EP0177860B1 - Vorrichtung zum Absichern des Kühlmittelkreislaufs eines Verbrennungsmotors - Google Patents

Vorrichtung zum Absichern des Kühlmittelkreislaufs eines Verbrennungsmotors Download PDF

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Publication number
EP0177860B1
EP0177860B1 EP85112273A EP85112273A EP0177860B1 EP 0177860 B1 EP0177860 B1 EP 0177860B1 EP 85112273 A EP85112273 A EP 85112273A EP 85112273 A EP85112273 A EP 85112273A EP 0177860 B1 EP0177860 B1 EP 0177860B1
Authority
EP
European Patent Office
Prior art keywords
pressure relief
relief valve
container
float
valve
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.)
Expired
Application number
EP85112273A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0177860A3 (en
EP0177860A2 (de
Inventor
Hans Dipl.-Ing. Martin
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP0177860A2 publication Critical patent/EP0177860A2/de
Publication of EP0177860A3 publication Critical patent/EP0177860A3/de
Application granted granted Critical
Publication of EP0177860B1 publication Critical patent/EP0177860B1/de
Expired legal-status Critical Current

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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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/14—Indicating devices; Other safety devices
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/029—Expansion reservoirs
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/14—Indicating devices; Other safety devices
    • F01P11/18—Indicating devices; Other safety devices concerning coolant pressure, coolant flow, or liquid-coolant level
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0238—Closure caps with overpressure valves or vent valves

Definitions

  • the invention relates to a device for securing the coolant circuit of an internal combustion engine, in particular a motor vehicle internal combustion engine, according to the preamble of patent claim 1.
  • coolant circuit It is common practice to secure the coolant circuit to an opening pressure of approximately 1.1 bar to 1.15 bar. If the pressure in the coolant circuit exceeds this value, coolant, gases or water vapor can occur via pressure relief valves. If an internal combustion engine is operated for a certain time, thereby heated and then switched off, steam can form in the coolant circuit due to local overheating, for example on the cylinder heads. If the coolant circulation is interrupted after the internal combustion engine is switched off, the steam generated cannot separate out. This vapor formation causes an increase in volume, which can lead to coolant being ejected via a pressure relief valve. This ejected coolant is then no longer available for normal operation. In order to prevent such coolant ejection after the internal combustion engine has been switched off, it would be possible to set the cooling water circuit to a higher opening pressure. However, this would lead to an undesirable increase in the stress on the parts of the cooling system in normal operation.
  • a device for securing the cooling circuit of an internal combustion engine was known (DE-3 143 749 A1), in which two pressure relief valves are arranged in the upper region of a container carrying coolant. One of the pressure relief valves is set to a lower opening pressure, the operating pressure, and the other pressure relief valve is set to an increased opening pressure.
  • the pressure relief valve set to the operating pressure is preceded by a solenoid valve which is opened when the motor is switched on and closed when the motor is switched off. By switching the motor on and off, a switch from operating pressure to the increased opening pressure is thus effected via the additional solenoid valve.
  • the invention has for its object to provide a device according to the preamble of claim 1 so that a simple construction with high functional reliability is obtained, in which a coolant ejection can be largely prevented during the shutdown phase of the internal combustion engine.
  • the pressure relief valve built into the float is connected in series with the first pressure relief valve. This results in a pressure addition between the opening pressures of the two pressure relief valves, so that the second pressure relief valve only has to be designed for the difference between the opening pressure of the first pressure relief valve and the desired increased opening pressure. If steam forms during the shutdown phase of the internal combustion engine, i.e. If there is a risk of coolant ejection, the coolant circuit is thus sealed by the added opening pressures. Since the float is guided in a cage, it moves in a defined path so that the effect of the second pressure relief valve is always maintained.
  • the float with the second pressure relief valve and the cage is designed as an insert which can be inserted sealingly into an opening of the container and contains the feed to the first pressure relief valve.
  • This insert forms a preassembled unit that is inserted as a whole into the container.
  • the insert is inserted into a filler neck of the container and has a valve seat for the valve plate of the first pressure relief valve held by means of a bayonet lock.
  • the filler neck of the container can then have a relatively simple design.
  • the insert has a tubular extension adjoining the feed to the first pressure relief valve, in which the float is guided with play and the end pointing into the container is divided into individual legs by axial slots.
  • a simple cage for guiding the float is obtained on the one hand, while on the other hand an overfill protection for the container is created.
  • a is relative large opening cross-section to the container through which the coolant can be filled. If the float reaches the unslit area of the attachment with increasing liquid level, there is only a small free cross section, so that further refilling of coolant is at least severely hindered.
  • the legs of the extension are provided at their free ends with radially inwardly directed stops.
  • the legs are slightly elastically spread when the float is inserted and secure the lowest position after the float is inserted.
  • the float can thus be easily combined with the insert to form a structural unit.
  • a throttle opening bypassing the float is guided from the interior of the container to the first pressure relief valve. This ensures that when the coolant circuit is overfilled, the pressure in the cooling water circuit can decrease to the opening pressure of the first pressure relief valve over a predeterminable period of time, so that even if the coolant circuit is overfilled, it is not exposed to the increased pressure for a prolonged period.
  • the cross section of the throttle opening is selected so that no coolant ejection occurs through the throttle opening during normal filling during the engine shutdown phase.
  • the inlet of the throttle opening is arranged in the region of the highest point of the container. As a result, the excessive pressure is released by the escape of gas or water vapor.
  • the inlet of the throttle opening is arranged at a point immersed in the cooling water. It is thereby achieved that the pressure is reduced by ejecting coolant, but only the amount of coolant given by any overfilling is ejected.
  • FIG. 1 shows an internal combustion engine 1 which has an internal coolant guide. Water, which is provided with an antifreeze, is usually used as the coolant.
  • a cooler is connected to the coolant guide of the internal combustion engine 1 via lines in which a coolant pump 2 is arranged.
  • the coolant pump 2 conveys the coolant to the internal combustion engine 1, from which it flows in the direction of the arrow A to the radiator 3.
  • a short-circuit line 5 is arranged in front of the cooler 3 and is connected to the supply line to the internal combustion engine 1 via a thermostatic valve 4.
  • an expansion tank 6 is arranged, which is located at the highest point in the coolant circuit.
  • the inlet 11 of the expansion tank 6 is connected via a line 31 to the highest point of the cooler 3.
  • the outlet 10 of the expansion tank 6 is connected via a line 30 to the suction side of the coolant pump 2.
  • the coolant is degassed, i.e.
  • the vapor or gas inclusions contained in the coolant reach the expansion tank 6 in an emulsion, in which they can be separated from the coolant and can escape via an overflow 8.
  • the coolant circuit is secured by two pressure relief valves 16 and 21 to predetermined opening pressures against excess pressure.
  • the pressure relief valve 16 is in normal operation and is set, for example, to an opening pressure P1 of approximately 1.15 bar.
  • the pressure relief valve 21, which only functions in certain operating states, is set to a higher opening pressure P2 , which can be, for example, 1.5 to 1.6 bar.
  • the pressure relief device containing the two pressure relief valves 16 and 21 is arranged on the expansion tank 6. It is of course also possible to provide them at another point in the coolant circuit, in particular on the top of the cooler 3, for example if no separate expansion tank 6 is provided in the coolant circuit.
  • An insert 30 containing the two pressure relief valves 16 and 21 is inserted into the filler neck 12 of the expansion tank 6 and has an essentially cylindrical outer contour.
  • the insert 30 engages around the edge of the flange 33 of the filler neck 12 with a flange 32 and is secured in a latching manner thereon.
  • at least two sealing rings 39 are arranged between the filler neck 12 and the insert 30.
  • a so-called bayonet lock 31 is removably attached to the flange 32 of the insert 30 and carries a valve disk 13 of the first pressure relief valve 16.
  • the valve disk 13 is guided in the axial direction on a bolt 40 of the bayonet lock 31 and is loaded by means of a compression spring 14.
  • a valve seat 15 is assigned to the valve plate 13 and is formed by a narrowed shoulder of the insert 30. Outside the valve seat 15, the insert 30 is connected to a plurality of axially directed openings 41, which lead to an annular groove-shaped circumferential channel 42, to which the overflow 8 connects, which is attached to the filler neck 12.
  • the compression spring 14 of the first pressure relief valve 16 is designed for an opening pressure in the range of approximately 1.15 bar. This pressure relief valve 16 is in the normal range drive the internal combustion engine 1 in function, ie the coolant circuit is designed for an excess pressure of about 1.15 bar. If a higher overpressure occurs, the overpressure valve 16 opens, so that gas or water vapor enclosed in the coolant can escape via the connection openings 41, the channel 42 and the overflow 8.
  • the insert 30 projects into the expansion tank 6 with a tubular extension 18.
  • the approach 18, which is closed in its upper area, is divided into individual legs 34 in its lower area by axial slots.
  • a float 19 is inserted, which can be inserted with elastic expansion of the legs 34.
  • the ends of the legs 34 are provided with radially directed stops 35 which prevent the float 19 from falling out.
  • the tubular extension 19 is bounded at the top by a valve seat 27 which has a smaller diameter than the tubular extension 18.
  • the valve seat 27 is located on a feed, designed as a cylindrical channel, to the valve seat 15 of the first pressure relief valve 16.
  • the valve seat 27 is assigned as a valve plate, the float 19, the upper side of which is provided with a sealing washer 26:
  • the float 19 is designed as a cylindrical hollow body which is tightly sealed to the outside. If there is a risk of leaks, it is expedient to provide buoyancy bodies within the hollow body of the float 19, which are made of a foam, for example.
  • the float 19 contains a second pressure relief valve 21, which releases or blocks a connection between the interior of the expansion tank 6 and the first pressure relief valve 16.
  • This pressure relief valve 21 has a valve disk 23, the bent edge of which bears from the outside against the sealing disk 26, which is arranged on the upper side of the float 19.
  • the float 19 is provided with a continuous channel 24, to which an opening of the sealing disk 26 is assigned and which is closed by the valve plate 23.
  • an extension 36 which is guided through the channel 24 of the float and on whose end protruding from the other side of the float engages a conical closing spring 22 which is supported on a securing ring 43 attached to the extension 36.
  • the other end of the closing spring 22 is supported on the underside of the float 19.
  • webs projecting inward into the channel 24 are provided, which serve to radially guide the extension 36.
  • the float 19 guided in the neck 18 of the insert 30 has two functions. In one function it serves as an overfill protection.
  • Line 17a indicates the liquid level up to which the coolant circuit is to be filled in the cold state. Up to this liquid level 17a, the float 19 is in the lowest position in which it rests on the stops 35.
  • the axial slots of the extension 18 are dimensioned such that they are sufficiently longer than the height of the float 19, so that they release a sufficient cross-section when coolant is refilled through the insert 30 with the bayonet lock 31 removed. If the coolant in the expansion tank 6 rises above the level 17a, the float 19 is raised and reaches with its upper edge in the no longer slotted area of the tubular extension 18.
  • the inflow cross section to the expansion tank 6 is due to the game between the upper Edge of the float 19 and the approach 18 limited, so that it is significantly reduced.
  • coolant liquid collects in the feed above the float until the coolant runs off via the overflow 8. Even with less careful operation, this is a sufficiently reliable indication that the further supply of coolant should be interrupted.
  • the play between the float 19 and the approach 18 is still large enough so that a perfect degassing can take place via the first pressure relief valve 16.
  • the tubular extension 18 projecting into the expansion tank 6 also ensures that an air cushion is present in any case in the upper region of the expansion tank 6.
  • the coolant circuit is designed in such a way that, due to the heating of the coolant, the increased coolant level 17b is set, at which the float 19 is still at a sufficient distance from the valve seat 27. In this operating state, only the first pressure relief valve 16 is in operation, i.e. the coolant circuit is secured to the opening pressure of this pressure relief valve 16.
  • the coolant circulation is interrupted. There is then the risk that vapor bubbles form at overheated points within the coolant guide of the internal combustion engine, which lead to an increase in the volume of the coolant in the coolant circuit.
  • the coolant then rises in the expansion tank 6 to an elevated level, which is shown, for example, by line 17c.
  • the float 19 is then moved upwards so far that it lies against the valve seat 27 with its sealing washer 26.
  • the pressure relief valve 16 is thus separated from the coolant circuit, so that it is out of function.
  • the possible overpressure in the coolant circuit is then no longer limited by the overpressure valve 16.
  • the first pressure relief valve 16 By shutting off the first pressure relief valve 16, it is prevented that, in the case of a further increase in volume due to the formation of vapor bubbles or the like. Coolant is ejected via the first pressure relief valve 16. A higher overpressure can occur within the coolant circuit, leading to this leads to further vapor bubble formation being restricted.
  • the possible overpressure is determined by the second overpressure valve 21, which is designed for a corresponding opening pressure. Since the first pressure relief valve 16 and the second pressure relief valve 21 are arranged in series one behind the other, this opening pressure is determined from the addition of the opening pressures of the first pressure relief valve 16 and the second pressure relief valve 21.
  • the second pressure relief valve 21 then becomes an opening pressure of 0.45 designed by appropriate dimensioning of the closing spring 22.
  • a throttle opening 28 is provided, which under Bypassing the float 19 and the second pressure relief valve 21 connects the interior of the expansion tank 6 to the first pressure relief valve 16.
  • this throttle opening consists of a channel 28 penetrating the valve plate 23 and the shoulder 36. The cross section of this throttle opening, i. H.
  • the channel 28 is dimensioned such that no coolant is ejected through it in the shutdown phase when there is a risk of vapor bubble formation, but after a predetermined period of time the pressure reduction to the opening pressure of the first pressure relief valve 16 is ensured.
  • the extension 36 dips into the coolant with the channel 28 serving as a throttle opening, so that the possible pressure reduction is caused by ejection of coolant, thereby reducing the overfill.
  • a throttle opening 37 which is shown in broken lines in FIG. 2, is guided through the insert 30 directly from the highest point of the expansion tank 6 to the area in front of the first pressure relief valve 16. In this case, the pressure is reduced in the event of overfilling by the escape of steam or gas or air via this throttle opening 37.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Safety Valves (AREA)
  • Motor Or Generator Cooling System (AREA)
EP85112273A 1984-10-06 1985-09-27 Vorrichtung zum Absichern des Kühlmittelkreislaufs eines Verbrennungsmotors Expired EP0177860B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843436702 DE3436702A1 (de) 1984-10-06 1984-10-06 Vorrichtung zum absichern des kuehlmittelkreislaufs eines verbrennungsmotors
DE3436702 1984-10-06

Publications (3)

Publication Number Publication Date
EP0177860A2 EP0177860A2 (de) 1986-04-16
EP0177860A3 EP0177860A3 (en) 1987-03-25
EP0177860B1 true EP0177860B1 (de) 1989-12-20

Family

ID=6247260

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112273A Expired EP0177860B1 (de) 1984-10-06 1985-09-27 Vorrichtung zum Absichern des Kühlmittelkreislaufs eines Verbrennungsmotors

Country Status (4)

Country Link
US (1) US4640235A (enrdf_load_stackoverflow)
EP (1) EP0177860B1 (enrdf_load_stackoverflow)
DE (2) DE3436702A1 (enrdf_load_stackoverflow)
ES (1) ES8608629A1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4228185A1 (de) * 1992-08-25 1994-03-03 Daimler Benz Ag Vorrichtung zur Steuerung des Druckes der Kühlflüssigkeit einer Brennkraftmaschine
DE19642114A1 (de) * 1996-10-14 1997-03-27 Guenter Kuhlmann Kühlkreislauf-Sicherheitsventil mit "hot stop"-Ventil für PKW- und LKW-Motoren
WO2024179780A1 (de) * 2023-03-01 2024-09-06 Bayerische Motoren Werke Aktiengesellschaft Messadapter für einen ausgleichsbehälter eines kraftfahrzeugs, ausgleichsbehälter sowie kraftfahrzeug

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Publication number Priority date Publication date Assignee Title
DE3517715C2 (de) * 1985-05-17 1993-10-28 Laengerer & Reich Kuehler Kühlflüssigkeitsbehälter für den Kühlflüssigkeitskreislauf einer Brennkraftmaschine
US4739824A (en) * 1987-01-08 1988-04-26 Susan E. Lund Hermetically sealed, relatively low pressure cooling system for internal combustion engines and method therefor
DE3803165C2 (de) * 1988-02-03 1994-05-19 Laengerer & Reich Kuehler Kühlflüssigkeitsbehälter für flüssigkeitsgekühlte Brennkraftmaschinen
DE4020866C1 (enrdf_load_stackoverflow) * 1990-06-29 1991-05-23 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4107183C1 (enrdf_load_stackoverflow) * 1991-03-06 1992-08-06 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4124182C1 (enrdf_load_stackoverflow) * 1991-07-20 1992-06-04 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4233038C1 (de) * 1992-10-01 1993-11-25 Daimler Benz Ag Überdrucksicherung für einen Kühlmittelkreislauf
DE19611095A1 (de) * 1996-03-21 1997-09-25 Bayerische Motoren Werke Ag Kühlsystem für eine flüssigkeitsgekühlte Brennkraftmaschine
DE29617824U1 (de) * 1996-10-14 1997-02-13 Kuhlmann, Günter, 83413 Fridolfing Kühlkreislauf-Sicherheitsvorrichtung
DE19753592A1 (de) * 1997-12-03 1999-06-10 Heinrich Reutter Verschlußdeckel
US6397826B1 (en) 1998-12-18 2002-06-04 Clean Fuel Technology, Inc. Fuel cooling system for fuel emulsion based compression ignition engine
DE10034762A1 (de) * 2000-03-13 2002-01-31 Heinrich Reutter Verschlussdeckel
DE10034761A1 (de) * 2000-03-31 2002-01-31 Heinrich Reutter Verschlussdeckel
US7152555B2 (en) * 2001-02-20 2006-12-26 Volvo Trucks North America, Inc. Engine cooling system
US6532910B2 (en) 2001-02-20 2003-03-18 Volvo Trucks North America, Inc. Engine cooling system
RU2217609C1 (ru) * 2002-04-15 2003-11-27 Государственное унитарное предприятие "Уральское конструкторское бюро транспортного машиностроения" Расширительный бачок системы охлаждения
JP2006151131A (ja) * 2004-11-26 2006-06-15 Yamaha Motor Co Ltd 車両
DE102007051758B4 (de) * 2007-10-30 2017-11-30 Bayerische Motoren Werke Aktiengesellschaft Verschlussdeckel mit einer integrierten durchsichtigen Linse für einen Kühlmittelausgleichsbehälter
CN102033589B (zh) * 2009-09-29 2014-01-22 鸿富锦精密工业（深圳）有限公司 水冷式散热系统及其储水器
KR101542985B1 (ko) 2013-12-20 2015-08-07 현대자동차 주식회사 준 가압식 냉각수 리저버 탱크
US9856777B2 (en) * 2014-12-08 2018-01-02 Toledo Molding & Die, Inc. Dual chamber coolant reservoir
TWM533845U (en) * 2016-06-06 2016-12-11 Cooler Master Technology Inc Pressurized infusion device and liquid cooling system
RU168690U1 (ru) * 2016-08-05 2017-02-15 Общество с ограниченной ответственностью "АЛЬСТОМ Атомэнергомаш "( ООО "ААЭМ ") Дыхательное устройство расширительного бака
KR102783402B1 (ko) * 2019-12-16 2025-03-19 현대자동차주식회사 자동차용 통합 리저버

Citations (2)

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GB1488484A (en) * 1974-11-01 1977-10-12 Chrysler Uk Header tanks for coolant radiators
DE3045357A1 (de) * 1980-12-02 1982-06-09 Daimler-Benz Ag, 7000 Stuttgart "kuehlsystem fuer eine brennkraftmaschine"

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FR1014869A (fr) * 1950-03-20 1952-08-25 Tech Et Commerciale D Installa Dispositif de sécurité, notamment pour réservoirs mobiles à produits volatils inflammables
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JPS5417900B2 (enrdf_load_stackoverflow) * 1974-03-14 1979-07-03
FR2439922A1 (fr) * 1978-10-24 1980-05-23 Perolo Claude Dispositif limiteur de remplissage pour reservoirs enterres
FR2476790A1 (fr) * 1980-02-21 1981-08-28 Lafon Georges Limiteur de remplissage pour cuves de stockage de fluide
DE3143749A1 (de) * 1981-11-04 1983-05-11 Magirus-Deutz Ag, 7900 Ulm Vorrichtung zur absicherung des wasserdruckes im kuehlwasserkreislauf einer brennkraftmaschine
FR2529951A1 (fr) * 1982-07-08 1984-01-13 Renault Vehicules Ind Dispositif de pressurisation du circuit de refroidissement d'un moteur thermique

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1488484A (en) * 1974-11-01 1977-10-12 Chrysler Uk Header tanks for coolant radiators
DE3045357A1 (de) * 1980-12-02 1982-06-09 Daimler-Benz Ag, 7000 Stuttgart "kuehlsystem fuer eine brennkraftmaschine"

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4228185A1 (de) * 1992-08-25 1994-03-03 Daimler Benz Ag Vorrichtung zur Steuerung des Druckes der Kühlflüssigkeit einer Brennkraftmaschine
DE19642114A1 (de) * 1996-10-14 1997-03-27 Guenter Kuhlmann Kühlkreislauf-Sicherheitsventil mit "hot stop"-Ventil für PKW- und LKW-Motoren
WO2024179780A1 (de) * 2023-03-01 2024-09-06 Bayerische Motoren Werke Aktiengesellschaft Messadapter für einen ausgleichsbehälter eines kraftfahrzeugs, ausgleichsbehälter sowie kraftfahrzeug

Also Published As

Publication number Publication date
DE3574899D1 (de) 1990-01-25
US4640235A (en) 1987-02-03
DE3436702C2 (enrdf_load_stackoverflow) 1987-09-03
EP0177860A3 (en) 1987-03-25
ES8608629A1 (es) 1986-07-16
DE3436702A1 (de) 1986-04-10
EP0177860A2 (de) 1986-04-16
ES547595A0 (es) 1986-07-16

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