US3851629A - Cooling installation for piston internal combustion engines - Google Patents

Cooling installation for piston internal combustion engines Download PDF

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Publication number
US3851629A
US3851629A US00331036A US33103673A US3851629A US 3851629 A US3851629 A US 3851629A US 00331036 A US00331036 A US 00331036A US 33103673 A US33103673 A US 33103673A US 3851629 A US3851629 A US 3851629A
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United States
Prior art keywords
cooling medium
valve
installation according
cooling
limit value
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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.)
Expired - Lifetime
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US00331036A
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English (en)
Inventor
B Mayr
R Henning
E Schweiger
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Priority claimed from DE19722206266 external-priority patent/DE2206266C2/de
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
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    • 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
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/30—Engine incoming fluid temperature
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/32—Engine outcoming fluid temperature
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/34—Heat exchanger incoming fluid temperature
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/36—Heat exchanger mixed fluid temperature
    • 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
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/50—Temperature using two or more temperature sensors

Definitions

  • ABSTRACT A cooling circulation system for piston internal combustion engines with a cooling jacket and a control system which interrupts the cooling medium circulation through the cooling jacket at least within the area of the combustion zones up to a first predetermined limit value of the temperature of the engine and/or of the time after the start of the engine, which above the first predetermined limit value at first limits the same to a closed circulation in by-passing relationship to a radiator and avoiding fresh water exchange, and which above a second further predetermined limit value incorporates into the cooling medium circulation the radiator, a heater-heat-exchanger and/or the fresh water exchange; the control system thereby includes a cooling medium valve and a three-way thermostat each with a separate control element, for example, in the form of an expansion element, of which the cooling medium valve is actuated upon reaching the first limitvalue and the three-way thermostat upon reaching the second limit value.
  • the present invention relates to a circulatory cooling installation for piston internal combustion engines with a cooling jacket and a control mechanism which interrupts the cooling medium circulation at least within the area of the combustion zones up to a first predetermined limited value of the temperature of the engine and/or of the time after the starting of the engine, above the first predetermined limit value then limits at first the circulation to a closed circulation in by-passing a radiator and avoiding a fresh water exchange, and above a further predetermined limit value includes in the cooling medium circulation the radiator, a heater heat-exchanger and/or the fresh water exchange.
  • a cooling system is described in the German Offenlegungsschrift No. 2,061,762 in which, for purposes of achieving good running properties of .the engine under different load conditions, the through-passage of fresh water is limited below the limit value to a first area of the cooling jacket outside of the combustion zones with a throttled flow.
  • the overflow of the cooling medium into a second area of the combustion zones is controlled by means of valves in dependence on the temperature of the cooling medium after the passage through the first area.
  • control system includes a cooling medium valve and a conventional three-way thermostat, with a separate control element each, of which the cooling medium valve is actuated after reaching the first limit value and the three-way thermostat is actuated after reaching the further limit value.
  • a cooling medium pump may be provided which is adapted to be stopped up to a predetermined limit value.
  • This cooling medium pump may be controlled as a function of time as also as a function of the temperature of the cooling medium or of a structural part within the second area of the cooling jacket.
  • FIG. 1 is a schematic view of a cooling system for an internal combustion engine in accordance with the present invention
  • FIGS. 2a, 2b and 2c are schematic views illustrating the operation of the cooling system according to FIG. 1 in three phases;
  • FIG. 3 is a diagram illustrating the temperature rise as a function of warming-up time of an' internal combustion engine with and without the construction of the cooling system according to the present invention
  • FIGS. 4a and 4b are a longitudinal and transverse cross-sectional view through a three-way thermostat with a cooling medium valve in a structural unit according to the present invention, the cross section of FIG. 4a being taken along line lVa-IVa of FIG. 4b and the cross section of FIG. 4b being taken along line IV- bIVb of FIG. 4a;
  • FIG. 5 is a schematic view, similar to FIG. 1, of a modified embodiment of the arrangement of the threeway thermostat with a cooling medium valve as a structural unit in accordance with the present invention.
  • FIG. 6 is a schematic view, similar to FIG. 1, of a modified embodiment showing the addition of return line 35.
  • FIG. 1 illustrates in schematic view the cooling system of an internal combustion engine generally designated by reference numeral 1.
  • the cooling jacket of the internal combustion engine 1 which is constructed in a conventional manner includes a first area or zone 2 which is arranged in the cylinder block of the engine 1 and encloses essentially the cylinder sliding surfaces of the pistons of the engine.
  • a second area or zone 3 of the cooling jacket is arranged in the cylinder head of the engine 1 and encloses above all the combustion zones, namely, the combustion spaces as well as the gasexchange channels.
  • the engine 1 For the circulation of the cooling medium, the engine 1 includes at the usual places a cooling medium inlet aperture 4 into the first area 2 of the cooling jacket at a low location and a cooling medium outlet or discharge aperture 5 out of the second area 3 of the cooling jacket at a high location. An additional discharge aperture 6 out of the first area 2 is arranged at a place adjacent the inlet aperture 4. Finally, still a further high discharge aperture 7 out of the second area 3 of the cooling jacket may be provided.
  • a free, unobstructed cooling medium line 8 leads from the discharge aperture 5 to a radiator 9.
  • the coolingrnedium line 8 includes a branch place 1t] from which branches off a by-pass 11 which by-passes the radiator 9 and which terminates at a mixing place 14 in the return line 13 leading from the radiator 9 to a cooling medium pump 12 and to the inlet aperture 4.
  • the mixing place 14 includes a three-way thermostat 15 with one disk valve 16 and 17 each for the alternate control of the cooling medium inlet out of the bypass 11 and out of the return line 13 into the continuation of the return line 13 to the cooling medium pump 12 and to the inlet aperture 4.
  • An expansion element 18 located in the mixing place 14 between the disk valves 16 and 17 is present for the control of the three-way thermostat 15.
  • a circulation line 19 leads from the additional discharge aperture 6 out of the first area 2 of the cooling jacket by way of a heater heatexchanger 20 and a cooling medium valve 21 into the return line 13 and further by way of the cooling medium pump 12 into the inlet aperture 4.
  • the cooling medium valve 21 also includes a disk valve 22 and an expansion element 23. This cooling medium valve 21 closes the portion of the return line 13 which connects the mixing place 14 with the cooling medium pump 12, up to a predetermined temperature of the cooling medium flowing through the circulation line 19.
  • a parallel circulation line 24 branches off from the circulation line 19 between the additional discharge aperture 6 and the heater heatexchanger 20 and terminates again in the circulation line 19 upstream of the cooling medium valve 21.
  • a heater jacket 25 for a suction line throttle valve 26 as well as' a temperature pick-up or transmitter 27 for a conventional fuel metering system of the engine are disposed in this parallel circulation line 24.
  • the disk valve 22 of the cooling medium valve 21 is closed (FIG. 2a) so that no cooling medium can flow from the discharge aperture 5 to the cooling medium pump 12.
  • the cooling medium remains stationary or stands still in the second area 3 of the cooling jacket of the engine 1 so that a reduced heat transfer takes place thereat from the walls of the combustion spaces and gas-exchange channels arranged thereat to the cooling medium.
  • a closed circulation of the cooling medium by way of the inlet aperture 4 and the discharge aperture 6 disposed near the same encompasses only a portion of the first area 2 of the cooling jacket of the engine 1. Since the warmup of the cooling medium partaking in this closed circulation lies at a fixed and nearly always far-reachingly constant ratio to the warm-up of the cooling medium v in the second area 3 of the cooling jacket, no overheating danger exists in the area 3 of the cooling jacket as demonstrated by exhaustive and conclusive test results, insofar as the expansion element 23 is matched corresponding to these temperature conditions to an opening temperature of correspondingly lower value.
  • cooling medium pump 12 as is usual, is driven directly by the engine 1, then at higher rotational speeds of the engine 1 and therewith of the cooling pump 12, there results an increase of the cooling medium portion encompassed by this circulation in the cooling jacket due to the thereby increased cooling medium feed quantity in the closed circulation. At particularly high rotational speeds, this cooling medium movement includes nearly the entire cooling jacket in the first and in the second area 2 and 3. In this manner, local overheating appearances of the engine are precluded during the warm-up period also at extreme loads.
  • the cooling medium also flows through the second area 3 of the cooling jacket out of the discharge aperture 5 by way of the bypass line 11, the opened by-pass disk valve 17 of the three-way thermostat into the mixing place 14 and by way of the return line 13 into an additional closed circulation in by-passing relationship to the radiator 9 (FIG. 2b).
  • the closed circulation of the cooling medium through the circulation line 19 thereby remains preserved far-reachingly unchanged.
  • the disk valve 16 opens the return line 13 from the radiator 9 with simultaneous continuous closing of the bypass disk valve 17 for the by-pass line 11.
  • the threeway thermostat 15 thereby controls at the mixing place 14 a cooling medium temperature which represents the most favorable operating temperature for the operation of the engine 1.
  • the closed circulation through the circulation line 19 also remains thereby operable without change with an opened disk valve 22 of the cooling medium valve 21.
  • the by-pass disk valve 17 of the three-way thermostat 13 closes the bypass 11 (FIG. 2c) so that apart from the continuing present closed circulation through the circulation line 19 the entire cooling water discharged through the discharge aperture 5 out of the cooling jacket of the engine is conducted to the radiator 9 by way of the cool-.
  • Reference numerals 30 and 31 designate curves according to which the temperature of the cooling medium rises in the second area 3 with and without-a construction according to the present invention, respectively; the curves 32 and 33 are thereby indicative for the first area 2 of the cooling jacket.
  • the shape of these curves illustrates that the warming up of the cooling medium in the cooling jacket during the warm-up of the engine is influenced only insignificantly. A disadvantageous effect of the temperature progress on engine structural parts is precluded, at any rate.
  • FIG. 1 Possible modifications of the construction of the cooling system illustrated and described above are indicated in FIG. 1 in dash lines. Accordingly, there exists the possibility to provide a further disk valve 34 in the cooling medium valve 21, which closes the inlet of the circulation line 19 into the cooling medium valve 21 after the opening of the disk valve 22. It can be achieved thereby that the closed circulation through the circulation line 19 no longer represents a by-pass of the radiator 9 upon reaching the operating temperature of the engine.
  • a return line 35 may be provided in this case which terminates uncontrolled in the three-way thermostat 15 between the disk valves 16 and 17 and as a result thereof also influences the expansion element 18 thereof.
  • the cooling medium from the first area 2 or the second area 3 of the cooling jacket may be conducted either selectively or also automatically controlled from the further high discharge aperture 7 out of the second area 3 of the cooling jacket by way of a heating water line 36 and a heating three-way valve 37 to the heatexchanger 20.
  • a further advantageous embodiment of the present invention resides in combining the cooling medium valve 21 with the three-way thermostat 15 into a structural unit.
  • the cooling medium line 35 is prerequisite which, according to FIG. 1, terminates between the disk valves 16 and 17 of the three-way thermostat 15 in the latter.
  • the cooling medium valve 21 is thereby dispensed with completely so that the circulation line 19' continues directly in the cooling medium line 35 without branching off and the return line 13 out of the three-way thermostat 15 terminates directly in the cooling medium pump 12.
  • the by-pass disk valve 17 of the three-way thermostat 15 thereby has to assume the operation of the disk valve 22 in the cooling medium valve 21.
  • a further expansion element 38 is provided in the three-way thermostat 15 according to FIGS.
  • FIGS. 4a and 4b The internal construction of the three-way thermostat combined with the cooling medium valve is illustrated in detail in FIGS. 4a and 4b.
  • the pipe line 39 represents in FIG. 4b a connection between the cooling medium discharge aperture according to FIG. 1, the branch place and the cooling medium line 8 leading freely to the radiator 9.
  • the by-pass 11 (FIG. 4b) consists also in this case exclusively of a short by-pass section.
  • the housing 40 of the three-way thermostat is constructed in one piece together with the pipe line 39 and has an essentially cylindrical shape, at the two end faces of which are arranged the disk valves 16 and 17.
  • a housing cover 40 enables the assembly of the three-way thermostat 15.
  • the disk valve 17* serves simultaneously as by-pass valve and as cooling medium valve and, for this purpose is left closed as cooling medium valve up to the control temperature thereof, is then opened and is again closed by the expansion element 18 of the three-way thermostat l5, simultaneously with the-opening of the disk valve 16 at the control temperature of the expansion element 18.
  • the expansion element 18 is thereby connected directly with the disk valve 16.
  • the piston rod 18 thereof is supported by way of a curved support member 41 and a valve seat 42 at the housing 40.
  • a cylindrical closure spring 44 is supported at a curved support member 43 which is fixed at the housing 40 by way of the valve seat 42; the closure spring 44 acts on the disk valve 16 in the closing direction.
  • the curved support member 43 carries a pair of centering sheet metal members 45 for the freely projecting end of the expansion element 18. Additionally, the curved support member 43 includes a central guide bore 46 for the also freely projecting end of the expansion element 38.
  • the piston rod 38 of the expansion element 38 is supported at a curved connecting member 47 which is secured at the disk valve 16 and again serves as abutment for a coil compression spring 49 under interconnection of a supporting ring 48; the coil spring 49 acts upon the by-pass disk valve 8 17 in the closing direction.
  • a curved draw member 50 is secured at the by-pass disk valve 17 which encloses the expansion element 38 and is slidingly supported at the latter against an abutment 51 constructed as annular oflset.
  • the housing finally also carries one short connecting pipe stub 13, 13" and 35 each as parts of the cooling medium line 35 and of the return line 13 from the radiator 9 and to the cooling medium pump 12.
  • the structural parts of the three-way thermostat 15' assume the position illustrated in FIGS. 4a and 4b. Both the by-pass disk valve 17 in its operation as cooling medium valve as also the disk valve 16 for the return line 13 from the radiator 9 are thereby closed.
  • a closed circulation of the cooling medium exists through the cooling medium line 35 and the connecting pipe stub 35' thereof at the housing 40 into the interior of the three-way thermostat 15 and through the return line 13 and the connecting pipe stub 13' at the housing 40 back' to the cooling medium pump 12 and thus through a part of the first area 2 of the cooling jacket of the engine 1 between the inlet aperture 4 and the discharge aperture 6 thereof.
  • the cooling medium remains unmoved, i.e., stationary in the second area 3 of the cooling jacket whereby a rapid warm-up of the walls of the combustion spaces of the engine 1 is assured.
  • the temperature thereof Due to the increasing warm-up of the cooling medium circulating in the closed circulation, the temperature thereof finally reaches the control temperature of the expansion element 38.
  • the latter displaces its piston rod 38' outwardly whereby as a result of its support against the curved connecting member 47, the expansion element 38 itself is displaced in fact and after a slight idling or lost-motion movement opens by way of the curved draw member the by-pass disk valve 17 against the return force of the coil spring 49.
  • the draw member .50 is thereby drivingly supported against the abutment 51 of the expansion element 38.
  • the cooling medium can flow into the interior of the housing 40 through the by-pass 11 in addition to the inlet through the connecting pipe stub 35 for the cooling medium line 35 whereby, according to FIG. 1, a through-flow also of the second area 3 of the cooling jacket of the engine 1 is established in the closed circulation without the inclusion of the radiator 9.
  • the disk valve 17 soon as the disk valve 17 comes into abutment, it can displace itself together with the draw member 50 against the force of the coil spring 49 relative to the expansion element 38 whereby the draw member 50 lifts off from the abutment 51 at the expansion element 38.
  • the cooling medium flows into the interior of the housing 40 through the connecting stub 35 for the cooling medium line 35 in the closed circulation through the first area 2 as also through the connecting stub 13" for the return line 13 in the housing cover 40' and through the opening of the disk valve 16 in a circulation containing the radiator 9 through the entire cooling jacket of the engine 1.
  • FIG. 5 illustrates a schematic view of a modified embodiment of a cooling system according to the present invention in which a three-way thermostat 115 is arranged at the branch place of the cooling medium line 8 leading to the radiator 9 and of the by-pass 11. Similar parts are thereby designated by similar reference numerals as used in FIGS. 1 to 4 and are therefore not described again.
  • the three-way thermostat 115 and the cooling medium valve 121 are combined into a structural unit within a common housing. However, it includes one disk valve 116 and 117 each as well as one expansion element 118 and 138 each.
  • the circulation line 19 terminates already upstream of the cooling medium valve 121 in the return line 13 of the radiator 9.
  • the disk valves 116 and 117 assume in FIG. 5 with a cold cooling medium the full-line position and are both closed.
  • the cold cooling medium thus circulates exclusively in the closed circulation through the first area 2 of the cooling jacket of the engine 1. It leaves by way of the discharge aperture 6, flows through the circulation line 19 and the heater heat-exchanger 20, terminates in the return line 13 and flows through the cooling medium valve 121 before it is again fed by the cooling medium pump 12 through the inlet aperture 4 into the first area 2 of the cooling jacket.
  • the cooling medium in addition to flowing through the circulation line 19, also flows through the parallel circulation line 24 and as a result thereof, the heater jacket 25 of the suction line throttle valve 26 as well as the temperature pick-up 27 for a fuel metering device of the engine are acted upon thereby.
  • the cooling medium valve 121 In the cooling medium valve 121, the increasing warming-up cooling medium over the expansion element 138 thereof, after which reaching its control temperature actuates the disk valve 117 into the open position thereof illustrated in dash line. As a result thereof, a' cooling medium circulation commences also through the bypass l1 and thus through the second area 3 of the cooling jacket, the discharge aperture 5 thereof and the three-way thermostat 115 at thebranch place 10.
  • the closed disk valve 116 continues to prevent a cooling medium flow to the radiator 9 up to the warm-up of the cooling medium disposed in the closed circulation to the control temperature of the expansion element 118. As soon as the control temperature of the expansion element 118 is exceeded, the disk valve 116 opens with simultaneous continuous reclosing of the by-pass 11 by means of the disk valve 117.
  • a circulatory cooling installation for piston internal combustion engines having combustion zones comprising a cooling jacket means and a control means which is operable to interrupt the cooling medium circulation through the cooling jacket means at least within the area of the combustion zones up to a predetermined first limit value, which above the first predetermined limit value is operable to limit the circulation at first to a closed circulation in by-passing relationship to a radiator and under avoidance of a fresh water exchange, and which above a further predetermined limit value is operable to include into the cooling medium circulation at least one of radiator, fresh water exchange and a heater heat-exchanger means, characterized in that the control means includes in effect a cooling medium valve means and a three-way thermostat means each having a separate control element, of which the cooling medium valve means is actuated upon reaching the first limit value and the three-way thermostat means is actuated upon reaching the further limit value.
  • cooling medium valve means and the three-way thermostat means include disk valve means, temperature-sensing sensing means and aperture means for the cooling medium-valve-means and the three-way thermostat means which are arranged substantially coaxially.
  • cooling medium valve means and the three-way thermostat means are arranged in a common housing means with two mutually coaxially oppositely disposed disk valves, and in that the two temperature sensing means with the disk valves secured thereon and with mutually opposite thermostat inlet aperture means are arranged substantially coaxially.
  • a first expansion element operable as temperature sensing means carries a first valve disk of the three-way thermostat means and includes a piston rod supported at the housing means, and in that additionally said first-mentioned expansion element is operatively connected with a second expansion element which axially adjusts the second common valve disk of the three-way thermostat means and of the cooling valve means with respect to the first valve disk.
  • cooling medium valve means below the predetermined limit value additionally closes the cooling medium passage opened by the three-way thermostat means below the predetermined temperature limit value whereby a cooling medium from the closed circulation acts upon the temperature sensing means of the cooling medium valve means.
  • cooling medium valve means and the three-way thermostat means include disk valve means, temperature-sensing means and aperture means for the cooling medium-valve-means and the three-way thermostat means which are arranged substantially coaxially.
  • a first expansion element operable as temperature sensing means carries a first valve disk of the three-way thermostat means and includes a piston rod supported at the housing means, and in that additionally said first-mentioned expansion element is operatively connected with a second expansion element which axially adjusts the second common valve disk of the three-way thermostat means and of the cooling valve means with respect to the first valve disk.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US00331036A 1972-02-10 1973-02-09 Cooling installation for piston internal combustion engines Expired - Lifetime US3851629A (en)

Applications Claiming Priority (1)

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DE19722206266 DE2206266C2 (de) 1972-02-10 Umlaufkühlvorrichtung für Kolbenbrennkraftmaschinen

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US (1) US3851629A (pt)
BE (1) BE795230A (pt)
CH (1) CH571649A5 (pt)
FR (1) FR2171823A5 (pt)
GB (1) GB1421002A (pt)
IT (1) IT978871B (pt)
SE (1) SE394491B (pt)

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US3877443A (en) * 1973-03-22 1975-04-15 Bayerische Motoren Werke Ag Circulating cooling installation for piston internal combustion engines
US3907199A (en) * 1974-11-18 1975-09-23 Ford Motor Co Combination engine cooling system and passenger compartment heating system for an automotive vehicle
US4144849A (en) * 1976-04-10 1979-03-20 Daimler-Benz Aktiengesellschaft Liquid-cooled internal combustion engine
US4147139A (en) * 1976-04-10 1979-04-03 Daimler-Benz Aktiengesellschaft Liquid-cooled internal combustion engine
US4364338A (en) * 1978-10-31 1982-12-21 Alfa Romeo S.P.A. Circuit of the coolant in internal combustion engines for improving engine operation after cold starting
US4393819A (en) * 1981-04-30 1983-07-19 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for water-cooled engine
US4399776A (en) * 1981-05-01 1983-08-23 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for a water-cooled engine
US4399775A (en) * 1981-04-30 1983-08-23 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for a water-cooled engine
US4409927A (en) * 1980-03-31 1983-10-18 Halliburton Company Flameless nitrogen skid unit with transmission retarder
US4430966A (en) * 1981-03-24 1984-02-14 Labavia - S.G.E. Heat regulation circuits for vehicles equipped with an electric retarder
US4438729A (en) * 1980-03-31 1984-03-27 Halliburton Company Flameless nitrogen skid unit
US4458633A (en) * 1981-05-18 1984-07-10 Halliburton Company Flameless nitrogen skid unit
US4509481A (en) * 1984-01-25 1985-04-09 Nissan Motor Co., Ltd. Internal combustion engine with cooling system
US4520767A (en) * 1983-09-16 1985-06-04 Cummins Engine Company Low flow cooling system and apparatus
US4537158A (en) * 1983-06-04 1985-08-27 Behr-Thomson Degnstoffregler GmbH Apparatus for cooling an internal combustion engine
US4539944A (en) * 1981-04-06 1985-09-10 Alfa Romeo Auto S.P.A. Temperature-controlling system for the liquid coolant of a motor car internal-combustion engine
US5488937A (en) * 1993-08-13 1996-02-06 Kuze; Yoshikazu Temperature control system for keeping temperature of an element of an internal combustion engine at a constant value
US5967101A (en) * 1998-05-01 1999-10-19 Chrysler Corporation Engine cooling system and thermostat with improved bypass control
US5970927A (en) * 1997-09-09 1999-10-26 Toyota Jidosha Kabushiki Kaisha Apparatus for circulating cooling water for internal combustion engine
US5970655A (en) * 1997-07-03 1999-10-26 Freeman; Jerry K. M. Christmas tree support apparatus and method
US6196168B1 (en) * 1996-09-17 2001-03-06 Modine Manufacturing Company Device and method for cooling and preheating
US6318076B1 (en) * 1999-07-15 2001-11-20 Hyundai Motor Company Apparatus for treating the exhaust gas of an internal combustion engine
WO2004046516A1 (de) * 2002-11-16 2004-06-03 Daimlerchrysler Ag Thermostatventil für ein kühlsystem einer brennkraftmaschine
US20050205683A1 (en) * 2002-03-08 2005-09-22 Manfred Schmitt Cooling circuit for an internal combustion engine
US20070079774A1 (en) * 2005-10-08 2007-04-12 Itw Automotive Products Gmbh & Co. Kg Cooling system for a combustion engine
US20100095908A1 (en) * 2008-10-17 2010-04-22 Caterpillar Inc. Multi-thermostat engine cooling system
US20100122671A1 (en) * 2008-11-18 2010-05-20 Hyundai Motor Company Cooling circuit of engine
US20100326375A1 (en) * 2008-02-20 2010-12-30 Toyota Jidosha Kabushiki Kaisha Thermostat device
FR3002281A1 (fr) * 2013-02-19 2014-08-22 Peugeot Citroen Automobiles Sa Circuit de refroidissement pilote pour moteur thermique de vehicule automobile et moteur thermique de vehicule automobile correspondant
US20150053778A1 (en) * 2012-04-05 2015-02-26 Scania Cv Ab Thermostat device and cooling system
US20150101549A1 (en) * 2013-10-14 2015-04-16 GM Global Technology Operations LLC Cooling system for an internal combustion engine
US20150267603A1 (en) * 2012-05-14 2015-09-24 Nissan Motor Co., Ltd. Cooling control device and cooling control method for internal combustion engine
US20170114700A1 (en) * 2015-10-27 2017-04-27 Ford Global Technologies, Llc Cooling system for an internal combustion engine

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DE4330215A1 (de) * 1993-09-07 1995-03-09 Behr Thomson Dehnstoffregler Kühlanlage für einen Verbrennungsmotor eines Kraftfahrzeuges mit einem Ventil

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US3921600A (en) * 1973-03-22 1975-11-25 Bayerische Motoren Werke Ag Circulating cooling system for piston internal combustion engines
US3877443A (en) * 1973-03-22 1975-04-15 Bayerische Motoren Werke Ag Circulating cooling installation for piston internal combustion engines
US3907199A (en) * 1974-11-18 1975-09-23 Ford Motor Co Combination engine cooling system and passenger compartment heating system for an automotive vehicle
US4144849A (en) * 1976-04-10 1979-03-20 Daimler-Benz Aktiengesellschaft Liquid-cooled internal combustion engine
US4147139A (en) * 1976-04-10 1979-04-03 Daimler-Benz Aktiengesellschaft Liquid-cooled internal combustion engine
US4364338A (en) * 1978-10-31 1982-12-21 Alfa Romeo S.P.A. Circuit of the coolant in internal combustion engines for improving engine operation after cold starting
US4438729A (en) * 1980-03-31 1984-03-27 Halliburton Company Flameless nitrogen skid unit
US5551242A (en) 1980-03-31 1996-09-03 Halliburton Company Flameless nitrogen skid unit
US4409927A (en) * 1980-03-31 1983-10-18 Halliburton Company Flameless nitrogen skid unit with transmission retarder
US4430966A (en) * 1981-03-24 1984-02-14 Labavia - S.G.E. Heat regulation circuits for vehicles equipped with an electric retarder
US4539944A (en) * 1981-04-06 1985-09-10 Alfa Romeo Auto S.P.A. Temperature-controlling system for the liquid coolant of a motor car internal-combustion engine
US4399775A (en) * 1981-04-30 1983-08-23 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for a water-cooled engine
US4393819A (en) * 1981-04-30 1983-07-19 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for water-cooled engine
US4399776A (en) * 1981-05-01 1983-08-23 Fuji Jukogyo Kabushiki Kaisha System for controlling cooling water temperature for a water-cooled engine
US4458633A (en) * 1981-05-18 1984-07-10 Halliburton Company Flameless nitrogen skid unit
US4537158A (en) * 1983-06-04 1985-08-27 Behr-Thomson Degnstoffregler GmbH Apparatus for cooling an internal combustion engine
US4520767A (en) * 1983-09-16 1985-06-04 Cummins Engine Company Low flow cooling system and apparatus
US4509481A (en) * 1984-01-25 1985-04-09 Nissan Motor Co., Ltd. Internal combustion engine with cooling system
US5488937A (en) * 1993-08-13 1996-02-06 Kuze; Yoshikazu Temperature control system for keeping temperature of an element of an internal combustion engine at a constant value
US6196168B1 (en) * 1996-09-17 2001-03-06 Modine Manufacturing Company Device and method for cooling and preheating
US5970655A (en) * 1997-07-03 1999-10-26 Freeman; Jerry K. M. Christmas tree support apparatus and method
US5970927A (en) * 1997-09-09 1999-10-26 Toyota Jidosha Kabushiki Kaisha Apparatus for circulating cooling water for internal combustion engine
US5967101A (en) * 1998-05-01 1999-10-19 Chrysler Corporation Engine cooling system and thermostat with improved bypass control
US6318076B1 (en) * 1999-07-15 2001-11-20 Hyundai Motor Company Apparatus for treating the exhaust gas of an internal combustion engine
US20050205683A1 (en) * 2002-03-08 2005-09-22 Manfred Schmitt Cooling circuit for an internal combustion engine
WO2004046516A1 (de) * 2002-11-16 2004-06-03 Daimlerchrysler Ag Thermostatventil für ein kühlsystem einer brennkraftmaschine
US7096831B2 (en) 2002-11-16 2006-08-29 Daimlerchrysler Ag Thermostatic valve for a cooling system of an internal combustion engine
US20070079774A1 (en) * 2005-10-08 2007-04-12 Itw Automotive Products Gmbh & Co. Kg Cooling system for a combustion engine
US7392769B2 (en) * 2005-10-08 2008-07-01 Itw Automotive Products Gmbh & Co. Kg Cooling system for a combustion engine
US20100326375A1 (en) * 2008-02-20 2010-12-30 Toyota Jidosha Kabushiki Kaisha Thermostat device
US8109242B2 (en) 2008-10-17 2012-02-07 Caterpillar Inc. Multi-thermostat engine cooling system
US20100095908A1 (en) * 2008-10-17 2010-04-22 Caterpillar Inc. Multi-thermostat engine cooling system
US8127723B2 (en) * 2008-11-18 2012-03-06 Hyundai Motor Company Cooling circuit of engine
US20100122671A1 (en) * 2008-11-18 2010-05-20 Hyundai Motor Company Cooling circuit of engine
US20150053778A1 (en) * 2012-04-05 2015-02-26 Scania Cv Ab Thermostat device and cooling system
US20150267603A1 (en) * 2012-05-14 2015-09-24 Nissan Motor Co., Ltd. Cooling control device and cooling control method for internal combustion engine
US10436101B2 (en) * 2012-05-14 2019-10-08 Nissan Motor Co., Ltd. Cooling control device and cooling control method for internal combustion engine
FR3002281A1 (fr) * 2013-02-19 2014-08-22 Peugeot Citroen Automobiles Sa Circuit de refroidissement pilote pour moteur thermique de vehicule automobile et moteur thermique de vehicule automobile correspondant
US9567892B2 (en) * 2013-10-14 2017-02-14 GM Global Technology Operations LLC Cooling system for an internal combustion engine
US20150101549A1 (en) * 2013-10-14 2015-04-16 GM Global Technology Operations LLC Cooling system for an internal combustion engine
US20170114700A1 (en) * 2015-10-27 2017-04-27 Ford Global Technologies, Llc Cooling system for an internal combustion engine
CN106988854A (zh) * 2015-10-27 2017-07-28 福特全球技术公司 用于内燃发动机的冷却系统
US10161290B2 (en) * 2015-10-27 2018-12-25 Ford Global Technologies, Llc Cooling system for an internal combustion engine
RU2698379C2 (ru) * 2015-10-27 2019-08-26 Форд Глобал Текнолоджиз, Ллк Система охлаждения двигателя внутреннего сгорания и узел термостатов для системы охлаждения
CN106988854B (zh) * 2015-10-27 2020-08-11 福特全球技术公司 用于内燃发动机的冷却系统

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Publication number Publication date
CH571649A5 (pt) 1976-01-15
BE795230A (fr) 1973-05-29
GB1421002A (en) 1976-01-14
DE2206266A1 (pt) 1973-08-23
SE394491B (sv) 1977-06-27
DE2206266B1 (de) 1973-08-23
IT978871B (it) 1974-09-20
FR2171823A5 (pt) 1973-09-21

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