of pump piston longitudinal shaft.The longitudinal axis of push rod is substantially the same with the longitudinal axis of pump piston.In push rod, install a supporting element in its end regions towards live axle, a roller is rotatably supported in this supporting element.This roller can roll on the cam of live axle.The spin axis of roller is parallel to the spin axis of live axle at least approx.Supporting element has recessed portion, wherein a support roll on its side towards live axle.
Have its shortcoming by the known high-pressure service pump of DE 10 2,005 046 670 A1, namely roller is closely directed in push rod, so that obtains the disadvantageous roadability of roller and produce frictional force and wearing and tearing.
In order to improve the roadability of roller, can expect: allow roller to have certain mobility along its spin axis and one and columniform variform roller configuration can be selected in addition.Roller arris can be avoided thus to roll under a load on roller boots or on the cam of live axle.But also obtain a shortcoming thus, namely because columniform variform roller configuration makes the friction between roller and roller boots increase, because make flow dynamic characteristic be deteriorated due to gap larger between roller and roller boots.Make the more difficult smoothness of the rolling of roller thus, this also can cause the damage of driving mechanism in any case.
Summary of the invention
According to the present invention, a kind of high-pressure service pump is proposed, there is at least one pump assembly and a live axle, this live axle has at least one configuration to the cam of this pump assembly, wherein, this pump assembly has a roller rolled on the rolling surface of cam, wherein, this cam has at least one descending branch on its rolling surface, make fixed at one of roller in home position between the end section and rolling surface of roller, form a gap, thus on roller, apply a reposition force when cam opposed roller starts obliquely by descending branch.
Described high-pressure service pump is in particular for the radial direction of the fuel injection system of pressurized air, self ignition formula internal-combustion engine or inline plunger pump.
High-pressure service pump according to the present invention has its advantage, and namely the rolling characteristic of roller on the rolling surface of cam improves.Especially can improve the fluid dynamic between roller and roller boots and realize the favourable rolling characteristic of roller on the rolling surface of cam simultaneously.
The favourable further configuration of the above high-pressure service pump provided can be obtained by advantageous measures.
Advantageously, descending branch and the roller of rolling surface are so constituted, make fixed at one of roller in home position between the end section and rolling surface of roller, form a gap.In the case also advantageously: rolling surface to be constructed to convex arch in the region of descending branch.In addition advantageously, the descending branch of rolling surface is so constructed, so that between the end section and rolling surface of roller, also forms a gap in roller departs from the position in determining.The like of opposed roller boots or support roll relatively wherein can ensure a constant small―gap suture thus.In roller can being made to be determined on its track by the descending branch on camshaft thus.When between roller and the cam of live axle during angle of arrival error roller curve through descending branch to lead around cam by the roller that produced the extruding force that formed by pressure and cause.Reaction is played thus by the inclination startup of descending branch to cam opposed roller.Especially can prevent thus or at least avoid the side of roller to slide.
Favourable in the case is also: roller depart from fixed in position in the gap that formed between the end section and rolling surface of roller be constructed at least approx with the gap formed objects in the home position in fixed, depart from fixed in position central roll moved towards the direction of the descending branch of rolling surface by the home position in fixed.On roller, a reposition force is applied all the time thus when there is a given angular error between roller boots and cam.Favourable in the case is also: the descending branch of rolling surface is constructed to until an end face of cam.
In addition advantageously, rolling surface has the scrolling bands of a centre, and the scrolling bands of this centre is constructed at least to be similar to cylinder side face shape and descending branch adjoins with middle scrolling bands.The roadability that between roller and cam one is favourable is achieved thus in the home position of center.In addition advantageously, be provided with roller boots, wherein a support roll, and roller boots can realize roller certain mobility vertical with the rotating direction of roller on rolling surface.Here roller is preferably constructed to columniform roller substantially.Even if also can ensure the small―gap suture that between roller boots and roller one is constant thus when roller and rotating direction vertically move.Also a fluid dynamic improved between roller and roller boots is obtained thus.Therefore obtain the roadability that of roller is favourable always.
Favourable is also, cam has other descending branch on its rolling surface, and descending branch and other descending branch opposed roller fixed in home position form symmetrically.Here be favourablely also, descending branch and other descending branch are so constituted, make roller import to fixed in home position in.Therefore by the descending branch on cam, roller is fixed on its track.Therefore the inclination of cam opposed roller is started and produce reaction.Prevent on both sides thus or at least avoided that the side of sliding roller is slided.
Accompanying drawing explanation
To carry out the preferred embodiment of the present invention will be described in detail by accompanying drawing in the following description, parts corresponding in accompanying drawing are provided with consistent label.Accompanying drawing represents:
Fig. 1: the high-pressure service pump according to an embodiment of the invention represented with the axial sectional view of summary, and
With the section figure of the high-pressure service pump of this embodiment of the present invention of II instruction in Fig. 2: Fig. 1.
Embodiment
Fig. 1 represents high-pressure service pump 1 according to an embodiment of the invention with the axial sectional view of summary.This high-pressure service pump 1 especially can be constructed to radial pump or inline plunger pump.This high-pressure service pump 1 is especially suitable as the petrolift of the fuel injection system of compressed-air actuated, self ignition formula internal-combustion engine.An advantageous applications of this high-pressure service pump 1 distributes the fuel injection system of bar, a so-called common rail, and this common rail storage is in the diesel fuel under high pressure.But high-pressure service pump 1 according to the present invention is also applicable to other application.
High-pressure service pump 1 has a manifold pump case 2.Here this pump case 2 comprises a housing parts 3 and a flange 4 be connected with housing parts 3.In addition be provided with a cylinder head 5, it is connected with housing parts 3.
A live axle 6 is provided with in pump case 2.Live axle 6 comprises a cam 7.Cam 7 also can be constructed to multiple cam.This external cam 7 also can be constructed to the eccentric portion of live axle 6.A bearing part 8 is configured with in housing parts 3.This external flange 4 is also provided with an other bearing part 9.Live axle 6 is bearing in bearing part 8, on 9.
In the work of high-pressure service pump 1, live axle 6 rotates around its spin axis 10.Bearing part 8,9 relative rotation axi lines 10 are spaced from each other and are arranged on the not homonymy of cam 7.
High-pressure service pump 1 has a pump assembly 15.High-pressure service pump 1 also can have multiple pump assembly.Pump assembly 15 drives by the cam 7 of live axle 6.As long as high-pressure service pump 1 has other pump assembly, these pump assemblies can be driven by cam 7 together with pump assembly 15.Can also be on live axle 6, be provided with the cam that at least one is other, this cam corresponding to cam 7 for driving at least one pump assembly.A radial direction or inline plunger pump can be realized thus depending on configuration.
The housing parts 3 of pump case 2 has a hole 16.Cylinder head 5 is configured with a projection 17, and this projection extend in the hole 16 of housing parts 3.Pump assembly 15 is arranged on projection 17 with the region in hole 16.Projection 17 has a cylinder holes 18, pump piston 19 and leads in this cylinder holes for this reason.Here pump piston 19 defines a pump working chamber 20 here in cylinder holes 18.Fuel arrives in pump working chamber 20 by entering valve 21.In addition be provided with an expulsion valve 22, fuel can be transported in a connecting tube 23 by pump working chamber 20 by this expulsion valve.This connecting tube 23 such as leads to a common rail.
Cylinder holes 18 has an axis 24, and this axis points to spin axis 10 and vertically directed with spin axis 10 at least approx.Pump piston 19 can move along axis 24, as passed through indicated by double-head arrow 25.
In addition pump assembly 15 has the pusher body 26 of a hollow cylinder, and this pusher body leads in hole 16.One is installed in and takes the flange 28 that moving part 27 fastens pump piston 19 later in pusher body 26.Take moving part 27 to be loaded by the direction of a push rod spring 29 towards cam 7 this this.When pusher body 26 moves, pump piston 19 is driven thus.
In this external pusher body 26, roller boots 30 are installed.The flange 28 of pump piston 19 abuts against on roller boots 30.In roller boots 30, support a roller 31, this roller is constructed to sliding roller 31.Roller 31 is constructed to cylindrical at least substantially in the case.Obtain the favourable guiding of roller 31 in roller boots 30 thus.Especially between roller 31 and roller boots 30, favourable fluid dynamic is obtained.Namely one is had between roller 31 and roller boots 30 with constant closely spaced large regions.Therefore ensure that the favourable supporting of roller 31 in roller boots 30.
Cam 7 has one towards the end face 32 of position of bearings 9 and another end face 33 towards position of bearings 8.End face 32,33 carry mutually.This external cam 7 has a rolling surface 34.Roller 31 such as rolls along rolling surface 34 on traffic direction 35 at work.Here rolling surface 34 has scrolling bands 36 in the middle of, and in this middle scrolling bands, rolling surface 34 is constructed to cylinder side face shape at least approx.Obtain thus roller 31 on rolling surface 34 fixed in home position, this home position represents in FIG.Roller 31 rotates around its axis 37 in the case.
When live axle 6 rotates around its spin axis 10, roller 31 rolls along rolling surface 34, so that carries out the operation of pump piston 19 of pump assembly 15 according to the cam stroke of cam 7.Fuel is alternately inhaled into pump working chamber 20 and is then under high pressure carried by connecting tube 23 thus.
The configuration of high-pressure service pump 1 is below also described with reference to Fig. 2 in further detail.
Fig. 2 to represent in Fig. 1 with the section figure of high-pressure service pump 1 of this embodiment of II instruction, indicates cam 7 with wherein indicating roller boots 30, roller 31 and section.Cam 7 has a descending branch 40 and an other descending branch 41 on its rolling surface 34.Here descending branch 40 extends to end face 32.This other descending branch 41 extends to other end face 33.In addition descending branch 40,41 adjoin with the both sides of the middle scrolling bands 36 of rolling surface 34.Therefore, middle scrolling bands 36 and two descending brancies 40,41 extend on the whole rolling surface 34 of cam 7 together in this embodiment.
Descending branch 40,41 descending brancies 40,41 being constructed to convex arch.Relatively form columniform roller 31 at least approx, by descending branch 40,41 define little gap 42,43 between roller 31 and rolling surface 34.Here gap 42,43 end section 44 and another end section 45 relating to roller 31.The intermediate section 46 of roller 31 abuts against in middle scrolling bands 36.
Therefore the roller 31 shown in Fig. 1 and 2 fixed in home position in can ensure the rolling that roller 31 is favourable in the middle scrolling bands 36 of rolling surface 34.
The angular error of with an angle 47 can be caused in the work of high-pressure service pump 1.When angular error occurs, at roller boots 30 together with just obtaining a not inappreciable angle 47 between roller 31 and cam 7 or axis 24.For high-pressure service pump 1 reliably working also can need such gap.
By having descending branch 40, cam 7 configuration of 41 can ensure that this system reset is in home position.When angular error, effect has one towards the reposition force of home position in the case.One not inappreciable angle 47 time roller 31 curve through descending branch 40 by the roller 31 that produced the extruding force that formed by pressure and cause around cam 7,41 lead.Therefore on roller 31, also also on roller boots 30, a reposition force is applied thus by descending branch 40,41 when cam opposed roller 31 starts obliquely.Thus the inclination of cam opposed roller 31 is started and play reaction.Slide depending on the side that this pair roller 31 of configuration of high-pressure service pump 1 is possible and also play reaction.
Because ensure that the favourable guiding of roller 31 in roller boots 30 in this configuration, so the guiding favourable on rolling surface 34 with roller 31 combines just obtain roller 31 optimum operation characteristic at work.
From the configuration that can be imagined, namely wherein the configuration that is located on roller 31 of descending branch is different, avoids the gap between roller boots 30 and roller 31.Therefore in the configuration of this embodiment, maintain the fluid dynamic between roller boots 30 and roller 30.Avoid sliding roller 31 from the beginning not smooth, so that also prevent the damage of driving mechanism or similar situation.The edge support of the cam 7 under it also avoid opposed roller boots 30 in the case or being relatively in load.
In order to exempt edge support, descending branch 40,41 is required.Be positioned on camshaft by making descending branch instead of be positioned on roller 31, the fluid dynamic between roller 31 and roller boots 30 can be very perfect.
The present invention is not confined in the above embodiments.
Claims (10)
1. high-pressure service pump (1), there is at least one pump assembly (15) and a live axle (6), this live axle has at least one configuration to the cam (7) of this pump assembly (15), wherein, this pump assembly (15) has the upper roller (31) rolled of a rolling surface in cam (7) (34), it is characterized in that: this cam (7) has at least one descending branch (40) on its rolling surface (34), make fixed at one of roller (31) in home position between the end section (44) and rolling surface (34) of roller (31), form a gap (42), thus pass through descending branch (40) when cam opposed roller (31) starts obliquely at the upper applying reposition force of roller (31).
2. high-pressure service pump according to claim 1, is characterized in that: this rolling surface (34) is constructed to convex arch in the region of descending branch (40).
3. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: the descending branch (40) of this rolling surface (34) is so constructed, make between the end section (44) and rolling surface (34) of roller (31), also to form a gap (42) in roller (31) departs from the position in determining.
4. high-pressure service pump according to claim 3, it is characterized in that: roller (31) depart from fixed in position in the gap (42) that formed between the end section (44) and rolling surface (34) of roller (31) be constructed at least approx with the gap formed objects in the home position in fixed, moved towards the direction of the descending branch (40) of rolling surface (34) by the home position in fixed departing from the position central roll (31) calmly.
5. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: the descending branch (40) of this rolling surface (34) is constructed to until the end face (32) of cam (7).
6. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: this rolling surface (34) has the scrolling bands (36) of a centre, this scrolling bands is constructed at least to be similar to cylinder side face shape and descending branch (40) adjoins with middle scrolling bands (36).
7. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: be provided with a roller boots (30), roller (31) is bearing in these roller boots, and these roller boots (30) can realize roller (31) in the upper mobility vertical with the rotating direction (35) of roller (31) of rolling surface (34).
8., according to the high-pressure service pump of claim 1 or 2, it is characterized in that: cam (7) there is an other descending branch (41) on its rolling surface (34) and descending branch (40) and other descending branch (41) about roller (31) fixed in home position form symmetrically.
9. high-pressure service pump according to claim 8, is characterized in that: descending branch (40) and other descending branch (41) are so constituted, and roller (31) is directed in the home position in determining.
10. according to the high-pressure service pump of claim 1 or 2, it is characterized in that: described high-pressure service pump (1) is radial direction for the fuel injection system of pressurized air, self ignition formula internal-combustion engine or inline plunger pump.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010027792.4 | 2010-04-15 | ||
| DE102010027792A DE102010027792A1 (en) | 2010-04-15 | 2010-04-15 | high pressure pump |
| PCT/EP2011/053108 WO2011128151A1 (en) | 2010-04-15 | 2011-03-02 | High-pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102939456A CN102939456A (en) | 2013-02-20 |
| CN102939456B true CN102939456B (en) | 2015-04-08 |
Family
ID=44041758
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180029004.7A Active CN102939456B (en) | 2010-04-15 | 2011-03-02 | High-pressure pump |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2558707B1 (en) |
| JP (1) | JP5395308B2 (en) |
| CN (1) | CN102939456B (en) |
| DE (1) | DE102010027792A1 (en) |
| WO (1) | WO2011128151A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013212047A1 (en) * | 2013-06-25 | 2015-01-08 | Robert Bosch Gmbh | Pump device, in particular high-pressure fuel pump device for a fuel injection device |
| US9835123B2 (en) * | 2015-01-13 | 2017-12-05 | Roller Bearing Company Of America, Inc. | Roller for a fuel pump actuator |
| DE112021003235T5 (en) * | 2020-08-14 | 2023-04-27 | Cummins Inc. | SLIDING CAM LEVER |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB536181A (en) * | 1939-02-08 | 1941-05-06 | Sulzer Ag | Improvements in or relating to cam mechanisms |
| CN1460154A (en) * | 2001-04-06 | 2003-12-03 | 罗伯特·博施有限公司 | Single-plunger injection pump for pressure accumulating tube-fuel injection system |
| CN1840900A (en) * | 2005-03-28 | 2006-10-04 | 颜志江 | Pump body of high-pressure cleaning machine |
| CN1894504A (en) * | 2003-12-20 | 2007-01-10 | Itw有限公司 | Pump |
| DE102005046670A1 (en) * | 2005-09-29 | 2007-04-05 | Robert Bosch Gmbh | High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet |
| DE102008040081A1 (en) * | 2008-07-02 | 2010-01-07 | Robert Bosch Gmbh | high pressure pump |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05332222A (en) * | 1992-05-27 | 1993-12-14 | Nippondenso Co Ltd | Fuel injection pump |
| JPH0821329A (en) * | 1994-07-08 | 1996-01-23 | Toyota Motor Corp | Fuel injection pump |
| JP3867758B2 (en) * | 1999-06-22 | 2007-01-10 | 株式会社デンソー | High pressure supply pump |
| US6722864B2 (en) * | 2001-12-12 | 2004-04-20 | Denso Corporation | Fuel injection pump |
| DE102006045933A1 (en) * | 2006-09-28 | 2008-04-03 | Robert Bosch Gmbh | Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly |
| DE102006051332A1 (en) * | 2006-10-31 | 2008-05-08 | Robert Bosch Gmbh | Feed pump, in particular for the promotion of diesel fuel with improved storage of the drive shaft |
| JP2009281289A (en) * | 2008-05-22 | 2009-12-03 | Toyota Motor Corp | Fuel pump for internal combustion engine |
-
2010
- 2010-04-15 DE DE102010027792A patent/DE102010027792A1/en not_active Withdrawn
-
2011
- 2011-03-02 CN CN201180029004.7A patent/CN102939456B/en active Active
- 2011-03-02 WO PCT/EP2011/053108 patent/WO2011128151A1/en active Application Filing
- 2011-03-02 EP EP11709037.3A patent/EP2558707B1/en not_active Not-in-force
- 2011-03-02 JP JP2013504183A patent/JP5395308B2/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB536181A (en) * | 1939-02-08 | 1941-05-06 | Sulzer Ag | Improvements in or relating to cam mechanisms |
| CN1460154A (en) * | 2001-04-06 | 2003-12-03 | 罗伯特·博施有限公司 | Single-plunger injection pump for pressure accumulating tube-fuel injection system |
| CN1894504A (en) * | 2003-12-20 | 2007-01-10 | Itw有限公司 | Pump |
| CN1840900A (en) * | 2005-03-28 | 2006-10-04 | 颜志江 | Pump body of high-pressure cleaning machine |
| DE102005046670A1 (en) * | 2005-09-29 | 2007-04-05 | Robert Bosch Gmbh | High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet |
| DE102008040081A1 (en) * | 2008-07-02 | 2010-01-07 | Robert Bosch Gmbh | high pressure pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5395308B2 (en) | 2014-01-22 |
| WO2011128151A1 (en) | 2011-10-20 |
| JP2013524095A (en) | 2013-06-17 |
| DE102010027792A1 (en) | 2011-10-20 |
| EP2558707A1 (en) | 2013-02-20 |
| EP2558707B1 (en) | 2018-05-16 |
| CN102939456A (en) | 2013-02-20 |
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