EP2273115A1 - Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression - Google Patents

Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression Download PDF

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Publication number
EP2273115A1
EP2273115A1 EP10176791A EP10176791A EP2273115A1 EP 2273115 A1 EP2273115 A1 EP 2273115A1 EP 10176791 A EP10176791 A EP 10176791A EP 10176791 A EP10176791 A EP 10176791A EP 2273115 A1 EP2273115 A1 EP 2273115A1
Authority
EP
European Patent Office
Prior art keywords
housing
fluid pump
damper
pressure
pump
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
Application number
EP10176791A
Other languages
German (de)
English (en)
Other versions
EP2273115B1 (fr
Inventor
Klaus Lang
Peter Ropertz
Yasushi Ohno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2273115A1 publication Critical patent/EP2273115A1/fr
Application granted granted Critical
Publication of EP2273115B1 publication Critical patent/EP2273115B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041—Means for damping pressure pulsations
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047—Layout or arrangement of systems for feeding fuel

Definitions

  • the invention relates to a fluid pump, in particular high-pressure fuel pump, with a housing and with at least one inlet-side low-pressure connection, an inlet valve, and a delivery chamber which is delimited by a delivery element.
  • a fluid pump of the type mentioned is from the DE 195 39 885 A1 known and used for example in internal combustion engines with direct fuel injection.
  • the fuel from the fluid pump is compressed to a high pressure and conveyed into a fuel rail. From this, the fuel passes under high pressure via fuel injectors directly into the combustion chambers of the internal combustion engine.
  • the fluid pump sucks the fuel via a low pressure port and an inlet valve into a delivery chamber. This is limited by the delivery piston.
  • a pressure damper is arranged there. This includes a spring loaded piston defining a damping chamber connected to the fuel line via a bag port.
  • the EP 1 342 911 A2 shows a fuel pump with a pump housing, a reciprocating pump piston, a low pressure port, a high pressure port and a compression chamber.
  • a pressure damper is provided between the low pressure port and the compression space.
  • Object of the present invention is to provide a fluid pump of the type mentioned in such a way that on the one hand compact builds and that on the other hand, the upstream of the low-pressure connection arranged components, such as a low-pressure fuel line, are as little as possible.
  • a fluid pump of the type mentioned above comprises a pressure damper which damps inlet-side pressure fluctuations and which comprises at least one compressible volume, which is arranged directly in the flow path between low-pressure port and inlet valve.
  • the pressure damper has a damper housing with two axial end faces, wherein the damper housing is clamped between the housing body of the fluid pump and the housing cover, the installation is particularly simple and the reliability is significantly improved. Clamping the damper housing effectively prevents material fatigue in the damper and damper housing of the damper.
  • the arrangement of the compressible volume directly in the flow path between low pressure port and inlet valve has the advantage that Pump internal coupling vibrations are prevented, which then load the low pressure port and a low pressure line connected to this.
  • the reason for this is that the usual pressure fluctuations occur at the inlet valve itself when it is forcibly opened, for example, to control the flow rate of the fluid pump during a delivery stroke of the delivery piston.
  • the inventive arrangement of the compressible volume the pressure fluctuations are attenuated immediately at the place of their emergence.
  • cheaper components can be used for the low pressure port and the low pressure line, which reduces their cost.
  • otherwise required holes in the pump housing can be omitted.
  • the use of a compressible volume instead of the usual spring-loaded piston also has the advantage that it is easy to build and therefore the fluid pump is overall comparatively inexpensive.
  • the compressible volume is a gas volume which is delimited by at least one membrane.
  • the compressibility of gas allows a very simple construction of the corresponding pressure damper, which reduces the manufacturing cost of the fluid pump.
  • such a gas volume can be formed almost arbitrarily, so that it can be easily integrated into the area between the inlet valve and the low-pressure port of the fluid pump.
  • the compressible volume is received in an extension of the flow path, which by a Housing cover is covered.
  • the housing cover can be deep-drawn, for example, and screwed or welded to a corresponding counterpart of the pump housing.
  • the radial dimensions of the fluid pump are reduced when the housing cover is arranged on an axial end face of the pump housing.
  • a further reduction of the radial dimensions of the fluid pump is achieved in that the low-pressure connection is arranged on the housing cover.
  • a connection piece is used for the low pressure connection, which is welded to the housing cover or screwed to it.
  • the nozzle can be straight or angular, so that the same fluid pump can be easily adapted to different installation situations. In principle, any exit direction is possible.
  • a particularly advantageous embodiment of the fluid pump according to the invention provides that the pressure damper has a substantially rotationally symmetrical damper housing with two axial end faces, towards which, starting from an axial center plane, in whose area it has its maximum diameter, tapers, that it in each End face has at least one opening, and / or that in the housing walls between the two end faces and the center plane in each case at least one opening is present.
  • a damper housing thus has approximately discus-like shape.
  • the compressible volume can be easily absorbed and thereby have such large boundary surfaces that an effective damping of pressure pulsations is possible.
  • it builds in the axial direction short, what the dimensions of the Fluid pump benefits.
  • the installation of the pressure damper is simplified when the damper housing is jammed with its two end faces between a pump body and the housing cover. It is understood that to achieve reproducible balance of power damper housing should at least partially (for example, at least one housing half in a two-part housing) and in the clamping direction should have a certain spring elasticity.
  • the damper housing distributed over the circumference arranged and a total radially projecting centering sections which radially center the damper housing relative to the extension of the flow path.
  • the pressure damper can be used in the extension of the flow path and is then, after installation of the housing cover, automatically set in the installed position. This facilitates the assembly of the fluid pump.
  • the centering sections each have an end section extending approximately axially and somewhat beyond the median plane of the damper housing, on which the compressible volume is radially centered relative to the damper housing.
  • the centering sections are assigned a double function: they do not serve only the Centering of the damper housing relative to the extension of the flow path, but also for the radial centering of the compressible volume, which is accommodated in the damper housing. As a result, the assembly of the pressure damper itself is simplified.
  • a radially outer edge of the compressible volume at least partially rests against the wall of the extension of the flow path and is thus centered with respect to this.
  • the wall of the extension of the flow path for example, distributed over the circumference arranged impressions.
  • the damper housing comprises two housing halves and the compressible volume is clamped between the two housing halves. Again, this allows for easy assembly of the compressible volume within the damper housing without the need for additional fixtures. It is understood that the compressible volume is preferably clamped at its edge. Otherwise, the damper housing itself should at least partially (in a two-part housing, for example, a housing half) and in the axial direction have resilient properties, so as not to hinder the change in volume of the compressible volume.
  • a further advantageous embodiment of the fluid pump according to the invention is characterized in that the housing cover has a protuberance on which the low pressure port is arranged. By such a protuberance, the connection of a connecting piece of the low-pressure connection is facilitated. Likewise, a direct connection of the low pressure line is conceivable.
  • a fuel system carries the overall reference numeral 10. It comprises a fuel tank 12, from which a prefeed pump 14 conveys the fuel into a low-pressure line 16. This leads to a Low pressure port 18 of a high-pressure piston pump designed as a fluid pump 20, the FIG. 1 is indicated by a dashed line.
  • a high pressure port 22 of the high pressure piston pump 20 is connected to a fuel rail 24. This is also called “Rail”. In it, the compressed by the high-pressure piston pump 20 fuel is stored under high pressure. To the fuel manifold 24 a plurality of fuel injectors 26 are connected, which inject the fuel directly into each associated combustion chamber 28.
  • the fuel system 10 thus belongs to an internal combustion engine with direct fuel injection.
  • the inlet valve device 34 comprises on the one hand a spring-loaded check valve 40, which represents the actual inlet valve. Via an electromagnetic actuator 42, the inlet valve 40 can be forcibly brought into its open position. This is represented by the switching symbol 44. Between the low-pressure connection 18 and the inlet valve device 34, a pressure damper 48 is arranged in a flow path 46. Although this is from the hydraulic diagram of the FIG. 1 not apparent, the pressure damper 48 is not in a bag circuit, but as compressible volume disposed directly in the flow path 46 between the low pressure port 18 and inlet valve means 34. This will be further detailed below with reference to FIG. 2 be explained.
  • the delivery rate of the high pressure piston pump 20 can be adjusted.
  • the inlet valve 40 is brought into its forced open position 44 during a delivery stroke of the delivery piston 30.
  • the fuel is not discharged to the fuel rail 24 but back into the low-pressure passage 16 via the flow path 46.
  • the pressure pulsations that occur, inter alia, in the flow path 46 and in the low-pressure line 16 are smoothed by the pressure damper 48.
  • the high-pressure piston pump 20 comprises a housing 50, which comprises a housing body 52, a piston bushing 53, and a housing cover 54.
  • the housing cover 54 has a cylindrical shape with a peripheral wall 56 and a base 58. The free edge of the peripheral wall 56 is welded to the housing body 52.
  • the housing cover 54 forms in FIG. 2 the upper cover of the housing 50 and is so far as seen in the longitudinal direction of the delivery piston 30 disposed on an axial end face of the pump housing 50.
  • the low-pressure connection 18 is formed by an inlet connection, which is welded centrally to the base 58 of the housing cover 54.
  • a space 62 is limited, which, as will be shown below, an expanded portion of the flow path 46 from the inlet port 18 to the inlet valve 40 back out.
  • the high-pressure port 22 is formed by an outlet, which is welded to the housing body 52.
  • the pressure damper 48 is inserted into the extension 62. It comprises a rotationally symmetrical damper housing 66. This extends from an axial center plane 68, in the region of which it has its maximum diameter, to two end faces with a smaller diameter, in each of which an opening 70 is present (it should be noted that the pressure damper 48th is formed identically on both sides of the median plane 68, so for reasons of illustration, the reference numerals are entered only for one side). Also in one of the region of the median plane 68 to the end face conically tapered wall 72 of the damper housing 66 distributed over the circumference arranged openings 74 are present.
  • a compressible gas volume 76 between two substantially and generally parallel diaphragms 78a and 78b.
  • the damper housing 66 is in two parts with a top 66a and a bottom 66b. The edges of the two membranes 78a and 78b are clamped in the region of the median plane 68 between the two parts 66a and 66b of the damper housing 66.
  • the axial longitudinal extension of the damper housing 66 is slightly larger than the height of the extension 62. This leads to that in the in FIG. 2 shown installation position, the damper housing 66 is clamped between the housing cover 54 and the housing body 52. It lies in the FIG. 2 Upper opening 70 of the damper housing 66 exactly in the region of the inlet nozzle 18th
  • the gas volume 76 enclosed between the two diaphragms 78a and 78b which has the actual pressure damping task, lies directly in the flow path 46 of the fuel and is flowed around directly by it. If it comes, starting from the inlet valve 40, to a pressure surge, this can be smoothed by the pressure damper 48 before he can propagate through the inlet port 18 into the low pressure line 16.
  • FIG. 3 For example, that portion of an alternative embodiment of a high pressure piston pump 20 is shown in which the pressure damper 48 is disposed is.
  • the same reference numerals which have equivalent functions to elements and areas of the figures described above, the same reference numerals. They are not explained again in detail. Incidentally, this also applies to all subsequent figures.
  • the damper housing 66 has a plurality of centering sections 80 distributed over the circumference and projecting radially in total.
  • the centering sections 80 are formed by a radially outwardly extending extension of the conical wall 72. They each have an end section 82 extending approximately axially relative to the respective other housing half.
  • the radially outer side of the end portions 82 abuts against the inside of the peripheral wall 56 of the housing cover 54.
  • the end portions 82 extend slightly beyond the median plane 68.
  • the radially outer edges of the membranes 78a and 78b abut the radially inner side of the end portion 82.
  • FIG. 4 in addition to the housing cover 54 distributed over the circumference several impressions 86 may be present.
  • the radially outer edges of the membranes 78a and 78b can center directly opposite the housing cover 54.
  • FIG. 5 The area of the inlet nozzle 18 and the housing cover 54 of yet another embodiment of a high-pressure piston pump 20 is in FIG. 5 shown. It can be seen that in the housing cover 54, a protuberance 84 is present, with which the inlet port 18 is welded.
  • a further modified variant shows this FIG. 6 In this, a thread 86 is rolled into the inside of the protuberance 84, into which the inlet port 18 is screwed.

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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)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP10176791.1A 2003-10-01 2004-09-29 Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression Expired - Fee Related EP2273115B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10345725.9A DE10345725B4 (de) 2003-10-01 2003-10-01 Kraftstoff-Hochdruckpumpe
EP04787240A EP1671031B1 (fr) 2003-10-01 2004-09-29 Pompe a fluide, en particulier pompe a carburant haute pression

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP04787240A Division EP1671031B1 (fr) 2003-10-01 2004-09-29 Pompe a fluide, en particulier pompe a carburant haute pression
EP04787240.3 Division 2004-09-29

Publications (2)

Publication Number Publication Date
EP2273115A1 true EP2273115A1 (fr) 2011-01-12
EP2273115B1 EP2273115B1 (fr) 2014-04-16

Family

ID=34353249

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10176791.1A Expired - Fee Related EP2273115B1 (fr) 2003-10-01 2004-09-29 Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression
EP04787240A Expired - Fee Related EP1671031B1 (fr) 2003-10-01 2004-09-29 Pompe a fluide, en particulier pompe a carburant haute pression

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP04787240A Expired - Fee Related EP1671031B1 (fr) 2003-10-01 2004-09-29 Pompe a fluide, en particulier pompe a carburant haute pression

Country Status (4)

Country Link
EP (2) EP2273115B1 (fr)
JP (1) JP4235647B2 (fr)
DE (2) DE10345725B4 (fr)
WO (1) WO2005031161A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039955A1 (fr) * 2013-09-19 2015-03-26 Robert Bosch Gmbh Système de transport de fluide
WO2015090676A1 (fr) * 2013-12-17 2015-06-25 Delphi International Operations Luxembourg S.À R.L. Pompe à haute pression
EP3205873A4 (fr) * 2014-10-09 2018-04-18 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression

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JP4415884B2 (ja) 2005-03-11 2010-02-17 株式会社日立製作所 電磁駆動機構，電磁弁機構及び電磁駆動機構によって操作される吸入弁を備えた高圧燃料供給ポンプ，電磁弁機構を備えた高圧燃料供給ポンプ
JP4686501B2 (ja) 2007-05-21 2011-05-25 日立オートモティブシステムズ株式会社 液体脈動ダンパ機構、および液体脈動ダンパ機構を備えた高圧燃料供給ポンプ
JP5002523B2 (ja) 2008-04-25 2012-08-15 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
DE102008043217A1 (de) 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102010027858A1 (de) * 2010-04-16 2011-11-24 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102010064221A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Einspritzpumpe für ein Kraftstoffeinspritzsystem
JP5310748B2 (ja) * 2011-01-12 2013-10-09 トヨタ自動車株式会社 高圧ポンプ
US9109593B2 (en) 2011-08-23 2015-08-18 Denso Corporation High pressure pump
CN102562395A (zh) * 2011-12-30 2012-07-11 成都威特电喷有限责任公司 稳定电控高压油泵低压系统压力的电控高压油泵
DE102013207393A1 (de) * 2013-04-24 2014-10-30 Robert Bosch Gmbh Kolbenpumpe, insbesondere Hochdruckpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine
JP5923549B2 (ja) * 2014-05-20 2016-05-24 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ、及び高圧燃料供給ポンプの製造方法
JP6260478B2 (ja) * 2014-07-10 2018-01-17 株式会社デンソー 高圧ポンプ
JP6361337B2 (ja) * 2014-07-10 2018-07-25 株式会社デンソー 高圧ポンプ
JP2015017619A (ja) * 2014-10-27 2015-01-29 株式会社デンソー 高圧ポンプ
JP6012785B2 (ja) * 2015-01-30 2016-10-25 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
DE102015220870A1 (de) * 2015-10-26 2017-04-27 Robert Bosch Gmbh Hochdruckpumpe
DE102016200125B4 (de) 2016-01-08 2018-05-30 Continental Automotive Gmbh Kraftstoffhochdruckpumpe
DE102016203217B4 (de) * 2016-02-29 2020-12-10 Vitesco Technologies GmbH Dämpferkapsel, Druckpulsationsdämpfer und Kraftstoffhochdruckpumpe
DE102016205428A1 (de) 2016-04-01 2017-10-05 Robert Bosch Gmbh Druckdämpfungseinrichtung für eine Fluidpumpe, insbesondere für eine Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102016205427A1 (de) 2016-04-01 2017-10-05 Robert Bosch Gmbh Druckdämpfungseinrichtung für eine Fluidpumpe, insbesondere für eine Hochdruckpumpe eines Kraftstoffeinspritzsystems
JP6310026B2 (ja) * 2016-09-20 2018-04-11 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
JP6888408B2 (ja) 2017-05-11 2021-06-16 株式会社デンソー パルセーションダンパおよび燃料ポンプ装置
DE102017213891B3 (de) * 2017-08-09 2019-02-14 Continental Automotive Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
WO2019111692A1 (fr) * 2017-12-05 2019-06-13 日立オートモティブシステムズ株式会社 Pompe d'alimentation en carburant haute pression
KR102021892B1 (ko) * 2017-12-26 2019-09-18 (주)모토닉 엔진의 연료맥동 저감용 댐핑기구
JP6511559B2 (ja) * 2018-03-13 2019-05-15 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
DE102018212223A1 (de) * 2018-07-23 2020-01-23 Continental Automotive Gmbh Pumpe für ein Kraftfahrzeug
KR102417695B1 (ko) 2020-11-10 2022-07-07 주식회사 현대케피코 고압 연료펌프의 방사소음 저감을 위한 댐퍼스프링 구조

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EP2273115B1 (fr) 2014-04-16
JP4235647B2 (ja) 2009-03-11
WO2005031161A2 (fr) 2005-04-07
DE10345725A1 (de) 2005-04-21
EP1671031A2 (fr) 2006-06-21
DE10345725B4 (de) 2017-01-05
DE502004012379D1 (de) 2011-05-19
EP1671031B1 (fr) 2011-04-06
JP2006521487A (ja) 2006-09-21
WO2005031161A3 (fr) 2006-11-16

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