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WO2000025007A1 - Dispositif de commande pour circuit de refroidissement d'un moteur a combustion interne - Google Patents

Dispositif de commande pour circuit de refroidissement d'un moteur a combustion interne Download PDF

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Publication number
WO2000025007A1
WO2000025007A1 PCT/EP1999/007145 EP9907145W WO0025007A1 WO 2000025007 A1 WO2000025007 A1 WO 2000025007A1 EP 9907145 W EP9907145 W EP 9907145W WO 0025007 A1 WO0025007 A1 WO 0025007A1
Authority
WO
WIPO (PCT)
Prior art keywords
circuit
cooler
control device
connection
short
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP1999/007145
Other languages
German (de)
English (en)
Inventor
Kai Lehmann
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.)
Mercedes Benz Group AG
Original Assignee
DaimlerChrysler AG
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 DaimlerChrysler AG filed Critical DaimlerChrysler AG
Priority to EP99948869A priority Critical patent/EP1125040A1/fr
Publication of WO2000025007A1 publication Critical patent/WO2000025007A1/fr
Priority to US09/841,318 priority patent/US20010042525A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/167—Controlling of coolant flow the coolant being liquid by thermostatic control by adjusting the pre-set temperature according to engine parameters, e.g. engine load, engine speed
    • 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
    • F01P2031/00—Fail safe
    • F01P2031/32—Deblocking of damaged thermostat
    • 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
    • F01P2060/08—Cabin heater
    • 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

Definitions

  • the invention relates to a control device for a cooling circuit of an internal combustion engine according to the kind defined in the preamble of claim 1.
  • thermostatic valves are generally used which, depending on the temperature, switch a short-circuit circuit in the warm-up phase of the internal combustion engine, then switch to mixed operation when the internal combustion engine is heated accordingly, the coolant partly still through the short-circuit circuit and partly already via a cooler Heat exchanger is guided in the cooling circuit. In later normal operation, the coolant is then generally passed completely through the cooler in the cooling circuit.
  • DE 44 38 552 Cl, DE 44 38 237 Cl and DE 42 31 649 C2 are mentioned as generic control devices.
  • thermostatic valves react very slowly to changes in temperature.
  • they are fixed to a controlled variable, namely an opening temperature, and also have high pressure losses.
  • DE 41 25 366 Cl describes a 3/2-way valve for flow liquid circuits known in vehicles, which has an axial inlet and two radial outlets.
  • the previously known valve is used as a distributor valve or mixing valve in a liquid circuit used for heating motor vehicle compartments and in a liquid circuit used for cooling motor vehicle compartments. This valve also enables mixed operation between heating and cooling.
  • the present invention has for its object to provide a control device of the type mentioned that does not have the disadvantages of the prior art, in particular that allows multiple control variables and acts quickly and without large pressure drops.
  • control device allows fast switching times and thus a quick reaction to temperature fluctuations. Furthermore, it is possible for the control variables of the control valve to be set on the control valve according to the invention from the engine in a map-controlled manner. This can e.g. done easily by an electric drive for the control valve.
  • control valve can be kept very flexible in its mode of operation, the through-flows being optimized and pressure losses in switched-on states being reduced to a minimum.
  • Another very important advantage of the solution according to the invention is that by closing all sub-circuits during a cold start or when the internal combustion engine is warming up, a clear reduction in cold start emissions can be achieved. Through the full Closing the partial circuits does not even circulate the water jacket of the internal combustion engine. In this way, the internal combustion engine can heat up even more quickly and emits fewer cold start emissions, in particular hydrocarbons.
  • a further fuel saving and thus a reduction in emissions is also achieved in that, according to the invention, it is possible to additionally reduce the power consumption of the water pump with a very low water requirement and a corresponding position of the control valve in front of the water pump by means of suction throttling.
  • the control valve according to the invention can be inserted at any point in the cooling circuit. It can advantageously be e.g. integrate in the coolant pump, preferably in the suction mouth of the pump or in the cooler. An arrangement in or on the control housing of the internal combustion engine is also possible.
  • FIG. 1 shows a cooling circuit with the control device according to the invention in cold start or warm-up, all circuits being closed,
  • FIG. 3 shows the cooling circuit according to FIG. 1 in mixed operation with a coolant flow through the short circuit and the cooler circuit
  • FIG. 4 shows the cooling circuit according to FIG. 1 with the cooler circuit fully open
  • FIG. 5 shows a simplified embodiment of the control valve according to the invention as a control element in the cold start position, corresponding to the cooling circuit according to FIG. 1,
  • FIGS. 1 to 4 Basically, the cooling circuit shown in FIGS. 1 to 4 is of a known type, which is why only the components and cooling elements essential for the invention are described below. medium flows is discussed in more detail.
  • An internal combustion engine 1 cooled by a cooling circuit is connected to a cooler circuit 2, in which a cooler 3 is located as a heat exchanger, and to a short circuit. circuit 4 connected.
  • a control valve 5 As a control element for dividing the coolant flow in the cooling circuit.
  • a coolant pump 6 Between the internal combustion engine 1 and the control valve 5 there is a coolant pump 6 through which the coolant is circulated.
  • a heating circuit 7 branches off from the cooler circuit 2 and contains a control valve 8, a heater 9 and a pump 10. The heating circuit 7 is fed to the coolant pump 6 on the suction side after the control valve 5.
  • a configuration is to be selected which enables four positions, namely a complete blocking position, a position in which the coolant, in general water, is conducted exclusively via the short circuit 4, a position in which the coolant exclusively via the Radiator circuit 2 is performed and another position in which a mixed operation, ie a partial opening of the short circuit 4 and the cooler circuit 2 is given.
  • Fig. 1 shows the cooling circuit, in which the control valve 5 is in a blocking position, so that both the short-circuit circuit 4 and the radiator circuit 2 are shut off. So that there is no circulation of the coolant in the water jacket of the internal combustion engine 1, it is of course also to be ensured in this position that the control valve 8 for the heating circuit 7 is also closed. In this position there is a suction throttling on the coolant pump 6 with a correspondingly reduced energy consumption. It is only necessary to ensure that the coolant pump 6 is designed for operation in suction throttling.
  • control valve 5 is in a position in which the cooler circuit 2 is shut off, but the short-circuit circuit 4 is open.
  • mixed operation is provided by a corresponding position of the control valve 5, a partial connection to the short-circuit circuit 4 and the cooler circuit 2 being present.
  • a switching device (not shown) can also ensure that the flow of coolant through the internal combustion engine 1 is interrupted.
  • control valve 8 for heating the passenger compartment of the vehicle can be partially or completely opened.
  • the control valve 5 can be in any way, e.g. to be driven by an electric motor. In this way it can also be controlled with regard to its positions. For optimal operation, a control device will be provided for this, the controlled variables being set under engine control.
  • a control valve 5 in principle, for example. As can be seen, it is designed in such a way that it has a rotary slide valve 11 in the form of a sleeve which is arranged in a cylindrical valve housing 12 so as to be rotatable about its longitudinal axis.
  • the rotary valve 11 is provided with an axial common connection 13 on one end face, while it is closed on the other side and there is provided with a drive device, not shown, for pivoting it about its longitudinal axis.
  • the valve housing 12 is also closed on the side facing away from the drive device, not shown.
  • the rotary valve 11 has a control opening 14 in its peripheral wall. According to the selected configuration, the control opening 14 of the rotary slide valve 11 extends over a circumferential range of more than 180 °, preferably approximately 190 to 200 °.
  • the valve housing 12 has in its cylindrical peripheral wall each an opening for a connection 15 to the short circuit 4 and a connection 16 to the cooler circuit 2.
  • the connections 15 and 16 each represent inlets, while the common connection 13 the outlet to the Coolant pump 6 forms.
  • FIG. 5 shows the position of the rotary valve 11, in which, according to FIG. 1, both the cooler circuit 2 and the short-circuit circuit 4 are completed.
  • Fig. 6 shows the position of the rotary valve 11, in which, according to the circuit of FIG. 2, the coolant circulates in the short circuit 4.
  • the position of the rotary valve 11 is selected so that the port 15 is completely opened. According to the exemplary embodiment, however, only a partial opening with a correspondingly throttled circulation of the coolant through the short circuit 4 is possible. In this way, a very sensitive control with a continuous course from a blocking position according to FIG. 5 to a completely open position according to FIG. 6 can be achieved.
  • Fig. 7 shows a mixed operation with a coolant flow both via the short circuit 4 and the cooler circuit 2.
  • the distribution it is not necessary for the distribution to be uniform, but there are also intermediate positions with different flow rates through the cooler circuit 2 and the short circuit 4 possible.
  • Fig. 8 shows a cooling circuit with an almost complete sole flow through the cooler circuit 2.
  • the short circuit 4 is closed. Throttled operation via the cooler circuit 2 is also possible here by a corresponding intermediate position of the rotary valve 11 with a partial opening of the connection 16.
  • control valve 5 can be kept very flexible.
  • rotary valve 11 with axial, semi-axial and / or radial connections or connections possible.
  • other control members can be used instead of a rotary valve 11.
  • the suction side of the coolant pump 6 is only one possible arrangement. an arrangement on the pressure side of the coolant pump 6 between the latter and the internal combustion engine 1 or also after the internal combustion engine is possible.
  • the axial collective connection 13 serves as a supply to the control valve 5 and the connections 15 and 16 serve to discharge the coolant to the cooler circuit 2 and the short-circuit circuit 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

L'invention concerne un dispositif de commande pour circuit de refroidissement d'un moteur à combustion interne, comprenant un radiateur servant d'échangeur thermique, une pompe pour le réfrigérant et un organe de commande régulant le circuit de refroidissement. Le circuit de refroidissement présente un circuit pour le radiateur et un circuit by-pass. L'organe de commande présente une soupape de commande, avec un raccordement pour le circuit du radiateur et le circuit by-pass et un collecteur pour l'entrée et la sortie du réfrigérant vers le circuit du radiateur, ou à partir de ce dernier, et vers le circuit by-pass. La soupape de commande comporte un organe de soupape permettant d'obtenir, au choix, une position de fermeture pour le circuit du radiateur et le circuit by-pass, une connexion entre le circuit du radiateur ou le circuit by-pass et le collecteur, ou une connexion entre le circuit du radiateur et le circuit by-pass vers le collecteur, en cas de marche en régime mixte.
PCT/EP1999/007145 1998-10-27 1999-09-25 Dispositif de commande pour circuit de refroidissement d'un moteur a combustion interne Ceased WO2000025007A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP99948869A EP1125040A1 (fr) 1998-10-27 1999-09-25 Dispositif de commande pour circuit de refroidissement d'un moteur a combustion interne
US09/841,318 US20010042525A1 (en) 1998-10-27 2001-04-24 Control arrangement for a cooling circuit of an internal combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19849492A DE19849492B4 (de) 1998-10-27 1998-10-27 Steuervorrichtung für einen Kühlkreislauf einer Brennkraftmaschine
DE19849492.0 1998-10-27

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US09/841,318 Continuation-In-Part US20010042525A1 (en) 1998-10-27 2001-04-24 Control arrangement for a cooling circuit of an internal combustion engine

Publications (1)

Publication Number Publication Date
WO2000025007A1 true WO2000025007A1 (fr) 2000-05-04

Family

ID=7885791

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/007145 Ceased WO2000025007A1 (fr) 1998-10-27 1999-09-25 Dispositif de commande pour circuit de refroidissement d'un moteur a combustion interne

Country Status (4)

Country Link
US (1) US20010042525A1 (fr)
EP (1) EP1125040A1 (fr)
DE (1) DE19849492B4 (fr)
WO (1) WO2000025007A1 (fr)

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DE10101826B4 (de) * 2001-01-17 2006-12-21 Daimlerchrysler Ag Steuervorrichtung für den Kühlkreislauf einer Brennkraftmaschine
DE10210303B4 (de) * 2002-03-08 2007-05-03 Robert Bosch Gmbh Kühlkreislauf für einen Verbrennungsmotor
DE10243778A1 (de) 2002-09-20 2004-03-25 Siemens Ag Stelleinrichtung
DE10321880B4 (de) * 2003-05-15 2005-09-08 Daimlerchrysler Ag Drehschieber Thermostatventil
US6920845B2 (en) * 2003-08-14 2005-07-26 Visteon Global Technologies, Inc. Engine cooling disc valve
DE10351852A1 (de) * 2003-11-06 2005-06-16 Itw Automotive Products Gmbh & Co. Kg Kühlsystem für Verbrennungskraft in Maschinen, insbesondere für Automobile
DE102004012372A1 (de) * 2004-03-13 2005-09-29 Daimlerchrysler Ag Kühlkreislauf für eine kühlmittelgekühlte Brennkraftmaschine
FR2893113B1 (fr) * 2005-11-04 2009-03-06 Valeo Systemes Thermiques Vanne de commande a etancheite amelioree pour circuit de circulation de fluide
DE102006038213B4 (de) * 2006-08-16 2010-11-11 Itw Automotive Products Gmbh & Co. Kg Thermostatventil
DE102008018296A1 (de) 2008-04-11 2009-10-15 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Zulaufrohr
DE102008030768A1 (de) 2008-06-28 2009-12-31 Audi Ag Anordnung eines Drehschiebers mit einer Wasserpumpe
DE102008035961A1 (de) 2008-07-31 2010-02-04 Schaeffler Kg Wärmemanagementmodul des Kühlsystems einer Verbrennungskraftmaschine
DE102009009854B4 (de) 2009-02-20 2012-05-24 Audi Ag Kühlmittelkreislauf für eine Brennkraftmaschine
DE102009014048A1 (de) 2009-03-19 2010-09-23 Schaeffler Technologies Gmbh & Co. Kg Wärmemanagementmodul mit schraubenförmig bewegtem Regelschieber
DE102010005731B4 (de) 2010-01-26 2023-10-26 Mercedes-Benz Group AG Kühlmittelfördereinheit
DE102010034484B4 (de) 2010-08-17 2014-03-20 Schaeffler Technologies AG & Co. KG Kühlsystem mit einem Thermomanagementmodul
DE102013208193A1 (de) 2013-05-03 2014-11-06 Behr Thermot-Tronik Gmbh Elektrisch antreibbares Ventil für eine Regelung von Volumenströmen in einem Heiz- und/oder Kühlsystem eines Kraftfahrzeuges
DE102013209582A1 (de) 2013-05-23 2014-11-27 Schaeffler Technologies Gmbh & Co. Kg Drehschieberkugel für ein Thermomanagementmodul
DE102013212493B3 (de) * 2013-06-27 2014-09-25 Schaeffler Technologies Gmbh & Co. Kg Schaltbare Sperrvorrichtung, die eine Aktuatorik sowie einen Drehschieber einschließt
DE102013222157A1 (de) 2013-10-31 2015-05-21 Schaeffler Technologies AG & Co. KG Leitgeometrie innerhalb eines Drehschiebers eines Wärmemanagementmoduls
DE102013222644A1 (de) 2013-11-07 2015-05-07 Schaeffler Technologies Gmbh & Co. Kg Mehrstufig schaltbare Sperrvorrichtung mit einer Aktuatorik und Drehschiebern
DE102013222828A1 (de) 2013-11-11 2015-05-28 Schaeffler Technologies AG & Co. KG Abdichtung eines Pumpkolbens für eine Aktuatorik einer Kühlmittelpumpe
DE102013222825A1 (de) 2013-11-11 2015-05-13 Schaeffler Technologies Gmbh & Co. Kg Einzellagerung einer Drehschieberwelle mit reduziertem Radialspiel und angepasster Führungslänge
DE102014000109A1 (de) 2014-01-11 2015-07-16 Thomas Ramminger Drehventil hydraulisch betätigt mit elektronischer Regelung und Arretierung
DE102014206480A1 (de) 2014-04-04 2015-10-08 Schaeffler Technologies AG & Co. KG Wärmemanagementmodul kombiniert mit einer thermostatischen Regelung
DE102014110706A1 (de) 2014-07-29 2016-02-18 Mahle International Gmbh Ventil
DE102014110703A1 (de) 2014-07-29 2016-02-04 Mahle International Gmbh Ventil
DE102014218386A1 (de) 2014-09-12 2016-03-17 Mahle International Gmbh Ventil für eine Regelung von Volumenströmen
DE102015107926A1 (de) * 2015-05-20 2016-11-24 Volkswagen Aktiengesellschaft Brennkraftmaschine und Kraftfahrzeug
JP6330748B2 (ja) * 2015-07-29 2018-05-30 トヨタ自動車株式会社 内燃機関の冷却装置

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DE320400C (de) * 1917-09-12 1920-04-17 Edwin Oetiker Dipl Ing Kuehleinrichtung an Fahrzeugexplosionsmotoren
US4644909A (en) * 1984-05-10 1987-02-24 Aisin Seiki Kabushiki Kaisha System for cooling internal combustion engines
DE4033261A1 (de) * 1990-10-19 1992-04-23 Freudenberg Carl Fa Verbrennungskraftmaschine
DE4324749A1 (de) * 1993-07-23 1995-01-26 Freudenberg Carl Fa Regelventil

Also Published As

Publication number Publication date
DE19849492A1 (de) 2000-05-11
US20010042525A1 (en) 2001-11-22
EP1125040A1 (fr) 2001-08-22
DE19849492B4 (de) 2005-12-22

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