WO2012143601A1 - Système de fluide et moteur à combustion interne - Google Patents

Système de fluide et moteur à combustion interne Download PDF

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Publication number
WO2012143601A1
WO2012143601A1 PCT/FI2012/050205 FI2012050205W WO2012143601A1 WO 2012143601 A1 WO2012143601 A1 WO 2012143601A1 FI 2012050205 W FI2012050205 W FI 2012050205W WO 2012143601 A1 WO2012143601 A1 WO 2012143601A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
fluid
circuit
chamber
intensifier
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.)
Ceased
Application number
PCT/FI2012/050205
Other languages
English (en)
Inventor
Ilari Kallio
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.)
Wartsila Finland Oy
Original Assignee
Wartsila Finland Oy
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 Wartsila Finland Oy filed Critical Wartsila Finland Oy
Priority to KR1020137030768A priority Critical patent/KR101751674B1/ko
Priority to CN201280019022.1A priority patent/CN103518058B/zh
Priority to EP12712285.1A priority patent/EP2699789B1/fr
Publication of WO2012143601A1 publication Critical patent/WO2012143601A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F02D11/08—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the pneumatic type
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/08—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of non-mechanically driven auxiliary apparatus
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/105—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 hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers

Definitions

  • the present invention relates to a fluid system for an internal combustion engine according to the preamble of claim 1.
  • the invention also concerns an internal combustion engine in accordance with the preamble of the other independent claim.
  • the object of the present invention is to provide an improved fluid system for an internal combustion engine.
  • the fluid system comprises at least a first fluid circuit and a second fluid circuit, each of the fluid circuits forming part of a subsystem of an internal combustion engine.
  • the characterizing features of the fluid system according to the invention are given in the characterizing part of claim 1.
  • Another object of the invention is to provide an improved internal combustion engine.
  • the internal combustion engine is characterized by a fluid system according to the present invention.
  • a fluid system according to the present invention comprises a pressure intensification arrangement comprising at least one pressure intensifier and having at least two alternative intensification ratios.
  • some of the fluid circuits can be provided with a low-pressure pump instead of a high-pressure pump, which also helps to reduce costs of the system. Because of the simple construction of pressure intensifiers, the reliability of the system is improved.
  • the invention also enables adjustment of the volume flow in the second circuit by controlling the operating frequency of the pressure intensifiers.
  • a pressure intensification arrangement with at least two alternative intensification ratios enables the use of the invention for fluid circuits with varying pressure requirements.
  • the first fluid circuit can be, for instance, a hydraulic circuit operating gas exchange valves of the engine, or a lubricating oil circuit of the engine.
  • the second fluid circuit can be, for instance, a hydraulic circuit operating fuel injectors of the engine, or a hydraulic circuit operating means for pressurizing fuel.
  • the fluid system can comprise two pressure intensifiers with different intensification ratios.
  • Another option is to provide the pressure intensification arrangement with a pressure intensifier having at least two intensification ratios.
  • the pump can be a variable displacement pump enabling variable output pressures and flows.
  • the pressure intensifiers can be activated and deactivated for example by using electrically controllable means.
  • each pressure intensifier comprises a first chamber and a second chamber. At least one of the first chambers of the pressure intensifiers in the system is in fluid communication with the first fluid circuit and at least one of the second chambers is in fluid communication with the second fluid circuit.
  • Each of the pressure intensifiers further comprises a reciprocating plunger having a first pressure surface in the first chamber and a second pressure surface in the second chamber, the area of the second pressure surface being smaller than the area of the first pressure surface.
  • the pressure intensifiers are connected in parallel so that the first chamber of each pressure intensifier is in flow communication with the first fluid circuit and the second chamber of each pressure intensifi- er is in flow communication with the second fluid circuit.
  • the second fluid circuit can be operated with constant pressure. While one of the pressure intensifiers pressurizes fluid in the second fluid circuit, other pressure intensifiers can be reloaded.
  • the redundancy of pressure intensifiers also improves the reliability and safety of the system, which is important especially in marine applications.
  • the system comprises means for selectively connecting a first pressure intensifier and a second pressure intensifier in parallel or in series.
  • first chamber of the first pressure intensi- bomb is in flow communication with the first fluid circuit
  • second chamber of the first pressure intensifier is in flow communication with the first chamber of the second pressure intensifier
  • the second chamber of the second pressure intensifier is in flow communication with the second fluid circuit.
  • Fig. 1 shows schematically the main parts of the fluid system.
  • Fig. 2 shows a fluid system according to an embodiment of the invention.
  • Fig. 3 shows a fluid system according to another embodiment of the invention.
  • Fig. 4 shows a simplified illustration of a piston-type pressure intensifier.
  • FIG 1 is shown schematically the main parts of the fluid system according to the invention.
  • the fluid system comprises a first fluid circuit 1 and a second fluid circuit 2.
  • the fluid circuits 1, 2 are part of subsystems of a large internal combustion engine and work within different pressure ranges.
  • the engine can be for instance a main or an auxiliary engine of a ship.
  • the first fluid circuit 1 can be for example part of the lubrication oil system of the engine, or a hydraulic circuit operating gas exchange valves of the en- gine.
  • the second fluid circuit 2 can be for example a hydraulic circuit that is used for operating fuel injectors of the engine or for pressurizing the fuel to be injected. In general, the required pressure level in the second fluid circuit 2 is higher than in the first fluid circuit 1.
  • the pressure in the first fluid circuit 1 can be for example in the range between 200 and 350 bar. If the second fluid circuit 2 is used for pressurizing fuel, the pressure in the second fluid circuit 2 can be for example in the range between 250 and 700 bar.
  • the fluid system comprises a pump 3 for supplying pressurized fluid into the system.
  • the same pump 3 is used for supplying fluid into the first fluid circuit 1 through a first fluid supply line 20, and into the second fluid circuit 2 through a second fluid supply line 21.
  • the second fluid supply line 21 is provided with a check valve 24 for protecting the pump 3 and the first fluid circuit 1 from the higher pressure of the second fluid circuit 2.
  • the pump 3 is a variable displacement pump that is capable of supplying fluid at different pressures and flow rates. From the first fluid circuit 1, the fluid is returned to the tank 5 through a first return line 22, and from the second fluid circuit 2 through a second return line 23.
  • the fluid system is provided with a pressure intensification arrangement 4.
  • the pressure intensification arrangement 4 is constructed so that at least two different pressure intensification ratios can be selected. Different intensification ratios can be achieved by different means.
  • the pressure intensification arrangement is provided with at least two pressure intensifiers. If the pressure intensifiers have different intensification ratios, the desired intensification ratio can be selected by using the pressure intensifier that is most suitable for those operating conditions. It is also possible that different combinations of the pressure intensifiers are used. For instance, for smaller amplification, only one of the pressure intensifiers is used. When greater amplification is needed, the pres- sure intensifiers can be connected in series.
  • the pressure intensification arrangement 4 can also comprise a single pressure intensifier with at least two different intensification ratios.
  • the first fluid circuit 1 is arranged to operate gas exchange valves 14 of the engine and the second fluid circuit 2 is arranged to operate means 15 for pressurizing the fuel that is injected into the engine.
  • the pressure intensification arrangement 4 comprises three pressure intensifiers 6, 7, 8.
  • a first pressure intensifier 6 and a second pressure intensifier 7 are connected in parallel.
  • a first control valve 9 is located between the first fluid circuit 1 and the first pressure intensifier 6, and a second control valve 10 is located between the first fluid circuit 1 and the second pressure intensifier 7.
  • the first control valve 9 is arranged to open and close the fluid communication between the first fluid circuit 1 and the first pressure intensifier 6.
  • the second control valve 10 is arranged to open and close the fluid communication between the first fluid circuit 1 and the second pressure intensifier 7.
  • the first pressure intensifier 6 and the second pressure intensifier 7 have different intensification ratios. This enables different pressure amplification according to the required pressure level in the second fluid circuit 2.
  • a third pressure intensifier 8 is arranged between the first and second pressure intensifiers 6, 7 and the second fluid circuit 2.
  • a third control valve 11 is ar- ranged to open and close flow communication between the first and second pressure intensifiers 6, 7 and the third pressure intensifier 8.
  • the control valves 9, 10, 11 are solenoid valves. Since the control valves 9, 10, 11 can be used to prevent fluid flow from the first fluid circuit 1 to the second fluid circuit 2, they can be used as means for activating and deactivating the pressure intensifiers 6, 7, 8.
  • FIG 4 is shown an example of a suitable pressure intensifier 6, 7, 8.
  • the pressure intensifier 6, 7, 8 comprises a reciprocating plunger 17 having a first pressure surface Al and a second pressure surface A2.
  • the plunger 17 is moved. Consequently, fluid in a se- cond chamber 19 of the pressure intensifier 6, 7, 8 is pressurized.
  • the intensification ratio of the pressure intensifier 6, 7, 8 depends on the ratio between the areas of the first pressure surface Al and the second pressure surface A2.
  • a drain valve 25, 26, 27 is arranged between each control valve 9, 10, 11 and pressure intensifier 6, 7, 8.
  • each pressure intensifier 6, 7, 8 can be emptied to the tank 5 for re- loading the pressure intensifier 6, 7, 8.
  • the duct connecting the second chamber 19 of each pressure intensifier 6, 7, 8 with the respective control valve 9, 10, 11 is provided with a first check valve 28 for allowing filling of the second chamber 18 when the pressure intensifier 6, 7, 8 is reloaded, but preventing the pressurized fluid from flowing to the wrong direction.
  • the duct through which the pressurized fluid flows from each pres- sure intensifier 6, 7, 8 to the second fluid circuit 2 or to the third pressure intensifier 8 is provided with a second check valve 29 for preventing flow from the second fluid circuit 2 or from the third pressure intensifier 8 to the respective pressure intensifier 6, 7, 8.
  • a fourth control valve 12 is arranged to open and close the flow communication be- tween the first and the second pressure intensifier 6, 7 and the second fluid circuit 2.
  • the third pressure intensifier 8 can be either bypassed or connected in series with either the first pressure intensifier 6 or the second pressure intensifier 7. If the third pressure intensifier 8 is by-passed, the total intensification ratio of the pressure intensification arrangement 4 is the same as that of the pres- sure intensifier 6, 7 that is used in the first pressure intensification stage. If the third pressure intensifier 8 is connected in series with the first or the second pressure intensifier 6, 7, the total intensification ratio is the product of the intensification ratios in the first and the second stages. Thus, with the pressure intensification arrangement according to the embodiment of figure 2, four different intensification ratios can be achieved. All the control valves 9, 10, 11, 12 and the drain valves 25, 26, 27 can be electrically controlled.
  • the pressure intensification arrangement 4 is provided with a first pressure intensifier 6 and a second pressure intensifier 7.
  • the pressure inten- sifters 6, 7 can be selectively connected in parallel or in series.
  • a first control valve 9 and a second control valve 10 can be used to choose which one of the first and the second pressure intensifiers 6, 7 is used for increasing pressure in the second fluid circuit 2.
  • a third control valve 1 1 and a fourth control valve 12 are used for controlling whether the first pressure intensifier 6 is used alone or together with the second pressure intensifier 7.
  • the control valves 9, 10, 11, 12 work thus as means for selectively connecting the pressure intensifiers 6, 7, 8 in parallel or in series. If the third control valve 11 is closed and the fourth control valve 12 is open, the first pressure intensifier 6 and the second pressure intensifier 7 are connected in series. The fluid from the second chamber 19 of the first pressure intensifier 6 flows into the first chamber 18 of the second pressure intensifier 7. The total intensification ratio of the pressure inten- sification arrangement 4 is thus the product of the intensification ratios of the two pressure intensifiers 6, 7. If the intensification ratios of the first and the second pressure intensifiers 6, 7 are different, three different intensification ratios can be achieved with the pressure intensification arrangement 4.
  • the pressure intensifiers 6, 7 are provided with drain valves 25, 26 enabling reloading of the pressure intensi- flers 6, 7, and with check valves 28, 29 for guiding the pressurized fluid to the right direction.
  • the pressure intensification arrangement 4 could also comprise more than two intensification stages. For instance, three pressure intensifiers could be arranged so that the pressure intensifiers can be selectively connected in parallel, all three pressure intensifiers in series, or any combination of two pressure intensifiers in series.
  • the fluid system can be provided with more than two fluid circuits.
  • the additional fluid circuits can have the same or different pressure level than the first and second fluid circuits.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Abstract

L'invention porte sur un système de fluide pour moteur à combustion interne qui comprend au moins un premier circuit de fluide (1) et un second circuit de fluide (2), chacun des circuits de fluide (1, 2) faisant partie d'un sous-système d'un moteur à combustion interne. Le système de fluide comprend en outre une pompe (3) servant à introduire un fluide dans le système, et un dispositif d'amplification de pression (4) qui comprend au moins un amplificateur de pression (6, 7, 8) et ayant au moins deux rapports d'amplification au choix.
PCT/FI2012/050205 2011-04-21 2012-03-01 Système de fluide et moteur à combustion interne Ceased WO2012143601A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020137030768A KR101751674B1 (ko) 2011-04-21 2012-03-01 유체 시스템 및 내연 엔진
CN201280019022.1A CN103518058B (zh) 2011-04-21 2012-03-01 流体系统及内燃机
EP12712285.1A EP2699789B1 (fr) 2011-04-21 2012-03-01 Système de fluide et moteur à combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20115391 2011-04-21
FI20115391A FI20115391A0 (fi) 2011-04-21 2011-04-21 Fluidijärjestelmä ja polttomoottori

Publications (1)

Publication Number Publication Date
WO2012143601A1 true WO2012143601A1 (fr) 2012-10-26

Family

ID=43919710

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FI2012/050205 Ceased WO2012143601A1 (fr) 2011-04-21 2012-03-01 Système de fluide et moteur à combustion interne

Country Status (5)

Country Link
EP (1) EP2699789B1 (fr)
KR (1) KR101751674B1 (fr)
CN (1) CN103518058B (fr)
FI (1) FI20115391A0 (fr)
WO (1) WO2012143601A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2784331B1 (fr) * 2013-03-25 2021-08-11 miniBOOSTER HYDRAULICS A/S Système hydraulique
CN117605719A (zh) * 2023-11-21 2024-02-27 佛山市康思达液压机械有限公司 一种串联式液压增压系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2198081A (en) * 1986-11-25 1988-06-08 Rexroth Mannesmann Gmbh Arrangement for producing high hydraulic pressures
DE10024268A1 (de) * 2000-05-17 2001-11-22 Bosch Gmbh Robert Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
DE102006034242A1 (de) * 2006-07-21 2008-01-31 Ricardo Deutschland Gmbh Vorrichtung zum Einspritzen von Kraftstoff und zur Betätigung eines Gaswechselventils

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010029691B4 (de) * 2010-06-03 2012-02-16 Mtu Friedrichshafen Gmbh Brennkraftmaschine und Ladefluid-Kühler

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2198081A (en) * 1986-11-25 1988-06-08 Rexroth Mannesmann Gmbh Arrangement for producing high hydraulic pressures
DE10024268A1 (de) * 2000-05-17 2001-11-22 Bosch Gmbh Robert Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
DE102006034242A1 (de) * 2006-07-21 2008-01-31 Ricardo Deutschland Gmbh Vorrichtung zum Einspritzen von Kraftstoff und zur Betätigung eines Gaswechselventils

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2784331B1 (fr) * 2013-03-25 2021-08-11 miniBOOSTER HYDRAULICS A/S Système hydraulique
CN117605719A (zh) * 2023-11-21 2024-02-27 佛山市康思达液压机械有限公司 一种串联式液压增压系统
CN117605719B (zh) * 2023-11-21 2024-10-15 佛山市康思达液压机械有限公司 一种串联式液压增压系统

Also Published As

Publication number Publication date
FI20115391A0 (fi) 2011-04-21
KR101751674B1 (ko) 2017-06-28
EP2699789B1 (fr) 2015-07-15
CN103518058A (zh) 2014-01-15
KR20140025478A (ko) 2014-03-04
CN103518058B (zh) 2016-03-16
EP2699789A1 (fr) 2014-02-26

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