EP0360252A2 - Closure cover for the filling aperture of a coolant tank in motor vehicle cooling systems - Google Patents

Closure cover for the filling aperture of a coolant tank in motor vehicle cooling systems Download PDF

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Publication number
EP0360252A2
EP0360252A2 EP89117413A EP89117413A EP0360252A2 EP 0360252 A2 EP0360252 A2 EP 0360252A2 EP 89117413 A EP89117413 A EP 89117413A EP 89117413 A EP89117413 A EP 89117413A EP 0360252 A2 EP0360252 A2 EP 0360252A2
Authority
EP
European Patent Office
Prior art keywords
housing
sleeve
spring
valve
cover
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
EP89117413A
Other languages
German (de)
French (fr)
Other versions
EP0360252A3 (en
EP0360252B1 (en
Inventor
Konrad Scharrer
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.)
Blau KG
Blau KG Fabrik fuer Kraftfahrzeugteile
Original Assignee
Blau KG
Blau KG Fabrik fuer Kraftfahrzeugteile
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 Blau KG, Blau KG Fabrik fuer Kraftfahrzeugteile filed Critical Blau KG
Priority to AT89117413T priority Critical patent/ATE84761T1/en
Publication of EP0360252A2 publication Critical patent/EP0360252A2/en
Publication of EP0360252A3 publication Critical patent/EP0360252A3/en
Application granted granted Critical
Publication of EP0360252B1 publication Critical patent/EP0360252B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • 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
    • 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
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • F01P2011/0266—Safety; Locking against opening activated by pressure

Definitions

  • the invention relates to a closure lid for the filling opening of a coolant container in automotive cooling systems
  • a lid housing engaging in the filling opening with a channel connecting the container space to be sealed with the outside air and a valve for shutting off the same with a valve membrane which has a sealing surface under the force of a Spring acting in the direction of the channel axis and supported on a surface fixed to the housing rests against a valve seat surrounding the channel and can be lifted off from it by the overpressure in the container space against the spring force.
  • the pressure value is set at which the valve opens in order to reduce an excess pressure prevailing in the cooling system to a predetermined value and thus prevent the radiator from bursting as a result of excess pressure.
  • a coolant pump that circulates the coolant in the cooling system is also put into operation, which creates a pressure difference between the suction side and the pressure side of the coolant pump within the cooling system.
  • the internal pressure of the cooler is reduced by a certain amount. The pressure difference that has to be overcome increases by exactly this amount until the safety valve in the sealing cap opens as a result of the excess pressure.
  • the coolant heats up, which increases the pressure in the cooling system. Due to the increased pressure difference on the suction side of the coolant pump, in the vicinity of which the closure cap is also located, the pressure can rise to a value which is above the opening pressure or pressure threshold value at which the valve in the closure cap would open when the coolant pump is at a standstill. If the engine is switched off in this state and the coolant pump is also shut down, there is no immediate pressure reduction on the suction side of the coolant pump. The pressure in the cooling system is above the opening pressure of the valve of the closure cover, so that it opens suddenly. This can result not only in loss of coolant, but also in injuries to people due to sudden escaping hot coolant or coolant vapor.
  • the invention has for its object to provide a cap of the type mentioned, in which the pressure difference until the opening pressure of the valve of the cap is reached regardless of whether the coolant pump is working or not.
  • valve seat is formed on a sleeve which is axially adjustable in the cover housing against the force of the spring and which, with an at least approximately axially normal surface facing away from the spring, adjoins a pressure chamber which, in the closed position of the closure cover, is opposite the Outside air and the container space closed and can be connected to the suction side of a coolant pump circulating the coolant in the cooling system.
  • a negative pressure is generated in the pressure chamber compared to the state when the coolant pump is at a standstill, as a result of which the sleeve is adjusted in the direction of the valve spring acting on the valve membrane.
  • the valve spring relaxes in the process, it now opens at a lower overpressure - in absolute terms. Due to the adjustable travel of the sleeve, the change in the opening pressure or threshold value can be selected so that it corresponds to the pressure reduction caused by switching on the coolant pump on the suction side thereof. If the coolant pump is switched off, the outlet pressure prevails again in the pressure chamber. The sleeve carrying the valve seat and thus also the valve spring are again adjusted into their starting position corresponding to the stationary coolant pump. The valve is thus opened both when the drive machine is at a standstill and when it is running, regardless of the pressure change caused by the coolant pump, in each case with the same pressure increase in the coolant tank. A sudden opening of the valve after switching off the coolant pump can no longer occur.
  • the guidance of the sleeve in the lid housing must be designed so that no pressure equalization between the interior of the container and the outside air can take place between the sleeve and the surrounding housing section. This can be achieved in a simple and effective manner in that a sealing membrane which enables the movement of the sleeve is arranged between the sleeve and the housing section surrounding it.
  • the sealing of the pressure chamber can be achieved in a structurally simple manner in that the pressure chamber is designed as an annular space surrounding the sleeve, which is at least partially enclosed by a bellows which can be expanded against the spring force. As a result, it is not necessary to seal parts which can be moved relative to one another.
  • the pressure chamber can be connected to the suction side of the coolant pump in a simple manner in that the pressure chamber has a connection opening that is open to the peripheral surface of the cover housing and that sealing rings are arranged axially on both sides of the cover housing on the peripheral surface, which seal seals against the filling opening Wall are determined, a connection channel which can be connected to the suction side of the coolant pump opening on this wall. If the cover is thus inserted into the filling opening, the connection between the suction side of the coolant pump and the pressure chamber is automatically established.
  • the closure cover When the closure cover is designed as a screw cover, it is expedient if the cover consists of a first housing part provided with an externally threaded connection and a second housing part which is freely rotatably connected to the latter and which receives the valve and carries the sealing rings. If this sealing cap is inserted into the filling opening, the first housing part can be screwed in without the second housing part carrying the sealing rings being rotated. It is only moved axially when the first housing part is screwed in.
  • 10 denotes an expansion tank of a motor vehicle radiator, in the filler neck 12 of which a screw cap generally designated 14 is screwed.
  • This comprises a first cover part 16 with a handle part 18 and an external thread connector 20 which is screwed into an internal thread section 22 of the filling opening 12.
  • a second cover part 24 is connected to the first cover part 16.
  • This has an essentially tubular housing 26, which is provided at its end facing the first cover part 16 with an annular extension 28 which engages in a tubular extension 30 of the first cover part 16 and with a radially outwardly directed ring claw 32 a radially after internally directed annular claw 34 of the tubular extension 30 engages behind, the extension 28 being able to be clipped into the tubular extension 30 due to the inclined surfaces 36 and 38 formed on the annular claws 32 and 34.
  • the second cover part 24 is thus held on the first cover part 16 in a freely rotatable manner.
  • sealing rings 40 which lie in axially spaced grooves 42 on the outer circumferential surface of the housing 26, on the inner circumferential surface 44 of the filling opening 12.
  • a sleeve 46 is held axially displaceably in the housing 26. This comprises a larger-diameter section 48 facing the first cover part 16 and a smaller-diameter section 50 facing the interior of the expansion tank 10.
  • the space between the sleeve 46 and the housing 26 is sealed by an annular sealing membrane 52, which with its inner bead-shaped edge 54 into a Groove 56 of the sleeve 46 engages and is clamped with its outer bead-shaped edge 58 between a shoulder 60 on the housing 26 and a support ring 62 engaging in it.
  • the support ring 62 also carries a radially inwardly extending annular bellows 64 which, together with the support ring 62, forms a closed annular space which is only accessible via a bore 66 passing through the support ring 62.
  • the support ring 62 and the bellows 64 are held by a closure part 68, which is inserted into the free end of the housing 26 facing the interior of the pressure compensating container 10 and is secured by a clip connection comprising an annular claw on the closure part 68 and an annular claw 72 on the housing 26 . With its annular surface 74 facing away from the closure part 68, the bellows 64 lies against an axially normal annular surface 76 of the sleeve.
  • the sleeve 46 has a radially outward-pointing flange 78 at the free end of the smaller-diameter section 50 on, which engages in an annular groove 80 of the closure member 68, the axial extent of which is greater than the axial extent of the flange 78.
  • the sleeve 46 can move axially when the bellows 64 is expanded between the position shown in FIG. 1 and the position shown in FIG.
  • the edge of the sleeve section 48 facing the first cover part 16 is designed as a valve seat 82 for an annular seal 84 which is clamped between a first steel membrane 86 and a second steel membrane 88.
  • the first steel membrane 86 is prestressed by a helical compression spring 90 against the valve seat 82, the helical compression spring 90 being supported on the one hand in a cup-shaped depression 92 in the cover 94 of the housing 26 and on the other hand in a pot-shaped depression of the first membrane 86.
  • the second membrane 88 is tensioned by a helical compression spring 98 against the surface of the ring seal 84 facing the sleeve 46, this helical compression spring 98 being supported on the one hand on the membrane 88 and on the other hand on an inner shoulder 100 of the sleeve 46.
  • the ring seal 84 lifts off the valve seat 82, so that a pressure equalization can take place through the sleeve 46 and openings 102 in the housing cover surface 94 into the cover space 104, which via one or more gaps 106 in the annular extension 28 and a vent 108 in the expansion tank 10 communicates with the outside air.
  • the membrane 88 lifts off the ring seal 84 so that a pressure equalization between these two parts and a central opening 109 in the membrane 86 can take place.
  • the wall section of the filling opening 12 lying between the sealing rings 40 has a larger diameter than the outer circumference of the cover housing 26, so that an annular space 110 is thereby formed which is connected to a connecting piece 114 via a radial connecting channel 112. At the same time, this annular space 110 is connected to the interior 116 of the bellows 64 via a bore 115 in the cover housing 26 and the bore 66 aligned with the bore 114.
  • the connecting piece 114 is connected to the suction side of the coolant pump circulating the cooling medium in the motor vehicle cooling system.
  • the bellows 64 By connecting the interior 116 of the bellows 64 to the suction side of the coolant pump, the bellows contracts due to the reduced pressure, as a result of which the sleeve 46 is moved downward into the position of FIG. 1 by the force of the spring 90. As a result, the spring 90 is relaxed and thus the overpressure threshold value is reduced, so that the pressure difference by which the pressure in the coolant tank has to rise until the valve opens is the same when the coolant pump is at a standstill and is working.

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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)
  • Closures For Containers (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

In a closure lid for the filling-opening (12) of a cooling medium container (10) in motor vehicle cooling systems comprising a cover housing (16, 24) which engages in the filling-opening (12), having a channel which connects the container space to be sealed to the exterior air and a valve (82, 84, 86, 88, 90, 98) for shutting off same with a valve membrane (86) which rests with a sealing face (84) against a valve seat (82), which surrounds the channel, under the force of a spring (90) which acts in the direction of the channel axis and is supported on a face (92) fixed to the housing and can be lifted by said valve seat counter to the spring force by means of overpressure in the container space, the valve seat (82) is constructed on a sleeve (46) which can be adjusted in the cover housing (26) axially counter to the force of the spring (90), which sleeve is adjacent, with a surface (76) facing away from the spring (90) and at least approximately normal to the axis, to a pressure space (116) which, in the closed position of the closure lid (14), is shut off from the exterior air and the container space and can be connected to the suction side of a cooling means pump which circulates the cooling means in the cooling system. <IMAGE>

Description

Die Erfindung betrifft einen Verschlußdeckel für die Füll­öffnung eines Kühlmittelbehälters in Kfz-Kühlanlagen um­fassend ein in die Füllöffnung eingreifendes Deckelgehäuse mit einem den zu verschließenden Behälterraum mit der Außenluft verbindenden Kanal und ein Ventil zum Absperren desselben mit einer Ventilmembran, die mit einer Dichtflä­che unter der Kraft einer in Richtung der Kanalachse wir­kenden und sich an einer gehäusefesten Fläche abstützenden Feder an einem den Kanal umgebenden Ventilsitz anliegt und von diesem durch Überdruck in dem Behälterraum gegen die Federkraft abhebbar ist.The invention relates to a closure lid for the filling opening of a coolant container in automotive cooling systems comprising a lid housing engaging in the filling opening with a channel connecting the container space to be sealed with the outside air and a valve for shutting off the same with a valve membrane which has a sealing surface under the force of a Spring acting in the direction of the channel axis and supported on a surface fixed to the housing rests against a valve seat surrounding the channel and can be lifted off from it by the overpressure in the container space against the spring force.

Durch die Wahl der Federvorspannung wird der Druckwert ein­gestellt, bei dem das Ventil öffnet, um einen in der Kühl­anlage herrschenden Überdruck bis auf einen vorgegebenen Wert abzubauen und damit ein Platzen des Kühlers infolge Überdrucks zu verhindern. Beim Start des Fahrzeuges wird auch eine das Kühlmittel in der Kühlanlage umwälzende Kühlmittelpumpe in Betrieb gesetzt, durch die innerhalb der Kühlanlage eine Druckdifferenz zwischen Saugseite und Druckseite der Kühlmittelpumpe entsteht. Auf der Saugseite der Kühlmittelpumpe vermindert sich der Innendruck des Kühlers um einen bestimmten Betrag. Um genau diesen Be­trag wächst damit die Druckdifferenz, die zu überwinden ist, bis das Sicherheitsventil im Verschlußdeckel infolge des Überdrucks öffnet. Liegt beispielsweise der Druck­schwellwert, bei dem das Ventil öffnet, bei einem Über­druck von 1,2 Bar und vermindert sich der Druck auf der Saugseite beim Anlaufen der Kühlmittelpumpe um 0,6 Bar, so ist bei laufendem Motor eine Druckdifferenz von 1,8 Bar zu überwinden, bis das Ventil im Verschlußdeckel öffnet.By selecting the spring preload, the pressure value is set at which the valve opens in order to reduce an excess pressure prevailing in the cooling system to a predetermined value and thus prevent the radiator from bursting as a result of excess pressure. When the vehicle is started, a coolant pump that circulates the coolant in the cooling system is also put into operation, which creates a pressure difference between the suction side and the pressure side of the coolant pump within the cooling system. On the suction side of the coolant pump, the internal pressure of the cooler is reduced by a certain amount. The pressure difference that has to be overcome increases by exactly this amount until the safety valve in the sealing cap opens as a result of the excess pressure. For example, if the pressure threshold at which the valve opens is at an overpressure of 1.2 bar and the pressure on the suction side decreases by 0.6 bar when the coolant pump starts, a pressure difference of 1.8 bar must be overcome with the engine running until the valve in the sealing cap opens.

Im Betrieb heizt sich nun das Kühlmittel auf, wodurch sich der Druck im Kühlsystem erhöht. Aufgrund der vergrößerten Druckdifferenz an der Saugseite der Kühlmittelpumpe, in deren Nähe auch der Verschlußdeckel liegt, kann der Druck auf einen Wert steigen, der über dem Öffnungsdruck oder Druckschwellwert liegt, bei dem das Ventil im Verschluß­deckel bei stillstehender Kühlmittelpumpe öffnen würde. Wird in diesem Zustand der Motor abgestellt und damit auch die Kühlmittelpumpe stillgesetzt, entfällt augenblicklich die Druckminderung an der Saugseite der Kühlmittelpumpe. Der Druck in dem Kühlsystem liegt über dem Öffnungsdruck des Ventils des Verschlußdeckels, so daß dieses schlagar­tig öffnet. Dadurch kann es nicht nur zu Kühlmittelver­lusten, sondern auch zu Verletzungen von Personen durch schlagartig austretendes heißes Kühlmittel oder Kühlmittel­dampf kommen.During operation, the coolant heats up, which increases the pressure in the cooling system. Due to the increased pressure difference on the suction side of the coolant pump, in the vicinity of which the closure cap is also located, the pressure can rise to a value which is above the opening pressure or pressure threshold value at which the valve in the closure cap would open when the coolant pump is at a standstill. If the engine is switched off in this state and the coolant pump is also shut down, there is no immediate pressure reduction on the suction side of the coolant pump. The pressure in the cooling system is above the opening pressure of the valve of the closure cover, so that it opens suddenly. This can result not only in loss of coolant, but also in injuries to people due to sudden escaping hot coolant or coolant vapor.

Der Erfindung liegt die Aufgabe zugrunde, einen Verschluß­deckel der eingangs genannten Art anzugeben, bei dem die Druckdifferenz bis zum Erreichen des Öffnungsdruckes des Ventiles des Verschlußdeckels unabhängig davon ist, ob die Kühlmittelpumpe arbeitet oder nicht.The invention has for its object to provide a cap of the type mentioned, in which the pressure difference until the opening pressure of the valve of the cap is reached regardless of whether the coolant pump is working or not.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der Ventilsitz an einer in dem Deckelgehäuse axial gegen die Kraft der Feder verstellbaren Hülse ausgebildet ist, die mit einer der Feder abgewandten, mindestens annähernd achs­normalen Fläche an einen Druckraum angrenzt, der in der Schließstellung des Verschlußdeckels gegenüber der Außen­luft und dem Behälterraum abgeschlossenen und mit der Saug­seite einer das Kühlmittel in der Kühlanlage umwälzenden Kühlmittelpumpe verbindbar ist. Bei der erfindungsgemäßen Lösung wird bei arbeitender Kühl­mittelpumpe in dem Druckraum gegenüber dem Zustand bei stillstehender Kühlmittelpumpe ein Unterdruck erzeugt, wo­durch die Hülse in Richtung der auf die Ventilmembran einwirkenden Ventilfeder verstellt wird. Da sich dabei die Ventilfeder entspannt, öffnet sie nun bei einem - absolut betrachtet - geringeren Überdruck. Durch den einstellbaren Stellweg der Hülse, kann die Änderung des Öffnungsdruckes oder Schwellwertes gerade so gewählt werden, daß sie der durch das Einschalten der Kühlmittelpumpe an der Saugseite derselben bewirkten Druckminderung entspricht. Wird die Kühlmittelpumpe abgestellt, so herrscht in dem Druckraum wieder der Ausgangsdruck. Die den Ventilsitz tragende Hülse und damit auch die Ventilfeder werden wieder in ihre der stillstehenden Kühlmittelpumpe entsprechende Ausgangsstel­lung verstellt. Die Öffnung des Ventiles erfolgt somit sowohl bei stillstehender als auch bei laufender Antriebs­maschine unabhängig von der durch die Kühlmittelpumpe be­wirkten Druckänderung jeweils bei derselben Drucksteigerung in dem Kühlmittelbehälter. Eine schlagartige Öffnung des Ventils nach dem Abstellen der Kühlmittelpumpe kann nicht mehr auftreten.This object is achieved in that the valve seat is formed on a sleeve which is axially adjustable in the cover housing against the force of the spring and which, with an at least approximately axially normal surface facing away from the spring, adjoins a pressure chamber which, in the closed position of the closure cover, is opposite the Outside air and the container space closed and can be connected to the suction side of a coolant pump circulating the coolant in the cooling system. In the solution according to the invention, when the coolant pump is operating, a negative pressure is generated in the pressure chamber compared to the state when the coolant pump is at a standstill, as a result of which the sleeve is adjusted in the direction of the valve spring acting on the valve membrane. Since the valve spring relaxes in the process, it now opens at a lower overpressure - in absolute terms. Due to the adjustable travel of the sleeve, the change in the opening pressure or threshold value can be selected so that it corresponds to the pressure reduction caused by switching on the coolant pump on the suction side thereof. If the coolant pump is switched off, the outlet pressure prevails again in the pressure chamber. The sleeve carrying the valve seat and thus also the valve spring are again adjusted into their starting position corresponding to the stationary coolant pump. The valve is thus opened both when the drive machine is at a standstill and when it is running, regardless of the pressure change caused by the coolant pump, in each case with the same pressure increase in the coolant tank. A sudden opening of the valve after switching off the coolant pump can no longer occur.

Die Führung der Hülse in dem Deckelgehäuse muß so ausge­bildet sein, daß zwischen der Hülse und dem sie umgebenden Gehäuseabschnitt kein Druckausgleich zwischen dem Behälter­innenraum und der Außenluft stattfinden kann. Dies läßt sich auf einfache und wirksame Weise dadurch erreichen, daß zwischen der Hülse und dem sie umgebenden Gehäuseab­schnitt eine die Hülsenbewegung ermöglichende Dichtmembran angeordnet ist.The guidance of the sleeve in the lid housing must be designed so that no pressure equalization between the interior of the container and the outside air can take place between the sleeve and the surrounding housing section. This can be achieved in a simple and effective manner in that a sealing membrane which enables the movement of the sleeve is arranged between the sleeve and the housing section surrounding it.

Um die Einstellung definierter Schwellwerte zu ermöglichen, ist es zweckmäßig, wenn der Stellweg der Hülse durch gehäu­sefeste Axialanschläge begrenzt ist.To enable the setting of defined threshold values, it is expedient if the travel of the sleeve is limited by axial stops fixed to the housing.

Die Abdichtung des Druckraumes läßt sich auf konstruktiv einfache Weise dadurch erreichen, daß der Druckraum als die Hülse umgebender Ringraum ausgebildet ist, der mindestens teilweise von einem entgegen der Federkraft dehnbaren Balg eingeschlossen ist. Dadurch ist eine Abdichtung von gegen­einander verschiebbaren Teile nicht erforderlich.The sealing of the pressure chamber can be achieved in a structurally simple manner in that the pressure chamber is designed as an annular space surrounding the sleeve, which is at least partially enclosed by a bellows which can be expanded against the spring force. As a result, it is not necessary to seal parts which can be moved relative to one another.

Der Anschluß des Druckraumes an die Saugseite der Kühlmit­telpumpe kann auf einfache Weise dadurch erfolgen, daß der Druckraum eine zur Umfangsfläche des Deckelgehäuses hin of­fene Anschlußöffnung aufweist und daß axial beiderseits desselben an der Umfangsfläche des Deckelgehäuses Dichtringe angeordnet sind, die zur Anlage an eine die Füllöffnung be­grenzenden Wand bestimmt sind, wobei an dieser Wand ein mit der Saugseite der Kühlmittelpumpe verbindbarer Anschlußkanal mündet. Wird der Verschlußdeckel somit in die Füllöffnung eingesetzt, wird automatisch die Verbindung zwischen der Saugseite der Kühlmittelpumpe und dem Druckraum hergestellt.The pressure chamber can be connected to the suction side of the coolant pump in a simple manner in that the pressure chamber has a connection opening that is open to the peripheral surface of the cover housing and that sealing rings are arranged axially on both sides of the cover housing on the peripheral surface, which seal seals against the filling opening Wall are determined, a connection channel which can be connected to the suction side of the coolant pump opening on this wall. If the cover is thus inserted into the filling opening, the connection between the suction side of the coolant pump and the pressure chamber is automatically established.

Bei Ausbildung des Verschlußdeckels als Schraubdeckel ist es zweckmäßig, wenn der Deckel aus einem mit einem Außengewin­destutzen versehenen ersten Gehäuseteil und einem mit die­sem frei drehbar verbundenen zweiten Gehäuseteil besteht, welches das Ventil aufnimmt und die Dichtringe trägt. Wird dieser Verschlußdeckel in die Füllöffnung eingesetzt, so läßt sich das erste Gehäuseteil einschrauben, ohne daß dabei das die Dichtringe tragende zweite Gehäuseteil gedreht wird. Es wird lediglich beim Einschrauben des ersten Gehäuseteils axial verschoben.When the closure cover is designed as a screw cover, it is expedient if the cover consists of a first housing part provided with an externally threaded connection and a second housing part which is freely rotatably connected to the latter and which receives the valve and carries the sealing rings. If this sealing cap is inserted into the filling opening, the first housing part can be screwed in without the second housing part carrying the sealing rings being rotated. It is only moved axially when the first housing part is screwed in.

Die folgende Beschreibung erläutert in Verbindung mit der beigefügten Zeichnung die Erfindung anhand eines Ausführungs­beispiels. Es zeigt:

  • Fig. 1 einen die Deckelachse enthaltenden Schnitt durch einen erfindungsgemäßen Verschlußdeckel, der in die Füllöffnung eines schematisch an­gedeuteten Ausgleichsgefäßes eines Kraftfahr­zeugkühlers eingeschraubt ist, wobei die Dar­stellung dem Fahrbetrieb entspricht, und
  • Fig. 2 einen der Figur 1 entsprechenden Teilschnitt, welcher den Verschlußdeckel bei stillstehen­dem Fahrzeug zeigt.
The following description explains in connection with the attached drawing the invention using an exemplary embodiment. It shows:
  • Fig. 1 shows a section containing the lid axis through a closure lid according to the invention, which is screwed into the fill opening of a schematically indicated expansion tank of a motor vehicle radiator, the representation corresponding to the driving operation, and
  • Fig. 2 is a partial section corresponding to Figure 1, which shows the cap when the vehicle is stationary.

In Figur 1 ist mit 10 ein Ausgleichsbehälter eines Kraft­fahrzeugkühlers bezeichnet, in dessen Einfüllstutzen 12 ein allgemein mit 14 bezeichneter Verschlußdeckel einge­schraubt ist. Dieser umfaßt ein erstes Deckelteil 16 mit einem Griffteil 18 und einem Außengewindestutzen 20, der in einem Innengewindeabschnitt 22 der Einfüllöffnung 12 ein­geschraubt ist.In Figure 1, 10 denotes an expansion tank of a motor vehicle radiator, in the filler neck 12 of which a screw cap generally designated 14 is screwed. This comprises a first cover part 16 with a handle part 18 and an external thread connector 20 which is screwed into an internal thread section 22 of the filling opening 12.

Mit dem ersten Deckelteil 16 ist ein zweites Deckelteil 24 verbunden. Dieses weist ein im wesentlichen rohrförmiges Gehäuse 26 auf, das an seinem dem ersten Deckelteil 16 zuge­wandten Ende mit einem ringförmigen Ansatz 28 versehen ist, der in einen rohrförmigen Ansatz 30 des ersten Deckelteiles 16 eingreift und mit einer radial nach außen gerichteten Ringklaue 32 eine radial nach innen gerichtete Ringklaue 34 des rohrförmigen Ansatzes 30 hintergreift, wobei der An­satz 28 aufgrund der an den Ringklauen 32 und 34 ausgebilde­ten Schrägflächen 36 bzw. 38 in den Rohransatz 30 eingeklipst werden kann. Damit ist das zweite Deckelteil 24 frei drehbar an dem ersten Deckelteil 16 gehalten. Wird der Verschlußdek­ kel 14 in die Füllöffnung 12 eingesetzt, so legen sich Dicht­ringe 40, die in axial beabstandeten Nuten 42 an der Außen­umfangsfläche des Gehäuses 26 liegen, an die Innenumfangs­fläche 44 der Einfüllöffnung 12 an. Die freie Drehbarkeit zwischen den beiden Deckelteilen 16 und 24 erlaubt es, das erste Deckelteil 16 einzuschrauben, ohne daß sich das zwei­te Deckelteil 24 mitdreht, was zu einem höheren Verschleiß der Dichtringe 40 führen würde.A second cover part 24 is connected to the first cover part 16. This has an essentially tubular housing 26, which is provided at its end facing the first cover part 16 with an annular extension 28 which engages in a tubular extension 30 of the first cover part 16 and with a radially outwardly directed ring claw 32 a radially after internally directed annular claw 34 of the tubular extension 30 engages behind, the extension 28 being able to be clipped into the tubular extension 30 due to the inclined surfaces 36 and 38 formed on the annular claws 32 and 34. The second cover part 24 is thus held on the first cover part 16 in a freely rotatable manner. If the closure dec kel 14 inserted into the filling opening 12, so sealing rings 40, which lie in axially spaced grooves 42 on the outer circumferential surface of the housing 26, on the inner circumferential surface 44 of the filling opening 12. The free rotatability between the two cover parts 16 and 24 allows the first cover part 16 to be screwed in without the second cover part 24 rotating, which would lead to increased wear of the sealing rings 40.

In dem Gehäuse 26 ist eine Hülse 46 axial verschiebbar ge­halten. Diese umfaßt einen dem ersten Deckelteil 16 zuge­wandten durchmessergrößeren Abschnitt 48 und einen dem In­nenraum des Ausgleichsbehälters 10 zugewandten durchmesser­kleineren Abschnitt 50. Der Zwischenraum zwischen der Hülse 46 und dem Gehäuse 26 wird durch eine ringförmige Dichtmem­bran 52 abgedichtet, die mit ihrem inneren wulstförmigen Rand 54 in eine Nut 56 der Hülse 46 eingreift und mit ihrem äußeren wulstförmigen Rand 58 zwischen einer Schulter 60 an dem Gehäuse 26 und einem in diesen eingreifenden Stützring 62 eingeklemmt ist. Der Stützring 62 trägt ferner einen sich ra­dial nach innen erstreckenden ringförmigen Balg 64, der zu­sammen mit dem Stützring 62 einen abgeschlossenen Ringraum bildet, welcher nur über eine den Stützring 62 durchsetzen­de Bohrung66 zugänglich ist. Der Stützring 62 und der Balg 64 werden durch ein Verschlußteil 68 gehalten, das in das dem Innenraum des Druckausgleichsbehälters 10 zugekehrte freie Ende des Gehäuses 26 eingesetzt und durch eine eine Ringklaue an dem Verschlußteil 68 sowie eine Ringklaue 72 an dem Ge­häuse 26 umfassende Klipsverbindung gesichert ist. Mit seiner dem Verschlußteil 68 abgewandten Ringfläche 74 liegt der Balg 64 an einer achsnormalen Ringfläche 76 der Hülse an.A sleeve 46 is held axially displaceably in the housing 26. This comprises a larger-diameter section 48 facing the first cover part 16 and a smaller-diameter section 50 facing the interior of the expansion tank 10. The space between the sleeve 46 and the housing 26 is sealed by an annular sealing membrane 52, which with its inner bead-shaped edge 54 into a Groove 56 of the sleeve 46 engages and is clamped with its outer bead-shaped edge 58 between a shoulder 60 on the housing 26 and a support ring 62 engaging in it. The support ring 62 also carries a radially inwardly extending annular bellows 64 which, together with the support ring 62, forms a closed annular space which is only accessible via a bore 66 passing through the support ring 62. The support ring 62 and the bellows 64 are held by a closure part 68, which is inserted into the free end of the housing 26 facing the interior of the pressure compensating container 10 and is secured by a clip connection comprising an annular claw on the closure part 68 and an annular claw 72 on the housing 26 . With its annular surface 74 facing away from the closure part 68, the bellows 64 lies against an axially normal annular surface 76 of the sleeve.

Die Hülse 46 weist an dem freien Ende des durchmesserkleineren Abschnittes 50 einen radial nach außen weisenden Flansch 78 auf, der in eine Ringnut 80 des Verschlußteiles 68 eingreift, deren axiale Ausdehnung größer als die axiale Ausdehnung des Flansches 78 ist. Dadurch kann sich die Hülse 46 bei einer Ausdehnung des Balges 64 zwischen der in Figur 1 dargestell­ten Stellung und der in Figur 2 dargestellten Stellung axial verschieben.The sleeve 46 has a radially outward-pointing flange 78 at the free end of the smaller-diameter section 50 on, which engages in an annular groove 80 of the closure member 68, the axial extent of which is greater than the axial extent of the flange 78. As a result, the sleeve 46 can move axially when the bellows 64 is expanded between the position shown in FIG. 1 and the position shown in FIG.

Der dem ersten Deckelteil 16 zugekehrte Rand des Hülsenab­schnittes 48 ist als Ventilsitz 82 für eine Ringdichtung 84 ausgebildet, die zwischen einer ersten Stahlmembran 86 und einer zweiten Stahlmembran 88 eingespannt ist. Die erste Stahlmembran 86 wird durch eine Schraubendruckfeder 90 gegen den Ventilsitz 82 vorgespannt, wobei sich die Schraubendruck­feder 90 einerseits in einer topfförmigen Vertiefung 92 in dem Deckel 94 des Gehäuses 26 und andererseits in einer topf­förmigen Vertiefung der ersten Membran 86 abstützt. Die zwei­te Membran 88 wird durch eine Schraubendruckfeder 98 gegen die der Hülse 46 zugekehrte Fläche der Ringdichtung 84 gespannt, wobei sich diese Schraubendruckfeder 98 einerseits an der Membran 88 und andererseits an einer Innenschulter 100 der Hülse 46 abstützt. Die Membranen 86 und 88 und der zwischen ihnen eingeschlossene Dichtring 84 bilden in Verbindung mit den Federn 90 und 98 ein Ventil, das sowohl bei Überdruck als auch bei Unterdruck in dem Ausgleichsbehälter 10 öffnen kann, wobei die Öffnungsschwellwerte durch die jeweilige Fe­derkraft und Federvorspannung vorgegeben sind. Bei einer Öff­nung des Ventils aufgrund eines Überdruckes hebt die Ring­dichtung 84 von dem Ventilsitz 82 ab, so daß ein Druckaus­gleich durch die Hülse 46 und Öffnungen 102 in der Gehäuse­deckfläche 94 hindurch in den Deckelraum 104 erfolgen kann, der über einen oder mehrere Spalte 106 in dem ringförmigen Ansatz 28 und eine Entlüftungsöffnung 108 in dem Ausgleichs­behälter 10 mit der Außenluft in Verbindung steht.The edge of the sleeve section 48 facing the first cover part 16 is designed as a valve seat 82 for an annular seal 84 which is clamped between a first steel membrane 86 and a second steel membrane 88. The first steel membrane 86 is prestressed by a helical compression spring 90 against the valve seat 82, the helical compression spring 90 being supported on the one hand in a cup-shaped depression 92 in the cover 94 of the housing 26 and on the other hand in a pot-shaped depression of the first membrane 86. The second membrane 88 is tensioned by a helical compression spring 98 against the surface of the ring seal 84 facing the sleeve 46, this helical compression spring 98 being supported on the one hand on the membrane 88 and on the other hand on an inner shoulder 100 of the sleeve 46. The membranes 86 and 88 and the sealing ring 84 enclosed between them, in conjunction with the springs 90 and 98, form a valve which can open in the expansion tank 10 both under excess pressure and under pressure, the opening threshold values being predetermined by the respective spring force and spring preload . When the valve is opened due to excess pressure, the ring seal 84 lifts off the valve seat 82, so that a pressure equalization can take place through the sleeve 46 and openings 102 in the housing cover surface 94 into the cover space 104, which via one or more gaps 106 in the annular extension 28 and a vent 108 in the expansion tank 10 communicates with the outside air.

Bei Unterdruck hebt die Membran 88 von der Ringdichtung 84 ab, so daß ein Druckausgleich zwischen diesen beiden Teilen und eine zentrale Öffnung 109 in der Membran 86 hindurch er­folgen kann.In the event of negative pressure, the membrane 88 lifts off the ring seal 84 so that a pressure equalization between these two parts and a central opening 109 in the membrane 86 can take place.

Der zwischen den Dichtringen 40 liegende Wandabschnitt der Füllöffnung 12 besitzt einen gegenüber dem Außenumfang des Deckelgehäuses 26 größeren Durchmesser, so daß dadurch ein Ringraum 110 gebildet ist, der über einen radialen Anschluß­kanal 112 mit einem Anschlußstutzen 114 in Verbindung steht. Gleichzeitig ist dieser Ringraum 110 über eine Bohrung 115 in dem Deckelgehäuse 26 und die mit der Bohrung 114 fluch­tende Bohrung 66 mit dem Innenraum 116 des Balges 64 verbun­den. Der Anschlußstutzen 114 wird mit der Saugseite der das Kühlmedium in der Kraftfahrzeug-Kühlanlage umwälzenden Kühl­mittelpumpe verbunden. Bei stillstehendem Motor des Kraft­fahrzeuges, wobei auch die Kühlmittelpumpe stillsteht, herrscht in dem Ausgleichsbehälter 10 und in dem Ringraum 116 des Bal­ges 64 zumindest annähernd derselbe Druck. Die Hülse 46 be­findet sich in ihrer in Figur 2 dargestellten Stellung. Bei einem in dem Ausgleichsbehälter auftretenden Überdruck öff­net das Ventil somit bei Überschreiten des durch die Vorspan­nung der Feder 90 in dieser Stellung vorgegebenen Schwell­wertes. Wird der Antriebsmotor des Kraftfahrzeuges angelassen und damit auch die Kühlmittelpumpe in Betrieb gesetzt, wird an deren Saugseite der Kühlmitteldruck vermindert. Durch die Verbindung des Innenraums 116 des Balges 64 mit der Saugseite der Kühlmittelpumpe, zieht sich durch den verminderten Druck der Balg zusammen, wodurch die Hülse 46 durch die Kraft der Feder 90 nach unten in die Stellung der Fig. 1 verschoben wird. Dadurch wird die Feder 90 entspannt und damit der Überdruck­schwellwert herabgesetzt, so daß die Druckdifferenz, um die der Druck im Kühlmittelbehälter bis zum Öffnen des Ventils steigen muß, bei stillstehender und bei arbeitender Kühlmit­telpumpe gleich groß ist.The wall section of the filling opening 12 lying between the sealing rings 40 has a larger diameter than the outer circumference of the cover housing 26, so that an annular space 110 is thereby formed which is connected to a connecting piece 114 via a radial connecting channel 112. At the same time, this annular space 110 is connected to the interior 116 of the bellows 64 via a bore 115 in the cover housing 26 and the bore 66 aligned with the bore 114. The connecting piece 114 is connected to the suction side of the coolant pump circulating the cooling medium in the motor vehicle cooling system. When the motor of the motor vehicle is at a standstill, and the coolant pump is also at a standstill, there is at least approximately the same pressure in the expansion tank 10 and in the annular space 116 of the bellows 64. The sleeve 46 is in its position shown in Figure 2. If there is an overpressure in the expansion tank, the valve thus opens when the threshold value predetermined by the pretension of the spring 90 is exceeded in this position. If the drive motor of the motor vehicle is started and the coolant pump is thus also put into operation, the coolant pressure is reduced on its suction side. By connecting the interior 116 of the bellows 64 to the suction side of the coolant pump, the bellows contracts due to the reduced pressure, as a result of which the sleeve 46 is moved downward into the position of FIG. 1 by the force of the spring 90. As a result, the spring 90 is relaxed and thus the overpressure threshold value is reduced, so that the pressure difference by which the pressure in the coolant tank has to rise until the valve opens is the same when the coolant pump is at a standstill and is working.

Claims (6)

1. Verschlußdeckel für die Füllöffnung (12) eines Kühlmit­telbehälters (10) in Kfz-Kühlanlagen umfassend ein in die Füllöffnung (12) eingreifendes Deckelgehäuse (16, 24) mit einem den zu verschließenden Behälterraum mit der Außenluft verbindenden Kanal und ein Ventil (82, 84, 86, 88, 90, 98) zum Absperren desselben mit einer Ventilmem­bran (86), die mit einer Dichtfläche (84) unter der Kraft einer in Richtung der Kanalachse wirkenden und sich an einer gehäusefesten Fläche (92) abstützenden Fe­der (90) an einem den Kanal umgebenden Ventilsitz (82) anliegt und von diesem durch Überdruck in dem Behälter­raum gegen die Federkraft abhebbar ist, dadurch gekennzeichnet, daß der Ventilsitz (82) an einer in dem Deckelgehäuse (26) axial gegen die Kraft der Feder (90) verstellbaren Hülse (46) ausgebildet ist, die mit einer der Feder (90) abgewandten, mindestens an­nähernd achsnormalen Fläche (76) an einen Druckraum (116) angrenzt, der in der Schließstellung des Verschlußdeckels (14) gegenüber der Außenluft und dem Behälterraum abge­schlossen und mit der Saugseite einer das Kühlmittel in der Kühlanlage umwälzenden Kühlmittelpumpe verbindbar ist.1. closure cap for the filling opening (12) of a coolant container (10) in vehicle cooling systems comprising a cover housing (16, 24) engaging in the filling opening (12) with a channel connecting the container space to be closed with the outside air and a valve (82, 84, 86, 88, 90, 98) for shutting off the same with a valve membrane (86) which has a sealing surface (84) under the force of a spring (90) acting in the direction of the channel axis and supported on a surface (92) fixed to the housing. on a valve seat surrounding the duct (82) abuts and can be lifted from it by overpressure in the container space against the spring force, characterized in that the valve seat (82) is formed on a sleeve (46) which is axially adjustable in the cover housing (26) against the force of the spring (90) and which with a surface (76) facing away from the spring (90) and at least approximately axially normal, adjoins a pressure chamber (116) which, when the closure cover (14) is in the closed position, is closed off from the outside air and the container chamber and with the suction side of the coolant in the cooling system circulating coolant pump is connectable. 2. Verschlußdeckel nach Anspruch 1, dadurch gekenn­zeichnet, daß zwischen der Hülse (46) und dem sie umgebenden Gehäuseabschnitt (26) eine die Hülsenbewegung ermöglichende Dichtmembran (52) angeordnet ist.2. Cap according to claim 1, characterized in that between the sleeve (46) and the surrounding housing portion (26) is arranged a sealing membrane (52) enabling the sleeve movement. 3. Verschlußdeckel nach Anspruch 1 oder 2, dadurch ge­kennzeichnet, daß der Stellweg der Hülse (46) durch gehäusefeste Axialanschläge begrenzt ist.3. Cap according to claim 1 or 2, characterized in that the travel of the sleeve (46) is limited by axial stops fixed to the housing. 4. Verschlußdeckel nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Druckraum (116) als die Hülse (46) umgebener Ringraum ausgebildet ist, der mindestens teilweise von einem entgegen der Federkraft dehnbaren Balg (64) eingeschlossen ist.4. Cap according to one of claims 1 to 3, characterized in that the pressure chamber (116) is designed as an annular space surrounding the sleeve (46) which is at least partially enclosed by a bellows (64) which can be stretched against the spring force. 5. Verschlußdeckel nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Druckraum (116) eine zur Umfangsfläche des Deckelgehäuses (26) hin offene Anschlußöffnung (66, 114) aufweist, und daß axial beider­seits derselben an der Umfangsfläche des Deckelgehäuses (26) Dichtringe (40) angeordnet sind, die zur Anlage an einer die Füllöffnung (12) begrenzenden Wand (44) bestimmt sind, wobei an dieser Wand (44) ein mit der Saugseite der Kühlmittelpumpe verbindbarer Anschlußkanal (112) mündet.5. Cap according to one of claims 1 to 4, characterized in that the pressure chamber (116) has a connection opening (66, 114) open towards the peripheral surface of the cover housing (26), and that axially on both sides thereof on the peripheral surface of the cover housing (26 ) Sealing rings (40) are arranged which are intended to rest against a wall (44) delimiting the filling opening (12) are, a connection channel (112) which can be connected to the suction side of the coolant pump opening on this wall (44). 6. Verschlußdeckel nach Anspruch 5, dadurch gekenn­zeichnet, daß er als Schraubdeckel ausgebildet ist und ein mit einem Außengewindestutzen (20) versehenes erstes Gehäuseteil (16) und ein mit diesem frei drehbar verbundenes zweites Gehäuseteil (24) umfaßt, welches das Ventil (82, 84, 86, 88, 90, 98) aufnimmt und die Dicht­ringe (40) trägt.6. A closure cap according to claim 5, characterized in that it is designed as a screw cap and a first housing part (16) provided with an external threaded connection (20) and a second housing part (24) which is freely rotatably connected to the latter and which comprises the valve (82, 84, 86, 88, 90, 98) and carries the sealing rings (40).
EP89117413A 1988-09-21 1989-09-20 Closure cover for the filling aperture of a coolant tank in motor vehicle cooling systems Expired - Lifetime EP0360252B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89117413T ATE84761T1 (en) 1988-09-21 1989-09-20 CAP FOR THE FILLING OPENING OF A COOLANT TANK IN CAR COOLING SYSTEMS.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3832103A DE3832103C2 (en) 1988-09-21 1988-09-21 Sealing lid for the filling opening of a coolant tank in automotive cooling systems
DE3832103 1988-09-21

Publications (3)

Publication Number Publication Date
EP0360252A2 true EP0360252A2 (en) 1990-03-28
EP0360252A3 EP0360252A3 (en) 1990-08-29
EP0360252B1 EP0360252B1 (en) 1993-01-20

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ID=6363436

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89117413A Expired - Lifetime EP0360252B1 (en) 1988-09-21 1989-09-20 Closure cover for the filling aperture of a coolant tank in motor vehicle cooling systems

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EP (1) EP0360252B1 (en)
AT (1) ATE84761T1 (en)
DE (1) DE3832103C2 (en)
ES (1) ES2040430T3 (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464317A1 (en) * 1990-06-29 1992-01-08 Mercedes-Benz Ag Pressure valve unit in an expansion tank of a cooling circuit of an internal combustion engine
WO1995014621A1 (en) * 1993-11-22 1995-06-01 Reutter Metallwarenfabrik Gmbh Closure cap which can screw onto a reservoir neck
WO1995014619A1 (en) * 1993-11-22 1995-06-01 Reutter Metallwarenfabrik Gmbh Closure cap which can screw onto a reservoir neck
EP0894955A1 (en) * 1997-07-30 1999-02-03 BLAU Kunststofftechnik Zweigniederlassung der Tesma Europa GmbH Closure cap with safety lock for a container
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
FR3011306A1 (en) * 2013-10-01 2015-04-03 Illinois Tool Works VALVE, COOLANT DEGASSING ASSEMBLY, AND COOLANT DEGASSING METHOD

Families Citing this family (2)

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Publication number Priority date Publication date Assignee Title
DE19753592A1 (en) 1997-12-03 1999-06-10 Heinrich Reutter Sealing cover
KR100980880B1 (en) * 2007-08-17 2010-09-10 현대자동차주식회사 Clutch oil reservoir cap

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US2574254A (en) * 1944-12-28 1951-11-06 Gen Motors Corp Aircraft cooling valve
US2799260A (en) * 1955-10-13 1957-07-16 Charles R Butler Cooling system for internal combustion engines

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3631528A1 (en) * 1986-09-17 1988-03-24 Deere & Co CLOSING PART FOR AN IMMEDIATELY FILLED LIQUID CONTAINER

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
US2574254A (en) * 1944-12-28 1951-11-06 Gen Motors Corp Aircraft cooling valve
US2799260A (en) * 1955-10-13 1957-07-16 Charles R Butler Cooling system for internal combustion engines

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0464317A1 (en) * 1990-06-29 1992-01-08 Mercedes-Benz Ag Pressure valve unit in an expansion tank of a cooling circuit of an internal combustion engine
WO1995014621A1 (en) * 1993-11-22 1995-06-01 Reutter Metallwarenfabrik Gmbh Closure cap which can screw onto a reservoir neck
WO1995014619A1 (en) * 1993-11-22 1995-06-01 Reutter Metallwarenfabrik Gmbh Closure cap which can screw onto a reservoir neck
EP0894955A1 (en) * 1997-07-30 1999-02-03 BLAU Kunststofftechnik Zweigniederlassung der Tesma Europa GmbH Closure cap with safety lock for a container
US6532910B2 (en) 2001-02-20 2003-03-18 Volvo Trucks North America, Inc. Engine cooling system
US6886503B2 (en) 2001-02-20 2005-05-03 Volvo Trucks North America, Inc. Engine cooling system
US7152555B2 (en) 2001-02-20 2006-12-26 Volvo Trucks North America, Inc. Engine cooling system
FR3011306A1 (en) * 2013-10-01 2015-04-03 Illinois Tool Works VALVE, COOLANT DEGASSING ASSEMBLY, AND COOLANT DEGASSING METHOD
WO2015050830A1 (en) * 2013-10-01 2015-04-09 Illinois Tool Works Inc. Valve, assembly for degassing a coolant, and method for degassing the coolant
CN105593488B (en) * 2013-10-01 2019-03-01 伊利诺斯工具制品有限公司 Valve, the component for coolant degassing and the method for coolant degassing

Also Published As

Publication number Publication date
EP0360252A3 (en) 1990-08-29
ATE84761T1 (en) 1993-02-15
ES2040430T3 (en) 1993-10-16
DE3832103A1 (en) 1990-03-22
EP0360252B1 (en) 1993-01-20
DE3832103C2 (en) 1996-08-29

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