EP0177860A2 - Dispositif pour protéger le circuit de refroidissement d'un moteur à combustion interne - Google Patents

Dispositif pour protéger le circuit de refroidissement d'un moteur à combustion interne Download PDF

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Publication number
EP0177860A2
EP0177860A2 EP85112273A EP85112273A EP0177860A2 EP 0177860 A2 EP0177860 A2 EP 0177860A2 EP 85112273 A EP85112273 A EP 85112273A EP 85112273 A EP85112273 A EP 85112273A EP 0177860 A2 EP0177860 A2 EP 0177860A2
Authority
EP
European Patent Office
Prior art keywords
pressure relief
relief valve
float
container
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.)
Granted
Application number
EP85112273A
Other languages
German (de)
English (en)
Other versions
EP0177860A3 (en
EP0177860B1 (fr
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/fr
Publication of EP0177860A3 publication Critical patent/EP0177860A3/de
Application granted granted Critical
Publication of EP0177860B1 publication Critical patent/EP0177860B1/fr
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 engine, against overpressure with an overpressure valve arranged in the upper region of a coolant-carrying container, which is set to an opening pressure p 1 .
  • the pressure relief valve of a coolant circuit of the type mentioned is usually set to an opening pressure of approximately 1.1 to 1.15 bar. If the pressure in the coolant circuit exceeds this value, coolant, gases or water vapor can escape via this pressure relief valve. If an internal combustion engine is operated for a certain time and thereby heated and then switched off, local overheating can produce steam, for example, on the cylinder heads. If the coolant circulation is interrupted, the steam generated cannot separate out. This vapor formation results in an increase in volume, so that there is a risk that coolant is ejected via the pressure relief valve, which is then missing for normal operation.
  • the invention has for its object to provide a device of the type mentioned, in which the escape of coolant is prevented after switching off a heated internal combustion engine without the entire coolant circuit must be protected with a higher overpressure during operation.
  • a float is arranged in the container, which is sealingly deliverable to a feed to the pressure relief valve.
  • the invention takes advantage of the fact that in the event of vapor formation due to local overheating and the associated increase in volume, the coolant level in the container rises and entrains the float, so that it seals against the supply to the pressure relief valve. As a result, there is no longer a direct connection between the interior of the coolant-carrying container and the pressure relief valve, so that coolant can no longer escape to the outside.
  • the increased overpressure now possible in the cooling water circuit essentially prevents further steam formation.
  • a second pressure relief valve is provided, which is designed for a higher opening pressure P 2 than the first pressure relief valve.
  • the increased opening pressure of the second pressure relief valve which is, for example, 1.5 bar, prevents an excessive pressure occurring in the coolant circuit when steam is formed during the shutdown phase of the internal combustion engine.
  • the opening pressure P2 of the second pressure relief valve is expediently chosen so that on the one hand the risk of damage due to increased stress on the parts of the coolant circuit due to the high pressure is excluded, but that on the other hand during this shutdown phase of the internal combustion engine Vapor formation is restricted and coolant ejection is prevented.
  • the second pressure relief valve is installed in the float and connects the feed to the first pressure relief valve with the container.
  • the second pressure relief valve is thus connected in series with the first pressure relief valve.
  • the float is guided in a cage arranged in the container. This ensures that the float moves in a defined path.
  • the float with the second pressure relief valve and the cage is designed as an insert which can be inserted sealingly into an opening in 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.
  • the float is in the area of the slots in the extension, there is a relatively 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 connects to the internal combustion engine 1 via a thermostatic valve 4 connected is.
  • an expansion tank 6 is arranged, which is located at the highest point of 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 in the expansion tank 6, ie 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 protected against overpressure by two pressure relief valves 16 and 21 at predetermined opening pressures.
  • the pressure relief valve 16 operates 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 p 2 , which can be, for example, 1.5 to 1.6 bar.
  • the overpressure safety 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.
  • 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, which is attached to the filler neck 12, connects.
  • 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 functional during normal operation of the internal combustion engine 1, ie the coolant circuit is designed for an excess pressure of approximately 1.15 bar. If a higher overpressure occurs, the overpressure valve 16 opens, so that gas or water trapped in the coolant can escape via the connecting 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 used, 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 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 replenished via the insert 30 with the bayonet lock 31 removed. If the coolant rises in the expansion tank 6 the level 17a, the float 19 is raised and its upper edge reaches the no longer slotted area of the tubular extension 18.
  • the inflow cross-section to the expansion tank 6 thus becomes subject to the play between the upper edge of the float 19 and the extension 18 limited so that it is significantly reduced.
  • coolant liquid collects in the feed line 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 to the expansion tank 6 increased level, which is shown for example with the 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, which means that further vapor bubble formation is 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 is then adjusted to an opening pressure of 0.45 designed by appropriate dimensioning of the closing spring 22.
  • a throttle opening 28 is provided which, bypassing the float 19 and the second pressure relief valve 21, connects the interior of the expansion tank 6 with the first pressure relief valve 16.
  • This throttle opening is the one shown Embodiment of a channel 28 penetrating the valve plate 23 and the shoulder 36.
  • the cross section of this throttle opening ie the channel 28, is dimensioned such that no coolant is ejected through it in the shutdown phase when there is a risk of vapor bubbles forming, but after a predeterminable 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 Dispositif pour protéger le circuit de refroidissement d'un moteur à combustion interne Expired EP0177860B1 (fr)

Applications Claiming Priority (2)

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

Publications (3)

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

Family

ID=6247260

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112273A Expired EP0177860B1 (fr) 1984-10-06 1985-09-27 Dispositif pour protéger le circuit de refroidissement d'un moteur à combustion interne

Country Status (4)

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

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3803165A1 (de) * 1988-02-03 1989-08-17 Laengerer & Reich Kuehler Kuehlfluessigkeitsbehaelter fuer fluessigkeitsgekuehlte brennkraftmaschinen
EP0464317A1 (fr) * 1990-06-29 1992-01-08 Mercedes-Benz Ag Unité de soupape de pression dans un vase d'expansion d'un circuit de refroidissement d'un moteur à combustion interne
FR2673679A1 (fr) * 1991-03-06 1992-09-11 Daimler Benz Ag Reservoir de compensation d'eau de refroidissement.
DE4233038C1 (de) * 1992-10-01 1993-11-25 Daimler Benz Ag Überdrucksicherung für einen Kühlmittelkreislauf
DE29617824U1 (de) * 1996-10-14 1997-02-13 Kuhlmann, Günter, 83413 Fridolfing Kühlkreislauf-Sicherheitsvorrichtung
WO1999028605A1 (fr) * 1997-12-03 1999-06-10 Heinrich Reutter Couvercle de fermeture
WO2001069057A1 (fr) * 2000-03-13 2001-09-20 Heinrich Reutter Couvercle de fermeture
WO2001075282A1 (fr) * 2000-03-31 2001-10-11 Heinrich Reutter Bouchon de fermeture
WO2016094410A1 (fr) * 2014-12-08 2016-06-16 Toledo Molding & Die, Inc. Réservoir de liquide de refroidissement à double chambre

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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
DE4124182C1 (fr) * 1991-07-20 1992-06-04 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4228185C2 (de) * 1992-08-25 1996-02-15 Daimler Benz Ag Vorrichtung zur Steuerung des Druckes der Kühlflüssigkeit einer Brennkraftmaschine
DE19611095A1 (de) * 1996-03-21 1997-09-25 Bayerische Motoren Werke Ag Kühlsystem für eine flüssigkeitsgekühlte Brennkraftmaschine
DE19642114A1 (de) * 1996-10-14 1997-03-27 Guenter Kuhlmann Kühlkreislauf-Sicherheitsventil mit "hot stop"-Ventil für PKW- und LKW-Motoren
US6397826B1 (en) 1998-12-18 2002-06-04 Clean Fuel Technology, Inc. Fuel cooling system for fuel emulsion based compression ignition engine
US6532910B2 (en) 2001-02-20 2003-03-18 Volvo Trucks North America, Inc. Engine cooling system
US7152555B2 (en) * 2001-02-20 2006-12-26 Volvo Trucks North America, Inc. Engine cooling system
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***及其储水器
KR101542985B1 (ko) 2013-12-20 2015-08-07 현대자동차 주식회사 준 가압식 냉각수 리저버 탱크
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
KR20210076445A (ko) * 2019-12-16 2021-06-24 현대자동차주식회사 자동차용 통합 리저버

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US1531579A (en) * 1923-09-26 1925-03-31 Alfred L Sohm Indicator
US1541073A (en) * 1924-09-12 1925-06-09 Alfred L Sohm Indicator
FR644445A (fr) * 1927-11-24 1928-10-08 Dispositif de retenue d'eau dans les radiateurs d'automobiles ou moteurs à combustion
FR1014869A (fr) * 1950-03-20 1952-08-25 Tech Et Commerciale D Installa Dispositif de sécurité, notamment pour réservoirs mobiles à produits volatils inflammables
DE2104071A1 (de) * 1970-02-17 1971-08-26 Muller, Jacques, La Garenne Colom bes, Seine (Frankreich) Sicherheitsvorrichtung zum Auffüllen von Behaltern und Tanks
DE2509995A1 (de) * 1974-03-14 1975-12-18 Nippon Denso Co Kuehlerverschluss
GB1488484A (en) * 1974-11-01 1977-10-12 Chrysler Uk Header tanks for coolant radiators
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
DE3045357A1 (de) * 1980-12-02 1982-06-09 Daimler-Benz Ag, 7000 Stuttgart "kuehlsystem fuer eine brennkraftmaschine"
DE3143749A1 (de) * 1981-11-04 1983-05-11 Magirus-Deutz Ag, 7900 Ulm Vorrichtung zur absicherung des wasserdruckes im kuehlwasserkreislauf einer brennkraftmaschine

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US1703163A (en) * 1921-11-28 1929-02-26 Harrison Radiator Corp Cooling system
US2127271A (en) * 1936-11-17 1938-08-16 Schenk William Water protective device for automobile motors
US3284004A (en) * 1964-11-18 1966-11-08 Ford Motor Co Temperature and pressure responsive filler cap
FR2529951A1 (fr) * 1982-07-08 1984-01-13 Renault Vehicules Ind Dispositif de pressurisation du circuit de refroidissement d'un moteur thermique

Patent Citations (11)

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Publication number Priority date Publication date Assignee Title
US1531579A (en) * 1923-09-26 1925-03-31 Alfred L Sohm Indicator
US1541073A (en) * 1924-09-12 1925-06-09 Alfred L Sohm Indicator
FR644445A (fr) * 1927-11-24 1928-10-08 Dispositif de retenue d'eau dans les radiateurs d'automobiles ou moteurs à combustion
FR1014869A (fr) * 1950-03-20 1952-08-25 Tech Et Commerciale D Installa Dispositif de sécurité, notamment pour réservoirs mobiles à produits volatils inflammables
DE2104071A1 (de) * 1970-02-17 1971-08-26 Muller, Jacques, La Garenne Colom bes, Seine (Frankreich) Sicherheitsvorrichtung zum Auffüllen von Behaltern und Tanks
DE2509995A1 (de) * 1974-03-14 1975-12-18 Nippon Denso Co Kuehlerverschluss
GB1488484A (en) * 1974-11-01 1977-10-12 Chrysler Uk Header tanks for coolant radiators
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
DE3045357A1 (de) * 1980-12-02 1982-06-09 Daimler-Benz Ag, 7000 Stuttgart "kuehlsystem fuer eine brennkraftmaschine"
DE3143749A1 (de) * 1981-11-04 1983-05-11 Magirus-Deutz Ag, 7900 Ulm Vorrichtung zur absicherung des wasserdruckes im kuehlwasserkreislauf einer brennkraftmaschine

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3803165A1 (de) * 1988-02-03 1989-08-17 Laengerer & Reich Kuehler Kuehlfluessigkeitsbehaelter fuer fluessigkeitsgekuehlte brennkraftmaschinen
EP0464317A1 (fr) * 1990-06-29 1992-01-08 Mercedes-Benz Ag Unité de soupape de pression dans un vase d'expansion d'un circuit de refroidissement d'un moteur à combustion interne
GB2253695B (en) * 1991-03-06 1994-08-31 Daimler Benz Ag A cooling water expansion tank
FR2673679A1 (fr) * 1991-03-06 1992-09-11 Daimler Benz Ag Reservoir de compensation d'eau de refroidissement.
GB2253695A (en) * 1991-03-06 1992-09-16 Daimler Benz Ag A cooling water expansion tank
US5163506A (en) * 1991-03-06 1992-11-17 Mercedes-Benz Ag Cooling water expansion tank
US5357909A (en) * 1992-10-01 1994-10-25 Mercedes-Benz Ag Arrangement for protecting a cooling system from excessive pressure
FR2696501A1 (fr) * 1992-10-01 1994-04-08 Daimler Benz Ag Dispositif de protection contre la surpression pour un circuit de fluide de refroidissement.
DE4233038C1 (de) * 1992-10-01 1993-11-25 Daimler Benz Ag Überdrucksicherung für einen Kühlmittelkreislauf
DE29617824U1 (de) * 1996-10-14 1997-02-13 Kuhlmann, Günter, 83413 Fridolfing Kühlkreislauf-Sicherheitsvorrichtung
WO1999028605A1 (fr) * 1997-12-03 1999-06-10 Heinrich Reutter Couvercle de fermeture
US6367644B1 (en) 1997-12-03 2002-04-09 Heinrich Reutter Sealing cap
WO2001069057A1 (fr) * 2000-03-13 2001-09-20 Heinrich Reutter Couvercle de fermeture
WO2001075282A1 (fr) * 2000-03-31 2001-10-11 Heinrich Reutter Bouchon de fermeture
WO2016094410A1 (fr) * 2014-12-08 2016-06-16 Toledo Molding & Die, Inc. Réservoir de liquide de refroidissement à double chambre
US9856777B2 (en) 2014-12-08 2018-01-02 Toledo Molding & Die, Inc. Dual chamber coolant reservoir

Also Published As

Publication number Publication date
DE3436702A1 (de) 1986-04-10
DE3574899D1 (de) 1990-01-25
EP0177860A3 (en) 1987-03-25
EP0177860B1 (fr) 1989-12-20
ES8608629A1 (es) 1986-07-16
US4640235A (en) 1987-02-03
ES547595A0 (es) 1986-07-16
DE3436702C2 (fr) 1987-09-03

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