CN103026048B - High-pressure service pump - Google Patents
High-pressure service pump Download PDFInfo
- Publication number
- CN103026048B CN103026048B CN201180036724.6A CN201180036724A CN103026048B CN 103026048 B CN103026048 B CN 103026048B CN 201180036724 A CN201180036724 A CN 201180036724A CN 103026048 B CN103026048 B CN 103026048B
- Authority
- CN
- China
- Prior art keywords
- pump
- boss
- pump piston
- pressure service
- rotor seat
- 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.)
- Expired - Fee Related
Links
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
- 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
Abstract
The present invention relates to a kind of high-pressure service pump (1), especially the fuel injection apparatus of compressed-air actuated self ignition formula internal-combustion engine is used for as radial plunger pump or curved shaft type plunger pump, comprise at least one pump assembly (6) and a live axle (3), live axle (3) comprises at least one and attaches troops to a unit in the cam (5) of this pump assembly (6).The roller (23) that the rolling surface (24) that pump assembly (6) is included in cam (5) above rolls, the rotor seat (22) receiving roller (23), rotor seat (22) insert pusher body (20), pump piston (11) wherein and take element (25), pump piston (11) above can be operated at direction of operating (13) by roller (23) and rotor seat (22) by cam (5), takes element (25) and takes pump piston (11) against direction of operating (13).That takes that element (25) is configured to partly elastically deformable takes element (25).In addition, take element (25) and have at least one boss towards rotor seat (22) (37), pump piston (11) is supported on this boss (37).The gap between pump piston (11) and rotor seat (22) can be reduced thus, thus undesirable noise can be reduced.
Description
Technical field
The present invention relates to a kind of high-pressure service pump, especially radial plunger pump or curved shaft type plunger pump.The present invention be more particularly directed to the field of the petrolift of the fuel injection apparatus for compressed-air actuated self ignition formula internal-combustion engine.
Background technique
By the known a kind of high-pressure service pump for fuel indection device in internal combustion engine of DE102005046670A1.This known high-pressure service pump has pump case, and pump element is arranged in this pump case, and described pump element comprises driven shaft and drives the pump piston carrying out stroke movement.Pump piston be directed to movably in the cylinder holes of a part for pump case and in this cylinder holes gauge one pump working chamber.Pump piston is supported on the driving shaft indirectly by the push rod of hollow cylinder, and wherein, push rod is directed to movably in the hole of a part for pump case in the longitudinal axis of pump piston.In push rod, on the end regions of live axle, supporting member is housed at it, roller is placed in this supporting member rotationally, and roller rolls on the cam of live axle.The spin axis of roller is at least approximately parallel to the spin axis of live axle.Supporting member has a recess in its side towards live axle, and roller is settled in the recess.The action of reset spring of one pretension is on push rod or on pump piston, and this Returnning spring is supported on pump case part.By this Returnning spring, pump piston and push rod are loaded by the cam towards live axle, even if even if thus suction pump piston points to towards live axle and drive shaft speed height also can ensure that roller abuts on cam.Pump piston can at least be coupled with push rod in its longitudinal axis.Alternatively, pump piston also can not be connected with push rod, now then ensures that pump piston abuts on push rod by Returnning spring.Can arrange, Returnning spring such as by spring seat act on pump piston on the piston footing diametrically expanded, this piston bottom hem facing is kept to lean against one on push rod from pusher table towards the interior flange stretched thus, this flange keeps again reclining on a support element, thus the whole compound body be made up of pump piston, push rod and the supporting member with roller is loaded by the cam towards live axle.
The shortcoming had by the high-pressure service pump that DE102005046670A1 is known is, may occur gap between the supporting member being used as rotor seat and the piston footing of pump piston.When high-pressure service pump runs, this gap is crossed, thus piston footing impacts on rotor seat.Produce undesirable noise thus.
Summary of the invention
The advantage that the high-pressure service pump with the feature of claim 1 according to the present invention has can prevent or at least reduce undesirable noise.Particularly can prevent or at least avoid the gap between rotor seat and pump piston.
By the measure enumerated in the dependent claims, the favourable improvement project of the high-pressure service pump proposed in claim 1 is possible.
Advantageously, take element and there is a middle through-hole, pump piston extends through this through hole, pump piston has a shoulder, this shoulder of pump piston is arranged in be taken between element and the surface of rotor seat, further, take element and have at least one space, described space is arranged in the side of described middle through-hole.In addition advantageously, this pore structure being arranged in middle through-hole side is the space of slot shape and at least approximately extends in the circumferential.Thus can the on purpose elastic deformability taking element given in advance.Improve taking of pump piston thus.If desired, at original state just certain precompression given in advance, element can be taken and with this precompression, pump piston loaded towards rotor seat.
This external this advantageously, take element and have multiple space, these spaces are radial to be arranged around middle through-hole distribution, and constructs the connection strap of elastically deformable between these spaces.Therefore particularly elastic deformability can be realized in the region of connection strap.On purpose moulding can be carried out in order to pump piston abuts on boss or in order to push rod spring or reclining of analog in other regions.Can require to optimize the design taking element for the difference existed thus.
Also advantageously, pump piston has shoulder, and this shoulder of pump piston is arranged in be taken between element and the surface of rotor seat, and the boss taking element is arranged on described through hole side, and wherein, the shoulder of pump piston abuts on this boss.At this also advantageously, the boss at least segmentation ground circular structure on through hole side is arranged on.Also possible that, the boss being arranged on through hole side surrounds this through hole circlewise.Thus, in the region of through hole, pump piston advantageously can abut in its shoulder and take on element.In the region that radial direction is more outer a little, the through hole that some can realize the flexibility taken desired by element then can be set.A supporting surface can be constructed in an advantageous manner again, such as to support push rod spring in a radial outer region.
Also advantageously, the boss taking element has an abutment face, and the shoulder of pump piston abuts in this abutment face, takes the side that element has this abutment face deviating from this boss, and this side is configured to an at least substantially smooth side.Also advantageously, the distance between this abutment face of this boss and this side taking element is not less than 0.2mm.To guarantee on the one hand thus on boss favourable reclines, and this reclines and pump piston is reliably remained on rotor seat.Taking element can construct to obtain relative thin on the other hand, to guarantee the elasticity of wishing.In addition, take element and can construct relatively light thus, this produces Beneficial Effect to the gross mass that will accelerate that is in operation of pump assembly.Therefore, described boss advantageously so designs, and makes to keep the shoulder of pump piston to keep reclining with the surface of rotor seat.Flexibly constructing by taking componentry floor spring, can also apply certain precompression at this.
Also advantageously, a push rod spring is set, take the supporting surface that element has an at least approximate circle annular on the side deviating from rotor seat, and push rod spring is supported on the supporting surface of this ring.Take element and can bear multiple function thus.Reliably taking of pump piston can be realized on the one hand, wherein, guarantee that pump piston and rotor seat recline.The beneficial support of push rod spring can be guaranteed on the other hand, so that regulating pushing rod body and other element, especially rotor seat together.Also simplify the design of pusher body thus.
Advantageously, rotor seat and pusher body are formed by two components, and rotor seat is inserted in this pusher body.But also possibility, rotor seat and pusher body construct integratedly and form a component.
Advantageously, described hole configuration is circular through hole.But this through hole also can be configured to the through hole of slot shape.This through hole can also be configured to the through hole of long hole shape.
Accompanying drawing explanation
Illustrate the preferred embodiments of the present invention in more detail by accompanying drawing in the following description, in the accompanying drawings, identical reference character represents corresponding element.Shown in accompanying drawing:
The schematic selected parts sectional drawing corresponding to one embodiment of the invention of Fig. 1 high-pressure service pump 1;
Fig. 2 corresponding to this embodiment of the invention Fig. 1 shown in high-pressure service pump take element and
The stereogram of element is taken shown in Fig. 3 Fig. 2.
Embodiment
Fig. 1 illustrates high-pressure service pump 1 corresponding to one embodiment of the present of invention with schematic selected parts sectional drawing.This high-pressure service pump 1 especially can be configured to radial plunger pump or curved shaft type plunger pump.High-pressure service pump 1 is suitable as the fuel injection apparatus of petrolift for compressed-air actuated self ignition formula internal-combustion engine especially.A preferable use of high-pressure service pump 1 is the fuel injection apparatus with fuel distribution bar, so-called common rail, and this common rail under high pressure stores diesel fuel.But high-pressure service pump 1 according to the present invention is also applicable to other purposes.
High-pressure service pump 1 has the pump case of multi-part type, and this pump case has housing member 2.In housing member 2, be furnished with live axle 3, this live axle 3 is placed in pump case by rights.At this, live axle 3 can by internal-combustion engine rotary actuation, thus live axle 3 rotates around spin axis 4.Live axle 3 is provided with cam 5.Cam 5 can be configured to single cam or many cams at this.In addition, cam 5 also can be formed by an eccentric portion of live axle 3.Cam 5 configures to the pump assembly 6 of high-pressure service pump 1.
High-pressure service pump 1 has cylinder head 7, and this cylinder head 7 is connected with housing member 2.Cylinder head 7 has extension 8, and this extension 8 extend in the push-rod hole 9 of housing member 2.Extension 8 has columniform hole 10.
Pump assembly 6 comprises pump piston 11, to be arranged in hole 10 and longitudinal axis 12 along hole 10 in hole 10 is directed to this pump piston 11 range selector.Longitudinal axis 12 is at this at least approximate spin axis 4 pointing to live axle 3.Can regulate on direction of operating 13 and against direction of operating 13 at this pump piston 11.
Side 14 gauge one pump working chamber 15 in cylindrical hole 10 of pump piston 11.At this, an inlet valve 16 and outlet valve 17 are set, first the fuel be under low pressure is directed in pump working chamber 15, then by pipeline 18 by loaded by pump piston 11, be in fuel area density under high pressure and distribute bar or analog to fuel.
The pusher body 20 of hollow cylinder at least is substantially furnished with in push-rod hole 9.Be directed to along longitudinal axis 12 in push-rod hole 9 at this pusher body 20.Pusher body 20 has the bead 21 radially-inwardly pointed to.In pusher body 20, insert rotor seat 22, rotor seat 22 is supported in the bead 21 of pusher body 20.
Rotor seat 22 is for receiving roller 23, and when live axle 3 rotates around spin axis 4, this roller 23 rolls on rolling surface 24.Therefore, corresponding to the stroke motion of cam 5, a steering force is delivered on rotor seat 22 by roller 23.
Partly the element 25 of taking of disk like is inserted in pusher body 20.At this, take element 25 and abut in one in bead 21 towards on the side 26 of rotor seat 22.
Pump piston 11 has piston footing 27, and piston footing 27 arranges the shoulder 28 of a tip side.The side 29 of the shoulder 28 of pump piston 11 abuts on the surface 30 of rotor seat 22 at this.Take element 25 to be loaded by push rod spring 31 at this.Push rod spring 31 is arranged in push-rod hole 9, and wherein, push rod spring 31 range selector ground surrounds the extension 8 of cylinder head 7.
Take the supporting surface 35 that element 25 has ring, this supporting surface 35 deviates from the described side 26 taking element 25.Push rod spring 31 1 aspect is supported on the supporting surface 35 of the ring taking element 25.Push rod spring 31 is supported on the downside 36 of cylinder head 7 on the other hand.
Therefore, the steering force be delivered to rotor seat 22 from cam 5 by roller 23 continues to be delivered to pump piston 11 from rotor seat 22.Thus, fuel transports out from pump working chamber 15 through outlet valve 17.Then, the reset of pusher body 20 against direction of operating 13 is realized by the power of push rod spring 31.At this, push rod spring 31 loads by taking element 25 pairs of pusher bodies 20.Therefore, rotor seat 22 and the roller 23 be placed in rotor seat 22 are also loaded by cam 5 direction, thus guarantee that roller 23 contacts with the rolling surface 24 of cam 5 all the time.
Particularly there is this problem through top dead center and lower dead center: due to direction transformation and power relationship change, in the effect chain between cam 5 and pump piston 11, tolerance and possible gap can cause the adjustment movement of bumping type.This particularly relates to piston footing 27 the reclining on the surface 30 of rotor seat 22 of pump piston 11.
The element 25 of taking of pump assembly 6 has towards the boss 37 of rotor seat 22 on its described side 26.The shoulder 28 of piston footing 27 is supported on to be taken on this boss 37 of element 25.In addition, take element 25 and be configured to partial elastic.Avoid thus or at least reduce the gap between piston footing 27 and the surface 30 of rotor seat 22.Therefore, even if also undesirable noise can be prevented when the rotating speed of high-pressure service pump 1 is high.At least reduce the noise especially produced on the surface 30 that may impinge upon rotor seat 22 due to piston footing 27 through top dead center or lower dead center.Especially the displacement of piston footing 27 relative to rotor seat 22 can be reduced significantly at this.The distance of supporting surface that ring supporting surface 35 can be formed with respect to boss 37 by boss 37, that be used for shoulder 28 adjusts to a value of wishing, this value is preferably minimum 0.2mm, described ring supporting surface 35 is the action plane of push rod spring 31 being used as the hollow spring of piston reset, and the described supporting surface for shoulder 28 is the action plane taken for the piston of pump piston 11.
Take element 25 and have the through hole 40 being preferably in center in this embodiment, pump piston 11 extends through this through hole 40.But this through hole 40 also can have other structures.The shoulder 28 of pump piston 11 is arranged in takes taking between the surface 30 of element 25 towards this of element 25 and rotor seat 22.The boss 37 taking element 25 is arranged on through hole 40 side, and wherein, the shoulder 28 of pump piston 11 abuts on this boss 37.
The structure taking element 25 is further described referring to Fig. 2 and 3.
What Fig. 2 illustrated the high-pressure service pump 1 shown in Fig. 1 with side view takes element 25.The supporting surface 35 of ring is configured in be taken on the side 38 of element 25.The supporting surface 35 of ring forms at this favourable abutment face being used for push rod spring 31.Side 38 preferably flatly constructs in an initial condition substantially.The boss 37 deviating from side 38 constructs an abutment face 39.The ring supporting surface 35 of this abutment face 39 and side 38 deviates from mutually.In the assembled condition, piston footing 27 is supported in abutment face 39 with its shoulder 28.At this, the shoulder 28 of piston footing 27 is applied in the abutment face 39 of boss 37 at least in part from behind.A distance 32 given in advance is realized between the ring supporting surface 35 and described abutment face of side 38.This distance 32 is given in advance for respective applicable cases.
Fig. 3 illustrates with three-dimensional view and takes element 25 shown in Fig. 2.
Take element 25 and there is middle through-hole 40.In the assembled condition, the piston footing 27 of pump piston 11 extends through this middle through-hole 40.The shoulder 28 of pump piston 11 is between the surface 30 taking element 25 and rotor seat 22.Boss 37 is configured to the boss 37 of ring in this embodiment.Produce the annular configuration of abutment face 39 thus.
Boss 37 by the space 41,42,43 of multiple slot shape around.Therefore, space 41 to 43 is arranged in the side of middle through-hole 40.The space 41 to 43 of slot shape extends around middle through-hole 40 in the circumferential.Connection strap 44,45,46 is configured with, these connection strap elastically deformables between the space 41 to 43 of slot shape.In addition, take element 25 and there is outer shroud 47, this outer shroud 47 is configured for the ring supporting surface 35 supporting push rod spring 31.Outer shroud 47 is connected with inner ring 48 by connection strap 44 to 46.Inner ring 48 has boss 37 at this.
The certain elastic movement between outer shroud 47 and inner ring 48 is allowed by the flexible construction of connection strap 44 to 46.This motion can along or carry out against direction of operating 13.
In the assembling condition of high-pressure service pump 1, certain precompression can be applied on piston footing 27 by taking element 25, thus this piston footing 27 is pressed onto on rotor seat 22 with certain precompression.Be in operation occur impact force or similar power can in an advantageous manner by taking the elastic construction of element 25 and/or being received by push rod spring 31 at this.Therefore produce the robust structure of high-pressure service pump 1, wherein stop or at least reduce possible noise.
Advantageously, arrange a push rod spring 31, take element 25 and have the side 38 deviating from rotor seat 22, and this side 38 has the supporting surface 35 of at least approximate circle annular, push rod spring 31 is supported on this supporting surface 35.
The present invention is not limited to described embodiment.
Claims (9)
1. a high-pressure service pump (1), for the fuel injection apparatus of compressed-air actuated self ignition formula internal-combustion engine, there is at least one pump assembly (6) and a live axle (3), described live axle (3) has configuration at least one cam (5) of this pump assembly (6), wherein, this pump assembly (6) has the upper roller (23) rolled of a rolling surface (24) in cam (5), the rotor seat (22) of the one described roller of reception (23), element (25) taken by one pump piston (11) and, this pump piston (11) above can be operated at direction of operating (13) by roller (23) and rotor seat (22) by cam (5), this is taken element (25) and takes described pump piston (11) against described direction of operating (13), it is characterized in that, described take that element (25) is partly configured to elastically deformable take element (25), and, described element (25) of taking has at least one boss towards described rotor seat (22) (37), pump piston (11) is supported on described boss (37), described element (25) of taking has multiple space (41-43), these spaces (41-43) are radially arranged around a through hole (40) distribution ground, and, the connection strap (44-46) of elastically deformable is configured with between these spaces (41-43).
2. high-pressure service pump according to claim 1, is characterized in that, described space (41-43) is configured to the space (41-43) of slot shape, and the space (41-43) of described slot shape is at least approximate to be extended in the circumferential.
3. according to the high-pressure service pump of claim 1 or 2, it is characterized in that, this through hole (40) taking element (25) described in pump piston (11) passes extends, described pump piston (11) has a shoulder (28), that takes element (25) and described rotor seat (22) described in this shoulder (28) of pump piston (11) is arranged in takes between the surface (30) of element (25) towards this, and, this described boss (37) taking element (25) is arranged on this through hole (40) side, wherein, the shoulder (28) of pump piston (11) abuts on this boss (37).
4. high-pressure service pump according to claim 3, is characterized in that, is arranged on described boss (37) at least range selector ground circular structure on described through hole (40) side, and/or
Be arranged on the described boss (37) on described through hole (40) side circlewise around described through hole (40).
5. high-pressure service pump according to claim 3, it is characterized in that, the described described boss (37) taking element (25) has an abutment face (39), the shoulder (28) of pump piston (11) abuts in this abutment face (39), take the side (38) that element (25) has this abutment face (39) deviating from this boss (37), further, this side (38) are configured at least substantially smooth side (38).
6. high-pressure service pump according to claim 5, it is characterized in that, the distance (32) between the described abutment face (39) of described boss (37) and the described described side (38) taking element (25) is not less than 0.2mm.
7. high-pressure service pump according to claim 3, it is characterized in that, the described described boss (37) taking element (25) so constructs, and makes the shoulder of pump piston (11) (28) keep reclining with the described surface (30) of rotor seat (22).
8. 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 plunger pump or curved shaft type plunger pump.
9. according to the high-pressure service pump of claim 1 or 2, it is characterized in that, described in described through hole (40) is in, take the middle part of element (25).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010038468.2 | 2010-07-27 | ||
| DE201010038468 DE102010038468A1 (en) | 2010-07-27 | 2010-07-27 | high pressure pump |
| PCT/EP2011/061222 WO2012013452A1 (en) | 2010-07-27 | 2011-07-04 | High pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103026048A CN103026048A (en) | 2013-04-03 |
| CN103026048B true CN103026048B (en) | 2015-12-16 |
Family
ID=44320389
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180036724.6A Expired - Fee Related CN103026048B (en) | 2010-07-27 | 2011-07-04 | High-pressure service pump |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP2598743B1 (en) |
| JP (1) | JP6042809B2 (en) |
| CN (1) | CN103026048B (en) |
| DE (1) | DE102010038468A1 (en) |
| RU (1) | RU2568359C2 (en) |
| WO (1) | WO2012013452A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011017573A1 (en) * | 2011-04-27 | 2012-10-31 | Robert Bosch Gmbh | Spring plate for a plunger assembly of a high pressure pump and high pressure pump |
| ITMI20120270A1 (en) * | 2012-02-23 | 2013-08-24 | Bosch Gmbh Robert | HIGH PRESSURE PUMP FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
| DE102013212302A1 (en) * | 2013-06-26 | 2014-12-31 | Robert Bosch Gmbh | High pressure pump and fuel injection system with a high pressure pump |
| US10655580B2 (en) * | 2014-10-09 | 2020-05-19 | Hitachi Automotive Systems, Ltd. | High pressure fuel supply pump |
| GB201503591D0 (en) * | 2015-03-03 | 2015-04-15 | Delphi International Operations Luxembourg S.�.R.L. | High pressure diesel fuel pumps and shoe arrangements |
| GB201506173D0 (en) * | 2015-04-13 | 2015-05-27 | Delphi Internat Operations Luxembourg S � R L | Fuel pump |
| GB2542349A (en) * | 2015-09-15 | 2017-03-22 | Gm Global Tech Operations Llc | Fuel unit pump and internal combustion engine comprising it |
| CN105370465A (en) * | 2015-12-11 | 2016-03-02 | 中国北方发动机研究所(天津) | Deformable compensation type high-pressure variable pump plunger |
| JP6305480B2 (en) * | 2016-09-01 | 2018-04-04 | 日機装株式会社 | Non-pulsating pump |
| US20210394524A1 (en) * | 2018-12-11 | 2021-12-23 | Hewlett-Packard Development Company, L.P. | Displacement pump |
| EP3742235B1 (en) * | 2019-05-23 | 2022-01-26 | Meco S.A. | Push button system, and timepiece comprising same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4241826A1 (en) * | 1992-12-11 | 1994-08-25 | Teves Gmbh Alfred | High-pressure pump having a radial piston and an attenuation layer |
| WO2003031816A1 (en) * | 2001-09-28 | 2003-04-17 | Siemens Aktiengesellschaft | Connecting element for connecting a piston to a restoring element |
| WO2005073554A1 (en) * | 2004-01-30 | 2005-08-11 | Robert Bosch Gmbh | High-pressure pump, particularly for a fuel injection device of a combustion engine |
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| SU1224433A1 (en) * | 1984-02-02 | 1986-04-15 | Производственное Объединение "Турбомоторный Завод" Им.К.Е.Ворошилова | High-pressure fuel pump |
| DE4401074B4 (en) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pump arrangement, in particular for conveying fuel from a reservoir to an internal combustion engine |
| IT1289796B1 (en) * | 1996-12-23 | 1998-10-16 | Elasis Sistema Ricerca Fiat | IMPROVEMENTS TO A PUMP DEVICE FOR SUPPLYING FUEL FROM A TANK TO AN INTERNAL COMBUSTION ENGINE. |
| JPH11324858A (en) * | 1998-05-19 | 1999-11-26 | Toyota Motor Corp | Plunger pump |
| JP2000193006A (en) * | 1998-12-22 | 2000-07-14 | Fukoku Co Ltd | Flat spring-integrated core and its manufacture |
| JP2002295559A (en) * | 2001-03-29 | 2002-10-09 | Ochiai:Kk | Buffer ring |
| JP2004218459A (en) * | 2003-01-10 | 2004-08-05 | Bosch Automotive Systems Corp | Fuel supply pump and tappet structure |
| DE10344459B4 (en) * | 2003-09-25 | 2012-06-14 | Robert Bosch Gmbh | Piston pump, in particular high-pressure piston 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 |
| DE102007012705A1 (en) * | 2007-03-16 | 2008-09-18 | Robert Bosch Gmbh | High-pressure pump for conveying fuel with a torsion-decoupled compression spring element in the plunger device |
| US8070464B2 (en) * | 2007-06-01 | 2011-12-06 | Caterpillar Inc. | Retention system |
| JP4815469B2 (en) * | 2008-05-13 | 2011-11-16 | 日本発條株式会社 | Spring |
| DE102008001871A1 (en) * | 2008-05-20 | 2009-11-26 | Robert Bosch Gmbh | High-pressure fuel pump |
| JP4742122B2 (en) * | 2008-07-02 | 2011-08-10 | 日本発條株式会社 | Vibration isolator |
-
2010
- 2010-07-27 DE DE201010038468 patent/DE102010038468A1/en not_active Withdrawn
-
2011
- 2011-07-04 RU RU2013108357/06A patent/RU2568359C2/en not_active IP Right Cessation
- 2011-07-04 CN CN201180036724.6A patent/CN103026048B/en not_active Expired - Fee Related
- 2011-07-04 EP EP11728881.1A patent/EP2598743B1/en active Active
- 2011-07-04 WO PCT/EP2011/061222 patent/WO2012013452A1/en active Application Filing
- 2011-07-04 JP JP2013521038A patent/JP6042809B2/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4241826A1 (en) * | 1992-12-11 | 1994-08-25 | Teves Gmbh Alfred | High-pressure pump having a radial piston and an attenuation layer |
| WO2003031816A1 (en) * | 2001-09-28 | 2003-04-17 | Siemens Aktiengesellschaft | Connecting element for connecting a piston to a restoring element |
| WO2005073554A1 (en) * | 2004-01-30 | 2005-08-11 | Robert Bosch Gmbh | High-pressure pump, particularly for a fuel injection device of a combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103026048A (en) | 2013-04-03 |
| RU2013108357A (en) | 2014-09-10 |
| JP2013532792A (en) | 2013-08-19 |
| RU2568359C2 (en) | 2015-11-20 |
| JP6042809B2 (en) | 2016-12-14 |
| DE102010038468A1 (en) | 2012-02-02 |
| WO2012013452A1 (en) | 2012-02-02 |
| EP2598743B1 (en) | 2014-11-05 |
| EP2598743A1 (en) | 2013-06-05 |
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