CN103154512A - High-pressure pump for a fuel injection device - Google Patents
High-pressure pump for a fuel injection device Download PDFInfo
- Publication number
- CN103154512A CN103154512A CN2011800493554A CN201180049355A CN103154512A CN 103154512 A CN103154512 A CN 103154512A CN 2011800493554 A CN2011800493554 A CN 2011800493554A CN 201180049355 A CN201180049355 A CN 201180049355A CN 103154512 A CN103154512 A CN 103154512A
- Authority
- CN
- China
- Prior art keywords
- pump
- push rod
- cup
- pressure service
- shaped push
- 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 19
- 238000002347 injection Methods 0.000 title claims abstract description 11
- 239000007924 injection Substances 0.000 title claims abstract description 11
- 238000005096 rolling process Methods 0.000 claims abstract description 37
- 238000002485 combustion reaction Methods 0.000 claims abstract description 7
- 238000005461 lubrication Methods 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 6
- 230000015572 biosynthetic process Effects 0.000 claims description 3
- 230000002349 favourable effect Effects 0.000 description 4
- 239000008041 oiling agent Substances 0.000 description 4
- 238000003860 storage Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 239000011248 coating agent Substances 0.000 description 3
- 238000000576 coating method Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000001965 increasing effect Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000008685 targeting Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000000243 solution Substances 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
- F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
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- 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
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
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- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention relates to a high-pressure pump (1) for a fuel injection device, which can be used, in particular, for a common rail injection device of an internal combustion engine. The high-pressure pump (1) comprises a pump or drive shaft which is connected to an eccentric (6) in a rotationally fixed manner and at least one pump part (8). The pump part (8) comprising a cup-shaped tappet (13), a part piston (12) and a tappet spring (14) is inserted in a housing bore (16) of the engine block (3). A cup-shaped plunger (13) acted upon by a plunger spring (14) is connected to a component piston (12) guided so as to be able to move back and forth in a cylinder bore (19) of a cylinder section (20), said component piston delimiting a pump working chamber (21) connected to a suction valve (22) and a high-pressure valve (23). The drive connection between the cup tappet (13) and the eccentric (6) comprises a rolling ring (9) which is mounted rotatably on the eccentric (6) and on which a sliding plate (18) of the cup tappet (13) is supported in a force-fitting manner.
Description
Technical field
The present invention relates to the high-pressure service pump of fuel injection system, it especially can be used in the common-rail injection system of internal-combustion engine.This high-pressure service pump comprises a pump shaft or live axle, and this axle is connected without being connected with relatively rotating and forming function with the pump parts with an eccentric wheel.This comprises a cup-shaped push rod, and the pump parts of a parts piston and a push rod spring are arranged in the housing bore of engine block.With eccentric wheel by cup-shaped push rod form drive be connected and in a cylinder hole up and down the parts piston of leading define a pump working chamber that is connected with suction valve and high pressure valve.
Background technique
This high-pressure service pump is used in vehicle structure, in order to provide the volume flow of necessity and required fluid pressure to common rail fuel injection apparatus.High-pressure service pump suffers strong load, the load of machinery especially, to material and structure is had high requirement.The cup-shaped push rod that is connected with eccentric wheel or cam track formation function plays the reciprocating effect of oscillating type that is transformed into a parts piston or pump piston by rotatablely moving of live axle.The to-and-fro motion of parts piston can be divided into an aspiration stroke and a compression stroke.Fuel is inhaled into pump working chamber by a suction valve in aspiration stroke.Compressed the reaching of fuel is transported in a storage (rail) by a high pressure valve of opening in the compression stroke of following.Due between parts piston and cylinder hole and the friction that occurs on cup-shaped push rod targeting part used a push rod spring that applies reposition force, this push rod spring produces contacting of force closure between cup-shaped push rod and eccentric wheel.
DE10157076A1 discloses a push-rod piston that is used for high-pressure service pump, and it has one and comprises one axially and push rod and a piston that is permanently connected with push rod of the roller of radially-directed.In order to guide this push rod of roller on push rod to be provided with roller boots, roller can be placed in these roller boots rotationally with axial clearance.
By DE19907311A1 known a high-pressure service pump, it has one with eccentric live axle, this eccentric wheel and pump parts interact.Be provided with a supporting element or roller boots between parts piston and eccentric wheel, insert therein that can roll, as to support a rotationally roller on eccentric wheel.Exist a crisis in this structure, namely form relatively large wearing and tearing being in the friction that strengthens between the member of direct function in connecting.The frictional influence of this enhancing rotatablely moves to roller, can occur thus sliding between roller and eccentric wheel and wearing and tearing are increased.
Summary of the invention
Task of the present invention is, provides a kind of simplification, firm and is connected in the optimised driving of eccentric wheel and the friction between cup-shaped push rod, and it can bear high mechanical load and can make simply.
This task will solve in this wise, and namely the driving attachment portion between cup-shaped push rod and eccentric wheel comprises a rolling ring that can be bearing in rotationally on eccentric wheel, is supported on this rolling ring to cup-shaped push rod force closure.Therefore cup-shaped push rod is connected with eccentric wheel formation driving by the rolling ring of energy rotating support.
Surround rolling ring that eccentric wheel and relative eccentric wheel carry out relative movement according to the present invention and advantageously play the effect that driving is connected or power is transmitted of a decoupling between cup-shaped push rod and eccentric wheel.This Structure Decreasing the reception of transverse force of cup-shaped push rod and lateral force or the favourable of transverse force therefore can realize that cup-shaped push rod leads on housing bore the time reduce.A simplification and the firm driving that has provided between eccentric wheel and cup-shaped push rod according to the solution of the present invention is connected, and it can advantageously bear strong load, mechanical load especially, and this is to its operating life generation positive impact.The driving connection of in addition should friction optimizing is irrelevant with frictional ratio, and this frictional ratio in existing scheme between cup-shaped push rod and eccentric wheel, for example be to need consideration between a roller and eccentric wheel.Connect insensitive to different fuel viscosity according to firm driving of the present invention in addition.
Another advantage of the present invention is: connect both can be diverted to according to driving according to the present invention and also can be diverted on high-pressure service pump with 1 heavy camming or eccentric wheel system on the high-pressure service pump with 2 heavy cammings or eccentric wheel system.Compare by the known schemes that a roller that is combined in the roller boots is supported on eccentric wheel with cup-shaped push rod wherein, connect by driving according to the present invention and advantageously reduced friction.Can realize advantageously that by the present invention driving durable between eccentric wheel and cup-shaped push rod is connected, it also can be used in the high power system with corresponding high pumping pressure and revolution speed.But the scheme according to simple conversion of the present invention has ensured and little reliable, the accurate work that interrelates of wearing and tearing simultaneously, reaches thus the raising of efficient always.
A preferred further configuration of the present invention is: cup-shaped push rod has configured a slide plate that is called as the power reception unit at driving side.The slide plate that this slide plate especially is pressed in cup-shaped push rod and this position is fixing is supported on a surface of contact and surrounds on the affiliated surface of contact of eccentric rolling ring, and wherein surface of contact jointly consists of a contact area.Slide plate is advantageously made by a kind of adapting to the material of constant load and lubrication state.In order to realize that high wear strength for example proposes: slide plate is made by hard metal or stupalith.The cup-shaped push rod that has made up in addition slide plate is aobvious outstanding by the structure of simplifying and member is optimized.Cup-shaped push rod advantageously neither needs directed mounting point also not need without relatively rotating take slide plate as prerequisite, and assembling is simplified.Comparing with the known schemes of the cup-shaped push rod of the roller with roller boots and combination according to simplification of the present invention and cup-shaped push rod scheme cost optimization in addition provides on a cost.
In order to reduce friction, rolling ring can be bearing on eccentric wheel rotationally by a rolling bearing or sliding bearing.Rolling bearing by the market popularity or sliding bearing can realize rolling ring firm on eccentric shaft, effectively reach supporting favourable on cost.Roller bearing preferably is suitable as rolling bearing, because this bearing does not receive axial force.Because required radial structure space I preferably supports rolling ring with needle bearing.
The feature of another special form of implementation of the present invention is: in the surface of contact that slide plate and rolling ring face toward each other, at least one is configured to slight spherical or convex.This measure has advantageously compensated during fabrication the slight angular error that can occur due to the PT positional tolerance that allows and/or shape tolerance.This convex configuration is used in addition: make slide plate and contact area between rolling ring narrow down to line and contact, can advantageously reduce thus friction.
Propose in order to reach the increasing according to the present invention of operating life that drives connection: at least one surface of contact of rolling ring or slide plate is by the material coating with high wear strength.In conversion or additionally the present invention also comprises the coating of the material that having of at least one surface of contact reduces to rub to this.
The form of implementation favourable according to another, the high-pressure service pump that is configured to inserted pump inserts in the housing bore of engine block with a plug-in type pump housing as an element of construction.Have a cylinder hole at a post section of the plug-in type pump housing, it be determined for the parts piston and consist of simultaneously pump working chamber.The present invention has advantageously provided the possibility that obtains a high-pressure service pump, wherein is connected combinedly with driving the principle of inserted pump, and this driving connection has one and is bearing in rolling ring on eccentric wheel and the cup-shaped push rod of a slide plate with combination.
Structural Tectonics of the present invention also comprises the different schemes for cup-shaped push rod guiding.The external orientation of cup-shaped push rod preferably, wherein cup-shaped push rod pusher body is directed in the housing bore of engine block by a circumferential surface.The external orientation of this cup-shaped push rod can stop the distortion of parts piston targeting part in the post section.This is proposed in conversion: cup-shaped push rod is directed on the post section of inboard at the plug-in type pump housing.
Also be provided with the layout of the push rod spring of a structure space optimization for the high-pressure service pump that is made to inserted pump in another configuration of the present invention.Push rod spring is supported on a spring seat that is combined in cup-shaped push rod for this reason, wherein push rod spring in cup-shaped push rod than big-length on be directed to.Be inserted into a surrounded by edges of the formula pump housing for the opposite side end of the push rod spring that leads.
For the guiding of cup-shaped push rod in housing bore reached targetedly effectively lubricate have in the circumferential surface of pusher body at least one be preferably around lubrication groove, this lubrication groove is connected by affiliated through hole and a push rod interior space.This measure will cause: oiling agent, the fuel of especially carrying by high-pressure service pump enter into the circular groove between the circumferential surface of the housing bore that appears at engine block and cup-shaped push rod.Can realize thus the lubricated of the cup-shaped push rod optimized, reduce to rub.In addition for lubricated and coolant/lubricant will arrive that eccentric wheel is connected with driving between cup-shaped push rod, by in rolling ring and slide plate definite contact area.Comprise at least one through flow hole as the slide plate to a cup-shaped push rod of additional measure of this contact area supply of lubricant.
Other favourable configuration of the present invention can by obtaining in the description of the drawings, will describe the embodiment shown in accompanying drawing in detail in this explanation.
Description of drawings
Fig. 1: have the sectional view that is located at a high-pressure service pump of the driving attachment portion between eccentric wheel and cup-shaped push rod according to of the present invention;
Fig. 2: according to the detailed drawing of the cup-shaped push rod of Fig. 1.
Embodiment
High-pressure service pump 1 that is used for the fuel injection system of internal-combustion engine of expression in Fig. 1, it preferably is determined the common-rail injection system for internal-combustion engine.Fuel is transported to a unshowned storage (rail) under pressure by high-pressure service pump 1, fuel is ejected in the affiliated firing chamber of internal-combustion engine by fuel injector targetedly by this storage.High-pressure service pump 1 consists of a radial piston pump, and it is inserted in an engine block 3 or its housing as the inserted pump with plug-in type pump housing 2.Also connecting a low voltage unit 4 that is called as cylinder head on the plug-in type pump housing 2.That can rotate in engine block 3 a, live axle that have axis 5 is connected with an eccentric wheel 6, and the relative axis 5 of this eccentric central axis 7 has a throw of eccentric S.This live axle can be an axle of internal-combustion engine, for example its camshaft or differential shaft.
Eccentric wheel 6 is surrounded by a rolling ring 9, this rolling ring by a rolling bearing 10, especially needle bearing with cylindrical rolling element 11 rotationally on supporting axle eccentric wheel 6 and this rolling ring form drivings with the cup-shaped push rod 13 of pump parts 8 and be connected.Pump parts 8 comprise cup-shaped push rod 13 and a push rod spring 14, are keeping a parts piston 12 or pump piston in cup-shaped push rod.Cup-shaped push rod 13 by a non-nothing of pusher body 15 relatively rotate in the housing bore 16 that the axis 5 of a relative drive shaft of engine block 3 radially extends leading.Cup-shaped push rod 13 embeds in locking manner on the receiving part 17 of cup-shaped push rod 13 and slide plate 18 that the position is fixed by a shape and is supported on the rolling ring 9 of eccentric wheel 6.In working order, the eccentric wheel 6 of rotation and rolling ring 9 cause an oscillatory movement of cup-shaped push rod 13 and connected parts piston 12 explicitly, and this parts piston is leading in the cylinder hole 19 of a post section 20 of the plug-in type pump housing 2.
Parts piston 8 defines a pump working chamber 21, and this pump working chamber has been configured a suction valve 22 and a high pressure valve 23.Suction valve 22 is opened when the aspiration stroke (moving downward) of parts piston 8, thus can be by 4 pairs of pump working chamber's 21 transfer the fuels of low voltage unit.The high pressure valve 23 of carrying out non-return valve function when fuel by one is transported to high-pressure storage (rail) before in a fuel line that continues to transmit, the extrusion stroke (moving upward) of parts piston 8 causes the compression of closing of suction valve 22 and fuel.Throw of eccentric S between the axis 5 of live axle or pump shaft and the central axis 7 of eccentric wheel 6 has determined the maximum stroke of parts piston 12 simultaneously.
Be supported between a spring seat 24 of inserted pump housing 2 and cup-shaped push rod 13 at the push rod spring 14 that causes reposition force on cup-shaped push rod 13 and cause the support of cup-shaped push rod 13 force closure on rolling ring 9.Here push rod spring 14 surrounds and takes out the post section 20 that connects the formula pump housing 2, and wherein push rod spring 14 spring end edge 25 of being inserted into the formula pump housing 2 surrounds and another enters spring end in cup-shaped push rod 13, that be supported on spring seat 24 and is surrounded by pusher body 15 in the outside.
For the angular error that compensates little angular error, for example caused by the machining tolerance of each member, the rolling ring 9 that surrounds eccentric wheel 6 is supported on the opposite of a respective configuration by a spherical protruding surface of contact 27, be on the surface of contact 28 of slide plate 18 of cup-shaped push rod 13.In order to realize that best frictional ratio additionally provides a coating that reduces to rub at least one surface of contact 27,28 to this.
Fig. 2 represents cup-shaped push rod 13 with the view that amplifies as details and shows other details.Being placed on spring seat in cup-shaped push rod 13, that determine to support push rod spring 14 plays simultaneously parts piston 12 is remained on effect on cup-shaped push rod 13.Parts piston 12 is inserted in a center hole 26 of spring seat 24 and the end side edges 35 by an overlap joint hole 26 keeps for this reason.Because be directed in the member that pusher body 15 is directed in engine block 3 and parts piston 12 is directed in post section 20 and separating thus, therefore parts piston 12 preferably imports in the hole 26 of spring seat 24 with the Spielpassung of compensation small angle error.As the measure that improves the friction of pusher body 15 in the housing bore 16 of engine block 3 have in the circumferential surface 29 of pusher body 15 one be preferably around lubrication groove 30 and the through hole 31 that arranges with the ground that distributes on circumference.Therefore oiling agent or the fuel carried by high-pressure service pump 1 can enter into annular space 32(Fig. 1 who is limited diametrically by pusher body 15 and housing bore 16 targetedly).Oiling agent also arrives contact area 33(Fig. 1 between rolling ring 9 and slide plate 18 towards the direction of eccentric wheel 6 therefrom) and impact this contact area with lubricated reach cooling.Additionally have a plurality of through flow holes 34 on slide plate 18, they allow oiling agent to flow through, in order to lubricate targetedly the member that reaches cooling contact area 33.
Claims (11)
1. the high-pressure service pump of fuel injection system (1), common-rail injection system in particular for internal-combustion engine, this high-pressure service pump has a pump shaft, this pump shaft is connected with an eccentric wheel (6) nothing with relatively rotating, this high-pressure service pump also has the pump parts (8) at least one housing bore that is inserted in engine block (3) (16), these pump parts comprise that one forms by cup-shaped push rod (13) and described eccentric wheel (6) that driving is connected, in the cylinder hole (19) of a post section (20) but in to-and-fro motion parts piston (12) and the push rod spring (14) that described cup-shaped push rod (13) is loaded of being directed to, wherein, described parts piston (12) limits a pump working chamber (21) that is connected with suction valve (22) and high pressure valve (23), it is characterized in that: the driving attachment portion between described cup-shaped push rod (13) and described eccentric wheel (6) comprises a rolling ring (9) that can be bearing in rotationally on described eccentric wheel (6), be supported on this rolling ring to described cup-shaped push rod (13) force closure.
2. according to claim 1 high-pressure service pump, it is characterized in that: described cup-shaped push rod (13) comprises a slide plate (18) at driving side, and this slide plate consists of contact area (33) jointly as the surface of contact (27) of the described rolling ring (9) of surface of contact (28) and the described eccentric wheel of encirclement (6).
3. according to claim 1 high-pressure service pump, it is characterized in that: described rolling ring (9) can be bearing on described eccentric wheel (6) rotationally by rolling bearing (10) or sliding bearing.
4. according to claim 3 high-pressure service pump is characterized in that: be provided for supporting the roller bearing of described rolling ring (9) or needle bearing as rolling bearing (10).
5. according to claim 1 and 2 high-pressure service pump, it is characterized in that: described rolling ring (9) and/or slide plate (18) have one and consist of spherical or surface of contact convex (27,28).
6. according to claim 1 and 2 high-pressure service pump, it is characterized in that: the described surface of contact (27) of described rolling ring (9) and/or the described surface of contact (28) of described slide plate (18) reduce frictionally coated.
7. according to claim 1 high-pressure service pump, it is characterized in that: the described high-pressure service pump (1) that is configured to inserted pump inserts with the plug-in type pump housing (2) in the described housing bore (16) of described engine block (3), and the described cylinder hole (19) guiding and formation definite pump working chamber (8) that is used for described parts piston (12) is bored in a post section (20) of the described plug-in type pump housing (2).
8. according to claim 1 high-pressure service pump is characterized in that: described cup-shaped push rod (13) is directed to or is directed on the plug-in type pump plunger shaft (20) of inboard at the described plug-in type pump housing (2) in by the described housing bore (16) of a pusher body (15) at described engine block (3) in the outside.
9. according to claim 1 high-pressure service pump, it is characterized in that: described push rod spring (14) is supported on spring seat (24) with spring end, and this spring seat is combined in described cup-shaped push rod (13).
10. according to claim 1 high-pressure service pump, it is characterized in that: for the lubriation material of the guiding of described cup-shaped push rod (13) is supplied with, have at least one lubrication groove (30) in described pusher body (15), this lubrication groove is connected with an inner space of described cup-shaped push rod (13) by affiliated through hole (31).
11. high-pressure service pump according to claim 1 and 2 is characterized in that: supply with for the lubriation material of the contact area (33) between described slide plate (18) and described rolling ring (9), have at least one through flow hole (34) in described slide plate (18).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201010042484 DE102010042484A1 (en) | 2010-10-15 | 2010-10-15 | High pressure pump for a fuel injection device |
| DE102010042484.6 | 2010-10-15 | ||
| PCT/EP2011/065472 WO2012048961A1 (en) | 2010-10-15 | 2011-09-07 | High-pressure pump for a fuel injection device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103154512A true CN103154512A (en) | 2013-06-12 |
| CN103154512B CN103154512B (en) | 2017-03-01 |
Family
ID=44583058
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180049355.4A Expired - Fee Related CN103154512B (en) | 2010-10-15 | 2011-09-07 | High-pressure pump for a fuel injection device |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2627903B1 (en) |
| CN (1) | CN103154512B (en) |
| DE (1) | DE102010042484A1 (en) |
| WO (1) | WO2012048961A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110092A (en) * | 2014-12-24 | 2017-08-29 | 罗伯特·博世有限公司 | Pump unit for fuel, preferably diesel oil to be fed to internal combustion engine |
| CN107939628A (en) * | 2017-12-26 | 2018-04-20 | 浙江三浪润滑科技有限公司 | A kind of bull radial plunger pump and its application method |
| CN108350845A (en) * | 2015-11-12 | 2018-07-31 | 罗伯特·博世有限公司 | The high-pressure pump of pump, especially fuel injection system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015111025B4 (en) | 2015-07-08 | 2024-07-25 | Volkswagen Ag | Self-lubricated high pressure pump |
| DE102018120777A1 (en) * | 2018-08-24 | 2020-02-27 | Volkswagen Aktiengesellschaft | High-pressure pump comprising pressure lubrication |
| WO2022066505A1 (en) | 2020-09-24 | 2022-03-31 | Cummins Inc. | Pump housing with relief cut for lobe clearance |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4315826A1 (en) * | 1993-05-12 | 1994-11-17 | Teves Gmbh Alfred | Unit consisting of an electric motor and an element which is to be driven |
| JPH09303252A (en) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | Hydraulic pump device |
| CN1186157A (en) * | 1996-12-23 | 1998-07-01 | 艾拉西斯·西斯特玛·里瑟卡·菲亚特·耐尔·麦兹奥吉奥尔诺有限公司 | Perfected pumping device for feeding fuel from tank to internal combustion engine |
| US20030110937A1 (en) * | 2001-11-29 | 2003-06-19 | Johannes Lang | Radial piston pump |
| CN1539060A (en) * | 2001-08-08 | 2004-10-20 | Crt公共铁路技术公司 | High pressure feed pump |
| WO2006037676A1 (en) * | 2004-10-06 | 2006-04-13 | Siemens Aktiengesellschaft | Radial piston pump comprising a roller tappet |
| EP1906011A2 (en) * | 2006-09-14 | 2008-04-02 | VDO Automotive AG | Fluid pump, in particular high pressure fuel pump for injection systems in combustion engines |
| DE102006060680A1 (en) * | 2006-12-21 | 2008-06-26 | Schaeffler Kg | Rolling bearings for a radial piston pump |
| CN101389858A (en) * | 2006-02-20 | 2009-03-18 | 罗伯特·博世有限公司 | High pressure pump in particular for a fuel injection device on an internal combustion engine |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19907311A1 (en) | 1999-02-22 | 2000-08-31 | Bosch Gmbh Robert | Hydraulic pump unit |
| DE10157076A1 (en) | 2001-11-21 | 2003-05-28 | Bosch Gmbh Robert | Tappet with piston has axial and/or radial roller guide adjustable on tappet by means of roller shoe fixed to tappet |
-
2010
- 2010-10-15 DE DE201010042484 patent/DE102010042484A1/en not_active Withdrawn
-
2011
- 2011-09-07 WO PCT/EP2011/065472 patent/WO2012048961A1/en active Application Filing
- 2011-09-07 CN CN201180049355.4A patent/CN103154512B/en not_active Expired - Fee Related
- 2011-09-07 EP EP11754404.9A patent/EP2627903B1/en not_active Not-in-force
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4315826A1 (en) * | 1993-05-12 | 1994-11-17 | Teves Gmbh Alfred | Unit consisting of an electric motor and an element which is to be driven |
| JPH09303252A (en) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | Hydraulic pump device |
| CN1186157A (en) * | 1996-12-23 | 1998-07-01 | 艾拉西斯·西斯特玛·里瑟卡·菲亚特·耐尔·麦兹奥吉奥尔诺有限公司 | Perfected pumping device for feeding fuel from tank to internal combustion engine |
| CN1539060A (en) * | 2001-08-08 | 2004-10-20 | Crt公共铁路技术公司 | High pressure feed pump |
| US20030110937A1 (en) * | 2001-11-29 | 2003-06-19 | Johannes Lang | Radial piston pump |
| WO2006037676A1 (en) * | 2004-10-06 | 2006-04-13 | Siemens Aktiengesellschaft | Radial piston pump comprising a roller tappet |
| CN101389858A (en) * | 2006-02-20 | 2009-03-18 | 罗伯特·博世有限公司 | High pressure pump in particular for a fuel injection device on an internal combustion engine |
| EP1906011A2 (en) * | 2006-09-14 | 2008-04-02 | VDO Automotive AG | Fluid pump, in particular high pressure fuel pump for injection systems in combustion engines |
| DE102006060680A1 (en) * | 2006-12-21 | 2008-06-26 | Schaeffler Kg | Rolling bearings for a radial piston pump |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110092A (en) * | 2014-12-24 | 2017-08-29 | 罗伯特·博世有限公司 | Pump unit for fuel, preferably diesel oil to be fed to internal combustion engine |
| CN107110092B (en) * | 2014-12-24 | 2020-05-05 | 罗伯特·博世有限公司 | Pump unit for feeding fuel, preferably diesel fuel, to an internal combustion engine |
| CN108350845A (en) * | 2015-11-12 | 2018-07-31 | 罗伯特·博世有限公司 | The high-pressure pump of pump, especially fuel injection system |
| CN107939628A (en) * | 2017-12-26 | 2018-04-20 | 浙江三浪润滑科技有限公司 | A kind of bull radial plunger pump and its application method |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2627903A1 (en) | 2013-08-21 |
| DE102010042484A1 (en) | 2012-04-19 |
| WO2012048961A1 (en) | 2012-04-19 |
| EP2627903B1 (en) | 2016-07-13 |
| CN103154512B (en) | 2017-03-01 |
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