EP2562379A1 - Circuit d'agent réfrigérant - Google Patents

Circuit d'agent réfrigérant Download PDF

Info

Publication number
EP2562379A1
EP2562379A1 EP11178432A EP11178432A EP2562379A1 EP 2562379 A1 EP2562379 A1 EP 2562379A1 EP 11178432 A EP11178432 A EP 11178432A EP 11178432 A EP11178432 A EP 11178432A EP 2562379 A1 EP2562379 A1 EP 2562379A1
Authority
EP
European Patent Office
Prior art keywords
coolant
water jacket
thermostat
cylinder head
radiator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11178432A
Other languages
German (de)
English (en)
Other versions
EP2562379B1 (fr
Inventor
Bernd Brinkmann
Jan Mehring
Hans Günther Quix
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.)
Ford Global Technologies LLC
Original Assignee
Ford Global Technologies LLC
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 Ford Global Technologies LLC filed Critical Ford Global Technologies LLC
Priority to EP11178432.8A priority Critical patent/EP2562379B1/fr
Priority to US13/591,076 priority patent/US8739745B2/en
Priority to RU2012135988/06A priority patent/RU2605493C2/ru
Priority to CN201210302833.4A priority patent/CN102953798B/zh
Publication of EP2562379A1 publication Critical patent/EP2562379A1/fr
Application granted granted Critical
Publication of EP2562379B1 publication Critical patent/EP2562379B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • F01P3/207—Cooling circuits not specific to a single part of engine or machine liquid-to-liquid heat-exchanging relative to marine vessels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • F01P2003/028—Cooling cylinders and cylinder heads in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/08—Cabin heater

Definitions

  • the invention relates to a separate coolant circuit of an internal combustion engine, wherein a cylinder head water jacket and an engine block water jacket is provided, wherein the separate coolant circuit comprises at least one pump, at least one cooler, at least one control, at least onedeffenauslrawgephaseuse and at least one heater, and wherein in the separate coolant circuit Coolant circulates.
  • the FR 2 860 833 A1 discloses a refrigeration cycle of an internal combustion engine having at least one cylinder head and a cylinder housing consisting of at least three cooling passages.
  • the circuit comprises heat exchange means, a drive means for a heat exchange medium and at least one control means for the flow of the heat exchange medium through the cylinder head, the cylinder housing or the heat exchange means on.
  • the refrigeration cycle has at least three independent passages for engine cooling, the first and second passages being disposed in the cylinder head, the third passage being disposed in the cylinder housing, and the passages being independent of each other and including at least one inlet and one outlet allow independent flow of the heat exchange medium through each of the passages of the cylinder head and the cylinder housing.
  • the FR 2 860 833 A1 discloses that three control means are provided to control various circulations of the heat exchange medium can. Of the control means in each case an inlet side and an outlet side is arranged. The third control means is connected to the respective other two control means.
  • the US 5,385,123 discloses a separate refrigerant circuit with a single thermostat, which is arranged in one embodiment in an outlet line of the outlet side of a cylinder head to a pump, the line opens inlet side in the cylinder head. From the outlet branch a bypass and a block line branch off, which opens in the cylinder block. The bypass leads to the pump.
  • the thermostat is arranged in this embodiment in the branch of the three lines. During the warm-up phase, the thermostat closes the block line with the bypass fully open. When the thermostat is closed, the coolant flows through the bypass to the pump and from there into the cylinder head. As the coolant temperature rises, the thermostat gradually closes the bypass, so that the direct flow towards the pump is continuously reduced, and is completely interrupted when the bypass is fully closed. The coolant then flows from the cylinder head through the exhaust duct and the block duct into the cylinder block which is connected to a radiator and from there to the pump.
  • the EP 1 900 919 B1 also deals with a split-cooling system.
  • an internal combustion engine having a refrigeration cycle having at least a first coolant channel and at least one second coolant channel disclosed in parallel with the first coolant channel is disclosed.
  • Control means are provided which provide manipulated variables for the individual control of the throttling means.
  • the DE 195 24 424 A1 relates to a liquid cooling of an internal combustion engine with a cooling liquid flow through a cooling liquid circuit in which a cooling liquid flowed through by the cooling chamber of the internal combustion engine, a cooler for the cooling liquid, a cooling liquid circulating pump and a thermostatically controlled valve is provided which at a low coolant temperature, the cooling liquid flow through the cooling space of the internal combustion engine at a low coolant temperature reduces the coolant flow through the radiator below the value of the coolant flow through the cooling chamber of the internal combustion engine.
  • a load sensor of the internal combustion engine which counteracts the reduction of the cooling liquid flow through the cooling space of the internal combustion engine at a high load of the internal combustion engine.
  • a heating heat exchanger connected to the cooling liquid circuit and an adjusting means may be provided which counteracts the reduction of the cooling liquid flow through the radiator when operating and / or increasing an operation of the heating heat exchanger.
  • the DE 102 61 070 A1 discloses a water jacket structure for a cylinder head and a cylinder block of an engine having a split cooling system adapted therein.
  • the water jackets for the cylinder head and the cylinder block are respectively and independently formed with an inlet shared between the cylinder head and the cylinder block. Its cross-sectional area is reduced to the inside, wherein positions of two outlets are shifted to the cylinder head.
  • KR 1020040033579 A discloses a split-cooling system, wherein a thermostat housing is designed as a single object and at a rear End of the internal combustion engine is arranged.
  • the DE 102 19 481 A1 is concerned with an internal combustion engine with a cylinder crankcase and a cylinder head, with a cooling water circuit with a cylinder head between an inlet opening and an outlet opening extending formed first water jacket and a separate thereof in the cylinder crankcase between an inlet opening and an outlet opening extending second cooling water channel and with a in the Cooling water circuit arranged, common cooling water pump.
  • a third cooling water channel connects the outlet opening of the first cooling water channel formed in the cylinder head with the inlet opening of the cooling water pump.
  • a fourth cooling water channel connects the outlet opening of the cooling water pump to the inlet opening of the second cooling water channel formed in the cylinder crankcase for passing the cooling water from the first into the second cooling water channel.
  • DE 196 28 542 A1 deals with a split-cooling system, wherein the cylinder head or the cylinder heads are cooled by a cooling water circuit, which runs only through the cylinder head and in which a cooling water pump is inserted.
  • the DE 34 40 504 C2 with the split-cooling system or separate coolant circuits for a cylinder block and the engine block.
  • the EP 0 816 651 B1 addresses the problem of providing a device which can reduce the heat-up time of an exhaust line and at the same time quickly raise and maintain the temperature of the walls of the engine block at a low load to a sufficient value, in any case to improve the operating conditions of the engine in all operating conditions .
  • the EP 0 816 651 B1 a device for the internal combustion engine, which has a cylinder block and a cylinder head, whose walls for defining a first part and a second thereof different part, and the same through these walls separate cooling circuit are designed.
  • the EP 1 239 129 A2 deals with a simple cooling system for cooling the internal combustion engine.
  • the invention has the object to improve a separate coolant circuit of the type mentioned by simple means.
  • the coolant from the cylinder head water jacket can be passed directly into the block water jacket, being dispensed with a hitherto conventional bypass line.
  • the engine block water jacket thus assumes the function of previous bypass line, namely bypassing the radiator, so that the coolant z. B. is not unnecessarily cooled in the warm-up phase of the internal combustion engine. This leads to higher material and oil temperatures, which reduces friction and thermal losses.
  • the advantageous embodiment of the coolant circuit according to the invention combines the advantages of the separate coolant circuit (rapid warm-up), whereby the fuel consumption and the generation of harmful emissions are significantly reduced, but also the life of the internal combustion engine is extended or increased.
  • the coolant circuit according to the invention advantageously has an opposite coolant flow in the two separate cooling areas (cylinder head water jacket / block water jacket).
  • the refrigerant flows from the inlet side to the outlet side, which is known per se.
  • the block water jacket however, the coolant is supplied to the side, which corresponds to the outlet side of the cylinder head water jacket.
  • the coolant flows in the block water jacket, based on the flow direction in the cylinder head water jacket so almost inverted from the outlet side to the inlet side.
  • the block water jacket has no flow contact, or coolant to the cylinder head water jacket, of course, small leakage quantities can not be excluded, as mentioned in the introduction.
  • This means in the context of the invention that coolant from the block water jacket does not enter directly into the cylinder head water jacket, and both water jackets are quasi connected in series, but are flowed through in opposite directions.
  • a pump line connects the pump to the inlet side of the cylinder head water jacket.
  • the coolant can thus get out of the cylinder head water jacket in the outlet housing.
  • From the proportional valve branches off the heating line, which leads to the heater.
  • the heating return flows in front of the pump in a radiator return, which opens into the pump.
  • the leading from the block water jacket return water pipe also opens in the radiator return also upstream of the pump.
  • the connection line leading from the thermostat opens advantageously in the cylinder head water line upstream of the radiator.
  • Other components of the coolant circuit can be provided.
  • a Venting device can be provided which communicates with the heating line and the radiator, and whose return line also opens upstream of the pump in the radiator return.
  • the thermostat which acts as a partial load thermostat, connected via the connecting line to the radiator, wherein the connecting line preferably upstream of the radiator but downstream of the proportional valve in the radiator line opens, the engine block water jacket conveniently, the radiator opens all around directly in the radiator return.
  • Target is when the control, so the proportional valve and the thermostat depending on operating modes of the engine such.
  • B. of a warm-up phase of the internal combustion engine and a "warm" internal combustion engine are switchable, wherein the two components are still switchable depending on the presence of a partial load or a high load of the internal combustion engine. In this respect, quasi four modes of operation, which influence the control characteristics.
  • the path of the proportional valve to the heater line opens continuously until it is fully open.
  • the no-flow strategy of the cylinder head water jacket is abandoned, a partial flow of the coolant flows from the outlet housing via the proportional valve in the heating line.
  • the path to the block water line is still closed, so that the coolant flow in the block water jacket has a value of zero.
  • the coolant flow in the cylinder head water jacket is rather low, which is a improved warm-up behavior benefits. Nevertheless, the heater can heat the vehicle cabin sufficiently.
  • the path to the heater line is fully open, the path to the block water line opens continuously.
  • a small flow of coolant is now made possible by the now-flow strategy.
  • the path to the radiator line is still closed.
  • the path to the heater line is still fully open.
  • the path to the block water line is controlled via the proportional valve so that the block temperature can be adjusted to a high amount, for example to above 105 ° C, preferably to about 115 ° C.
  • the thermostat also closes the path to the connecting line when the coolant temperature in the outlet housing or in the cylinder head water jacket below z. B. 100 ° C or preferably below 105 ° C.
  • control components can now be controlled depending on the operating state "operating engine and part load".
  • the path to the heating line is opened, the path to the block water pipe is regulated, so that the block water temperature to a high amount of z. B. 115 ° C einregelbar.
  • the thermostat opens to the connecting line. The coolant flow in the cylinder head water jacket is thus further increased. Characterized in that now an additional portion of the cylinder head coolant flow is passed over the main radiator, the temperature in the cylinder head water jacket is light, preferably adjustable below the opening temperature.
  • the coolant flow is advantageously controlled by means of the thermostat (opening temperature eg 100 ° C) together with the proportional valve when the internal combustion engine has its operating temperature and is operated at partial load.
  • the thermostat is therefore preferred as Partial load thermostat executed, and only opens in partial load operation when the temperature in the cylinder head water jacket or in the outlet housing has an amount above its opening temperature.
  • the internal combustion engine can thus be operated independently in both areas with elevated temperature.
  • the path of the proportional valve to the radiator line can be opened if necessary, if z. B. the internal combustion engine is operated at a higher load.
  • the proportional valve opens the line to the main cooler to the temperature of the cylinder head water jacket on z. B. 85 ° C to regulate.
  • the partial load thermostat is then closed because the opening temperature is not reached.
  • the branch to the water jacket is then fully open. It is preferably provided to regulate the path so that the coolant temperature in the block water jacket is low, for example, regulated to an amount of 90 ° C, since the cylinder block at higher load of the internal combustion engine has a higher cooling demand.
  • the part-load thermostat In the case of a malfunction of the proportional valve and thus an insufficient coolant flow to the main cooler, the part-load thermostat also has a protective function. In this case, as the coolant temperature rises above the opening temperature, the part load thermostat would open and direct coolant to the main radiator. The partial load thermostat can thus also act as a safety thermostat, as excessive overheating is avoided by opening to the radiator.
  • Another operating state or operating mode is when the internal combustion engine is operated in the warm-up phase at high load.
  • the path to the heating line is completely open, whereby the path to the block water line can also be regulated via the proportional valve. It is preferably provided to regulate the path so that the coolant temperature in the block water jacket is low, for example, regulated to an amount of 90 ° C, since the cylinder block at high load of the engine requires high cooling.
  • the coolant flow in the cylinder head water jacket is over the Proportional valve regulated, wherein in the cylinder head water jacket a temperature of 85 ° C is einregelbar.
  • Another mode is when the internal combustion engine has its operating temperature and is operated under high load or full load.
  • the path to the heating line can be closed. This is useful if z. B. at high outside temperatures, the largest cooling capacity to be generated.
  • the path to the block water line can be controlled via the proportional valve. It is preferably provided to regulate the path so that the coolant temperature in the block water jacket is low, for example, regulated to an amount of 90 ° C, since the cylinder block at high load of the engine requires high cooling.
  • the coolant flow in the cylinder head water jacket is controlled via the proportional valve, whereby a temperature of 85 ° C can be controlled in the cylinder head water jacket. Accordingly, the partial load thermostat will not open at all because the temperature is below its opening temperature. If the temperature still rises above the opening temperature, of course, opens the thermostat and takes over its protective function by coolant is passed in addition to the radiator.
  • Targeting in the sense of the invention is therefore when the control or the two components proportional valve and part load thermostat are controlled depending on the mode, which is conceivable with respect to the proportional valve by means of a control unit.
  • the control strategy can also be stored in the central control unit of the internal combustion engine or of the motor vehicle.
  • the entire internal combustion engine that is to say the block water jacket but also the head water jacket
  • the cabin heater can be supplied by the corresponding path of the proportional valve is opened.
  • the no-flow strategy of the headwater jacket is given up, but maintained beneficial in the block water jacket.
  • the coolant inlet temperature to the block is also increased by about 3 to 5 K, since the feed from the output of the cylinder head circuit.
  • the block temperature ie the material temperature itself, can also be increased, since the temperature is controlled by means of the partial load thermostat, and a reduced flow of coolant through the block water jacket can be generated.
  • a variable operating temperature adjustable depending on the above-mentioned modes. The temperature can even be raised up to 115 ° C at partial load, when this temperature is exceeded, the part-load thermostat opens, thus increasing the flow of refrigerant and transferring part of it through the radiator.
  • the coolant flow through the heater is variable during the warm-up phase.
  • the coolant flow in the block water jacket is opposite to the coolant flow in the cylinder head water jacket.
  • the fact that quasi-warmed coolant exiting from the cylinder head is also supplied to the block water jacket is advantageous with regard to the thermal management of the cylinder block, since inter alia frictional losses can be reduced.
  • the thermostat can be advantageously designed as a single-acting thermostat, which at relatively opens high temperatures, so as to allow increased coolant temperatures, in particular in the cylinder head water jacket, in other deviating modes, the cylinder head coolant temperature is reducible, that is variable.
  • a separate coolant circuit 1 is in the FIG. 1 shown.
  • the separate coolant circuit 1 has both a cylinder head water jacket 2 and an engine block water jacket 3, a pump 4, a radiator 6, a control element 7, a coolant outlet housing 8 and a heater 9. Furthermore, the coolant circuit 1 may have a degassing device 11.
  • the cylinder head water jacket 2 is separated from the block water jacket 3, so that there is a separate coolant circuit 1 in which a coolant circulates.
  • the flow direction of the coolant is marked with corresponding arrows.
  • the arranged on the outlet housing 8 control 7 is formed of a thermostat 12 and a proportional valve 13 separate therefrom, wherein the thermostat 12 is arranged parallel to the proportional valve 13, and wherein the proportional valve a block water line 14 to the block water jacket 3, a heating line 16 to the heater 9 and a radiator line 17 to the radiator 6, and wherein the thermostat 12 has a connection line 18 to the radiator.
  • a pump line 19 connects the pump 4 to the inlet side 21 of the cylinder head water jacket 2.
  • the coolant can thus pass from the cylinder head water jacket 2 into the outlet housing 8.
  • the heating return 22 opens in front of the pump 4 in a radiator return 23, which in the pump 4 opens.
  • the leading from the block water jacket 3 return water line 24 also opens into the radiator return 23 also upstream of the pump 4.
  • the leading from the thermostat 12 connecting line 18, however, opens advantageously in the radiator line 17 upstream of the radiator 6.
  • the vent is connected to the heating line 16 and the radiator 6 in connection, wherein the return line 26 also opens upstream of the pump 4 in the radiator return 23.
  • the aim of the invention is that can be dispensed with a bypass line.
  • the function of the bypass line takes over virtually the engine block water jacket 3. This is coolant, depending on operating modes of the internal combustion engine, supplied from the cylinder head water jacket 2 outflowing. It can be seen that the coolant flow in the block water jacket 3 is opposite to the coolant flow in the cylinder head water jacket 2.
  • the coolant is supplied to the block water jacket 3, based on the flow direction in the cylinder head water jacket 2 outlet side.
  • the coolant flows through the block water jacket 3 in opposite directions to the flow direction in the cylinder head water jacket 2 and, based on the flow of coolant in the cylinder head water jacket 2 on the inlet side, and flows into the radiator return 23rd
  • the coolant temperature can be controlled or controlled by means of the proportional valve depending on operating modes.
  • the coolant temperature in the cylinder head water jacket 2 is controlled by means of the thermostat 12.
  • the thermostat 12 may have an opening temperature of 100 ° C or even 115 ° C or an amount therebetween, so that the coolant temperature in the cylinder head water jacket is adjustable to this increased amount.
  • the thermostat does not open at these low temperatures, so that the coolant temperature is controlled solely by the proportional valve.
  • the modes of operation and the temperature control have already been described above, and become the preferred embodiment in their entirety.
  • FIG. 2 merely shows by way of example a diagram in which the coolant flows are represented by the heater (line 27), by the engine block water jacket (line 28) and by the radiator (line 29). On the vertical axis, the flow rate is plotted in l / min. On the horizontal, the opening of the proportional valve 13 is plotted in%.
  • the flow rate in all lines and the two water jackets 2 and 3 has a magnitude of zero (no-flow strategy).
  • coolant is increasingly flowing to the heater 9.
  • the coolant flows in the engine block water jacket 3 and in the cooler 6 are ZERO (no-flow strategy in the block).
  • the proportional valve 13 opens the heating line continuously until the path is fully opened. This corresponds to a total opening degree of up to 30% of the proportional valve 13.
  • a third phase 33 the no-flow strategy is also abandoned in the block water jacket.
  • the proportional valve opens this path continuously.
  • the path to the radiator 6 is closed before. This is possible in partial load operation, so that the temperature control in the cylinder head water jacket takes place only via the partial load thermostat 12.
  • the flow rate in the engine block water jacket 3 increases from 0 up to 40 l / min, in which phase the flow through the heater decreases from 25 l / min to about 20 l / min.
  • the proportional valve is open approx. 50%, ie the path to the water jacket and to the heating is open.
  • it is perfectly sufficient to regulate the temperature in the cylinder head water jacket only via the partial load thermostat and control it to a high amount.
  • the part-load thermostat opens to the radiator.
  • the cylinder head coolant temperature in a fourth phase 34 regulated to an amount of about 85 ° C.
  • the proportional valve 13 opens the path to the radiator continuously, so that it is flowed through with up to 120 / min.
  • the path to the heater can be closed.
EP11178432.8A 2011-08-23 2011-08-23 Circuit d'agent réfrigérant Active EP2562379B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11178432.8A EP2562379B1 (fr) 2011-08-23 2011-08-23 Circuit d'agent réfrigérant
US13/591,076 US8739745B2 (en) 2011-08-23 2012-08-21 Cooling system and method
RU2012135988/06A RU2605493C2 (ru) 2011-08-23 2012-08-22 Контур охлаждающей жидкости
CN201210302833.4A CN102953798B (zh) 2011-08-23 2012-08-23 冷却系统和方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11178432.8A EP2562379B1 (fr) 2011-08-23 2011-08-23 Circuit d'agent réfrigérant

Publications (2)

Publication Number Publication Date
EP2562379A1 true EP2562379A1 (fr) 2013-02-27
EP2562379B1 EP2562379B1 (fr) 2015-10-14

Family

ID=44681045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11178432.8A Active EP2562379B1 (fr) 2011-08-23 2011-08-23 Circuit d'agent réfrigérant

Country Status (2)

Country Link
EP (1) EP2562379B1 (fr)
RU (1) RU2605493C2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT514793A1 (de) * 2013-09-16 2015-03-15 Avl List Gmbh Kühlsystem für eine Brennkraftmaschine
CN108425733A (zh) * 2017-02-13 2018-08-21 铃木株式会社 内燃机的冷却装置
CN111502815A (zh) * 2017-02-14 2020-08-07 丰田自动车株式会社 内燃机的冷却装置
CN112065565A (zh) * 2020-09-15 2020-12-11 奇瑞汽车股份有限公司 节温器总成、冷却系统、发动机和汽车
WO2021163743A1 (fr) 2020-02-18 2021-08-26 Avl List Gmbh Système de refroidissement destiné à un moteur à combustion interne
DE102018107128B4 (de) 2017-03-28 2021-12-23 Toyota Jidosha Kabushiki Kaisha Kühlvorrichtung eines Verbrennungsmotors
US20220364494A1 (en) * 2021-05-13 2022-11-17 Mazda Motor Corporation Engine cooling system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6086132B2 (ja) * 2015-07-28 2017-03-01 トヨタ自動車株式会社 車両用熱交換器

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57176317A (en) * 1981-04-23 1982-10-29 Toyota Motor Corp Cooling equipment for engine
DE8702564U1 (fr) * 1986-02-20 1987-06-25 Fiat Auto S.P.A., Turin/Torino, It
DE3440504C2 (fr) 1983-11-25 1991-07-18 Toyota Jidosha K.K., Toyota, Aichi, Jp
US5385123A (en) 1993-10-08 1995-01-31 Evans; John W. Segregated cooling chambers for aqueous reverse-flow engine cooling systems
DE19524424A1 (de) 1994-07-21 1996-01-25 Volkswagen Ag Kühlmittelkreislauf
DE19628542A1 (de) 1996-07-16 1998-01-22 Juergen Dipl Ing Naegeler Kühlsystem für einen Verbrennungsmotor
EP0816651B1 (fr) 1996-06-24 2001-11-07 Automobiles Peugeot Dispositif de refroidissement d'un moteur à combustion interne
EP1239129A2 (fr) 2001-03-06 2002-09-11 Calsonic Kansei Corporation Système de refroidissement pour un moteur à combustion interne refroidi par eau et procédé pour le commander
DE10127219A1 (de) 2001-05-23 2002-11-28 Behr Thermot Tronik Gmbh Kühlanlage für einen Verbrennungsmotor
DE10219481A1 (de) 2002-04-30 2003-11-20 Audi Ag Verbrennungsmotor mit einem Zylinderkurbelgehäuse, mit einem Zylinderkopf und miteinem Kühlwasserkreislauf und Verfahren zum getrennten Kühlen des Zylinderkurbelgehäuses und des Zylinderkopfs, mit einem Kühlwasserkreislauf und einer gemeinsamen Kühlwasserpumpe
EP1405991A1 (fr) * 2002-10-02 2004-04-07 Mark IV Systemes Moteurs (Société Anonyme) Circuit de refroidissement pour un moteur à combustion interne de véhicule
KR20040033579A (ko) 2002-10-15 2004-04-28 현대자동차주식회사 분리 냉각 시스템이 적용되는 엔진의 서머 스탯
DE10261070A1 (de) 2002-10-24 2004-05-13 Hyundai Motor Co. Wasserummantelungsstruktur für einen Zylinderblock und Zylinderkopf eines Motors mit darin angepasstem geteilten Kühlsystem
FR2860833A1 (fr) 2003-10-08 2005-04-15 Peugeot Citroen Automobiles Sa Circuit de refroidissement d'un moteur a combustion interne constitue d'au moins trois passages de refroidissement
DE10342935A1 (de) 2003-09-17 2005-04-28 Bosch Gmbh Robert Verbrennungskraftmaschine mit einem Kühlkreislauf
EP1900919B1 (fr) 2006-09-13 2011-03-02 Ford Global Technologies, LLC Circuit de refroidissement

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1684533A1 (ru) * 1985-04-15 1991-10-15 Центральный научно-исследовательский дизельный институт Система охлаждени двигател внутреннего сгорани
RU2182238C2 (ru) * 2000-02-29 2002-05-10 Открытое акционерное общество "Ставровский завод автотракторного оборудования" Система охлаждения двигателя внутреннего сгорания

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57176317A (en) * 1981-04-23 1982-10-29 Toyota Motor Corp Cooling equipment for engine
DE3440504C2 (fr) 1983-11-25 1991-07-18 Toyota Jidosha K.K., Toyota, Aichi, Jp
DE8702564U1 (fr) * 1986-02-20 1987-06-25 Fiat Auto S.P.A., Turin/Torino, It
US5385123A (en) 1993-10-08 1995-01-31 Evans; John W. Segregated cooling chambers for aqueous reverse-flow engine cooling systems
DE19524424A1 (de) 1994-07-21 1996-01-25 Volkswagen Ag Kühlmittelkreislauf
EP0816651B1 (fr) 1996-06-24 2001-11-07 Automobiles Peugeot Dispositif de refroidissement d'un moteur à combustion interne
DE19628542A1 (de) 1996-07-16 1998-01-22 Juergen Dipl Ing Naegeler Kühlsystem für einen Verbrennungsmotor
EP1239129A2 (fr) 2001-03-06 2002-09-11 Calsonic Kansei Corporation Système de refroidissement pour un moteur à combustion interne refroidi par eau et procédé pour le commander
DE10127219A1 (de) 2001-05-23 2002-11-28 Behr Thermot Tronik Gmbh Kühlanlage für einen Verbrennungsmotor
DE10219481A1 (de) 2002-04-30 2003-11-20 Audi Ag Verbrennungsmotor mit einem Zylinderkurbelgehäuse, mit einem Zylinderkopf und miteinem Kühlwasserkreislauf und Verfahren zum getrennten Kühlen des Zylinderkurbelgehäuses und des Zylinderkopfs, mit einem Kühlwasserkreislauf und einer gemeinsamen Kühlwasserpumpe
EP1405991A1 (fr) * 2002-10-02 2004-04-07 Mark IV Systemes Moteurs (Société Anonyme) Circuit de refroidissement pour un moteur à combustion interne de véhicule
KR20040033579A (ko) 2002-10-15 2004-04-28 현대자동차주식회사 분리 냉각 시스템이 적용되는 엔진의 서머 스탯
DE10261070A1 (de) 2002-10-24 2004-05-13 Hyundai Motor Co. Wasserummantelungsstruktur für einen Zylinderblock und Zylinderkopf eines Motors mit darin angepasstem geteilten Kühlsystem
DE10342935A1 (de) 2003-09-17 2005-04-28 Bosch Gmbh Robert Verbrennungskraftmaschine mit einem Kühlkreislauf
FR2860833A1 (fr) 2003-10-08 2005-04-15 Peugeot Citroen Automobiles Sa Circuit de refroidissement d'un moteur a combustion interne constitue d'au moins trois passages de refroidissement
EP1900919B1 (fr) 2006-09-13 2011-03-02 Ford Global Technologies, LLC Circuit de refroidissement

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT514793A1 (de) * 2013-09-16 2015-03-15 Avl List Gmbh Kühlsystem für eine Brennkraftmaschine
AT514793B1 (de) * 2013-09-16 2015-06-15 Avl List Gmbh Kühlsystem für eine Brennkraftmaschine
US10858980B2 (en) 2013-09-16 2020-12-08 Avl List Gmbh Cooling system for an internal combustion engine
CN108425733A (zh) * 2017-02-13 2018-08-21 铃木株式会社 内燃机的冷却装置
CN108425733B (zh) * 2017-02-13 2020-07-24 铃木株式会社 内燃机的冷却装置
CN111502815A (zh) * 2017-02-14 2020-08-07 丰田自动车株式会社 内燃机的冷却装置
CN111502815B (zh) * 2017-02-14 2021-12-31 丰田自动车株式会社 内燃机的冷却装置
DE102018107128B4 (de) 2017-03-28 2021-12-23 Toyota Jidosha Kabushiki Kaisha Kühlvorrichtung eines Verbrennungsmotors
WO2021163743A1 (fr) 2020-02-18 2021-08-26 Avl List Gmbh Système de refroidissement destiné à un moteur à combustion interne
CN115135862A (zh) * 2020-02-18 2022-09-30 Avl李斯特有限公司 用于内燃机的冷却系统
CN115135862B (zh) * 2020-02-18 2023-09-29 Avl李斯特有限公司 用于内燃机的冷却系统
CN112065565B (zh) * 2020-09-15 2021-11-30 奇瑞汽车股份有限公司 节温器总成、冷却系统、发动机和汽车
CN112065565A (zh) * 2020-09-15 2020-12-11 奇瑞汽车股份有限公司 节温器总成、冷却系统、发动机和汽车
US20220364494A1 (en) * 2021-05-13 2022-11-17 Mazda Motor Corporation Engine cooling system
US11624311B2 (en) * 2021-05-13 2023-04-11 Mazda Motor Corporation Engine cooling system

Also Published As

Publication number Publication date
EP2562379B1 (fr) 2015-10-14
RU2012135988A (ru) 2014-02-27
RU2605493C2 (ru) 2016-12-20

Similar Documents

Publication Publication Date Title
EP2562379B1 (fr) Circuit d'agent réfrigérant
EP1900919B1 (fr) Circuit de refroidissement
EP2876274B1 (fr) Moteur à combustion interne
DE102010002082B4 (de) Separat gekühlter Abgassammler zur Aufrechterhaltung einer No-Flow Strategie des Zylinderblockkühlmittelmantels
DE102014215074B4 (de) Temperieranordnung für Getriebeöl eines Kraftfahrzeugs sowie Verfahren zum Temperieren von Getriebeöl eines Kraftfahrzeugs
DE102014201113B4 (de) Kühlmittelkreislauf mit in Reihe geschalteten Kopf- und Blockkühlmittelmantel
EP1947308B1 (fr) Système de refroidissement de moteur intégré
DE102012200005B4 (de) Verfahren zum Betreiben eines Kühlmittelkreislaufs
EP3523524B1 (fr) Moteur à combustion interne
DE102008035955B4 (de) Kühlstrategie
DE102014201717A1 (de) Brennkraftmaschine mit flüssigkeitsgekühltem Zylinderkopf und Zylinderblock und Verfahren zur Steuerung der Kühlung einer derartigen Brennkraftmaschine
EP3198124A1 (fr) Moteur à combustion interne
DE102014200054A1 (de) Flüssigkeitsgekühlte Brennkraftmaschine mit flüssigkeitsgekühltem Zylinderkopf und flüssigkeitsgekühltem Zylinderblock
EP2562378B1 (fr) Stratégie de fonctionnement d'un circuit d'agent réfrigérant séparé
DE102015201238B3 (de) Verfahren zum Betrieb einer Brennkraftmaschine mit Split-Kühlsystem und Zylinderabschaltung
DE102018110234B4 (de) Kühlvorrichtung für einen Verbrennungsmotor
DE102015201240B4 (de) Split-Kühlsystem sowie Brennkraftmaschine mit einem Split-Kühlsystem und entsprechend ausgestattetes Fahrzeug
DE102015201246A1 (de) Regelmittel zur Steuerung der Kühlmittelströme eines Split-Kühlsystems
EP3320197B1 (fr) Circuit à fluide de refroidissement pour boîte de vitesses à refroidissement par liquide
DE102015201242B4 (de) Regelmittel zur Steuerung der Kühlmittelströme eines Split-Kühlsystems
DE202015100582U1 (de) Regelmittel zur Steuerung der Kühlmittelströme eines Split Kühlsystems
DE102007048503A1 (de) Kühlsystem für einen Motor
DE102012019091A1 (de) Kurbelgehäuse für eine Verbrennungskraftmaschine sowie Verbrennungskraftmaschine mit einem solchen Kurbelgehäuse
DE102013203476A1 (de) Brennkraftmaschine mit flüssigkeitsgekühltem Zylinderkopf und flüssigkeitsgekühltem Zylinderblock und Verfahren zur Steuerung der Kühlung einer derartigen Brennkraftmaschine
DE102013217154A1 (de) Temperieranordnung für Getriebeöl eines Kraftfahrzeugs sowie Verfahren zum Temperieren von Getriebeöl eines Kraftfahrzeugs

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

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

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20130827

RBV Designated contracting states (corrected)

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

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F01P 7/14 20060101AFI20150522BHEP

Ipc: F01P 3/02 20060101ALN20150522BHEP

Ipc: F01P 7/16 20060101ALI20150522BHEP

INTG Intention to grant announced

Effective date: 20150623

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: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 755282

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151015

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011008084

Country of ref document: DE

REG Reference to a national code

Ref country code: RO

Ref legal event code: EPE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20151014

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: 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: 20151014

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: 20160114

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: 20151014

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: 20160214

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: 20151014

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: 20151014

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: 20151014

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: 20151014

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: 20160115

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: 20151014

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: 20160215

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: 20151014

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: 20151014

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: 20151014

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011008084

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

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: 20151014

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: 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: 20151014

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: 20151014

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: 20151014

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: 20151014

26N No opposition filed

Effective date: 20160715

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

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: 20151014

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: 20160831

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

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: 20151014

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20160831

Ref country code: CH

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

Effective date: 20160831

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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

Ref country code: IE

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

Effective date: 20160823

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 NON-PAYMENT OF DUE FEES

Effective date: 20160823

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 755282

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160823

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

Ref country code: AT

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

Effective date: 20160823

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: 20151014

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: 20110823

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

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: 20151014

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: 20151014

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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: 20151014

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: 20151014

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

Ref country code: FR

Payment date: 20190717

Year of fee payment: 9

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

Ref country code: GB

Payment date: 20190728

Year of fee payment: 9

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

Ref country code: RO

Payment date: 20200727

Year of fee payment: 10

Ref country code: TR

Payment date: 20200812

Year of fee payment: 10

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

Effective date: 20200823

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

Ref country code: FR

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

Effective date: 20200831

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

Ref country code: GB

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

Effective date: 20200823

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 NON-PAYMENT OF DUE FEES

Effective date: 20210823

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230620

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

Ref country code: DE

Payment date: 20230711

Year of fee payment: 13