EP1892389B1 - Vorrichtung zum steuern eines Kühlflüssigkeitskreislaufs sowie des Schmierölkreislaufs einer Fahrzeugwärmekraftmaschine - Google Patents

Vorrichtung zum steuern eines Kühlflüssigkeitskreislaufs sowie des Schmierölkreislaufs einer Fahrzeugwärmekraftmaschine Download PDF

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Publication number
EP1892389B1
EP1892389B1 EP07111596A EP07111596A EP1892389B1 EP 1892389 B1 EP1892389 B1 EP 1892389B1 EP 07111596 A EP07111596 A EP 07111596A EP 07111596 A EP07111596 A EP 07111596A EP 1892389 B1 EP1892389 B1 EP 1892389B1
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EP
European Patent Office
Prior art keywords
coolant
oil
solenoid valve
temperature
circulation
Prior art date
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Application number
EP07111596A
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English (en)
French (fr)
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EP1892389A1 (de
Inventor
Christian Noiret
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.)
PSA Automobiles SA
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Peugeot Citroen Automobiles SA
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Publication of EP1892389A1 publication Critical patent/EP1892389A1/de
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Classifications

    • 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
    • F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
    • F01M5/005—Controlling temperature of lubricant
    • 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
    • F01P2037/00—Controlling
    • F01P2037/02—Controlling starting
    • 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
    • F01P2060/04—Lubricant cooler
    • 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
    • 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
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/14—Lubrication of pumps; Safety measures therefor

Definitions

  • the present invention relates to a device for controlling a coolant circulation circuit and a lubricating oil circulation circuit of a vehicle engine, such as an automobile vehicle.
  • Such a device is known to DE 4 400 201 A1 .
  • the reduction of pollutant emissions, in particular NOx emitted by a diesel engine can be achieved by lowering the temperature of the engine.
  • the figure 1 represents a cooling circuit of a motor vehicle engine 1 traversed by a cooling liquid, such as water, under the action of a circulation pump 2 operating in a closed circuit.
  • a cooling liquid such as water
  • This circuit is fed via a calorstat or thermostat 3 with a two-way valve 3a, a liquid inlet 4 of which is connected to an inlet of cooling liquid coming from the cylinder head of the engine 1 via a pipe 5.
  • the latter communicates via conduits 6, 7, 8, respectively with a heater 9 for heating the passenger compartment of the vehicle, a cooling radiator 10 of the engine 1 via the thermostat 3 and a liquid / oil exchanger 11 for cooling the pressurized lubricating oil circulating in the engine 1 via an oil pump 12.
  • the heater 9 and the exchanger 11 are permanently traversed by the coolant while the radiator 10 is traversed by this liquid when the thermostat opens at a predetermined temperature as will be seen below.
  • the heat engine 1 is provided with an exhaust gas turbocharger shown schematically at 13 and whose turbine 14, having its axis rotatably mounted in the body 15 of the turbocharger 13, is driven by the exhaust gas of the engine 1 so that the air entering the turbocharger 13 as symbolized by the arrow F1 is compressed and supplied to the engine, the arrow F2 symbolizing the exhaust gas after passing through the turbocharger, the compressed air outlet to the inlet of the motor 1 not shown.
  • the turbocharger 13 is supplied with pressurized lubricating oil from the heat engine 1 as indicated in AL, this oil passing through the body 15 of the turbocharger 13 to lubricate the bearings of the axis or shaft of the turbine 14 and being removed from the turbocharger as indicated in S.
  • the lubricating oil outlet of the exchanger 11 is connected in particular to the supply inlet AL of the turbocompressor 13.
  • the thermostat 3 opens to provide a flow of coolant to the radiator 10.
  • Such a known thermal engine cooling circuit does not make it possible to reduce both the fuel consumption during cold running of the engine in order to rapidly reduce the mechanical friction losses of the various parts of the engine and the pollutant emissions of the engine by lowering the engine. the coolant temperature of it.
  • the present invention aims to solve the above problem of known cooling circuits of thermal engines.
  • a bypass circuit controlled by a control solenoid valve is connected parallel to the pressurized oil inlet and outlet passages, the solenoid valve being controlled at its open position, when the coolant temperature is lower than the second temperature in order to allow the circulation of oil in the bypass circuit to increase the flow rate of oil passing through through the turbocharger as long as the oil pressure therethrough and heated by the exhaust gas is greater than a predetermined pressure level which corresponds to a normal engine operating oil pressure while hot.
  • the turbocharger outlet passage is connected to the inlet of the engine lubricating oil circulation pump.
  • the control solenoid valve is controlled at its closed position when the temperature of the coolant is higher than the second set temperature.
  • the solenoid valve assembly comprises two two-way solenoid valves, a first solenoid valve connected in series in the bypass line of the liquid / oil exchanger, and a second solenoid valve connected in series between the inlet of the solenoid valve. exchanger and the point of connection of the bypass line to the connection line of the oil pump to the exchanger, the first solenoid valve being open and the second solenoid valve being closed when the coolant temperature is less than the second setpoint temperature, while the first solenoid valve is closed and the second solenoid valve is open when the coolant temperature is higher than the second setpoint temperature.
  • the solenoid valve assembly comprises a three-way solenoid valve.
  • the shaft 16 of the turbine of the turbocharger 13 is rotatably mounted in the body 15 thereof by at least two axially spaced bearings, only one of which is shown.
  • the pressurized lubricating oil from the engine enters the turbocharger 13 through a bore 18 formed in the body 15 and opening into the space between bearing 17 and shaft 16 to provide lubrication thereof.
  • the lubricating oil passes through the body 15 to be evacuated through the outlet bore 19 of the body 15 as symbolized in S. This outlet bore 19 is connected via a conduit 20 to the inlet of the pump with oil 12.
  • a controlled flow bypass circuit 21 connected parallel to the inlet bores 18 and the outlet bores 19 of the pressurized oil, so as to increase the flow rate of oil passing through the turbocharger 13 as the pressure of the oil therethrough and heated by the exhaust gas is greater than a predetermined pressure level which corresponds to a normal operating oil pressure of the hot engine.
  • the bypass circuit 21 comprises a control solenoid valve 22 controlled at its opening position of the circuit 21 to allow the circulation of oil in this circuit as long as the oil pressure value is greater than that of normal operation of the engine. hot.
  • the solenoid valve 22 makes it possible to control the parallel oil flow as close as possible to the normal operating pressure of this engine and, consequently, to increase the bypass flow rate.
  • the solenoid valve 22 can therefore be controlled so that the oil flow can be derived until the normal operating temperature or pressure of the motor is reached to accelerate the warming of the engine lubricating oil.
  • the bypass circuit 21 with solenoid valve 22 can be integrated into the turbocharger or simply attached thereto without modifying the circulation of the various turbocharger fluids comprising oil, air and exhaust gases compared with existing turbochargers. .
  • liquid / oil exchanger 11 comprises a bypass line 23 connected to the inlet and the lubricating oil outlet of the exchanger 11 and a solenoid valve 24 is associated with the bypass line 23 to control in all or nothing the flow of oil flowing through the pipe 23.
  • the portion 25a of the line 25 connecting the oil pump 12 to the inlet of the exchanger 11 and which is situated between this inlet and the connection junction of the bypass line 23 to the pipe 25, is provided with a solenoid valve 26 for controlling in all or nothing the oil flow through the exchanger 11.
  • the figure 2 represents the state of the circulation circuits of the coolant and the lubricating oil of the engine 1 when the temperature of the coolant at the inlet 4 of the thermostat 3 is lower than a first set temperature of about 40 ° vs.
  • the thermostat valve 3a occupies a closed position for passage of the cooling liquid towards the radiator 10 and the cooling liquid can circulate in closed circuit through the heater 9 in order to guarantee the rise in temperature of the liquid cooling system to satisfy the comfort of the passenger compartment of the vehicle and through the exchanger 11.
  • the solenoid valve 22 is controlled so as to allow an additional oil flow in the bypass circuit 21 through the turbocharger 13 to accelerate the climb in temperature of the lubricating oil.
  • the solenoid valve 24 is driven to its open position while the solenoid valve 26 is driven to its closed position to ensure the circulation of the lubricating oil through the bypass line 23 and, Therefore, to prevent the circulation of the lubricating oil through the exchanger 11 so as not to cool this oil.
  • the figure 3 represents the state of the circulation circuits of the coolant and lubricating oil of the engine 1 at a temperature of the coolant higher than the first set temperature, but lower than a second setpoint temperature of about 100 ° vs.
  • the valve 3a of the thermostat 3 opens from this first setpoint temperature to ensure the passage of the coolant through the radiator 10 to maintain the temperature of the liquid at a low level.
  • the solenoid valve 22 and the two other solenoid valves 24, 26 occupy their same open and closed position as figure 2 so that the exchanger 11 is short-circuited so as not to cool the lubricating oil and an additional flow of oil passes through the turbocharger 13 to accelerate the temperature rise of the lubricating oil up to the satisfaction of the pressure of this oil as explained previously.
  • the figure 4 represents the state of the coolant circulation circuits and the engine lubricating oil at a coolant temperature higher than the second set temperature.
  • the valve 3a of the thermostat 3 remains in its opening position for passage of the cooling liquid through the radiator 10, the cooling liquid continues to circulate in the heater 9 and the heat exchanger 11, but the solenoid valve 22 is controlled at its closing position of the bypass circuit 21, the solenoid valve 24 is controlled at its closed position preventing the passage of oil under lubricating pressure through the bypass line 23 and the solenoid valve 26 is driven to its open position to allow the oil under pressure from pump 12 to cross the exchanger 11 and to be cooled by the coolant passing through this exchanger.
  • the invention thus makes it possible to thermally manage the coolant circulation circuits and the lubricating oil of a heat engine by accelerating the temperature rise of the lubricating oil while maintaining the temperature of the coolant at a low level remaining compatible with the comfort in the cabin of the vehicle.
  • the invention makes it possible to maintain a fairly significant difference in temperatures between the coolant and the lubricating oil when the power demanded from the engine is relatively low. Such a gap makes it possible to reduce the emission of pollutants, in particular NOx emissions, while reducing the consumption of the engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (6)

  1. Vorrichtung, die das Steuern eines Kühlflüssigkeitskreislaufs eines Verbrennungsmotors (1) für Fahrzeug, wie zum Beispiel ein Kraftfahrzeug, erlaubt, der von einer Kühlflüssigkeit, wie zum Beispiel Wasser, unter der Einwirkung einer Umwälzpumpe (2) durchlaufen wird, wobei der Kreislauf von einem Thermostatventil versorgt wird, das einen Einlass (4) aufweist, der Kühlflüssigkeit empfängt, die von dem Motor (1) kommt, und einen Kühlflüssigkeitsauslass, der mit einem Kühler (10) verbunden ist, wobei der Empfangseinlass der Kühlflüssigkeit auch an einen Lufterhitzer für das Heizen des Fahrgastraums des Fahrzeugs und an einen Flüssigkeits-Öl-Wärmeaustauscher (11) für das Kühlen des Schmieröls des Motors (1), das in dem Austauscher (11) unter der Einwirkung einer Umwälzpumpe (12) zirkuliert, angeschlossen ist, dadurch gekennzeichnet, dass das Thermostatventil derart gesteuert wird, dass es eine Schließposition des Durchgangs der Kühlflüssigkeit zu dem Kühler bei einer Temperatur dieser Kühlflüssigkeit unter einer ersten Sollwerttemperatur von etwa 40 °C einnimmt, und eine Zirkulationsöffnungsposition der Kühlflüssigkeit durch den Kühler bei einer Temperatur dieser Flüssigkeit, die größer ist als der erste Temperatursollwert, und dass der Flüssigkeits-/Ölwärmeaustauscher eine Abzweigleitung aufweist, die an den Schmieröl-Einlass und -Auslass des Austauschers angeschlossen ist, und mit einem Öldurchsatz, der von einer Einheit gesteuert wird, die ein Magnetventil bildet, das in Abhängigkeit von der Temperatur der Kühlflüssigkeit am Einlass (4) des Thermostatventils derart gesteuert wird, dass es eine erste Unterbrechungsposition der Schmierölzirkulation durch den Austauscher und Schmierölzirkulation in der Abzweigleitung des Austauschers bei einem Temperaturwert der Kühlflüssigkeit unter einem zweiten Temperatursollwert von etwa 100 °C und einer zweiten Unterbrechungsposition der Schmierölzirkulation in der Abzweigleitung des Flüssigkeits-/Ölwärmeaustauschers (11) und Schmierölzirkulation durch den Wärmeaustauscher bei einem Temperaturwert der Kühlflüssigkeit über dem zweiten Temperatursollwert einnimmt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass, wenn der Verbrennungsmotor (1) mit einem Turboverdichter mit Abgas (13) versehen ist, der einen Einlassdurchgang (18) und einen Auslassdurchgang (19) für Öl unter Druck zum Schmieren der Lager (17) der Achse (16) der Turbine des Turboverdichters (13) aufweist, ein Abzweigkreislauf (21) mit einem Durchsatz, der von einem Regelmagnetventil (22) gesteuert wird, parallel an den Einlass- und Auslassdurchgängen (18, 19) für Öl unter Druck angeschlossen ist, wobei das Magnetventil (22) zu seiner Öffnungsposition gesteuert wird, wenn die Temperatur der Kühlflüssigkeit kleiner ist als der zweite Temperatursollwert, so dass die Ölzirkulation in dem Abzweigkreislauf (21) erlaubt wird, um den Ölzirkulationsdurchsatz, der durch den Turboverdichter (13) läuft, solange zu erhöhen, wie der Öldruck, der ihn durchquert und von den Abgasen erhitzt wird, größer ist als ein vorbestimmtes Druckniveau, das einem normalen Betriebsöldruck des warmen Motors entspricht.
  3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Auslassdurchgang (19) des Turboverdichters (13) mit dem Eingang der Umwälzpumpe (12) des Schmieröls des Motors verbunden ist.
  4. Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass das Reguliermagnetventil auf seine Verschlussposition gesteuert wird, wenn die Temperatur der Kühlflüssigkeit größer ist als der zweite Temperatursollwert.
  5. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Einheit, die das Magnetventil bildet, zwei 2-Wege-Magnetventile aufweist, ein erstes Magnetventil, das in Serie in der Abzweigleitung des Flüssigkeits-/Ölwärmeaustauschers angeschlossen ist, und ein zweites Magnetventil, das in Serie zwischen dem Einlass des Wärmeaustauschers und der Anschlussstelle der Abzweigleitung an die Anschlussleitung der Ölpumpe an den Wärmeaustauscher angeschlossen ist, dass das erste Magnetventil offen und das zweite Magnetventil geschlossen ist, wenn die Temperatur der Kühlflüssigkeit niedriger ist als der zweite Temperatursollwert, und dass das erste Magnetventil geschlossen und das zweite Magnetventil offen ist, wenn die Temperatur der Kühlflüssigkeit größer ist als der zweite Temperatursollwert.
  6. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Einheit, die das Magnetventil bildet, ein 3-Wege-Magnetventil aufweist.
EP07111596A 2006-08-09 2007-07-03 Vorrichtung zum steuern eines Kühlflüssigkeitskreislaufs sowie des Schmierölkreislaufs einer Fahrzeugwärmekraftmaschine Active EP1892389B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0653337A FR2904857B1 (fr) 2006-08-09 2006-08-09 Dispositif permettant de commander un circuit de circulation d'un liquide de refroidissement ainsi qu'un circuit de circulation d'huile de lubrification d'un moteur thermique de vehicule

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Publication Number Publication Date
EP1892389A1 EP1892389A1 (de) 2008-02-27
EP1892389B1 true EP1892389B1 (de) 2009-02-11

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EP07111596A Active EP1892389B1 (de) 2006-08-09 2007-07-03 Vorrichtung zum steuern eines Kühlflüssigkeitskreislaufs sowie des Schmierölkreislaufs einer Fahrzeugwärmekraftmaschine

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EP (1) EP1892389B1 (de)
AT (1) ATE422605T1 (de)
DE (1) DE602007000534D1 (de)
FR (1) FR2904857B1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107905867A (zh) * 2017-12-22 2018-04-13 潍柴西港新能源动力有限公司 发动机启停增压器保护系统
CN109538328A (zh) * 2018-12-30 2019-03-29 江西腾勒动力有限公司 一种发动机机油冷热控制结构
CN113847140B (zh) * 2021-09-08 2023-03-03 东风汽车集团股份有限公司 一种增程器润滑冷却系统、混动汽车和控制方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348991A (en) * 1980-10-16 1982-09-14 Cummins Engine Company, Inc. Dual coolant engine cooling system
JPS57124029A (en) * 1981-01-23 1982-08-02 Hitachi Ltd Lubricating oil controller for exhaust gas turbo-supercharger
DE4400201A1 (de) * 1994-01-05 1995-02-02 Daimler Benz Ag Flüssigkeitsgekühlte Brennkraftmaschine mit Schmiermittelkühlung
DE19750814C5 (de) * 1997-11-17 2005-08-18 Modine Manufacturing Co., Racine Wärmetauscher, insbesondere Ölkühler
ES2249094B1 (es) * 2003-07-29 2007-06-01 Valeo Termico, S.A. Sistema de regulacion de la temperatura del aceite para vehiculos equipados con un circuito de refrigeracion de liquidos y su correspondiente procedimiento.

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Publication number Publication date
DE602007000534D1 (de) 2009-03-26
FR2904857A1 (fr) 2008-02-15
FR2904857B1 (fr) 2008-11-07
EP1892389A1 (de) 2008-02-27
ATE422605T1 (de) 2009-02-15

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