EP2699789B1 - Fluid system and internal combustion engine - Google Patents

Fluid system and internal combustion engine Download PDF

Info

Publication number
EP2699789B1
EP2699789B1 EP12712285.1A EP12712285A EP2699789B1 EP 2699789 B1 EP2699789 B1 EP 2699789B1 EP 12712285 A EP12712285 A EP 12712285A EP 2699789 B1 EP2699789 B1 EP 2699789B1
Authority
EP
European Patent Office
Prior art keywords
pressure
fluid
circuit
chamber
fluid circuit
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.)
Active
Application number
EP12712285.1A
Other languages
German (de)
French (fr)
Other versions
EP2699789A1 (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
Publication of EP2699789A1 publication Critical patent/EP2699789A1/en
Application granted granted Critical
Publication of EP2699789B1 publication Critical patent/EP2699789B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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.
  • the invention has several advantages. Since a single pump can be used to supply fluid to several fluid circuits, the total number of pumps in the engine can be reduced. Alternatively, or in addition, 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 intensifier 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 intensifier 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 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 engine.
  • 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 pressure 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 arranged 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 A1 and a second pressure surface A2.
  • the plunger 17 is moved. Consequently, fluid in a second 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 A1 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.
  • 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 pressure 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 between the first and the second pressure intensifier 6, 7 and the second fluid circuit 2.
  • the third pressure intensifier 8 can be either by-passed 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 pressure 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.
  • 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 intensifiers 6, 7 can be selectively connected in parallel or in series. The functioning of this embodiment is described with reference to figures 3 and 4 .
  • 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. When the first control valve 9 is open and the second control valve 10 is closed, the first pressure intensifier 6 is in use.
  • a third control valve 11 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 intensification 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 intensifiers 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.

Description

    Technical field of the invention
  • 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.
  • Such system is disclosed in DE 10024268 .
    • Background of the invention
  • Large reciprocating engines typically have several hydraulically operated systems for different purposes, such as lubrication, fuel injection and actuation of the gas exchange valves. Often there are one or more pumps for each of these systems. Alternatively, a high-pressure pump is used to supply hydraulic fluid to the different systems at high pressure and pressure reducing devices are used to reduce the pressure to the required lower pressure level in each system. In many applications, for instance in fuel injection systems, where the fuel pressure is increased or where the injection event is controlled with a separate hydraulic circuit, the hydraulic pressure and flow needs to be adjusted according to the operating conditions, such as the load and speed of the engine. The need for different pressure levels and/or flow rates leads to complicated systems with multiple pumps and/or to poor energy efficiency in the systems. A further disadvantage of prior art systems is that high-pressure pumps with adjustable flow capacity and/or pressure are expensive.
    • Summary of the invention
  • 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.
  • The invention has several advantages. Since a single pump can be used to supply fluid to several fluid circuits, the total number of pumps in the engine can be reduced. Alternatively, or in addition, 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. There are different ways to implement the different intensification ratios. For instance, 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.
  • According to an embodiment of the invention, 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.
  • According to another embodiment of the invention, 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 intensifier is in flow communication with the second fluid circuit. With two or more pressure intensifiers connected in parallel, 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.
  • According to another embodiment of the invention, the system comprises means for selectively connecting a first pressure intensifier and a second pressure intensifier in parallel or in series. In a series connection, the first chamber of the first pressure intensifier is in flow communication with the first fluid circuit, the second chamber of the first pressure intensifier is in flow communication with the first chamber of the second pressure intensifier, and the second chamber of the second pressure intensifier is in flow communication with the second fluid circuit. With this arrangement, different intensification ratios can be selected according to the need.
    • Brief description of the drawings
    • 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.
    Detailed description of the invention
  • Embodiments of the invention are now described in more detail with reference to the accompanying drawings.
  • In figure 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 engine. 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. If the first fluid circuit 1 operates gas exchange valves of the engine, 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. In the embodiment of figure 1, 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.
  • For increasing the pressure in the second fluid circuit 2, the fluid system is provided with a pressure intensification arrangement 4. To meet the variable pressure requirements in the second fluid circuit 2, 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. According to an embodiment of the invention, 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 pressure 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.
  • In the embodiment of figure 2, 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 arranged to open and close flow communication between the first and second pressure intensifiers 6, 7 and the third pressure intensifier 8. In the embodiment of figure 2, 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.
  • In figure 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 A1 and a second pressure surface A2. When fluid is introduced into a first chamber 18 of the pressure intensifier 6, 7, 8, the plunger 17 is moved. Consequently, fluid in a second 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 A1 and the second pressure surface A2.
  • The functioning of the pressure intensification arrangement 4 is now described with reference to figures 2 and 4. A drain valve 25, 26, 27 is arranged between each control valve 9, 10, 11 and pressure intensifier 6, 7, 8. Through the drain valve 25, 26, 27, the first chamber 18 of each pressure intensifier 6, 7, 8 can be emptied to the tank 5 for reloading 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 pressure 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 between the first and the second pressure intensifier 6, 7 and the second fluid circuit 2. By means of the fourth control valve 12, the third pressure intensifier 8 can be either by-passed 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 pressure 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.
  • In the embodiment of figure 3, the pressure intensification arrangement 4 is provided with a first pressure intensifier 6 and a second pressure intensifier 7. The pressure intensifiers 6, 7 can be selectively connected in parallel or in series. The functioning of this embodiment is described with reference to figures 3 and 4. 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. When the first control valve 9 is open and the second control valve 10 is closed, the first pressure intensifier 6 is in use. A third control valve 11 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 intensification 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. Also in this embodiment, the pressure intensifiers 6, 7 are provided with drain valves 25, 26 enabling reloading of the pressure intensifiers 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.
  • It will be appreciated by a person skilled in the art that the invention is not limited to the embodiments described above, but may vary within the scope of the appended claims. For instance, 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.

Claims (11)

  1. A fluid system for an internal combustion engine, the fluid system comprising at least a first fluid circuit (1) and a second fluid circuit (2), each of the fluid circuits (1, 2) forming part of a subsystem of an internal combustion engine, the fluid system further comprising a pump (3) for supplying fluid into the system and a pressure intensification arrangement (4) having at least two alternative intensification ratios and comprising at least a first pressure intensifier (6) for increasing pressure in the second fluid circuit (2) and a second pressure intensifier (7) for increasing pressure in the second fluid circuit (2), characterized in that each of the pressure intensifiers (6, 7) comprises a first chamber (18) and a second chamber (19), at least one of the first chambers (18) being in fluid communication with the first fluid circuit (1) and at least one of the second chambers (19) being in fluid communication with the second fluid circuit (2), each of the pressure intensifiers (6, 7) further comprising a reciprocating plunger (17) having a first pressure surface (A1) in the first chamber (18) and a second pressure surface (A2) in the second chamber (19), the area of the second pressure surface (A2) being smaller than the area of the first pressure surface (A1).
  2. A fluid system according to claim 1, characterized in that the first fluid circuit (1) is a hydraulic circuit operating gas exchange valves (14) of the engine.
  3. A fluid system according to claim 1, characterized in that the first fluid circuit (1) is a lubricating oil circuit of the engine.
  4. A fluid system according to any of claims 1-3, characterized in that the second fluid circuit (2) is a hydraulic circuit operating fuel injectors (15) of the engine.
  5. A fluid system according to any of claims 1-3, characterized in that the second fluid circuit (2) is a hydraulic circuit operating means (16) for pressurizing fuel.
  6. A fluid system according to any of the preceding claims, characterized in that the pressure intensifiers (6, 7, 8) have different intensification ratios.
  7. A fluid system according to any of the preceding claims, characterized in that the pressure intensifiers (6, 7, 8) are connected in parallel so that the first chamber (18) of each pressure intensifier (6, 7, 8) is in flow communication with the first fluid circuit (1) and the second chamber (19) of each pressure intensifier (6, 7, 8) is in flow communication with the second fluid circuit (2).
  8. A fluid system according to any of claims 1-6, characterized in that the system comprises means (9, 10, 11, 12) for selectively connecting the first pressure intensifier (6) and the second pressure intensifier (7) in parallel or in series so that the first chamber (18) of the first pressure intensifier (6) is in flow communication with the first fluid circuit (1), the second chamber (19) of the first pressure intensifier (6) is in flow communication with the first chamber (18) of the second pressure intensifier (7), and the second chamber (19) of the second pressure intensifier (7) is in flow communication with the second fluid circuit (2).
  9. A fluid system according to any of the preceding claims, characterized in that the system comprises electrically controllable means (9, 10, 11) for activating and deactivating the pressure intensifiers (6, 7, 8).
  10. A fluid system according to any of the preceding claims, characterized in that each of the pressure intensifiers (6, 7, 8) has at least two different intensification ratios.
  11. An internal combustion engine, characterized by a fluid system in accordance with any of claims 1-10.
EP12712285.1A 2011-04-21 2012-03-01 Fluid system and internal combustion engine Active EP2699789B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20115391A FI20115391A0 (en) 2011-04-21 2011-04-21 Fluid system and internal combustion engine
PCT/FI2012/050205 WO2012143601A1 (en) 2011-04-21 2012-03-01 Fluid system and internal combustion engine

Publications (2)

Publication Number Publication Date
EP2699789A1 EP2699789A1 (en) 2014-02-26
EP2699789B1 true EP2699789B1 (en) 2015-07-15

Family

ID=43919710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12712285.1A Active EP2699789B1 (en) 2011-04-21 2012-03-01 Fluid system and internal combustion engine

Country Status (5)

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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3904699B1 (en) * 2013-03-25 2022-12-14 miniBOOSTER HYDRAULICS A/S Hydraulic system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3640236A1 (en) * 1986-11-25 1988-06-01 Rexroth Mannesmann Gmbh ARRANGEMENT FOR GENERATING HIGH HYDRAULIC PRESSURES
DE10024268B4 (en) 2000-05-17 2012-11-29 Robert Bosch Gmbh Device for gasoline direct injection in a reciprocating internal combustion engine
DE102006034242A1 (en) * 2006-07-21 2008-01-31 Ricardo Deutschland Gmbh Fuel injecting and gas exchange valve actuating device, has injecting valve and gas exchange valve which are adjusted between open and closed position and feed pump is designed for feed operations working intermittently with high frequency
DE102010029691B4 (en) * 2010-06-03 2012-02-16 Mtu Friedrichshafen Gmbh Internal combustion engine and charging fluid cooler

Also Published As

Publication number Publication date
KR101751674B1 (en) 2017-06-28
CN103518058B (en) 2016-03-16
CN103518058A (en) 2014-01-15
WO2012143601A1 (en) 2012-10-26
FI20115391A0 (en) 2011-04-21
EP2699789A1 (en) 2014-02-26
KR20140025478A (en) 2014-03-04

Similar Documents

Publication Publication Date Title
EP1153215B1 (en) Variable output pump for gasoline direct injection
US7690361B2 (en) System and method for metering fuel in a high pressure pump system
US8936009B2 (en) Fuel system having dual fuel pressure regulator
US6494182B1 (en) Self-regulating gasoline direct injection system
US7451742B2 (en) Engine having common rail intensifier and method
US10612503B2 (en) Dual-fuel injector
US6889657B2 (en) Fuel injection device for an internal combustion engine
US10989122B2 (en) Dual-fuel fuel injection system for an internal combustion engine
SE522351C2 (en) Fuel injection system for an internal combustion engine
EP2699805B1 (en) Hydraulic system and operating method
US7219659B2 (en) Fuel injection system comprising a pressure intensifier and a delivery rate-reduced low-pressure circuit
EP2699789B1 (en) Fluid system and internal combustion engine
US20160208793A1 (en) Hydraulic Drive for Cryogenic Fuel Pump
US20140116520A1 (en) Fuel system having dual fuel pressure regulator
US10247190B2 (en) Actuation method and efficiency
US20200040858A1 (en) Valve Assembly for a Fuel Injection System, and Fuel Injection System
CN111295508B (en) GDI pump with direct injection and port injection
EP3099924B1 (en) Common rail fuel injection system
FI124743B (en) Fuel Injection Arrangement
EP3262294B1 (en) Fuel injection system
EP3032091B1 (en) Fuel injection arrangement
KR102032013B1 (en) Fuel injection system and safety valve arrangement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20131015

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150320

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 736942

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602012008790

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 736942

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150715

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20150715

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151015

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151016

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151116

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602012008790

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

26N No opposition filed

Effective date: 20160418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160301

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160301

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160301

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160301

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20120301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150715

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230321

Year of fee payment: 12