EP3014119B1 - Pumpe - Google Patents

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Publication number
EP3014119B1
EP3014119B1 EP14720619.7A EP14720619A EP3014119B1 EP 3014119 B1 EP3014119 B1 EP 3014119B1 EP 14720619 A EP14720619 A EP 14720619A EP 3014119 B1 EP3014119 B1 EP 3014119B1
Authority
EP
European Patent Office
Prior art keywords
pressure
low
piston
chamber
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.)
Not-in-force
Application number
EP14720619.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3014119A1 (de
Inventor
Achim Koehler
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 EP3014119A1 publication Critical patent/EP3014119A1/de
Application granted granted Critical
Publication of EP3014119B1 publication Critical patent/EP3014119B1/de
Not-in-force 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B11/0033—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to a pump, in particular a high-pressure pump for fuel injection systems or hydraulic applications. Specifically, the invention relates to the field of diesel pumps, gasoline pumps and hydraulic pumps.
  • the known high-pressure pump has a pump assembly and a drive shaft, wherein the drive shaft comprises a cam associated with the pump assembly.
  • the pump assembly includes a roller that rolls on a tread of the cam.
  • the drive shaft is mounted at bearings in housing parts of the high-pressure pump. During operation of the high-pressure pump, a reciprocating movement of a piston is achieved, so that the delivery of high-pressure fuel to a common rail takes place.
  • the drive shaft rotates about an axis.
  • a damping device which, on the one hand, is connected at least indirectly to the low-pressure space and, on the other hand, is connected to a low-pressure level which is below a pressure in the low-pressure space during operation.
  • the Damping device has a piston displaceable in a piston bore, which is acted upon on the one hand by the pressure in the low-pressure chamber against a spring force and on the other hand limits a space in the piston bore.
  • the damping device also has a discharge device which connects the space with the low pressure level.
  • the relief device is a line that connects the room with the low pressure level.
  • the volume flowed off to the low pressure level must be compensated for again by a corresponding delivery of fuel into the low pressure chamber.
  • a gas volume is arranged to be compensated by the pressure pulsations. Over the lifetime it is difficult to ensure the required seal between gas volume and fuel.
  • the pump according to the invention with the features of claim 1 has the advantage that an improved structure and improved operation are possible.
  • pressure pulsations generated in the low-pressure space can be effectively damped, since during the movement of the piston of the damping device, a vapor volume is forced, which is available as a damping volume.
  • the throttle is in this case advantageously adjusted depending on a pulsation frequency and a pulsation amplitude and the low pressure level after the throttle so that when expanding the steam chamber as large a vapor volume is generated, the re-immersion of the piston until complete condensation of the steam as a damping volume Is available without a renewed volume displacement takes place.
  • a piston leakage can be removed via the check valve and by the check valve, a vapor volume is enforced, which is available as a damping volume.
  • the pump can in particular be configured as a high-pressure pump, which serves for conveying a fluid, in particular fuel, with high pressure.
  • the high pressure pump may be integrated with a fuel injection system or other hydraulic system.
  • a low-pressure circuit can be formed, which runs over the low-pressure chamber of the pump.
  • the low-pressure space can in this case be designed as an engine room of the pump, the drive being arranged at least partially in the low-pressure space designed as an engine compartment.
  • lubrication of the drive can be achieved via the low-pressure circuit at the same time.
  • Pressure pulsations, which are generated by the drive in the engine room designed as the low-pressure space of the pump are then preferably already damped within the housing of the pump by the at least one damping device.
  • the fluid, in particular the fuel can be guided in an advantageous manner via the low-pressure space at least indirectly to a pump working space of a pump assembly.
  • the low-pressure space may in particular be the engine room.
  • the pump has a plurality of pump assemblies and correspondingly a plurality of pump working chambers, to which the fluid, in particular the fuel, is led via the low-pressure chamber.
  • the throttle of the relief device opens radially into the piston bore.
  • the piston bore can be closed by a suitable closure element.
  • low low pressure level are kept, with which the vapor space is connected via the throttle.
  • a closure element is arranged, that the vapor space between the piston and the closure element is formed in the piston bore and that the throttle of the relief device is integrated into the closure element. In this way, the access required for the piston bore can be used at the same time to maintain the low pressure level.
  • the piston bore is arranged in a housing, that a low-pressure channel is formed in the housing, which opens into the vapor space of the piston bore, and that the check valve is arranged in the low-pressure channel.
  • a low-pressure channel is formed in the housing, which opens into the vapor space of the piston bore, and that the check valve is arranged in the low-pressure channel.
  • a spring element is arranged in the vapor space, which acts on the piston with the spring force.
  • the steam space can thus serve as a spring chamber at the same time.
  • the spring element can be pressurized by the piston in this case.
  • the piston may also be suitably connected to the spring element to urge the piston both on pressure and on train.
  • the piston is guided in the piston bore such that a leakage flow from the low-pressure space into the vapor space is made possible between the piston and the piston bore.
  • a lubrication of the piston guide is realized in the piston bore.
  • a Nachpound of fluid, in particular fuel is realized in the vapor space.
  • the leakage is then removed via the throttle or the check valve to the low pressure level. Thus, a maintenance-free operation is possible.
  • Fig. 1 shows a high pressure pump 1 of a fuel injection system 2 with a low pressure circuit 3 in a schematic representation according to a first embodiment.
  • the high-pressure pump 1 can be used in particular for air-compressing, self-igniting internal combustion engines or mixture-compressing, spark-ignited internal combustion engines. Furthermore, the high-pressure pump 1 can also be designed as a hydraulic pump for other hydraulic applications.
  • the high-pressure pump 1 has a low-pressure chamber 4 and a drive 5. In this case 5 pressure pulsations in the low-pressure space 4 are generated in operation by the drive.
  • the low-pressure space 4 is formed by an engine room, in which an axis 6 with a multiple cam 7 at least partially arranged is.
  • the multiple cam 7 of the axis 6 is used to drive a pump piston 8 of a pump assembly 9 of the high pressure pump 1.
  • a part of a cylinder head 10 is shown schematically, in which a cylinder bore 11 is configured.
  • the pump piston 8 is guided in the cylinder bore 11.
  • the actuation of the pump piston 8 by the multiple cam 7 is illustrated by a double arrow 12.
  • a metering unit 13 is provided, is guided over the operating at low pressure fuel in a pump working chamber 14.
  • the pump working chamber 14 is in this case limited by the pump piston 8 in the cylinder bore 11.
  • the high-pressure fuel is conducted via an outlet valve 15, for example, to a common rail.
  • the low-pressure circuit 3 comprises a tank 20 and a prefeed pump 21, which may be configured, for example, as an electric fuel pump 21.
  • a prefeed pump 21 By the prefeed pump 21, the fuel from the tank 20 is conveyed via a filter device 22 in the low-pressure chamber 4.
  • the filter device 22 comprises a filter and optionally also a water separator.
  • part of the fuel is led via a housing bearing 23 and a flange bearing 24 to a low-pressure level 25.
  • the axis 6 is mounted with the multiple cam 7.
  • the housing bearing 23 and the flange bearing 24 are hereby illustrated by throttles 23, 24, since they act as throttles.
  • a pressure p 1 prevails.
  • the low pressure level 25 has a pressure p 2 which is smaller than the pressure p 1 .
  • a device 26 can optionally be provided.
  • the pressure p 2 for example, be held slightly above the optionally pressure-relieved tank 20.
  • the device 26 may for example have a throttle or other low pressure limit.
  • the device 26 may also be omitted. Especially can already by the length of a return line 27, which leads from the low pressure level 25 to the tank 20, the desired low pressure p 2 in the low pressure level 25 can be achieved.
  • the high-pressure pump 1 has a damping device 30. Depending on the design of the high pressure pump 1, a plurality of such damping devices 30 may be provided.
  • the damping device 30 is connected on the one hand by means of a line 31 to the low pressure chamber 4 and on the other hand connected to the low pressure level 25.
  • the low pressure level 25 is at its pressure p 2 under the pressure p 1 in the low pressure space 4.
  • the damping device 30 in this embodiment, a piston 32, which serves as a compensating piston 32.
  • the piston 32 is guided displaceably in a piston bore 33.
  • the piston 32 divides the piston bore 33 into a vapor space 34 and a space 35.
  • the vapor space 34 serves at the same time as a spring space 34, in which a spring element 36 is arranged, which is designed, for example, as a spiral spring 36.
  • the damping device 30 also has a relief device 37, which connects the vapor space 34 with the low pressure level 25.
  • the relief device 37 includes a check valve 38.
  • the check valve 38 opens in this case to the low pressure level 25 back.
  • the fuel flow in the low-pressure circuit 3 is illustrated by arrows.
  • the piston 32 is guided in the piston bore 32 in such a way that a leakage flow from the space 35 connected to the low-pressure space 4 into the vapor space 34 is made possible between the piston 32 and the piston bore 33.
  • the leakage is in this case discharged via the check valve 38 to the low pressure level 25 during operation.
  • Fig. 2 shows a partial, schematic sectional view of the in Fig. 1 illustrated high-pressure pump 1 according to a second embodiment.
  • a housing part 45 is shown, which is part of a housing 46 of the high pressure pump 1, in which the low-pressure chamber 4 is configured.
  • the housing part 45 may also be the cylinder head 10.
  • a tubular sleeve 47 is inserted into the housing part 45, in which the piston bore 33 is configured.
  • a closure element 48 is inserted into the sleeve 47, which closes the piston bore 33 to an outer side 49 of the housing part 45 through.
  • the vapor space 34 is formed between the piston 32 and the closure member 48 in the piston bore 33.
  • a channel 50 is formed, which extends to the sleeve 47.
  • the low pressure level 25 with the pressure p 2 is in this case realized in the channel 50.
  • the relief device 37 has a throttle 51, which opens radially into the piston bore 33.
  • the throttle 51 is configured in the sleeve 47 in this embodiment. In this case, the throttle 51 connects the vapor space 34 with the channel 50.
  • the throttle effect of the throttle 51 is set so strong that at a pressure reduction in the low-pressure chamber 4, which is caused by a pressure pulsation and an adjustment of the piston 32 with the spring force of the spring element 36 allows up to a provision of the piston 32, by the of caused the pressure pulsation following increase in pressure in the low-pressure chamber 4 is carried out, temporarily a vapor volume is generated in the vapor space 34.
  • the damping device 30 can be tuned in particular by the spring element 36 and the throttle 51.
  • the throttling effect of the throttle 51 in response to a pulsation frequency and a pulsation amplitude and the low pressure level 25 with the pressure p 2 after the throttle 51 are tuned so that when expanding the spring element 36 as large a vapor volume is generated in the vapor space 34, the upon re-immersion of the piston 32 until complete condensation of the vapor is available as a damping volume, without a renewed volume displacement takes place.
  • Fig. 3 shows a partial, schematic sectional view of the in Fig. 1 illustrated high-pressure pump 1 according to a third embodiment.
  • the closure element 48 has a through hole 52.
  • the through hole 52 may be formed at least in sections with a sufficiently small diameter to form the throttle 51.
  • the throttle 51 can be integrated into the closure element 48.
  • the low pressure level 25 can be ensured with the pressure p 2 .
  • Fig. 4 shows a partial, schematic sectional view of the in Fig. 1 illustrated high pressure pump 1 according to a fourth embodiment.
  • the damping device 30 has a part 54 which is designed as a screw or plug-in part 54 and is screwed or inserted into the housing part 45.
  • the part 54 has a tubular portion 55 in which the piston bore 33 is formed.
  • the tubular portion 55 of the part 54 is sealed with respect to the housing part 55 with a sealing ring 56.
  • the closure element 48 is arranged in the piston bore 33 of the tubular portion 55. Furthermore, a further closure element 57 is provided, which closes the piston bore 33 from the environment. Between the further closure element 57 and the closure element 48, the low pressure level 25 is predetermined in a gap 58.
  • the gap 58 is suitably connected to the return line 27.
  • the check valve 38 is integrated into the closure element 48.
  • the check valve 38 enables a fuel flow from the vapor space 34 into the gap 58.
  • the leakage which enters the vapor space 34 due to the leakage flow between the piston 32 and the piston bore 33, are led to the return line 37.
  • Fig. 5 shows a partial, schematic sectional view of the in Fig. 1 illustrated high-pressure pump 1 according to a fifth embodiment.
  • the piston bore 33 of the part 54 is closed by the closure member 48 from the environment.
  • the tubular portion 55 has at least one radial connecting hole 59, 60, wherein in this embodiment, a plurality of radial connecting holes 59, 60 are provided.
  • the housing part 45 of the channel 50 is configured.
  • the channel 50 can be configured for example by a housing bore 50 in the housing part 45.
  • the check valve 38 is arranged in the channel 50.
  • the vapor space 34 is connected to the low pressure level 25 via the radial communication bores 59, 60 and the check valve 38.
  • Fig. 6 shows a diagram for explaining the operation of the high-pressure pump 1 according to a possible embodiment of the invention.
  • the time t is plotted on the abscissa, while the pressure p is plotted on the ordinate.
  • the pressure p results here from the pressure p 1 in the low pressure chamber 4 plus the pressure fluctuations caused by pressure pulsations.
  • the pressure pulsations are caused by the drive 5.
  • One possible pressure pulsation is illustrated by curve 61.
  • the pressure fluctuations represented by the curve 61 are effectively damped by the damping device 30. As a result, such pressure fluctuations do not affect the remaining low-pressure circuit 3.
  • the functionality of the metering unit 13 is ensured.

Landscapes

  • 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)
EP14720619.7A 2013-06-25 2014-04-30 Pumpe Not-in-force EP3014119B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013212145.8A DE102013212145A1 (de) 2013-06-25 2013-06-25 Pumpe
PCT/EP2014/058921 WO2014206607A1 (de) 2013-06-25 2014-04-30 Pumpe

Publications (2)

Publication Number Publication Date
EP3014119A1 EP3014119A1 (de) 2016-05-04
EP3014119B1 true EP3014119B1 (de) 2017-04-12

Family

ID=50628831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14720619.7A Not-in-force EP3014119B1 (de) 2013-06-25 2014-04-30 Pumpe

Country Status (6)

Country Link
EP (1) EP3014119B1 (ja)
JP (1) JP6356230B2 (ja)
KR (1) KR102139713B1 (ja)
CN (1) CN105339659B (ja)
DE (1) DE102013212145A1 (ja)
WO (1) WO2014206607A1 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109312790B (zh) * 2016-06-22 2021-11-05 日本电产东测有限公司 离合器控制装置
DE102017212003A1 (de) * 2016-09-16 2018-03-22 Robert Bosch Gmbh Überströmventil, insbesondere zur Verwendung in einem Kraftstoffeinspritzsystem, Hochdruckpumpe sowie Kraftstoffeinspritzsystem
DE102016219486A1 (de) * 2016-10-07 2018-04-12 Robert Bosch Gmbh Drosselelement, insbesondere für eine Hochdruckpumpe, insbesondere eines Niederdruckkreis eines Kraftstoffeinspritzsystems

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3212384B2 (ja) * 1992-11-11 2001-09-25 株式会社ニチリン アキュムレータ
DE10260750A1 (de) * 2002-12-23 2004-07-08 Robert Bosch Gmbh Kraftstoffpumpvorrichtung
JP4148861B2 (ja) * 2003-09-19 2008-09-10 臼井国際産業株式会社 フューエルデリバリパイプ
DE102005037537A1 (de) * 2005-08-09 2007-02-15 Robert Bosch Gmbh Kolbenpumpe mit wenigstens einem Kolbenelement
DE102009003054A1 (de) 2009-05-13 2010-11-18 Robert Bosch Gmbh Hochdruckpumpe
DE102009027335A1 (de) * 2009-06-30 2011-01-05 Robert Bosch Gmbh Kraftstoffsystem für eine Brennkraftmaschine
DE102010043439A1 (de) * 2010-11-05 2012-05-10 Robert Bosch Gmbh Kraftstoffeinspritzsystem einer Brennkraftmaschine
DE102010064185A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE102011006092A1 (de) * 2011-03-25 2012-09-27 Robert Bosch Gmbh Hochdruckpumpe zur Förderung von Kraftstoff sowie Kraftstoffeinspritzsystem
DE102011007352A1 (de) * 2011-04-14 2012-10-18 Robert Bosch Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem einer Brennkraftmaschine
CN102536780A (zh) * 2012-02-28 2012-07-04 浙江大学 基于rc滤波器原理的脉动衰减柱塞泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
DE102013212145A1 (de) 2015-01-08
CN105339659B (zh) 2018-02-23
JP6356230B2 (ja) 2018-07-11
JP2016524675A (ja) 2016-08-18
CN105339659A (zh) 2016-02-17
KR20160022831A (ko) 2016-03-02
WO2014206607A1 (de) 2014-12-31
EP3014119A1 (de) 2016-05-04
KR102139713B1 (ko) 2020-07-30

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