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EP0888494B1 - Systeme de refroidissement pour moteur a combustion interne refroidi par fluide - Google Patents

Systeme de refroidissement pour moteur a combustion interne refroidi par fluide Download PDF

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Publication number
EP0888494B1
EP0888494B1 EP97914252A EP97914252A EP0888494B1 EP 0888494 B1 EP0888494 B1 EP 0888494B1 EP 97914252 A EP97914252 A EP 97914252A EP 97914252 A EP97914252 A EP 97914252A EP 0888494 B1 EP0888494 B1 EP 0888494B1
Authority
EP
European Patent Office
Prior art keywords
valve
cooling system
coolant
disposed
venting
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 - Lifetime
Application number
EP97914252A
Other languages
German (de)
English (en)
Other versions
EP0888494A1 (fr
Inventor
Werner Lugs
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0888494A1 publication Critical patent/EP0888494A1/fr
Application granted granted Critical
Publication of EP0888494B1 publication Critical patent/EP0888494B1/fr
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
    • F01P11/029—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
    • 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 is based on the preamble of claim 1 of EP-A 0295445.
  • a flow line is used Container of air and fuel gas separation from the coolant, the separated Gases by means of a pressure relief valve in one against a closure the filler neck of this container elastically supported valve unit an atmospheric expansion, storage and air lock tank are fed.
  • This expansion tank contains a coolant supply an expansion volume that is less than a predetermined positive pressure standing gas cushion is fulfilled.
  • Expansion tank with at least partially elastically compliant devices are known from US 3238932 and DD-PS 136280.
  • the necessary pressure build-up takes place in the respective Cooling system by compressing a buffer air / gas volume preferably in the expansion tank.
  • the disadvantage here is a relatively large one Expansion volume to measure the volume increase of the coolant even under extreme Temperature conditions, such as reheating when the heat is off Internal combustion engine to be able to record a possible coolant ejection or prevent coolant loss. Since the pressure build-up is essential of the volume distribution in the expansion tank between the coolant supply and buffer air / gas volume is also determined taking into account Leakage and evaporation losses a minimum level in the expansion tank required. The requirement for large buffer air / gas volume and sufficient Minimum coolant supply results in a relatively large expansion tank, which is difficult to place in the engine compartment due to its space requirements and possibly unfavorable line arrangements.
  • the invention has for its object that generic cooling system in this regard to improve that in the cooling system to avoid premature boiling and to avoid pump cavitation required pressure without a preloaded buffer air / gas volume is achieved.
  • the advantage of the invention is in the combination of a mechanical stress generated in the coolant with to see a flow system pressure control, the pressure control in achieves an atmospheric and thus pressureless coolant supply is. This results in an advantageously small-sized filling, venting and pressure control device, which are preferably in the cooling system flow from the internal combustion engine is arranged to the cooler.
  • the compensation chamber with the Vent chamber and return valve connecting and a according to one Partial feature of claim 3, the flow line of the cooling system with the Vent and return valve connecting the feed chamber are each as one Thermal valve designed, the gas and from a predetermined operating temperature Prevent coolant exchange and thus safe opening of the Coolant supply chamber contribute advantageously.
  • claim 5 describes the displaceable limitation of the compensation chamber as a displacer piston arranged with this in a coolant-tight manner via a rolling bellows, which is acted upon by a prestressed compression spring.
  • the preload the compression spring can be chosen so that until the through generated thermal change in volume of the coolant in the cooling system Pressure predetermined height a correspondingly small displacement of the displacer given is.
  • a cooling system 1 for a liquid-cooled internal combustion engine 2 comprises one Flow 3 to the radiator 4 and from this back to the internal combustion engine 2 Return 5, which is connected to a housing 6 of a thermostat 7. Out the housing 6 with the short circuit 8 closing due to operation Thermostats 7 the coolant flows through a suction line 9 to a pump 10, which conveys the coolant into the internal combustion engine 2.
  • the device 11 comprises a container 12, which of a flow line 13 connected to the flow line 3 is penetrated.
  • the lead pipe 13 has a fixed valve socket 14, which has a partition 15 of the container 12 is arranged sealingly and with its valve opening 16 into a chamber 17 for an atmospheric coolant supply 18 flows.
  • the container 12 has a further, geodetically deeper arranged chamber 19, which by means of an elastic resistance a compression spring 20 displaceable displacer 21 a coolant volume compensation serves.
  • the displacement piston 21 is by means of a rolling bellows 22 assigned coolant-tight to the compensation chamber 19.
  • This compensation chamber 19 is connected via a connecting piece 23 and a line 23 'with the pump suction line 9 shown in Figure 1 in coolant-carrying Connection.
  • the compensation chamber 19 is provided with the coolant supply chamber 17 connected via a temperature-controlled vent and return valve 24.
  • Such thermal valves are known to be, for example, with a bimetal element equipped, which brings a ball valve into the closed position and stops after being exceeded a predetermined temperature.
  • valve stub 14 of the flow line 13 is for controlling the valve opening 16 a valve unit 25 against the resistance of one against one in a filler neck 26 of the plenum 17 screwed insert 27 supported Spring 28 arranged displaceably.
  • the valve unit 25 itself serves System pressure control of the cooling system 1 as in the atmospheric ventilated Coolant supply chamber 17 opening pressure relief valve 29.
  • the valve unit 25 further includes a vent and return valve 30, which as Thermo valve of the above-described configuration between the plenum 17 and the flow line 13 effective vent and return hole 31 in controls the pressure relief valve 29 designed as a seat valve depending on the temperature.
  • a vent and return valve 30 which as Thermo valve of the above-described configuration between the plenum 17 and the flow line 13 effective vent and return hole 31 in controls the pressure relief valve 29 designed as a seat valve depending on the temperature.
  • a closure 32 of the filler neck 26 of the plenum 17 includes in addition to the screwable, pot-shaped insert 27 a screwable with this insert 27 Cap 33 with a vent hole 34.
  • the pot-like Insert 27 furthermore serves as a stop for spring 28 of valve unit 25 Floor 35 one of the control of the hot fill level in the storage chamber 17 serving control opening 36 and arranged in the peripheral part 37 close to the cap Vent channels 38 on.
  • FIG. 4 shows the device 11 in operation of the internal combustion engine 2, the Valves 24 and 30 are to be considered closed.
  • the temperature-related coolant volume increase a clear, hysteresis-free Relationship between coolant temperature and spring force of the compression spring 20 or the pressure in the compensation chamber 19th
  • the arrangement according to the invention in device 11 advantageously offers Way a hot filling of the cooling system 1 without loss of System pressure and without risk through coolant ejection according to FIG. 5, that when inserted and against the screwed insert 27 elastically supported Valve unit 25 with an effectively closed thermal valve 30 only the Sealing cover 33 to the atmospheric supply chamber 17 is removed for a possible coolant refill via the control opening 36 in the bottom 35 of the insert 27.
  • the system pressure is maintained, the Missing coolant after opening the two vent and return valves 24 and 30 in the course of the next cooling process in internal combustion engine 2 and Cooler 4 air pockets can escape, as shown in Figure 6.
  • FIG. 6 finally shows the cooling system 1 cooling down the shutdown of the internal combustion engine 2, in particular a degassing process, where air and fuel gases through the open valves 24 and 30 and through the unpressurized supply chamber 17 through the ventilation channels 38 and the ventilation hole 34 escape into the atmosphere in the sealing cover 33 and then Coolant penetrates from the plenum 17 into the cooling system 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Safety Valves (AREA)
  • Exhaust Gas After Treatment (AREA)

Claims (6)

  1. Système de refroidissement pour un moteur à combustion interne refroidi par un liquide, comprenant :
    un système élastiquement flexible servant à compenser des variations de volume dues aux conditions thermiques jusqu'à l'obtention d'une pression prédéterminée dans le système de l'agent de refroidissement que l'on fait circuler au moyen d'une pompe (10), et
    un dispositif (11) servant à commander la pression du système dans une canalisation d'aller (13),
    la canalisation d'aller (13), disposée de façon à passer à travers un réservoir (12) présentant un ajutage de vanne (14), disposé de façon sensiblement alignée, pour recevoir une unité de vanne (25), commandant des sens opposés d'écoulement,
    l'unité de vanne est disposée de façon à pouvoir être déplacée dans l'ajutage de vanne (14) en prenant appui élastiquement contre une fermeture (32) de l'ajutage de remplissage (26),
    caractérisé en ce que
    l'ajutage de vanne (14) est disposé sur la canalisation d'aller (13), de façon à traverser de manière étanche l'une des parois de séparation (15) qui subdivise le réservoir (12) en deux chambres (17, 19), avec un orifice de vanne (16) qui reçoit l'unité de vanne (25) de commande de surpression, de désaération et d'alimentation en agent de refroidissement dans l'une des chambres (17) pour une collecte (18) d'agent de refroidissement mis à la pression atmosphérique,
    la collecte (18) est en liaison ensuite par l'intermédiaire d'une vanne (24) de désaération et de retour, disposée dans la cloison de séparation (15) et commandée en fonction de la température, avec l'autre chambre (19) disposée plus bas d'un point de vue géodésique,
    la chambre (19) sert de chambre de compensation (19) du volume de l'agent de refroidissement au moyen d'un organe de délimitation (21) qui peut être déplacé à l'aide du système de pression à l'encontre d'une résistance élastique, et
    la chambre de compensation (19) et la chambre de collecte (17) de l'agent de refroidissement, qui peut être reliée avec elle au moyen de la vanne de désaération et de retour (24), sont en liaison par l'intermédiaire d'un ajutage de raccordement (23) avec une conduite d'aspiration (9) de la pompe du système de refroidissement (1).
  2. Système de refroidissement selon la revendication 1,
    caractérisé en ce que
    l'ajutage de vanne (14) de la canalisation d'aller (13) est constitué avec une unité de vanne (25), disposée de façon à pouvoir être enlevée en vue de remplir à froid le système de refroidissement (1),
    l'unité de vanne (25) lors du remplissage à chaud du système de refroidissement (1) est insérée dans l'ajutage de vanne (14) en prenant appui de façon élastique contre une butée prévue à la hauteur du niveau du remplissage à chaud dans la chambre (17) de collecte, butée (fond 35) d'un insert (27) disposé de manière amovible dans l'ajutage (26) de remplissage.
  3. Système de refroidissement selon la revendication 1 ou 2,
    caractérisé en ce que
    l'unité de vanne (25) comprend une vanne (30) de désaération et de retour, qui est combinée de façon constructive avec une soupape de surpression (29),
    la vanne de désaération et de retour (30), constituée sous la forme d'une vanne thermostatique, commande en fonction de la température, un alésage de désaération et de retour (31), opérationnel entre la chambre (17) de collecte et la canalisation d'aller (13) dans la soupape de surpression (29) constituée sous la forme d'une vanne à siège.
  4. Système de refroidissement selon l'une des revendications 1 à 3,
    caractérisé en ce que
    la fermeture (32) de l'ajutage de remplissage (26) de la chambre (17) de collecte comprend un insert (27), constitué en forme de pot, que l'on peut visser avec l'ajutage de remplissage (26), et
    la fermeture (32) comprend un couvercle de fermeture (33) avec un alésage de désaération (34), couvercle de fermeture (33) qui coopère avec l'insert (27),
    l'insert (27) présente dans le fond (35) qui sert de butée au ressort (28) de l'unité de vanne (25) un orifice de contrôle (36), servant au contrôle de l'état du remplissage à chaud, ainsi que des canaux de désaération (38) disposés à proximité du couvercle de la fermeture dans le pourtour (37).
  5. Système de refroidissement selon les revendications 1 à 4,
    caractérisé en ce que
    la chambre de compensation (19) comprend en tant que délimitation déplaçable un piston de refoulement (21), disposé de façon étanche à l'agent de refroidissement au moyen d'un soufflet roulant (22), piston de refoulement (21) qui est sollicité par un ressort de compression (20), disposé, en étant précontraint, en appui contre le réservoir (12).
  6. Système de refroidissement selon les revendications 1 à 5,
    caractérisé en ce que
    le dispositif (11) de remplissage, de désaération et de commande de la pression est disposé directement dans la conduite d'aller (3) allant du moteur à combustion interne (2) au radiateur (4) avec le collecteur (18) d'agent de refroidissement mis à la pression atmosphérique par l'intermédiaire de la canalisation d'aller (13).
EP97914252A 1996-03-21 1997-03-15 Systeme de refroidissement pour moteur a combustion interne refroidi par fluide Expired - Lifetime EP0888494B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19611095 1996-03-21
DE19611095A DE19611095A1 (de) 1996-03-21 1996-03-21 Kühlsystem für eine flüssigkeitsgekühlte Brennkraftmaschine
PCT/EP1997/001318 WO1997035101A1 (fr) 1996-03-21 1997-03-15 Systeme de refroidissement pour moteur a combustion interne refroidi par fluide

Publications (2)

Publication Number Publication Date
EP0888494A1 EP0888494A1 (fr) 1999-01-07
EP0888494B1 true EP0888494B1 (fr) 2000-06-28

Family

ID=7788940

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914252A Expired - Lifetime EP0888494B1 (fr) 1996-03-21 1997-03-15 Systeme de refroidissement pour moteur a combustion interne refroidi par fluide

Country Status (6)

Country Link
US (1) US6125800A (fr)
EP (1) EP0888494B1 (fr)
JP (1) JP2000509454A (fr)
DE (2) DE19611095A1 (fr)
ES (1) ES2148949T3 (fr)
WO (1) WO1997035101A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI116803B (fi) * 2001-04-27 2006-02-28 Crane John Safematic Oy Sovitelma mekaanisen tiivisteen yhteydessä
ES2346146T3 (es) * 2005-03-18 2010-10-11 BEHR GMBH & CO. KG Intercambiador de calor con aireador.
DE102008019227B4 (de) 2008-04-17 2010-05-12 Audi Ag Verfahren und Vorrichtung zur Kompensation der thermischen Volumenausdehnung in einem Kühlmittelkreislauf einer flüssigkeitsgekühlten Brennkraftmaschine
DE102010018089B3 (de) * 2010-04-24 2011-07-14 Audi Ag, 85057 Ventilanordnung zur Entlüftung eines Kühlmittelkreislaufs einer Brennkraftmaschine
DE102010033715A1 (de) * 2010-08-07 2012-02-09 Audi Ag Ausgleichsbehälter für einen Kühlmittelkreislauf
DE102013226420A1 (de) 2013-12-18 2015-06-18 Volkswagen Aktiengesellschaft Entlüftungsventil und Kühlsystem für eine Brennkraftmaschine
CN204187069U (zh) * 2014-10-23 2015-03-04 讯凯国际股份有限公司 补水结构、具有该补水结构的泵及液冷散热装置
RU2640661C1 (ru) * 2017-02-14 2018-01-11 Марк Евгеньевич Дискин Система жидкостного охлаждения
JP2022054600A (ja) * 2020-09-28 2022-04-07 いすゞ自動車株式会社 車載タンクのキャップ

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DE136280C (fr) *
US3208438A (en) * 1964-03-20 1965-09-28 Ford Motor Co Cooling system for an internal combustion engine
US3238932A (en) * 1964-03-30 1966-03-08 Ford Motor Co Sealed cooling system for an internal combustion engine
US4052965A (en) * 1975-10-28 1977-10-11 Caterpillar Tractor Co. Engine cooling system vent means
US4167159A (en) * 1977-04-29 1979-09-11 Deere & Company Pressurized liquid cooling system for an internal combustion engine
DD136280A1 (de) * 1978-02-13 1979-06-27 Guenter Wagenlehner Fluessigkeitskuehlung mit geschlossenem kreislauf,insbesondere fuer verbrennungsmotoren
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
DE3226508C2 (de) * 1982-07-15 1985-12-12 Bayerische Motoren Werke AG, 8000 München Kühlkreis für Brennkraftmaschinen
DE3436702A1 (de) * 1984-10-06 1986-04-10 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Vorrichtung zum absichern des kuehlmittelkreislaufs eines verbrennungsmotors
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Also Published As

Publication number Publication date
DE19611095A1 (de) 1997-09-25
WO1997035101A1 (fr) 1997-09-25
US6125800A (en) 2000-10-03
JP2000509454A (ja) 2000-07-25
DE59701936D1 (de) 2000-08-03
EP0888494A1 (fr) 1999-01-07
ES2148949T3 (es) 2000-10-16

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