CN103026048A - High pressure pump - Google Patents
High pressure pump Download PDFInfo
- Publication number
- CN103026048A CN103026048A CN2011800367246A CN201180036724A CN103026048A CN 103026048 A CN103026048 A CN 103026048A CN 2011800367246 A CN2011800367246 A CN 2011800367246A CN 201180036724 A CN201180036724 A CN 201180036724A CN 103026048 A CN103026048 A CN 103026048A
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- China
- Prior art keywords
- pump
- hole
- taking
- boss
- pump piston
- Prior art date
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Classifications
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- 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
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a high pressure pump (1), which is used in particular as a radial or series piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines, comprising at least one pump assembly (6) and one drive shaft (3) which comprises at least one cam (5) assigned to the pump assembly (6). The pump assembly (6) comprises a roller (23) running on the running surface (24) of the cam (5), a roller shoe (22) which receives the roller (23), a tappet body (20) in which the roller shoe (22) is introduced, a pump piston (11) which can be actuated in an actuating direction (13) by the cam (5) by means of the roller (23) and the roller shoe (22) and a carrier element (25) which carries the pump piston (11) opposite the actuating direction (13). According to the invention, the carrier element (25) is designed as a partially elastically deformable carrier element (25). The carrier element (25) according to the invention further comprises at least one elevation (37) facing the roller shoe (22) on which the pump piston (11) is supported. A play between the pump piston (11) and the roller shoe (22) can thus be reduced according to the invention in such a manner that undesired noises 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 for the petrolift of the fuel injection apparatus of 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 DE 10 2,005 046 670 A1.This known high-pressure service pump has pump case, and pump element is arranged in this pump case, and described pump element comprises that driven shaft drives the pump piston that carries out stroke movement.Pump piston is directed in the cylinder hole of the part of pump case and gauge one pump working chamber in this cylinder hole movably.Pump piston is supported on the live axle indirectly by the push rod of hollow cylinder, and wherein, push rod is directed on the longitudinal axis of pump piston in the hole of the part of pump case movably.In push rod, at its end regions towards live axle supporting member is housed, roller is placed in this supporting member rotationally, and roller rolls at the cam of live axle.The approximate at least spin axis that is parallel to live axle of the spin axis of roller.Supporting member has a recess in its side towards live axle, and roller is placed in this recess.The action of reset spring of one pretension is on the push rod or on the pump piston, and this Returnning spring is supported on the pump case part.By this Returnning spring, pump piston and push rod are loaded by the cam towards live axle, thereby even even the suction pump piston can guarantee also that towards live axle sensing and drive shaft speed height roller abuts on the cam.Pump piston can be coupled with push rod on its longitudinal axis at least.Alternatively, pump piston can not be connected with push rod yet, and then guarantee that by Returnning spring pump piston abuts on the push rod this moment.Can arrange, Returnning spring for example by spring seat act on pump piston on the piston footing that diameter enlarges, keep thus this piston bottom hem facing lean against one on the push rod from pusher table on the interior flange of stretching, this flange keeps again abutting on the supporting member, thereby is loaded by the cam towards live axle by pump piston, push rod with the whole compound body that the supporting member of roller forms.
The shortcoming that is had by the known high-pressure service pump of DE 10 2,005 046 670 A1 is the gap may occur between the piston footing of the supporting member that is used as rotor seat and pump piston.This gap is crossed when high-pressure service pump moves, thereby the piston footing impacts on the rotor seat.Produce thus undesirable noise.
Summary of the invention
The advantage that high-pressure service pump with feature of claim 1 according to the present invention has is, can prevent or reduces at least undesirable noise.Particularly can prevent or avoid at least gap between rotor seat and the pump piston.
By the measure of enumerating in the dependent claims, the favourable improvement project of the high-pressure service pump that proposes in claim 1 is possible.
Advantageously, take element and have a middle through-hole, pump piston passes this through hole and extends, pump piston has a shoulder, this shoulder of pump piston is arranged between the surface of taking element and rotor seat, and, to take element and have at least one space, described space is arranged in the next door of described middle through-hole.In addition advantageously, this pore structure that is arranged in middle through-hole next door is that upwards extend in the space of slot shape and being similar at least in week.The elastically deformable of taking element given in advance on purpose thus.Improve thus taking of pump piston.In case of necessity, can in original state with regard to certain precompression given in advance, take element and with this precompression pump piston be loaded towards rotor seat.
This external this advantageously, take element and have a plurality of spaces, these spaces radially arrange around the middle through-hole ground that distributes, and between these spaces the connection strap of structure elastically deformable.Therefore particularly in the zone of connection strap, can realize elastically deformable.Can be on purpose in other zones abut on the boss or for push rod spring or reclining of analog and carry out moulding for pump piston.Can require to optimize the design of taking element for the difference that exists thus.
Also advantageously, pump piston has shoulder, and this shoulder of pump piston is arranged between the surface of taking element and rotor seat, and the boss of taking element is arranged on described through hole next door, and wherein, the shoulder of pump piston abuts on this boss.At this also advantageously, the boss that is arranged on through hole next door is segmentation ground circular structure at least.Also possible is that the boss that is arranged on the through hole next door surrounds this through hole circlewise.Thus, in the zone of through hole, pump piston can advantageously abut in its shoulder and take on the element.The through hole that some can realize taking the desired flexibility of element then can be set in a radially more outer a little zone.In a radially outer zone, can construct again in an advantageous manner a supporting surface, in order to for example support push rod spring.
Also advantageously, the boss of taking element has an abutment face, and the shoulder of pump piston abuts on this abutment face, take element and have the distolateral of this abutment face of deviating from this boss, and this distolateral be configured to one at least basically smooth distolateral.Also advantageously, this abutment face of this boss and take this of element distance between distolateral and be not less than 0.2mm.Guarantee on the one hand thus favourable the reclining on boss, this reclines pump piston is remained on the rotor seat reliably.Take on the other hand element and can construct to get relative thin, in order to guarantee the elasticity of wishing.In addition, take element and can construct thus relatively gently, this gross mass that will accelerate being in operation of pump assembly produces Beneficial Effect.Therefore, described boss is so design advantageously, so that keep the shoulder of pump piston to keep leaning on the surface label of rotor seat.Flexibly construct by taking the componentry floor spring, can also apply certain precompression at this.
Also advantageously, a push rod spring is set, take element and distolaterally have the supporting surface of approximate circle annular at least what deviate from rotor seat, and push rod spring is supported on the supporting surface of this ring.Take element and can bear a plurality of functions thus.Can realize reliably taking of pump piston on the one hand, wherein, guarantee that pump piston and rotor seat recline.Can guarantee on the other hand the favourable support of push rod spring, so that together regulating pushing rod body and other element, especially rotor seat.Also simplified thus the design of pusher body.
Advantageously, rotor seat and pusher body are formed by two members, and rotor seat is inserted in this pusher body.But also possible, a member is constructed and formed to rotor seat and pusher body integratedly.
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.
Description of drawings
Illustrate in more detail the preferred embodiments of the present invention by accompanying drawing in the following description book, in the accompanying drawings, identical reference character represents corresponding element.Shown in the 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 the high-pressure service pump shown in Figure 1 of this embodiment of the invention take element and
Fig. 3 stereogram of taking element shown in Figure 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 that petrolift is used for compressed-air actuated self ignition formula internal-combustion engine especially.A preferable use of high-pressure service pump 1 is to have fuel and distributes bar, the so-called altogether fuel injection apparatus of rail, and this common rail is under high pressure stored diesel fuel.Yet high-pressure service pump 1 according to the present invention also is 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.Be furnished with live axle 3 in housing member 2, this live axle 3 is placed in the pump case by rights.At this, live axle 3 can be by the internal-combustion engine rotary actuation, thereby live axle 3 is around spin axis 4 rotations.Be provided with cam 5 at live axle 3.Cam 5 can be configured to single cam or many cams at this.In addition, cam 5 also can form by an eccentric section of live axle 3.Cam 5 configurations are 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.
In push-rod hole 9, be furnished with at least basically pusher body 20 of hollow cylinder.Be directed to along longitudinal axis 12 in push-rod hole 9 at this pusher body 20.Pusher body 20 has the bead 21 of radially inwardly pointing to.Insert rotor seat 22 in pusher body 20, rotor seat 22 is supported on the bead 21 of pusher body 20.
Partly the element 25 of taking of dish shape is inserted in the pusher body 20.At this, take element 25 and abut in one on the bead 21 on the side 26 of rotor seat 22.
Take the supporting surface 35 that element 25 has ring, this supporting surface 35 deviates from the described side 26 of taking element 25.Push rod spring 31 is supported on the supporting surface 35 of the ring of taking element 25 on the one hand.Push rod spring 31 is supported on the downside 36 of cylinder head 7 on the other hand.
Therefore, continue to be delivered on the pump piston 11 from rotor seat 22 by the steering force that roller 23 is delivered on the rotor seat 22 from cam 5.Thus, fuel transports out from pump working chamber 15 through outlet valve 17.Then, the power by push rod spring 31 realizes pusher body 20 resetting against direction of operating 13.At this, push rod spring 31 loads by taking 25 pairs of pusher bodies of element 20.Therefore, rotor seat 22 and the roller 23 that is placed in the rotor seat 22 are also loaded to cam 5 directions, thereby guarantee that roller 23 contacts with the rolling surface 24 of cam 5 all the time.
Particularly have this problem through top dead center and lower dead center the time: because direction transformation and power relationship change, tolerance and possible gap can cause the adjustment movement of bumping type in the effect chain between cam 5 and the pump piston 11.This relates in particular 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 boss 37 towards rotor seat 22 in its described side 26.The shoulder 28 of piston footing 27 is supported on this boss 37 of taking element 25.In addition, taking element 25, to be configured to part flexible.Avoid thus or reduce at least gap between the surface 30 of piston footing 27 and rotor seat 22.Therefore, even in the high situation of the rotating speed of high-pressure service pump 1, also can prevent undesirable noise.At least reduce especially and through top dead center or lower dead center the time, may impinge upon owing to piston footing 27 noise that produces on the surface 30 of rotor seat 22.Especially can reduce significantly piston footing 27 with respect to the displacement of rotor seat 22 at this.Can be with ring supporting surface 35 with respect to the value of adjusting to a hope by boss distance 37 formation, that be used for the supporting surface of shoulder 28 by boss 37, this value is preferably minimum 0.2mm, described ring supporting surface 35 is that described supporting surface for shoulder 28 is the action plane of taking for the piston of pump piston 11 as the action plane of the push rod spring 31 of the hollow spring of piston reset.
Take element 25 and have in this embodiment the through hole 40 that preferably is in the center, pump piston 11 passes this through hole 40 and extends.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 of taking element 25 is arranged on through hole 40 next doors, and wherein, the shoulder 28 of pump piston 11 abuts on this boss 37.
Further describe the structure of taking element 25 referring to Fig. 2 and 3.
Fig. 2 takes element 25 with what side view illustrated the high-pressure service pump 1 shown in Fig. 1.The supporting surface 35 of ring be configured in take element 25 distolateral 38 on.The supporting surface 35 of ring is formed for the favourable abutment face of push rod spring 31 at this.Distolateral 38 preferably flatly construct under original state basically.In boss 37 structures one abutment face 39 that deviates from distolateral 38.This abutment face 39 and distolateral 38 ring supporting surface 35 deviate from mutually.Under assembling condition, piston footing 27 is supported on the abutment face 39 with its shoulder 28.At this, the shoulder 28 of piston footing 27 is applied on the abutment face 39 of boss 37 at least in part from behind.Realize a distance 32 given in advance between ring supporting surface 35 distolateral 38 and the described abutment face.This distance 32 is given in advance for applicable cases separately.
Fig. 3 illustrates with three-dimensional view and takes element 25 shown in Fig. 2.
Take element 25 and have middle through-hole 40.Under assembling condition, the piston footing 27 of pump piston 11 passes this middle through-hole 40 and extends.28 of the shoulders of pump piston 11 are between the surface 30 of taking element 25 and rotor seat 22.Boss 37 is configured to the boss 37 of ring in this embodiment.Produce thus the annular configuration of abutment face 39.
Boss 37 is centered on by the space 41,42,43 of a plurality of slot shapes.Therefore, space 41 to 43 is arranged in the next door of middle through-hole 40.Upwards extended around middle through-hole 40 in week in the space 41 to 43 of slot shape.Between the space 41 to 43 of slot shape, be configured with connection strap 44,45,46, these connection strap elastically deformables.In addition, take element 25 and have outer shroud 47, be configured for supporting the ring supporting surface 35 of push rod spring 31 at this outer shroud 47.Outer shroud 47 is connected with interior ring 48 by connection strap 44 to 46.Interior ring 48 has boss 37 at this.
By the flexible construction permission outer shroud 47 of connection strap 44 to 46 and the certain elastic movement between the interior ring 48.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 the piston footing 27 by taking element 25, thereby this piston footing 27 is pressed onto on the rotor seat 22 with certain precompression.The impact force that occurs of being in operation or similar power this can be in an advantageous manner by taking element 25 elastic construction and/or receive by push rod spring 31.Therefore produce the robust structure of high-pressure service pump 1, wherein stop or reduce at least possible noise.
Advantageously, a push rod spring 31 is set, takes element 25 and have and deviate from the distolateral 38 of rotor seat 22, and this distolateral 38 has at least supporting surface 35 of approximate circle annular, push rod spring 31 is supported on this supporting surface 35.
The present invention is not limited to described embodiment.
Claims (according to the modification of the 19th of treaty)
1. a high-pressure service pump (1), especially radial plunger pump or curved shaft type plunger pump, the fuel injection apparatus that is used for compressed-air actuated self ignition formula internal-combustion engine, have 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 roller (23) that a rolling surface in cam (5) (24) rolls, one receives the rotor seat (22) of described roller (23), one pump piston (11) and one is taken element (25), this pump piston (11) 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) partly is configured to elastically deformable take element (25), and, the described element (25) of taking has at least one boss towards described rotor seat (22) (37), pump piston (11) is supported on the described boss (37), the described element (25) of taking has a plurality of spaces (41-43), these spaces (41-43) are radially preferably arranged on through hole (40) the distribution ground at middle part around one, and, between these spaces (41-43), be configured with the connection strap (44-46) of elastically deformable.
2. according to claim 1 high-pressure service pump is characterized in that, described space (41-43) is configured to the space (41-43) of slot shape, and the space of described slot shape (41-43) is similar at least in week and upwards extends.
3. according to claim 1 and 2 high-pressure service pump, it is characterized in that, pump piston (11) passes described this through hole (40) of taking element (25) and extends, described pump piston (11) has a shoulder (28), this shoulder (28) of pump piston (11) is arranged in described the taking between the surface (30) of element (25) towards this of element (25) and described rotor seat (22) of taking, and, this described boss (37) of taking element (25) is arranged on this through hole (40) next door, wherein, the shoulder (28) of pump piston (11) abuts on this boss (37).
4. according to claim 3 high-pressure service pump is characterized in that, the described boss (37) that is arranged on described through hole (40) next door is range selector ground circular structure at least, and/or
Be arranged on the described boss (37) on described through hole (40) next door circlewise around described through hole (40).
5. according to each high-pressure service pump in the aforementioned claim, it is characterized in that, the described described boss (37) of taking element (25) has an abutment face (39), the shoulder (28) of pump piston (11) abuts on this abutment face (39), take distolateral (38) that element (25) has this abutment face (39) that deviates from this boss (37), and these distolateral (38) are configured at least basically smooth distolateral (38).
6. according to claim 5 high-pressure service pump is characterized in that, the distance (32) between the described abutment face (39) of described boss (37) and described described distolateral (38) of taking element (25) is not less than 0.2mm.
7. each high-pressure service pump in 6 according to claim 3 is characterized in that, the described described boss (37) of taking element (25) is structure so, so that the described surface (30) of the shoulder (28) of pump piston (11) and rotor seat (22) keeps reclining.
Claims (10)
1. a high-pressure service pump (1), especially radial plunger pump or curved shaft type plunger pump, the fuel injection apparatus that is used for compressed-air actuated self ignition formula internal-combustion engine, have 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 roller (23) that a rolling surface in cam (5) (24) rolls, one receives the rotor seat (22) of described roller (23), one pump piston (11) and one is taken element (25), this pump piston (11) 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) partly is configured to elastically deformable take element (25), and, the described element (25) of taking has at least one boss towards described rotor seat (22) (37), and pump piston (11) is supported on the described boss (37).
2. according to claim 1 high-pressure service pump is characterized in that, the described element (25) of taking has at least one space (41-43).
3. according to claim 2 high-pressure service pump is characterized in that, described space (41-43) is configured to the space (41-43) of slot shape, and the space of described slot shape (41-43) is similar at least in week and upwards extends.
4. according to claim 2 or 3 high-pressure service pump, it is characterized in that, described space (41-43) is arranged in a described through hole (40) next door of taking element (25), and this through hole (40) preferable configuration is taken the middle through-hole (40) of element (25) for this.
5. according to claim 4 high-pressure service pump, it is characterized in that, the described element (25) of taking has a plurality of spaces (41-43), these spaces (41-43) are radially arranged around the described preferably through hole (40) at the middle part with distributing, and, between these spaces (41-43), be configured with the connection strap (44-46) of elastically deformable.
6. each high-pressure service pump in 5 according to claim 1, it is characterized in that, the described element (25) of taking has a preferred through hole (40) at the middle part, pump piston (11) passes this through hole (40) and extends, described pump piston (11) has a shoulder (28), this shoulder (28) of pump piston (11) is arranged in described the taking between the surface (30) of element (25) towards this of element (25) and described rotor seat (22) of taking, and, this described boss (37) of taking element (25) is arranged on this through hole (40) next door, wherein, the shoulder (28) of pump piston (11) abuts on this boss (37).
7. according to claim 6 high-pressure service pump is characterized in that, the described boss (37) that is arranged on described through hole (40) next door is range selector ground circular structure at least, and/or
Be arranged on the described boss (37) on described through hole (40) next door circlewise around described through hole (40).
8. according to claim 5 or 6 high-pressure service pump, it is characterized in that, the described described boss (37) of taking element (25) has an abutment face (39), the shoulder (28) of pump piston (11) abuts on this abutment face (39), take distolateral (38) that element (25) has this abutment face (39) that deviates from this boss (37), and these distolateral (38) are configured at least basically smooth distolateral (38).
9. according to claim 8 high-pressure service pump is characterized in that, the distance (32) between the described abutment face (39) of described boss (37) and described described distolateral (38) of taking element (25) is not less than 0.2mm.
10. each high-pressure service pump in 9 according to claim 6 is characterized in that, the described described boss (37) of taking element (25) is structure so, so that the described surface (30) of the shoulder (28) of pump piston (11) and rotor seat (22) keeps reclining.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201010038468 DE102010038468A1 (en) | 2010-07-27 | 2010-07-27 | high pressure pump |
| DE102010038468.2 | 2010-07-27 | ||
| PCT/EP2011/061222 WO2012013452A1 (en) | 2010-07-27 | 2011-07-04 | High pressure pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103026048A true CN103026048A (en) | 2013-04-03 |
| CN103026048B 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) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105339646A (en) * | 2013-06-26 | 2016-02-17 | 罗伯特·博世有限公司 | High-pressure pump and fuel injection system having a high-pressure pump |
| 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 |
| CN107110097A (en) * | 2014-10-09 | 2017-08-29 | 日立汽车系统株式会社 | High-pressure fuel feed pump |
| CN111983910A (en) * | 2019-05-23 | 2020-11-24 | Meco有限公司 | Push-button system and timepiece comprising such a push-button system |
| TWI720231B (en) * | 2016-09-01 | 2021-03-01 | 日商日機裝股份有限公司 | Pulsationless pump |
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| 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 |
| 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 |
| WO2020122879A1 (en) * | 2018-12-11 | 2020-06-18 | Hewlett-Packard Development Company, L.P. | A displacement pump |
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2011
- 2011-07-04 CN CN201180036724.6A patent/CN103026048B/en not_active Expired - Fee Related
- 2011-07-04 EP EP11728881.1A patent/EP2598743B1/en not_active Not-in-force
- 2011-07-04 JP JP2013521038A patent/JP6042809B2/en not_active Expired - Fee Related
- 2011-07-04 RU RU2013108357/06A patent/RU2568359C2/en not_active IP Right Cessation
- 2011-07-04 WO PCT/EP2011/061222 patent/WO2012013452A1/en active Application Filing
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| 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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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105339646A (en) * | 2013-06-26 | 2016-02-17 | 罗伯特·博世有限公司 | High-pressure pump and fuel injection system having a high-pressure pump |
| CN105339646B (en) * | 2013-06-26 | 2019-09-10 | 罗伯特·博世有限公司 | High-pressure pump and fuel injection system having a high-pressure pump |
| CN107110097A (en) * | 2014-10-09 | 2017-08-29 | 日立汽车系统株式会社 | High-pressure fuel feed pump |
| 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 |
| TWI720231B (en) * | 2016-09-01 | 2021-03-01 | 日商日機裝股份有限公司 | Pulsationless pump |
| CN111983910A (en) * | 2019-05-23 | 2020-11-24 | Meco有限公司 | Push-button system and timepiece comprising such a push-button system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012013452A1 (en) | 2012-02-02 |
| CN103026048B (en) | 2015-12-16 |
| EP2598743A1 (en) | 2013-06-05 |
| JP2013532792A (en) | 2013-08-19 |
| DE102010038468A1 (en) | 2012-02-02 |
| EP2598743B1 (en) | 2014-11-05 |
| RU2568359C2 (en) | 2015-11-20 |
| JP6042809B2 (en) | 2016-12-14 |
| RU2013108357A (en) | 2014-09-10 |
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