EP0888494A1 - Cooling system for a liquid-cooled internal combustion engine - Google Patents

Cooling system for a liquid-cooled internal combustion engine

Info

Publication number
EP0888494A1
EP0888494A1 EP97914252A EP97914252A EP0888494A1 EP 0888494 A1 EP0888494 A1 EP 0888494A1 EP 97914252 A EP97914252 A EP 97914252A EP 97914252 A EP97914252 A EP 97914252A EP 0888494 A1 EP0888494 A1 EP 0888494A1
Authority
EP
European Patent Office
Prior art keywords
valve
coolant
cooling system
pressure
chamber
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
EP97914252A
Other languages
German (de)
French (fr)
Other versions
EP0888494B1 (en
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/en
Application granted granted Critical
Publication of EP0888494B1 publication Critical patent/EP0888494B1/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
    • F01P11/029—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.
  • the container through which a flow line is used serves to separate the air and fuel gas from the coolant, the separated gases being used by means of a pressure relief valve in a valve unit which is elastically supported against a closure of the filler neck of this container and an atmospheric compensation, Storage and air lock containers are supplied.
  • this expansion tank contains an expansion volume which is filled by a gas poister under a predetermined excess pressure.
  • elastic connecting hoses between the internal combustion engine and the cooler can be used as additional compensating devices, as is known per se, for example, from US 3208438.
  • Expansion tanks with at least partially elastically compliant devices are known from US 3238932 and DD-PS 136280.
  • the pressure is built up in the respective cooling system by compressing a buffer air / gas volume, preferably in the expansion tank.
  • the disadvantage here is a relatively large expansion volume in order to be able to absorb the increase in volume of the coolant even under extreme temperature conditions, such as, for example, reheating when the internal combustion engine is switched off hot, in order to prevent possible coolant ejection or loss of coolant.
  • the pressure build-up is also largely determined by the volume distribution in the expansion tank between the coolant supply and the buffer air / gas volume, a minimum fill level in the expansion tank is also required, taking leakage and evaporation losses into account.
  • the requirement for a large buffer air / gas volume and a sufficient minimum supply of coolant results in a relatively large expansion tank which is difficult to place due to its space requirement in the engine compartment and which may result in unfavorable line arrangements.
  • the object of the invention is to improve the generic cooling system in such a way that the pressure required in the cooling system to avoid premature sealing and to avoid pump cavitation is achieved without a prestressed buffer air / gas volume.
  • valve unit formed from overpressure and venting and return valve in the valve stub of the supply line enables rapid cold filling of the entire cooling system with rapid, reliable venting.
  • the use of a detachably arranged insert in the filler neck in connection with the pressureless coolant supply in the case of a warm cooling system has the advantage that opening the supply chamber without loss of pressure in the cooling system and without risk for the controller by means of coolant ejection means a check of the coolant supply and, if necessary, a check Hot filling is possible.
  • a venting and return valve connecting the equalization chamber with the plenum chamber and a venting and return valve connecting the flow line of the cooling system with the plenum chamber are each designed as a thermal valve, starting from a predetermined one Prevent operating temperature of gas and coolant exchange and thus advantageously contribute to a safe opening of the coolant supply chamber.
  • claim 5 describes the displaceable limitation of the compensation chamber as a displacer piston arranged with the latter in a coolant-tight manner via a bellows and which is acted upon by a prestressed compression spring.
  • the pretension of the compression spring can be selected such that there is a correspondingly small displacement of the displacer piston until the pressure generated by the thermally induced change in volume of the coolant in the cooling system is reached.
  • FIG. 1 shows a cooling system of a liquid-cooled internal combustion engine
  • FIG. 2 shows a filling, venting and pressure control device according to the invention
  • FIG. 3 prepares the seal according to FIG. 3 for cold filling
  • FIG. 4 shows the device according to FIG. 3 during engine operation
  • 5 shows the device according to FIG. 3 with hot filling, for example while the machine is running
  • a cooling system 1 for a liquid-cooled internal combustion engine 2 comprises a flow 3 to the cooler 4 and from there back to the internal combustion engine 2 a return 5, which is connected to a housing 6 of a thermostat 7.
  • the coolant flows out of the housing 6 with the thermostat 7 closing the short circuit 8 due to the operation, via a suction line 9 to a pump 10 which conveys the coolant into the internal combustion engine 2.
  • a filling, venting and pressure control device 11 according to the invention is arranged in advance 3 between internal combustion engine 2 and cooler 4.
  • the device 11 comprises a container 12, through which a flow line 13 connected to the flow line 3 passes.
  • the Vorlauf ⁇ line 13 has a fixed valve socket 14, which is arranged to penetrate a partition 15 of the container 12 and with its valve opening 16 opens into a chamber 17 for an atmospheric coolant pre-18.
  • the container 12 has a further, geodetically lower chamber 19 which serves to compensate for coolant volume by means of a displacement piston 21 which can be displaced against the elastic resistance of a compression spring 20.
  • the displacer piston 21 is assigned to the compensating chamber 19 in a coolant-tight manner by means of a rolling bellows 22.
  • This equalizing chamber 19 is connected via a connecting piece 23 and a line 23 'to the pump suction line 9 shown in FIG. 1 in a coolant-carrying connection.
  • the compensation chamber 19 is connected to the coolant supply chamber 17 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 holds after exceeding a predetermined temperature.
  • valve stub 14 of the flow line 13 is for controlling the valve opening
  • a valve unit 25 is arranged such that it can be displaced against the resistance of a spring 28 which is supported against an insert 27 which is screwed into a filler neck 26 of the receiving chamber 17.
  • the valve unit 25 itself serves to control the system pressure of the cooling system 1 as a pressure relief valve 29 opening into the atmospherically ventilated coolant supply chamber 17.
  • the valve unit 25 further comprises a venting and return valve 30, which, as a thermostatic valve, a configuration between the supply chamber
  • a closure 32 of the filler neck 26 of the supply chamber 17 comprises, in addition to the screw-in, pot-shaped insert 27, a closure cover 33 with a vent hole 34 that can be screwed to this insert 27.
  • the pot-like insert 27 also has the stop 28 of the valve unit 25 as a spring - Bottom 35 of a control opening 36 which serves to control the hot fill level in the supply chamber 17 and ventilation channels 38 arranged in the peripheral part 37 close to the closure cover.
  • FIG. 3 shows the device 11 in operation of the internal combustion engine 2, the valves 24 and 30 being considered closed.
  • the arrangement according to the invention in the device 11 advantageously provides a warm filling of the cooling system 1 without loss of the system pressure and without risk of coolant ejection according to FIG. 5 in that when the valve unit 25 is inserted and is elastically supported against the screwed-in insert 27 with the thermally valve 30 being effectively closed, only the cover 33 to the atmospheric supply chamber 17 is to be 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 the opening of the two Vent and return valves 24 and 30 can escape air inclusions in the course of the next cooling process in internal combustion engine 2 and cooler 4, as shown in FIG. 6.
  • Figure 6 shows a particular degassing process during a cooling process of the cooling system 1 after the internal combustion engine 2 has been switched off, air and combustion gases through the opened valves 24 and 30 and via the unpressurized supply chamber 17 through the venting channels 38 and the venting bore 34 in the sealing cover 33 escape into the atmosphere and then coolant penetrates from the plenum 17 into the cooling system 1.
  • the filling, venting and pressure control device 11 according to the invention has the following advantages in summary:

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)

Abstract

The invention concerns a cooling system for a liquid-cooled internal combustion engine, the system comprising a filling, venting and pressure-control device in which a compressive stress generated mechanically in the coolant is combined with a feed system pressure control step, the controlled pressure reduction being brought about in a reserve of coolant which is acted upon by the air and is therefore pressureless. The device enables the cooling system to be rapidly filled with coolant in the cold state and its also enables the level in the reserve chamber to be checked when the coolant is at operating temperature without pressure losses or the risk of coolant splashing out.

Description

Kühlsystem für eine flüssigkeitsgekühlte BrennkraftmaschineCooling system for a liquid-cooled internal combustion engine
Die Erfindung geht nach dem Oberbegriff des Patentanspruches 1 von der EP-A 0295445 aus.The invention is based on the preamble of claim 1 of EP-A 0295445.
Bei diesem bekannten Kühlsystem dient der von einer Vorlaufleitung durchsetzte Behälter der Luft- und Brenngasabscheidung aus dem Kühlmittel, wobei die abge¬ schiedenen Gase mittels eines Überdruckventiles in einer gegen einen Verschluß des Einfüllstutzens dieses Behälters elastisch abgestützt angeordneten Ventilein¬ heit einem atmosphärisch beaufschlagten Ausgleichs-, Vorrats- und Luftsperrbe¬ hälter zugeführt sind. Dieser Ausgleichsbehälter enthält neben einer Kühlmittelvor¬ lage ein Ausdehnungsvolumen, das von einem unter einem vorbestimmten Über¬ druck stehenden Gaspoister erfüllt ist.In this known cooling system, the container through which a flow line is used serves to separate the air and fuel gas from the coolant, the separated gases being used by means of a pressure relief valve in a valve unit which is elastically supported against a closure of the filler neck of this container and an atmospheric compensation, Storage and air lock containers are supplied. In addition to a coolant supply, this expansion tank contains an expansion volume which is filled by a gas poister under a predetermined excess pressure.
Zu den im wesentlichen aus starren Wänden gebildeten Ausgleichsbehälter zum Ausgleich thermisch bedingter Volumenänderungen des Kühlmittels kommen als zusätzliche Ausgleichseinrichtungen elastische Verbindungsschläuche zwischen der Brennkraftmaschine und dem Kühler in Frage, wie dies zum Beispiel aus der US 3208438 an sich bekannt ist.In addition to the compensating tank formed essentially from rigid walls to compensate for thermally induced changes in volume of the coolant, elastic connecting hoses between the internal combustion engine and the cooler can be used as additional compensating devices, as is known per se, for example, from US 3208438.
Ausgleichsbehälter mit zumindest bereichsweise elastisch nachgiebigen Einrich¬ tungen sind aus der US 3238932 und der DD-PS 136280 bekannt. Bei den vorbeschriebenen Systemen erfolgt der notwendige Druckaufbau im jewei¬ ligen Kühlsystem durch Komprimieren eines Puffer- Luft-/ Gasvolumens, und zwar vorzugsweise im Ausgleichsbehälter. Nachteilig hierbei ist ein relativ großes Ausdehnungsvolumen, um die Volumenzunahme des Kühlmittels auch unter ex- tremen Temperaturbedingungen, wie zum Beispiel Nachheizen bei heiß abgestell¬ ter Brennkraftmaschine, aufnehmen zu können, um einen eventuellen Kühlmittel- Auswurf bzw. Kühlmittel-Verlust zu verhindern. Da weiter der Druckaufbau wesent¬ lich von der Volumenaufteilung im Ausgleichsbehälter zwischen Kühlmittel-Vorlage und Puffer- Luft-/ Gasvolumen bestimmt ist, ist auch unter Berücksichtigung von Leckage- und Verdampfungsverlusten ein Mindest-Füllstand im Ausgleichsbehälter erforderlich. Die Anforderung nach großem Puffer- LufW Gasvolumen und ausrei¬ chender Mindest-Vorlage an Kühlmittel ergibt einen relativ großen Ausgleichsbe¬ hälter, der aufgrund seines Platzbedarfes im Motorraum schwierig zu plazieren ist und gegebenenfalls ungünstige Leitungsanordnuπgen bedingt.Expansion tanks with at least partially elastically compliant devices are known from US 3238932 and DD-PS 136280. In the systems described above, the pressure is built up in the respective cooling system by compressing a buffer air / gas volume, preferably in the expansion tank. The disadvantage here is a relatively large expansion volume in order to be able to absorb the increase in volume of the coolant even under extreme temperature conditions, such as, for example, reheating when the internal combustion engine is switched off hot, in order to prevent possible coolant ejection or loss of coolant. Since the pressure build-up is also largely determined by the volume distribution in the expansion tank between the coolant supply and the buffer air / gas volume, a minimum fill level in the expansion tank is also required, taking leakage and evaporation losses into account. The requirement for a large buffer air / gas volume and a sufficient minimum supply of coolant results in a relatively large expansion tank which is difficult to place due to its space requirement in the engine compartment and which may result in unfavorable line arrangements.
Der Erfindung liegt die Aufgabe zugrunde, daß gattungsgemäße Kühlsystem da¬ hingehend zu verbessern, daß der im Kühlsystem zur Vermeidung vorzeitigen Sie- dens und zur Vermeidung einer Pumpen-Kavitation erforderliche Druck ohne ein vorgespanntes Puffer- Luft-/ Gasvolumen erzielt ist.The object of the invention is to improve the generic cooling system in such a way that the pressure required in the cooling system to avoid premature sealing and to avoid pump cavitation is achieved without a prestressed buffer air / gas volume.
Diese Aufgabe ist mit dem Patentanspruch 1 gelöst. Der Vorteil der Erfindung ist in der Kombination einer mechanisch im Kühlmittel erzeugten Druckspannung mit einer Vorlauf-Systemdrucksteuerung zu sehen, wobei die Druckabsteuerung in eine atmosphärisch beaufschlagte und damit drucklose Kühlmittel-Vortage erzielt ist. Dies ergibt eine vorteilhaft kleinbauende Befüll-, Entlüftungs- und Drucksteuer- Vorrichtung, die vorzugsweise im Kühlsystem-Vorlauf von der Brennkraftmaschine zum Kühler angeordnet ist.This object is achieved with patent claim 1. The advantage of the invention is to be seen in the combination of a compressive stress generated mechanically in the coolant with a flow system pressure control, the pressure reduction being achieved in an atmospheric and thus depressurized coolant previous days. This results in an advantageously small-sized filling, venting and pressure control device, which is preferably arranged in the cooling system flow from the internal combustion engine to the radiator.
Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen beschrie- ben. Die im Anspruch 2 beschriebene lösbare Anordnung der aus Überdruck- und Entlüftungs- und Rücklauf-Ventil gebildeten Ventileinheit im Ventilstutzen der Vor¬ laufleitung ermöglicht eine rasche Kaltbefüllung des gesamten Kühlsystems mit rascher, zuverlässiger Entlüftung. Die weiter im Anspruch 2 beschriebene Anord¬ nung der Ventileinheit im Ventilstutzen mittels elastischer Abstützung gegen einen im Einfüllstutzen lösbar angeordneten Einsatz ergibt in Verbindung mit der drucklo¬ sen Kühlmittel-Vorlage bei betriebswarmen Kühlsystem den Vorteil, daß ein Öffnen der Vorlagekammer ohne Druckverlust im Kühlsystem und ohne Risiko für den Kontrollierenden durch Kühlmittel-Auswurf eine Überprüfung der Kühlmittel-Vorlage und gegebenenfalls eine Warmbefüllung möglich ist.Advantageous embodiments of the invention are described in the subclaims. The detachable arrangement of the valve unit formed from overpressure and venting and return valve in the valve stub of the supply line enables rapid cold filling of the entire cooling system with rapid, reliable venting. The arrangement of the valve unit further described in claim 2 in the valve socket by means of elastic support against one The use of a detachably arranged insert in the filler neck in connection with the pressureless coolant supply in the case of a warm cooling system has the advantage that opening the supply chamber without loss of pressure in the cooling system and without risk for the controller by means of coolant ejection means a check of the coolant supply and, if necessary, a check Hot filling is possible.
Ein nach einem Teilmerkmal des Anspruches 1 die Ausgleichskammer mit der Vorlagekammer verbindendes Entlüftungs- und Rücklaufventil und ein gemäß ei¬ nem Teilmerkmal des Anspruches 3 die Vorlaufleitung des Kühlsystems mit der Vorlagekammer verbindendes Entlüftungs- und Rücklaufventil sind jeweils als ein Thermoventil gestaltet, die ab einer vorbestimmten Betriebstemperatur Gas- und Kühlmittelaustausch unterbinden und somit zu einem gefahrlosen Öffnen der Kühlmittel-Vorlagekammer vorteilhaft beitragen.A venting and return valve connecting the equalization chamber with the plenum chamber and a venting and return valve connecting the flow line of the cooling system with the plenum chamber according to a partial feature of claim 3 are each designed as a thermal valve, starting from a predetermined one Prevent operating temperature of gas and coolant exchange and thus advantageously contribute to a safe opening of the coolant supply chamber.
Der weiter oben bereits erwähnte, im Einfüllstutzen lösbar angeordnete Einsatz als Wiederiager einer die Ventileinheit bezüglich des Überdruckventils in Schließstel¬ lung haltenden Feder ist gemäß Anspruch 4 vorzugsweise topfartig gestaltet mit einer im Boden angeordneten Kontrollöffnung zur Kontrolle des Warmfüllstandes. Schließlich beschreibt Anspruch 5 die verlagerbare Begrenzung der Ausgleichs- kammer als einen mit dieser über einen Rollbalg kühlmitteldicht angeordneten Ver¬ drängerkolben, der von einer vorgespannten Druckfeder beaufschlagt ist. Die Vor¬ spannung der Druckfeder kann so gewählt sein, daß bis zum Erreichen des durch thermisch bedingte Volumenänderung des Kühlmittels im Kühlsystem erzeugten Druckes vorbestimmte Höhe eine entsprechend geringe Verlagerung des Verdrän- gerkolbens gegeben ist.The above-mentioned use, releasably arranged in the filler neck, as a repeater of a spring holding the valve unit with respect to the pressure relief valve in the closed position, is preferably cup-shaped with a control opening arranged in the bottom for checking the warm fill level. Finally, claim 5 describes the displaceable limitation of the compensation chamber as a displacer piston arranged with the latter in a coolant-tight manner via a bellows and which is acted upon by a prestressed compression spring. The pretension of the compression spring can be selected such that there is a correspondingly small displacement of the displacer piston until the pressure generated by the thermally induced change in volume of the coolant in the cooling system is reached.
Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbei¬ spiels beschrieben. Es zeigtThe invention is described with reference to an exemplary embodiment shown in the drawing. It shows
Figur 1 ein Kühlsystem einer flüssigkeitsgekühlten Brennkraftmaschine, Figur 2 eine erfindungsgemäße Befüll-, Entlüftungs- und Drucksteuer-Vorrich¬ tung, Figur 3 die Voσichtung gemäß Figur 3 für eine Kaltbefüllung vorbereitet,1 shows a cooling system of a liquid-cooled internal combustion engine, FIG. 2 shows a filling, venting and pressure control device according to the invention, FIG. 3 prepares the seal according to FIG. 3 for cold filling,
Figur 4 die Vorrichtung gemäß Figur 3 bei Motorbetrieb, Figur 5 die Vorrichtung gemäß Figur 3 bei Warmbefüllung, z.B. bei laufendemFIG. 4 shows the device according to FIG. 3 during engine operation, 5 shows the device according to FIG. 3 with hot filling, for example while the machine is running
Motor, und schließlich Figur 6 die Vorrichtung gemäß Figur 3 beim Abkühl-Vorgang einer abgestell¬ ten Brennkraftmaschine.6, and finally the device according to FIG. 3 during the cooling process of a switched off internal combustion engine.
Ein Kühlsystem 1 für eine flüssigkeitsgekühlte Brennkraftmaschine 2 umfaßt einen Vorlauf 3 zum Kühler 4 und von diesem zur Brennkraftmaschine 2 zurück einen Rücklauf 5, der an ein Gehäuse 6 eines Thermostaten 7 angeschlossen ist. Aus dem Gehäuse 6 mit den Kurzschluß 8 betriebsbedingt verschließendem Thermostaten 7 fließt das Kühlmittel über eine Saugleituπg 9 einer Pumpe 10 zu, die das Kühlmittel in die Brennkraftmaschine 2 fördert.A cooling system 1 for a liquid-cooled internal combustion engine 2 comprises a flow 3 to the cooler 4 and from there back to the internal combustion engine 2 a return 5, which is connected to a housing 6 of a thermostat 7. The coolant flows out of the housing 6 with the thermostat 7 closing the short circuit 8 due to the operation, via a suction line 9 to a pump 10 which conveys the coolant into the internal combustion engine 2.
Im Vorlauf 3 ist zwischen der Brennkraftmaschine 2 und dem Kühler 4 eine erfin¬ dungsgemäße Befüll-, Entlüftungs- und Drucksteuer-Vorrichtung 11 angeordnet.A filling, venting and pressure control device 11 according to the invention is arranged in advance 3 between internal combustion engine 2 and cooler 4.
Gemäß den Figuren 2 mit 6 umfaßt die Vorrichtung 11 einen Behälter 12, der von einer mit dem Vorlauf 3 verbundenen Vorlaufleitung 13 durchsetzt ist. Die Vorlauf¬ leitung 13 weist einen fest angeordneten Ventilstutzen 14 auf, der eine Trennwand 15 des Behälters 12 dichtdurchsetzend angeordnet ist und mit seiner Ventilöffnung 16 in eine Kammer 17 für eine atmosphärisch beaufschlagte Kühlmittel-Voriage 18 mündet.According to FIGS. 2 to 6, the device 11 comprises a container 12, through which a flow line 13 connected to the flow line 3 passes. The Vorlauf¬ line 13 has a fixed valve socket 14, which is arranged to penetrate a partition 15 of the container 12 and with its valve opening 16 opens into a chamber 17 for an atmospheric coolant pre-18.
Unterhalb der Trennwand 15 weist der Behälter 12 eine weitere, geodätisch tiefer angeordnete Kammer 19 auf, die mittels eines gegen den elastischen Widerstand einer Druckfeder 20 verlagerbaren Verdrängerkolbens 21 einem Kühlmittelvolu¬ men-Ausgleich dient. Mittels eines Rollbalges 22 ist der Verdrängerkolben 21 kühlmitteldicht der Ausgleichskammer 19 zugeordnet.Below the partition 15, the container 12 has a further, geodetically lower chamber 19 which serves to compensate for coolant volume by means of a displacement piston 21 which can be displaced against the elastic resistance of a compression spring 20. The displacer piston 21 is assigned to the compensating chamber 19 in a coolant-tight manner by means of a rolling bellows 22.
Diese Ausgleichskammer 19 steht über einen Anschlußstutzen 23 und eine Leitung 23' mit der in Figur 1 dargestellten Pumpen-Saugleitung 9 in kühlmittelführender Verbindung. Mit der Kühlmittel-Vorlagekammer 17 ist die Ausgleichskammer 19 über ein temperaturgesteuertes Entlüftungs- und Rücklaufventil 24 verbunden. Derartige Thermoventile sind bekanntlich zum Beispiel mit einem Bimetallelement ausgerüstet, das ein Kugel-Ventil in Schließposition bringt und hält nach Über¬ schreiten einer vorbestimmten Temperatur.This equalizing chamber 19 is connected via a connecting piece 23 and a line 23 'to the pump suction line 9 shown in FIG. 1 in a coolant-carrying connection. The compensation chamber 19 is connected to the coolant supply chamber 17 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 holds after exceeding a predetermined temperature.
In dem Ventilstutzen 14 der Vorlaufleitung 13 ist zur Steuerung der VentilöffnungIn the valve stub 14 of the flow line 13 is for controlling the valve opening
16 eine Ventileinheit 25 gegen den Widerstand einer gegen einen in einem Ein¬ füllstutzen 26 der Vorlagekammer 17 eingeschraubt angeordneten Einsatz 27 ab¬ gestützten Feder 28 verlagerbar angeordnet. Die Ventileinheit 25 selbst dient zur Systemdrucksteuerung des Kühlsystems 1 als in die atmosphärisch belüftete Kühlmittel- Vorlagekammer 17 öffnendes Überdruckventil 29.16, a valve unit 25 is arranged such that it can be displaced against the resistance of a spring 28 which is supported against an insert 27 which is screwed into a filler neck 26 of the receiving chamber 17. The valve unit 25 itself serves to control the system pressure of the cooling system 1 as a pressure relief valve 29 opening into the atmospherically ventilated coolant supply chamber 17.
Die Ventiieinheit 25 umfaßt ferner ein Entlüftungs- und Rücklaufventil 30, das als Thermoventil vorbeschriebener Ausgestaltung eine zwischen der VorlagekammerThe valve unit 25 further comprises a venting and return valve 30, which, as a thermostatic valve, a configuration between the supply chamber
17 und der Vorlaufleitung 13 wirksame Entlüftungs- und Rücklaufbohrung 31 in dem als Sitzventil gestalteten Überdruckventil 29 temperaturabhängig steuert.17 and the flow line 13 effective venting and return bore 31 in the pressure relief valve 29 designed as a seat valve controls temperature-dependent.
Ein Verschluß 32 des Einfüllstutzens 26 der Vorlagekammer 17 umfaßt neben dem einschraubbaren, topfartig gestalteten Einsatz 27 einen mit diesem Einsatz 27 ver- schraubbaren Verschlußdeckel 33 mit einer Entlüftungsbohrung 34. Der topfartige Einsatz 27 weist ferner in dem als Anschlag der Feder 28 der Ventileinheit 25 die- nenden Boden 35 einer der Kontrolle des Warmfüllstandes in der Vorlagekammer 17 dienende Kontrollöffnung 36 sowie im Umfangsteil 37 verschlußdeckelnah an¬ geordnete Entlüftungskanäle 38 auf.A closure 32 of the filler neck 26 of the supply chamber 17 comprises, in addition to the screw-in, pot-shaped insert 27, a closure cover 33 with a vent hole 34 that can be screwed to this insert 27. The pot-like insert 27 also has the stop 28 of the valve unit 25 as a spring - Bottom 35 of a control opening 36 which serves to control the hot fill level in the supply chamber 17 and ventilation channels 38 arranged in the peripheral part 37 close to the closure cover.
Mit der vorbeschriebenen, erfindungsgemäßen Anordnung kann mit der Entfernung des Verschlußdeckels 33, des Einsatzes 27 und der Ventileinheit 25 aus dem Ventilstutzen 14 über diesen eine Kaltbefüllung des Kühlsystems 1 der Brenn¬ kraftmaschine 2 in zügigem Ablauf erfolgen. Bei der in Figur 3 dargestellten Kaltbe¬ füllung besteht gegenüber herkömmlichen Systemen eine Funktionsverbesserung, da das Kühlmittel gleichzeitig in die Brennkraftmaschine 2 und in den Kühler 4 ge- langt und die im Brennkraftmaschinen-Kühlmantel befindliche Luft während des Befüllvorganges über die offene Vorlagekammer 17 einerseits und durch das ge¬ öffnete Ventil 24 andererseits entweichen kann. Eine bekanntlich nur durch Unter¬ druck erzielbare schnelle und vollständige Befüllung ist mit dem dargestellten System ohne Zusatzaufwand möglich. Figur 4 zeigt die Vorrichtung 11 im Betrieb der Brennkraftmaschine 2, wobei die Ventile 24 und 30 geschlossen zu denken sind. Hierbei besteht entsprechend der temperaturbedingten Kühimittel-Volumenzunahme ein eindeutiger, hysterisefreier Zusammenhang zwischen Kühlmitteltemperatur und Federkraft der Druckfeder 20 bzw. dem Druck in der Ausgleichskammer 19.With the above-described arrangement according to the invention, when the closure cover 33, the insert 27 and the valve unit 25 are removed from the valve stub 14, the cooling system 1 of the internal combustion engine 2 can be cold-filled quickly and efficiently. In the cold filling shown in FIG. 3, there is an improvement in function compared to conventional systems, since the coolant simultaneously enters the internal combustion engine 2 and the cooler 4 and the air in the internal combustion engine cooling jacket during the filling process via the open supply chamber 17 on the one hand and on the other hand can escape through the opened valve 24. Fast and complete filling, which is known to be achieved only by negative pressure, is possible with the system shown without additional effort. FIG. 4 shows the device 11 in operation of the internal combustion engine 2, the valves 24 and 30 being considered closed. In accordance with the temperature-related increase in coolant volume, there is a clear, hysteresis-free relationship between the coolant temperature and the spring force of the compression spring 20 or the pressure in the compensation chamber 19.
Weiter bietet die erfindungsgemäße Anordnung in der Vorrichtung 11 in vorteilhaf¬ ter Weise eine Waπmbefüllung des Kühlsystems 1 ohne Verlust des Systemdruckes und ohne Risiko durch Kühlmittel-Auswurf gemäß Figur 5 dadurch, daß bei eingesetzter und gegen den eingeschraubten Einsatz 27 elastisch abge¬ stützter Ventileinheit 25 mit wirksam verschlossenem Thermoventil 30 lediglich der Verschlußdeckel 33 zu der atmosphärisch beaufschlagten Vorlagekammer 17 zu entfernen ist für eine eventuelle Kühlmittel-Nachfüllung über die Kontrollöffnung 36 im Boden 35 des Einsatzes 27. Hierbei bleibt der Systemdruck erhalten, wobei das fehlende Kühlmittel nach dem Öffnen der beiden Entlüftungs- und Rücklaufventile 24 und 30 im Verlauf des nächsten Abkühlvorganges in Brennkraftmaschine 2 und Kühler 4 Lufteinschlüsse entweichen können, wie dies in Bild 6 dargestellt ist.Furthermore, the arrangement according to the invention in the device 11 advantageously provides a warm filling of the cooling system 1 without loss of the system pressure and without risk of coolant ejection according to FIG. 5 in that when the valve unit 25 is inserted and is elastically supported against the screwed-in insert 27 with the thermally valve 30 being effectively closed, only the cover 33 to the atmospheric supply chamber 17 is to be 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 the opening of the two Vent and return valves 24 and 30 can escape air inclusions in the course of the next cooling process in internal combustion engine 2 and cooler 4, as shown in FIG. 6.
Bild 6 zeigt schließlich während eines Abkühlvorganges des Kühlsystems 1 nach dem Abstellen der Brennkraftmaschine 2 einen insbesondere Entgasungsvorgang, wobei Luft- und Brenngase durch die geöffneten Ventile 24 und 30 und über die drucklose Vorlagekammer 17 durch die Entlüftungskanäle 38 und die Entlüftungs¬ bohrung 34 im Verschlußdeckel 33 in die Atmosphäre entweichen und anschlie- ßend Kühlmittel aus der Vorlagekammer 17 in das Kühlsystem 1 vordringt.Finally, Figure 6 shows a particular degassing process during a cooling process of the cooling system 1 after the internal combustion engine 2 has been switched off, air and combustion gases through the opened valves 24 and 30 and via the unpressurized supply chamber 17 through the venting channels 38 and the venting bore 34 in the sealing cover 33 escape into the atmosphere and then coolant penetrates from the plenum 17 into the cooling system 1.
Die erfindungsgemäße Befüll-, Entlüftungs- und Drucksteuer-Vorrichtung 11 weist zusammengefaßt folgende Vorteile auf:The filling, venting and pressure control device 11 according to the invention has the following advantages in summary:
Druckbegrenzung im Bereich des Eintrittes des Vorlaufes 3 in den Kühler 4, wobei austretendes Kühlmittel nicht verloren geht, sondern in der Vorlagekammer 17 vor¬ gelagert und beim nächsten Abkühlvorgang wieder dem Kühlsystem 1 zugeführt wird;Pressure limitation in the area of the inlet 3 into the cooler 4, whereby emerging coolant is not lost, but is stored in the supply chamber 17 and is supplied to the cooling system 1 again during the next cooling process;
Trennung von Luft/Gas und Kühlmittel während der Druckaufbauphase beim Warmlauf; Systembelüftung nach jedem Abkühlvorgang. Damit wird die insbesondere bei Die¬ selmotoren durch Brenngas-Übertritt ins Kühlmittel hervorgerufene Aufpump-Nei¬ gung des Kühlsystems 1 unterdrückt;Separation of air / gas and coolant during the pressure build-up phase during warm-up; System ventilation after each cooling process. This suppresses the tendency of the cooling system 1 to inflate, particularly in diesel engines due to fuel gas transfer into the coolant;
Abhängigkeit des Druckaufbaues - abgesehen von systembedingten Größen wie Kühlmittel-Gesamtinhalt, Wasser/Glykol-Mischungsverhältnis und Schlauch- Elastizität - ausschließlich von einer Einflußgröße, nämlich der Steifigkeit der Druckfeder 20. Dependency of the pressure build-up - apart from system-related variables such as total coolant content, water / glycol mixture ratio and hose elasticity - depends solely on an influencing variable, namely the rigidity of the compression spring 20.

Claims

Patentansprüche claims
1. Kühisystem für eine flüssigkeitsgekühlte Brennkraftmaschine, - mit einer elastisch nachgiebigen Einrichtung zum Ausgleich thermisch be¬ dingter Volumenänderungen bis zu einem vorbestimmten Systemdruck des mittels einer Pumpe (10) umgewälzten Kühlmittels, und1. Cooling system for a liquid-cooled internal combustion engine, - with an elastically flexible device for compensating for thermally-induced changes in volume up to a predetermined system pressure of the coolant circulated by means of a pump (10), and
- einer Vorrichtung (11) zur Systemdrucksteuerung in einer Vorlaufleitung (13), wobei - die einen Behälter (12) durchsetzend angeordnete Vorlaufleitung (13) ei¬ nen mit einem Einfüllstutzen (26) im wesentlichen fluchtend angeordneten Ventilstutzen (14) aufweist zur Aufnahme einer entgegengesetzte Durch¬ flußrichtungen steuernden Ventileinheit (25), die- A device (11) for system pressure control in a flow line (13), - the flow line (13), which extends through a container (12) and has a filler neck (26) which is arranged essentially flush to accommodate a valve neck (14) opposite flow direction controlling valve unit (25), the
- gegen einen Verschluß (32) des Einfüllstutzens (26) elastisch abgestützt im Ventilstutzen (14) verlagerbar angeordnet ist, dadurch gekennzeichnet,- Is displaceably arranged against a closure (32) of the filler neck (26) in the valve neck (14), characterized in that
- daß der Ventilstutzen (14) eine Trennwand (15) des Behälters (12) dicht durchsetzend angeordnet ist mit einer Ventilöffnung (16) in eine Kammer (17) für eine atmosphärisch beaufschlagte Kühlmittel-Voriage (18), und - daß eine weitere, geodätisch tiefer angeordnete Kammer (19) des Behäl¬ ters (12) mittels einer gegen elastischen Widerstand verlagerbaren Be¬ grenzung (21) einem Kühlmittelvolumen-Ausgleich dient, wobei- That the valve stub (14) a partition (15) of the container (12) is arranged tightly penetrating with a valve opening (16) in a chamber (17) for an atmospheric coolant-Voriage (18), and - that a further, Chamber (19) of the container (12) which is arranged geodetically lower serves to compensate for coolant volume by means of a limit (21) which can be displaced against elastic resistance
- die Ausgleichskammer (19) über einen Anschlußstutzen (23) mit einer Pumpen-Saugleitung (9) des Kühlsystems (1) und ferner mit der Kühlmit- tei- Vorlagekammer (17) über ein temperaturgesteuertes Entlüftungs- und Rucklauf-Ventil (24) in Verbindung steht- The compensation chamber (19) via a connection piece (23) with a pump suction line (9) of the cooling system (1) and also with the coolant partial supply chamber (17) is connected via a temperature-controlled vent and return valve (24)
Kuhlsystem nach Anspruch 1 , dadurch gekennzeichnet, - daß der Ventilstutzen (14) der Vorlaufleitung (13) mit einer zur Kaltbeful- lung des Kuhlsystems (1) entfernbar angeordneten Ventilemheit (25) aus¬ gebildet ist, dieCooling system according to claim 1, characterized in that - the valve stub (14) of the flow line (13) is formed with a valve unit (25) which is removably arranged for cold cooling of the cooling system (1) and which
- bei Warmbefullung des Kύhlsystems (1) gegen einen in Niveauhohe des Warmfullstandes in der Vorlagekammer (17) vorgesehenen Anschlag (Boden 35) eines im Einfullstutzen (26) losbar angeordneten Einsatzes- When the cooling system (1) is filled with heat against a stop (bottom 35) of an insert which is detachably arranged in the filler neck (26) at the level of the warm fill level in the supply chamber (17)
(27) elastisch abgestutzt im Ventilstutzeπ (14) eingesetzt ist(27) is elastically supported in the valve support (14)
Kuhlsystem nach Anspruch 1 und 2, dadurch gekennzeichnet,Cooling system according to claim 1 and 2, characterized in
- daß die Ventilemheit (25) ein mit einem Überdruckventil (29) baulich kom- biniertes Entlüftungs- und Rucklauf-Ventil (30) umfaßt, wobei- That the Ventilemheit (25) with a pressure relief valve (29) structurally combined ventilation and return valve (30), wherein
- das als Thermoventil gestaltete Entlüftungs- und Rucklaufventil (30) eine zwischen Vorlagekammer (17) und Vorlaufleitung (13) wirksame Entlüf¬ tungs- und Rucklaufbohrung (31) in dem als Sitzventil gestalteten Über¬ druckventil (29) temperaturabhangig steuert- The venting and return valve (30) designed as a thermal valve controls a venting and return bore (31) effective between the supply chamber (17) and the supply line (13) in the pressure relief valve (29) designed as a seat valve, depending on the temperature
Kühisystem nach den Ansprüchen 1 bis 3, dadurch gekennzeichnet,Cooling system according to claims 1 to 3, characterized in that
- daß der Verschluß (32) des Einfύllstutzens (26) der Vorlagekammer (17) einen mit dem Einfullstutzen (26) verschraubbaren, topfartig gestalteten Einsatz (27) sowie - einen mit dem Einsatz (27) zusammenwirkenden Verschiußdeckel (33) mit einer Entluftungsbohrung (34) umfaßt, wobei- That the closure (32) of the filler neck (26) of the supply chamber (17) has a cup-shaped insert (27) which can be screwed to the filler neck (26), and - A cover (33) which interacts with the insert (27) and has a vent hole ( 34), wherein
- der Einsatz (27) in dem als Anschlag der Feder (28) der Ventilemheit (25) dienenden Boden (35) eine der Kontrolle des Warmfullstandes dienende Kontrolloffnung (36) sowie im Umfangsteil (37) verschlußdeckelnah ange- ordnete Entluftungskanale (38) aufweist- The insert (27) in the bottom (35) serving as a stop for the spring (28) of the valve unit (25) has a control opening (36) serving to check the hot fill level and in the peripheral part (37) there are ventilation channels (38) arranged close to the closure cover
Kanalsystem nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, - daß die Ausgleichskammer (19) als verlagerbare Begrenzung einen mittels eines Rollbalges (22) kühlmitteldicht angeordneten Verdrängerkolben (21) umfaßt, derChannel system according to claims 1 to 4, characterized in - That the compensation chamber (19) comprises a displaceable by means of a rolling bellows (22) coolant-tight displacement piston (21) as a displaceable limit, the
- von einer gegen den Behälter (12) abgestützt, vorgespannt angeordneten Druckfeder (20) beaufschlagt ist.- Is acted upon by a pressure spring (20), which is supported against the container (12) and is biased.
6. Kühlsystem nach den Ansprüchen 1 bis 5, dadurch gekennzeichnet, daß die Befüll-, Entlüftungs- und Drucksteuer- Vorrichtung (11) mit atmosphärisch be¬ aufschlagter Kühlmittel-Vorlage (18) über die Vorlaufleitung (13) unmittelbar im Vorlauf (3) von der Brennkraftmaschine (2) zum Kühler (4) angeordnet ist. 6. Cooling system according to claims 1 to 5, characterized in that the filling, venting and pressure control device (11) with atmospherically charged coolant template (18) via the flow line (13) directly in the flow (3) from the internal combustion engine (2) to the radiator (4).
EP97914252A 1996-03-21 1997-03-15 Cooling system for a liquid-cooled internal combustion engine Expired - Lifetime EP0888494B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19611095 1996-03-21
DE19611095A DE19611095A1 (en) 1996-03-21 1996-03-21 Cooling system for a liquid-cooled internal combustion engine
PCT/EP1997/001318 WO1997035101A1 (en) 1996-03-21 1997-03-15 Cooling system for a liquid-cooled internal combustion engine

Publications (2)

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

Family

ID=7788940

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97914252A Expired - Lifetime EP0888494B1 (en) 1996-03-21 1997-03-15 Cooling system for a liquid-cooled internal combustion engine

Country Status (6)

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

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Also Published As

Publication number Publication date
US6125800A (en) 2000-10-03
EP0888494B1 (en) 2000-06-28
JP2000509454A (en) 2000-07-25
DE59701936D1 (en) 2000-08-03
DE19611095A1 (en) 1997-09-25
ES2148949T3 (en) 2000-10-16
WO1997035101A1 (en) 1997-09-25

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