EP2587017A1 - Coolant circuit for a liquid-cooled combustion engine - Google Patents
Coolant circuit for a liquid-cooled combustion engine Download PDFInfo
- Publication number
- EP2587017A1 EP2587017A1 EP20120005202 EP12005202A EP2587017A1 EP 2587017 A1 EP2587017 A1 EP 2587017A1 EP 20120005202 EP20120005202 EP 20120005202 EP 12005202 A EP12005202 A EP 12005202A EP 2587017 A1 EP2587017 A1 EP 2587017A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cooling circuit
- rotary valve
- flow
- retarder
- line
- 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.)
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- 238000002485 combustion reaction Methods 0.000 title claims description 35
- 239000002826 coolant Substances 0.000 title abstract description 7
- 238000001816 cooling Methods 0.000 claims abstract description 91
- 230000001419 dependent effect Effects 0.000 claims abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 3
- 238000000034 method Methods 0.000 claims abstract 2
- 238000010438 heat treatment Methods 0.000 claims description 10
- 230000008878 coupling Effects 0.000 claims description 6
- 238000010168 coupling process Methods 0.000 claims description 6
- 238000005859 coupling reaction Methods 0.000 claims description 6
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 239000012809 cooling fluid Substances 0.000 claims description 2
- 238000005057 refrigeration Methods 0.000 claims 1
- 239000000110 cooling liquid Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000004886 process control Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000979 retarding effect Effects 0.000 description 1
- 210000002023 somite Anatomy 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
Images
Classifications
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- 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
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
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- 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
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
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- 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
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/06—Retarder
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86509—Sequentially progressive opening or closing of plural ports
- Y10T137/86517—With subsequent closing of first port
- Y10T137/86533—Rotary
Definitions
- the present invention relates to a cooling circuit for a liquid-cooled internal combustion engine for motor vehicles according to the preamble of patent claim 1.
- a generic cooling circuit describes the DE 103 32 907 A1 with a main cooling circuit for the internal combustion engine and a secondary cooling circuit for a retarder as a braking device of the motor vehicle.
- the main cooling circuit with an integrated short-circuit line for decoupling the radiator when the internal combustion engine is still cold is controlled by means of a thermostatic valve.
- the heat generated in the retarder in the activated state or braking mode is dissipated via the main cooling circuit.
- a changeover valve is integrated in the secondary cooling circuit, by means of which, when the retarder is not activated, the secondary cooling circuit can be decoupled to relieve the supply of the two cooling circuits.
- the object of the invention is to propose a cooling circuit of the generic type, which allows for structurally little effort an improved thermal design and control of the liquid flows of both circuits.
- the two cooling circuits are controlled by a single rotary slide valve, at whose openings having housing both cooling circuits are interconnected such that their flow rates to the radiator and / or the retarder in a predetermined or defined manner, preferably between 0% and 100% , are changeable.
- the rotary valve valve allows structurally and control technology simple manner not only the optionally decoupling of the radiator and / or the secondary circuit of the retarder, but also any intermediate positions for improved thermal control and adaptation to different operating conditions of the internal combustion engine and the retarder.
- the housing of the rotary valve may have four flow openings and be turned on in the flow line from the engine to the radiator, via a third flow opening the short-circuit line between the flow line and the return line of the main cooling circuit and finally the return line of the retarder to the fourth Flow opening is connected and further wherein the flow line of the retarder is connected upstream of the rotary valve with the flow line of the main cooling circuit.
- the fourth flow opening for the return line of the retarder opens axially to the rotary valve and constantly open is.
- a throttle element is provided which ensures a minimum flow rate of cooling fluid through the retarder.
- the throttle element may be formed in the region of the rotary valve inlet by a diaphragm or a cross-sectional taper.
- a conveying device in particular a feed pump, is switched on in the main cooling circuit, wherein it is preferably provided that the conveying device is in the main cooling circuit is designed power-controlled and / or temporarily depending on the switching position of the rotary valve with more or less capacity is operable.
- the conveyor may be formed for example by an electrically controllable feed pump or else alternatively be formed by means of a coupling device, such as a belt drive, to the internal combustion engine and thus their "speed" coupled mechanical feed pump.
- the delivery rate can in turn be regulated by means of an adjustment device, wherein the adjustment device can be, for example, a coupling device, such as a magnetic coupling or a viscous coupling, to name just a few examples.
- the adjustment device can also be formed by an adjustable guide vane arrangement. In such a structure, the drive power of the feed pump (with constant flow rate) at decoupled via the rotary valve retarder and / or operated in short circuit main cooling circuit (without flow through the radiator) can be significantly reduced and thus drive energy of the internal combustion engine can be saved.
- the rotary valve or the rotary valve can preferably be adjusted electrically via a stepping motor, wherein the operating temperatures of the cooling circuits, load conditions of the internal combustion engine and operating conditions of the service brake of the motor vehicle detected and adjusted in accordance with these data, the rotary valve and optionally the delivery rate of the pump.
- the stepper motor can preferably adjust the rotary slide valve in both directions of rotation and thus control different circuit sequences.
- the rotary valve may be provided with at least one position sensor, for example a rotation angle sensor, and its function may be electronically monitored in a feed back controller. In the case of a detected malfunction, a warning signal can then be generated and / or a safety position of the rotary valve can be approached (for example, both cooling circuits opened, increased output of the delivery pump, etc.).
- a heating function for the internal combustion engine for example at extremely low outside temperatures and / or for a comfortable cold running behavior and / or for a quick response of a to the main cooling circuit connected interior heating
- the retarder activated and its auxiliary cooling circuit be temporarily connected via the rotary valve to the short-circuited main cooling circuit. This results in a double effect by the heating of the retarder on the one hand, but its braking operation on the other hand causes a higher drive power of the internal combustion engine connected to a higher, temporary fuel flow rate and a faster heating of the internal combustion engine.
- the rotary valve of the rotary valve can be resiliently biased in a predetermined position, in which both the main cooling circuit and the secondary cooling circuit are fluidically connected to the radiator of the main cooling circuit. This ensures in an advantageous manner that in case of failure of the electrical operation of the rotary valve, the cooling of the engine and the retarder is secured.
- the bias voltage can be produced, for example, by acting in the circumferential direction, acting on the rotary valve and the housing torsion springs.
- the rotary valve and the feed pump of the main cooling circuit can be arranged in a common housing.
- Fig. 1 is roughly schematically illustrated the cooling circuit of a liquid-cooled internal combustion engine 1 for motor vehicles, with a main cooling circuit 2 and a secondary cooling circuit 3 for only indicated retarder 4 of a brake device (retarding brake) of the motor vehicle,
- the main cooling circuit 2 is composed essentially of a flow line 5 from the internal combustion engine 1 to an air-water heat exchanger or a cooler 6 and a return line 7 from the radiator 6 to the engine 1.
- a feed pump 8 with variable controllable Delivery arranged in the return line 7 .
- a short-circuit line 9 is turned on, which is (not shown) by means of an electric stepping motor actuated rotary valve 10 is controllable.
- the main cooling circuit 2 is shown only insofar as is necessary for the understanding of the present invention. Other cooling circuit connections such as an interior heating of the motor vehicle, etc. are not shown.
- the auxiliary cooling circuit 3 for cooling the retarder 4 also has a flow line 11 and a return line 12.
- the flow line 11 is connected upstream of the rotary valve 10 to a portion 5a of the flow line 5 of the main cooling circuit 2, wherein between the junction of the two flow lines 5a, 11 and the rotary valve 10, a throttle device 13 (for example, a defined constriction) may be provided in the flow line 5a can.
- a throttle device 13 for example, a defined constriction
- the feed pump 8 and the stepper motor of the rotary valve 10 are controlled via an electronic control unit 14 (indicated in dashed lines), the variable capacity of the feed pump 8, for example, by speed or volume flow change and the position of the rotary valve 10 in the yet to be described Switch positions effected. If appropriate, the control unit 14 can also control an electric radiator fan 16 on the radiator 6.
- control unit 14 to the data of temperature sensors T (not shown), for example, in the flow lines 5, 12, of load conditions L of the internal combustion engine (for example, drive or overrun), the operating state R of the retarder 4, etc. detected and processed control technology.
- Fig. 2 to 9 show a cross section through the housing 10a of the rotary valve 10, in which the crescent-shaped rotary valve 10b is rotatably mounted.
- the externally sealed rotary valve 10b may be moved, via the stepping motor, to the positions of, for example, zero degrees (e) described below.
- Fig. 2 ) up to 315 degrees ( Fig. 9 ) are adjusted.
- Another connecting piece 15 of the return line 12 is aligned coaxially with the axis of rotation of the rotary valve 10b, wherein the flow opening is constantly opened or connected depending on the rotary valve position with one or two of the other three flow openings.
- the secondary cooling circuit 3 is decoupled with the retarder 4 due to its higher flow resistance, which may be set by the throttle body 13, if necessary, a small minimum flow rate.
- the rotary valve 10 b via the stepping motor in the in the Fig. 4 adjusted switching position adjusted, in which the short-circuit line 9 is closed and the flow line section 5b to the radiator 6 and the flow line section 5a of the flow line 5 are fully open.
- the retarder 4 is further decoupled for the reasons mentioned above.
- the power of the feed pump 8 may optionally already be increased.
- Fig. 5 is the rotary valve 10b adjusted to a position in which the flow opening to the supply line section 5b further fully open, the flow opening of the supply line section 5a is partially closed but.
- the power of the feed pump 8 is further raised.
- both cooling circuits 2 and 3 are fully integrated in the cooling liquid conversion or switched to full cooling capacity.
- the flow of the cooling liquid flows via the supply line section 5a of the supply line 5, the supply line 11, the retarder 4, the return line 12, the supply line section 5b of the main cooling circuit, the cooler 6, etc.
- the rotary valve 10b can move into a switching position Fig. 7 be controlled, in which the flow line section 5a further closed, the flow opening for the short-circuit line 9 but is partially open. As a result, with full flow through the retarder 4, the flow through the internal combustion engine 1 is reduced.
- This state can be at a longer overrun phase with further optional cooling of the internal combustion engine 1 according to Fig. 8 be increased so that at closed flow openings of the flow line section 5a and the flow line section 5b and open flow opening of the short-circuit line 9 of the retarder 4 flows through full, the cooling liquid flow through the flow line 11 of the secondary cooling circuit 3, the retarder 4, the return line 12, the Short circuit line 9, the feed pump 8 and the upstream return line 7 takes place.
- the retarder 4 thus additionally causes a heating or temperature stabilization of the internal combustion engine 1, while the radiator 6 is decoupled.
- the rotary valve 10 is not limited to the illustrated embodiment.
- stepper motor instead of an adjustable in both directions stepper motor also another electrical mechanical, pneumatic, hydraulic or magnetic actuation may be provided.
- the rotary valve 10b can by means of resilient means (for example, torsion springs) in a switching position, for example according to Fig. 6 be biased, these move automatically in case of failure of electrical operation in this position and hold there. This ensures that both cooling circuits 2, 3 are in operation or impermissible overheating can not occur.
- resilient means for example, torsion springs
- the rotary valve 10 may be provided with at least one position sensor, for example a rotation angle sensor (not shown), which is connected to the controller 14 so as to electronically protect the function of the rotary valve 10b in a feed back control.
- a rotation angle sensor not shown
- the retarder 4 can be activated in a heating function for the internal combustion engine 1 and its secondary cooling circuit 3 temporarily connected via the rotary valve 10 to the short-circuited main cooling circuit 2 (switching position of the rotary valve 10b according to Fig. 8 ).
- the main difference is that the internal combustion engine 1 is fired and is to operate to overcome the applied braking power with higher load requirement. This represents a particularly effective heating phase of the internal combustion engine 1.
- the feed pump 8 and the rotary valve 10 may optionally be arranged in a common housing with integrated short-circuit line 9, whereby the structural complexity is reduced and a particularly compact and easy to install construction is created.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Of Braking Force In Braking Systems (AREA)
- Braking Arrangements (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
- Air-Conditioning For Vehicles (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Die vorliegende Erfindung betrifft einen Kühlkreislauf für eine flüssigkeitsgekühlte Brennkraftmaschine für Kraftfahrzeuge gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a cooling circuit for a liquid-cooled internal combustion engine for motor vehicles according to the preamble of patent claim 1.
Einen gattungsgemäßen Kühlkreislauf beschreibt die
Aufgabe der Erfindung ist es, einen Kühlkreislauf der gattungsgemäßen Art vorzuschlagen, der bei baulich geringem Aufwand eine verbesserte thermische Auslegung und Steuerung der Flüssigkeitsströme beider Kreisläufe zulässt.The object of the invention is to propose a cooling circuit of the generic type, which allows for structurally little effort an improved thermal design and control of the liquid flows of both circuits.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Patentanspruchs 1 gelöst. Vorteilhafte und besonders zweckmäßige Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved with the features of claim 1. Advantageous and particularly expedient developments of the invention are the subject of the dependent claims.
Erfindungsgemäß wird vorgeschlagen, dass die beiden Kühlkreisläufe über ein einziges Drehschieberventil gesteuert sind, an dessen Durchströmöffnungen aufweisendem Gehäuse beide Kühlkreisläufe derart zusammengeschaltet sind, dass deren Durchflussraten zum Kühler und/oder zum Retarder in vorgegebener bzw. definierter Weise, vorzugsweise zwischen 0% und 100%, veränderbar sind. Das Drehschieberventil ermöglicht in baulich und steuerungstechnisch einfacher Weise nicht nur die wahlweise Abkopplung des Kühlers und/oder des Nebenkreislaufs des Retarders, sondern auch beliebige Zwischenstellungen zu einer verbesserten thermischen Steuerung und Anpassung an verschiedene Betriebszustände der Brennkraftmaschine und des Retarders.According to the invention, it is proposed that the two cooling circuits are controlled by a single rotary slide valve, at whose openings having housing both cooling circuits are interconnected such that their flow rates to the radiator and / or the retarder in a predetermined or defined manner, preferably between 0% and 100% , are changeable. The rotary valve valve allows structurally and control technology simple manner not only the optionally decoupling of the radiator and / or the secondary circuit of the retarder, but also any intermediate positions for improved thermal control and adaptation to different operating conditions of the internal combustion engine and the retarder.
In einer baulich besonders günstigen Ausführung kann das Gehäuse des Drehschieberventils vier Durchflussöffnungen aufweisen und in die Vorlaufleitung von der Brennkraftmaschine zum Kühler eingeschaltet sein, wobei über eine dritte Durchflussöffnung die Kurzschlussleitung zwischen der Vorlaufleitung und der Rücklaufleitung des Hauptkühlkreislaufs und schließlich die Rücklaufleitung des Retarders an die vierte Durchflussöffnung angeschlossen ist und wobei ferner die Vorlaufleitung des Retarders stromauf des Drehschieberventils mit der Vorlaufleitung des Hauptkühlkreislaufs verbunden ist.In a structurally particularly advantageous embodiment, the housing of the rotary valve may have four flow openings and be turned on in the flow line from the engine to the radiator, via a third flow opening the short-circuit line between the flow line and the return line of the main cooling circuit and finally the return line of the retarder to the fourth Flow opening is connected and further wherein the flow line of the retarder is connected upstream of the rotary valve with the flow line of the main cooling circuit.
Dabei können bei einer konstruktiv einfachen Ausbildung des Drehschiebers drei der Durchflussöffnungen radial und in Umfangsrichtung verteilt am Gehäuse des Drehschieberventils angeordnet und über einen zum Beispiel im Querschnitt sichelförmigen Drehschieber gesteuert sein, wobei die vierte Durchflussöffnung für die Rücklaufleitung des Retarders axial zum Drehschieber mündet und ständig geöffnet ist. Dies hat insbesondere den Vorteil, dass nur drei Durchflussöffnungen über den Drehschieber zu steuern sind, während bei der ständig offenen Durchflussöffnung der Durchflusswiderstand des Nebenkühlkreislaufs in die Steuerung mit einbezogen ist.Here, in a structurally simple design of the rotary valve three of the flow openings radially and circumferentially distributed on the housing of the rotary valve and controlled by a cross-sectionally sickle-shaped rotary valve, the fourth flow opening for the return line of the retarder opens axially to the rotary valve and constantly open is. This has the particular advantage that only three flow openings are to be controlled via the rotary valve, while in the constantly open flow opening of the flow resistance of the secondary cooling circuit is included in the control.
Dazu kann es ferner vorteilhaft sein, wenn in der Vorlaufleitung von der Brennkraftmaschine zum Kühler stromauf des Drehschieberventils, jedoch stromab der Abzweigung der Vorlaufleitung des Nebenkühlkreislaufs ein Drosselelement vorgesehen ist, das einen Mindestdurchsatz an Kühlflüssigkeit durch den Retarder sicherstellt. Beispielsweise kann das Drosselelement im Bereich des Drehschieberzulaufs durch eine Blende oder eine Querschnittsverjüngung gebildet sein.For this purpose, it may also be advantageous if in the flow line from the internal combustion engine to the radiator upstream of the rotary valve, but downstream of the branch of the flow line of the secondary cooling circuit, a throttle element is provided which ensures a minimum flow rate of cooling fluid through the retarder. For example, the throttle element may be formed in the region of the rotary valve inlet by a diaphragm or a cross-sectional taper.
In besonders vorteilhafter Weiterbildung der vorliegenden Erfindungsidee ist in den Hauptkühlkreislauf eine Fördereinrichtung, insbesondere eine Förderpumpe, eingeschaltet, wobei bevorzugt vorgesehen ist, dass die Fördereinrichtung im Hauptkühlkreislauf leistungsgeregelt ausgebildet ist und/oder temporär abhängig von der Schaltstellung des Drehschieberventils mit mehr oder weniger Förderleistung betreibbar ist. Die Fördereinrichtung kann dabei zum Beispiel durch eine elektrisch regelbare Förderpumpe gebildet sein oder aber auch alternativ durch eine mittels einer Kupplungseinrichtung, wie zum Beispiel einem Riementrieb, an die Brennkraftmaschine und damit deren "Drehzahl" angekoppelte mechanische Förderpumpe ausgebildet sein. Bei letzterer kann die Förderleistung wiederum mittels einer Einstelleinrichtung regelbar sein, wobei als Einstelleinrichtung zum Beispiel eine Kupplungseinrichtung dienen kann, wie beispielsweise eine Magnetkupplung oder eine Viscokupplung, um nur einige Beispiele zu nennen. Alternativ oder zusätzlich kann die Einstelleinrichtung aber auch durch eine verstellbare Leitschaufelanordnung gebildet sein. Bei einem derartigen Aufbau kann die Antriebsleistung der Förderpumpe (bei gleichbleibender Förderleistung) bei über das Drehschieberventil abgekoppeltem Retarder und/oder bei im Kurzschluss betriebenen Hauptkühlkreis (ohne Durchströmung des Kühlers) deutlich vermindert sein und damit Antriebsenergie der Brennkraftmaschine eingespart werden.In a particularly advantageous embodiment of the present inventive concept, a conveying device, in particular a feed pump, is switched on in the main cooling circuit, wherein it is preferably provided that the conveying device is in the main cooling circuit is designed power-controlled and / or temporarily depending on the switching position of the rotary valve with more or less capacity is operable. The conveyor may be formed for example by an electrically controllable feed pump or else alternatively be formed by means of a coupling device, such as a belt drive, to the internal combustion engine and thus their "speed" coupled mechanical feed pump. In the case of the latter, the delivery rate can in turn be regulated by means of an adjustment device, wherein the adjustment device can be, for example, a coupling device, such as a magnetic coupling or a viscous coupling, to name just a few examples. Alternatively or additionally, however, the adjustment device can also be formed by an adjustable guide vane arrangement. In such a structure, the drive power of the feed pump (with constant flow rate) at decoupled via the rotary valve retarder and / or operated in short circuit main cooling circuit (without flow through the radiator) can be significantly reduced and thus drive energy of the internal combustion engine can be saved.
Das Drehschieberventil bzw. der Drehschieber kann bevorzugt elektrisch über einen Schrittmotor verstellbar sein, wobei die Betriebstemperaturen der Kühlkreisläufe, Lastzustände der Brennkraftmaschine und Betriebszustände der Betriebsbremse des Kraftfahrzeugs erfasst und nach Maßgabe dieser Daten der Drehschieber und gegebenenfalls die Förderleistung der Förderpumpe verstellt wird. Der Schrittmotor kann bevorzugt in beide Drehrichtungen den Drehschieber verstellen und somit unterschiedliche Schaltungsabfolgen steuern.The rotary valve or the rotary valve can preferably be adjusted electrically via a stepping motor, wherein the operating temperatures of the cooling circuits, load conditions of the internal combustion engine and operating conditions of the service brake of the motor vehicle detected and adjusted in accordance with these data, the rotary valve and optionally the delivery rate of the pump. The stepper motor can preferably adjust the rotary slide valve in both directions of rotation and thus control different circuit sequences.
Ferner kann zur Erzielung einer fail safe Schaltung das Drehschieberventil mit zumindest einem Positionssensor, zum Beispiel einem Drehwinkelsensor versehen und dessen Funktion in einer feed back Steuerung elektronisch überwacht sein. Bei einer festgestellten Fehlfunktion kann dann ein Warnsignal generiert und/oder eine Sicherheitsstellung des Drehschiebers angefahren werden (zum Beispiel beide Kühlkreisläufe geöffnet, erhöhte Leistung der Förderpumpe, etc.).
Des Weiteren kann in einer Aufheizfunktion für die Brennkraftmaschine (zum Beispiel bei extrem niedrigen Außentemperaturen und/oder zu einem komfortablen Kaltfahrverhalten und/oder zu einem schnellen Ansprechen einer an den Hauptkühlkreislauf angeschlossenen Innenraumheizung) der Retarder aktiviert und dessen Nebenkühlkreislauf temporär über das Drehschieberventil an den kurzgeschlossenen Hauptkühlkreislauf angeschlossen sein. Daraus resultiert ein Doppeleffekt durch das Zuheizen des Retarders einerseits, dessen Bremsbetrieb aber andererseits eine höhere Antriebsleistung der Brennkraftmaschine verbunden mit einem höheren, temporären Kraftstoffdurchsatz und einer schnelleren Erwärmung der Brennkraftmaschine bewirkt.Further, to achieve a fail-safe circuit, the rotary valve may be provided with at least one position sensor, for example a rotation angle sensor, and its function may be electronically monitored in a feed back controller. In the case of a detected malfunction, a warning signal can then be generated and / or a safety position of the rotary valve can be approached (for example, both cooling circuits opened, increased output of the delivery pump, etc.).
Furthermore, in a heating function for the internal combustion engine (for example at extremely low outside temperatures and / or for a comfortable cold running behavior and / or for a quick response of a to the main cooling circuit connected interior heating) of the retarder activated and its auxiliary cooling circuit be temporarily connected via the rotary valve to the short-circuited main cooling circuit. This results in a double effect by the heating of the retarder on the one hand, but its braking operation on the other hand causes a higher drive power of the internal combustion engine connected to a higher, temporary fuel flow rate and a faster heating of the internal combustion engine.
Der Drehschieber des Drehschieberventils kann in eine vorgegebene Stellung federnd vorgespannt sein, in der sowohl der Hauptkühlkreislauf als auch der Nebenkühlkreislauf mit dem Kühler des Hauptkühlkreislaufs strömungstechnisch verbunden sind. Damit wird in vorteilhafter Weise sichergestellt, dass bei einem Ausfall der elektrischen Betätigung des Drehschiebers die Kühlung der Brennkraftmaschine und des Retarders gesichert ist. Die Vorspannung kann zum Beispiel durch in Umfangsrichtung wirkende, am Drehschieber und am Gehäuse angreifende Schenkelfedern hergestellt sein.The rotary valve of the rotary valve can be resiliently biased in a predetermined position, in which both the main cooling circuit and the secondary cooling circuit are fluidically connected to the radiator of the main cooling circuit. This ensures in an advantageous manner that in case of failure of the electrical operation of the rotary valve, the cooling of the engine and the retarder is secured. The bias voltage can be produced, for example, by acting in the circumferential direction, acting on the rotary valve and the housing torsion springs.
Schließlich können in einer baulich kompakten und gewichtsgünstigen Konstruktion das Drehschieberventil und die Förderpumpe des Hauptkühlkreislaufs in einem gemeinsamen Gehäuse angeordnet sein.Finally, in a structurally compact and lightweight construction, the rotary valve and the feed pump of the main cooling circuit can be arranged in a common housing.
Ferner wird eine Verfahrensführung für einen derartigen erfindungsgemäßen Kühlkreislauf beansprucht, mit dem sich die zuvor genannten Vorteile ergeben.Furthermore, a process control for such a cooling circuit according to the invention is claimed, with which the advantages mentioned above result.
Ein Ausführungsbeispiel der Erfindung ist im Folgenden anhand der beiliegenden schematischen Zeichnung näher erläutert. Es zeigen:
-
Fig. 1 als vereinfachtes Blockschaltbild einen Kühlkreislauf für eine Brennkraftmaschine in Kraftfahrzeugen, mit einem Hauptkühlkreislauf und einem Nebenkühlkreislauf für einen Retarder als Bremseinrichtung des Kraftfahrzeuges, und mit einem elektrisch betätigten Drehschieberventil zur Steuerung beider Kühlkreisläufe, und -
Fig. 2 bis 9 einen Querschnitt durch das Gehäuse des Drehschieberventils mit acht möglichen Stellungen des Drehschiebers zur Steuerung des Haupt- und Nebenkühlkreislaufs.
-
Fig. 1 as a simplified block diagram of a cooling circuit for an internal combustion engine in motor vehicles, with a main cooling circuit and a secondary cooling circuit for a retarder as a braking device of the motor vehicle, and with an electrically operated rotary valve for controlling both cooling circuits, and -
Fig. 2 to 9 a cross section through the housing of the rotary valve with eight possible positions of the rotary valve to control the main and secondary cooling circuit.
In der
Der Hauptkühlkreislauf 2 setzt sich im Wesentlichen zusammen aus einer Vorlaufleitung 5 von der Brennkraftmaschine 1 zu einem Luft-Wasser-Wärmetauscher bzw. einem Kühler 6 und einer Rücklaufleitung 7 vom Kühler 6 zur Brennkraftmaschine 1. In der Rücklaufleitung 7 ist eine Förderpumpe 8 mit variabel steuerbarer Förderleistung angeordnet.The main cooling circuit 2 is composed essentially of a
Zwischen der Vorlaufleitung 5 und der Rücklaufleitung 7 ist stromab der Förderpumpe 8 eine Kurzschlussleitung 9 eingeschaltet, die über ein mittels eines elektrischen Schrittmotors (nicht dargestellt) betätigtes Drehschieberventil 10 steuerbar ist.Between the
Der Hauptkühlkreislauf 2 ist nur soweit dargestellt, als dies für das Verständnis der vorliegenden Erfindung erforderlich ist. Weitere Kühlkreislaufanschlüsse wie zum Beispiel eine Innenraumheizung des Kraftfahrzeugs, etc. sind nicht eingezeichnet.The main cooling circuit 2 is shown only insofar as is necessary for the understanding of the present invention. Other cooling circuit connections such as an interior heating of the motor vehicle, etc. are not shown.
Der Nebenkühlkreislauf 3 zur Kühlung des Retarders 4 (zum Beispiel über einen Wärmetauscher oder durch Direktbeaufschlagung) weist ebenfalls eine Vorlaufleitung 11 und eine Rücklaufleitung 12 auf.The
Die Vorlaufleitung 11 ist stromauf des Drehschieberventils 10 an einen Abschnitt 5a der Vorlaufleitung 5 des Hauptkühlkreislaufs 2 angeschlossen, wobei zwischen der Verbindungsstelle der beiden Vorlaufleitungen 5a, 11 und dem Drehschieberventil 10 eine Drosseleinrichtung 13 (zum Beispiel eine definierte Verengung) in der Vorlaufleitung 5a vorgesehen sein kann.The
Die Förderpumpe 8 und der Schrittmotor des Drehschieberventils 10 werden über ein elektronisches Steuergerät 14 (in gestrichelten Linien angedeutet) gesteuert, das die variable Leistung der Förderpumpe 8 zum Beispiel durch Drehzahl- bzw. Volumenstromveränderung und die Stellung des Drehschieberventils 10 in die noch zu beschreibenden Schaltstellungen bewirkt. Das Steuergerät 14 kann gegebenenfalls auch einen elektrischen Kühlerlüfter 16 am Kühler 6 ansteuern.The feed pump 8 and the stepper motor of the
Im Steuergerät 14 werden dazu die Daten von Temperatursensoren T (nicht dargestellt) beispielsweise in den Vorlaufleitungen 5, 12, von Lastzuständen L der Brennkraftmaschine (zum Beispiel Antriebs- oder Schubbetrieb), vom Betriebszustand R des Retarders 4, etc. erfasst und regelungstechnisch verarbeitet.In the
Die
An dem Gehäuse 10a sind drei über den Umfang wie ersichtlich versetzte, radial abzweigende Anschlussstutzen angeordnet, die an Durchflussöffnungen angrenzen, die mehr oder weniger von dem Drehschieber 10b gesperrt oder freigegeben sind. An die Anschlussstutzen sind der Abschnitt 5a (jeweils mit Pfeilen angedeutet) der Vorlaufleitung 5, die weiterführende Vorlaufleitungsabschnitt 5b und die Kurzschlussleitung 9 angeschlossen.Disposed on the
Ein weiterer Anschlussstutzen 15 der Rücklaufleitung 12 ist koaxial zur Drehachse des Drehschiebers 10b ausgerichtet, wobei dessen Durchflussöffnung ständig geöffnet bzw. je nach Drehschieberstellung mit einer oder zwei der übrigen drei Durchflussöffnungen verbunden ist.Another connecting
In der 0 Grad Ausgangsstellung des Drehschiebers 10b (
Die Durchflussöffnung des weiterführenden Vorlaufleitungsabschnitts 5b ist geschlossen. Diese Stellung entspricht einem Kaltstart der Brennkraftmaschine 1.In the 0 degree initial position of the
The flow opening of the continuing
In dieser Schaltstellung wird Kühlflüssigkeit von der Brennkraftmaschine 1 über die Kurzschlussleitung 9, die Förderpumpe 8 und den restlichen Abschnitt der Rücklaufleitung 7 wieder zur Brennkraftmaschine 1 umgewälzt. Der Kühler 6 ist abgekoppelt, wird also nicht durchströmt.In this switching position, coolant from the internal combustion engine 1 via the short-
Ebenso ist der Nebenkühlkreislauf 3 mit dem Retarder 4 aufgrund dessen höheren Durchflusswiderstands abgekoppelt, wobei durch die Drosselstelle 13 gegebenenfalls ein geringer Mindestdurchsatz eingestellt sein kann.Likewise, the
Die Aufteilung des Kühlflüssigkeits-Durchsatzes ist zum Beispiel wie folgt:
- Kühler 6 - 0%;
- Kurzschlussleitung 9 - 100%;
- Retarder 4 - 0%;
- Leistung der Förderpumpe 8 vermindert, oder sogar kurzfristig abgeschaltet.
- Die
Fig. 3 zeigt die Schaltstellung desDrehschiebers 10b bei zunehmender Erwärmung der Brennkraftmaschine 1, bei der die Durchflussöffnung des Vorlaufleitungsabschnitts 5a voll und die Durchflussöffnungen des Vorlaufleitungsabschnitts 5b und der Kurzschlussleitung 9 teilweise geöffnet sind und somit der Kühler 6 mit einem Anteil von ca. 50% in den Kühlflüssigkeitsumlauf eingeschaltet ist.Der Retarder 4 ist aufgrund des höheren Durchflusswiderstandes des Nebenkühlkreislaufs 3 nach wie vor unverändert abgekoppelt.
- Cooler 6 - 0%;
- Short circuit 9 - 100%;
- Retarder 4 - 0%;
- Performance of the feed pump 8 is reduced, or even switched off for a short time.
- The
Fig. 3 shows the switching position of therotary valve 10b with increasing heating of the internal combustion engine 1, in which the flow opening of theflow line section 5a full and the flow openings of theflow line section 5b and theshorting line 9 are partially open and thus thecooler 6 with a share of about 50% in the coolant circulation is turned on. Theretarder 4 is still uncoupled due to the higher flow resistance of thesecondary cooling circuit 3 as before.
Sobald die Brennkraftmaschine 1 ihre Betriebstemperatur erreicht hat, wird der Drehschieber 10b über den Schrittmotor in die in der
In der
Dies bewirkt, dass die Förderpumpe 8 sowohl über den Vorlaufleitungsabschnitt 5b des Hauptkühlkreislaufs 2 als auch über die Vorlaufleitung 11 des Nebenkühlkreislaufs 3 Kühlflüssigkeit ansaugt, bzw. beide Kreisläufe 1 und 2 angekoppelt sind. Dies kann zum Beispiel bei im Bremsbetrieb befindlichem Retarder 4 und relativ heißer Brennkraftmaschine 1 der Fall sein.This has the effect that the delivery pump 8 sucks in coolant both via the
In der Schaltstellung des Drehschiebers 10b gemäß
Demzufolge sind beide Kühlkreisläufe 2 und 3 voll in den Kühlflüssigkeitsumsatz eingebunden bzw. auf volle Kühlleistung geschaltet. Der Kühlflüssigkeitsstrom strömt über den Vorlaufleitungsabschnitt 5a der Vorlaufleitung 5, die Vorlaufleitung 11, den Retarder 4, die Rücklaufleitung 12, den Vorlaufleitungsabschnitt 5b des Hauptkühlkreislaufs, den Kühler 6, usw.As a result, both cooling
Nimmt zum Beispiel bei einer längeren Schubphase des Kraftfahrzeugs mit unbefeuerter Brennkraftmaschine 1 deren Temperatur T ab, so kann der Drehschieber 10b in eine Schaltstellung nach
Dieser Zustand kann bei einer längeren Schubphase bei gegebenenfalls weiterer Abkühlung der Brennkraftmaschine 1 gemäß
Schließlich ist in der Schaltstellung des Drehschiebers 10b nach
Das Drehschieberventil 10 ist nicht auf das dargestellte Ausführungsbeispiel beschränkt.The
So kann anstelle eines in beiden Drehrichtungen verstellbaren Schrittmotors auch eine andere elektrische mechanische, pneumatische, hydraulische oder magnetische Betätigung vorgesehen sein.Thus, instead of an adjustable in both directions stepper motor also another electrical mechanical, pneumatic, hydraulic or magnetic actuation may be provided.
Der Drehschieber 10b kann über federnde Mittel (zum Beispiel Schenkelfedern) in eine Schaltstellung zum Beispiel gemäß
Des Weiteren kann das Drehschieberventil 10 mit zumindest einem Positionssensor, zum Beispiel einem Drehwinkelsensor (nicht dargestellt), versehen sein, der an das Steuergerät 14 angeschlossen ist, um somit die Funktion des Drehschiebers 10b in einer feed back Steuerung elektronisch abzusichern.Furthermore, the
Zusätzlich zu den beschriebenen Funktionen des Drehschieberventils 10 kann in einer Aufheizfunktion für die Brennkraftmaschine 1 der Retarder 4 aktiviert und dessen Nebenkühlkreislauf 3 temporär über das Drehschieberventil 10 an den kurzgeschlossenen Hauptkühlkreislauf 2 angeschlossen sein (Schaltstellung des Drehschiebers 10b gemäß
Die Förderpumpe 8 und das Drehschieberventil 10 können gegebenenfalls in einem gemeinsamen Gehäuse mit integrierter Kurzschlussleitung 9 angeordnet sein, wodurch sich der bauliche Aufwand vermindert und eine besonders kompakte und montagegünstige Konstruktion geschaffen ist.The feed pump 8 and the
Neben den dargestellten Schaltstellungen des Drehschiebers 10b gemäß den
- 11
- Brennkraftmaschine (BKM)Internal combustion engine (BKM)
- 22
- HauptkühlkreislaufMain cooling circuit
- 33
- NebenkühlkreislaufSecondary cooling circuit
- 44
- Retarderretarder
- 55
- Vorlaufleitung von der BKM (1) zum Kühler (6)Supply line from the BKM (1) to the cooler (6)
- 5a5a
- Abschnitt der Vorlaufleitung von der BKM (1) zum Drehschieberventil (10)Section of the supply line from the BKM (1) to the rotary valve (10)
- 5b5b
- Abschnitt der Vorlaufleitung (vom Drehschieberventil (10) zum Kühler (6)Section of the supply line (from the rotary valve (10) to the cooler (6)
- 66
- Kühlercooler
- 77
- Rücklaufleitung vom Kühler (6)Return line from cooler (6)
- 88th
- Förderpumpefeed pump
- 99
- Kurzschlussleitung vom Drehschieberventil (10) zur Förderpumpe (8)Short circuit line from the rotary valve (10) to the feed pump (8)
- 1010
- DrehschieberventilRotary valve
- 10a10a
- Gehäusecasing
- 10b10b
- Drehschieberrotary vane
- 1111
- Vorlaufleitung von der BKM (1) zum Retarder (4)Supply line from the BKM (1) to the retarder (4)
- 1212
- Rücklaufleitung vom Retarder (4) zum Drehschieberventil (10)Return line from the retarder (4) to the rotary valve (10)
- 1313
- Drosselelementthrottle element
- 1414
- Steuergerätcontrol unit
- 1515
- Anschlussstutzenspigot
- 1616
- Kühlerlüfterradiator fan
Claims (13)
Applications Claiming Priority (1)
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DE201110116933 DE102011116933A1 (en) | 2011-10-26 | 2011-10-26 | Cooling circuit for a liquid-cooled engine |
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EP2587017A1 true EP2587017A1 (en) | 2013-05-01 |
EP2587017B1 EP2587017B1 (en) | 2015-05-13 |
Family
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EP20120005202 Active EP2587017B1 (en) | 2011-10-26 | 2012-07-14 | Vehicle with a liquid-cooled internal combustion engine |
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US (1) | US8800503B2 (en) |
EP (1) | EP2587017B1 (en) |
CN (1) | CN103075239B (en) |
BR (1) | BR102012027058B1 (en) |
DE (1) | DE102011116933A1 (en) |
RU (1) | RU2599882C2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015060768A1 (en) * | 2013-10-24 | 2015-04-30 | Scania Cv Ab | Cooling system in a vehicle |
WO2016026903A1 (en) * | 2014-08-21 | 2016-02-25 | Bayerische Motoren Werke Aktiengesellschaft | Method for operating a cooling system of an internal combustion engine and protection system in a cooling system |
EP3078827A1 (en) * | 2015-04-09 | 2016-10-12 | Renault S.A.S. | Method for diagnosing a zero flow rate of a motor vehicle coolant |
EP3137747A4 (en) * | 2014-04-30 | 2017-12-13 | Cummins, Inc. | System and method for optimizing the integration of engines and vehicle driveline retarders |
EP3260679A1 (en) * | 2016-06-20 | 2017-12-27 | Hyundai Motor Company | Diagnostic apparatus and method for coolant control valve |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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DE102014201170A1 (en) * | 2014-01-23 | 2015-07-23 | Bayerische Motoren Werke Aktiengesellschaft | Method and device for venting a thermal management system of an internal combustion engine |
DE102014201167A1 (en) * | 2014-01-23 | 2015-07-23 | Bayerische Motoren Werke Aktiengesellschaft | Thermal management system for an internal combustion engine |
CN104088693B (en) * | 2014-06-10 | 2016-08-10 | 吉林大学 | Engine pack |
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Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6371060B1 (en) * | 1999-07-10 | 2002-04-16 | Daimlerchrysler Ag | Control device for the cooling and heating circuit of an internal combustion engine |
US6539899B1 (en) * | 2002-02-11 | 2003-04-01 | Visteon Global Technologies, Inc. | Rotary valve for single-point coolant diversion in engine cooling system |
DE10215262A1 (en) * | 2002-04-06 | 2003-10-16 | Daimler Chrysler Ag | Cooling system, especially for motor vehicle engine with indirect charging air cooling, has coolant temperature detection arrangement near input coupling point or between it and coolant transport pump |
DE10332907A1 (en) | 2003-07-19 | 2005-02-17 | Voith Turbo Gmbh & Co. Kg | Automotive coolant circuit with pump and retarder |
WO2008080872A1 (en) * | 2006-12-29 | 2008-07-10 | Valeo Systemes Thermiques | High/low temperature water cooling system and a four port valve for such a system |
EP2037097A2 (en) * | 2007-09-11 | 2009-03-18 | Scania CV AB | Cooling system and thermostat device for motor vehicle |
US20090223657A1 (en) * | 2006-05-15 | 2009-09-10 | Hollis Thomas J | Digital Rotary Control Valve |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4700888A (en) * | 1986-06-18 | 1987-10-20 | Cummins Engine Company, Inc. | Auxiliary heater controller |
DE19641558A1 (en) | 1996-10-09 | 1998-04-16 | Voith Turbo Kg | Method and control for regulating the cooling circuit of a vehicle by means of a thermally controlled water pump |
DE19809124A1 (en) * | 1998-03-04 | 1999-09-16 | Daimler Chrysler Ag | Control device for the cooling and heating circuit of an internal combustion engine |
US5950576A (en) * | 1998-06-30 | 1999-09-14 | Siemens Canada Limited | Proportional coolant valve |
DE10001278A1 (en) * | 2000-01-14 | 2001-07-19 | Pierburg Ag | Cooling system for motor vehicle has second coolant circuit feed and outlet points connected to first coolant circuit line on outlet side of engine cooling channels |
SE523073C2 (en) * | 2001-06-28 | 2004-03-23 | Valeo Engine Cooling Ab | Methods and apparatus for cooling charge air and hydraulic oil |
US6668766B1 (en) * | 2002-07-22 | 2003-12-30 | Visteon Global Technologies, Inc. | Vehicle engine cooling system with variable speed water pump |
FR2896271B1 (en) * | 2006-01-19 | 2012-08-17 | Renault Sas | METHOD AND DEVICE FOR CONTROLLING THE TEMPERATURE OF AN INTERNAL COMBUSTION ENGINE |
US7506664B2 (en) * | 2006-04-27 | 2009-03-24 | Ranco Incorporated Of Delaware | Automotive coolant control valve |
US7690397B2 (en) * | 2006-05-15 | 2010-04-06 | Hollis Thomas J | Digital rotary control valve |
DE102006048714A1 (en) | 2006-10-14 | 2008-04-17 | Daimler Ag | Cooling circuit |
FR2908457A3 (en) * | 2006-11-10 | 2008-05-16 | Renault Sas | Recycled exhaust gas cooling system for e.g. oil engine of motor vehicle, has main circuit, and secondary circuit with secondary valve for limiting or preventing circulation of liquid in secondary circuit when cooling is not required |
DE102007055604B3 (en) | 2007-11-20 | 2009-05-07 | Voith Patent Gmbh | Vehicle cooling circuit, has control valve that is integrated in circuit, so that switching position of valve is adjusted based on working medium pressure in retarder, working medium feed line or working medium discharge line of retarder |
DE102010010222A1 (en) | 2010-03-03 | 2011-09-08 | Voith Patent Gmbh | Hydrodynamic retarder and method of operating a hydrodynamic retarder |
-
2011
- 2011-10-26 DE DE201110116933 patent/DE102011116933A1/en not_active Withdrawn
-
2012
- 2012-07-14 EP EP20120005202 patent/EP2587017B1/en active Active
- 2012-09-25 US US13/625,916 patent/US8800503B2/en active Active
- 2012-10-11 RU RU2012143562/06A patent/RU2599882C2/en active
- 2012-10-22 BR BR102012027058-7A patent/BR102012027058B1/en active IP Right Grant
- 2012-10-26 CN CN201210416381.2A patent/CN103075239B/en active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6371060B1 (en) * | 1999-07-10 | 2002-04-16 | Daimlerchrysler Ag | Control device for the cooling and heating circuit of an internal combustion engine |
US6539899B1 (en) * | 2002-02-11 | 2003-04-01 | Visteon Global Technologies, Inc. | Rotary valve for single-point coolant diversion in engine cooling system |
DE10215262A1 (en) * | 2002-04-06 | 2003-10-16 | Daimler Chrysler Ag | Cooling system, especially for motor vehicle engine with indirect charging air cooling, has coolant temperature detection arrangement near input coupling point or between it and coolant transport pump |
DE10332907A1 (en) | 2003-07-19 | 2005-02-17 | Voith Turbo Gmbh & Co. Kg | Automotive coolant circuit with pump and retarder |
US20090223657A1 (en) * | 2006-05-15 | 2009-09-10 | Hollis Thomas J | Digital Rotary Control Valve |
WO2008080872A1 (en) * | 2006-12-29 | 2008-07-10 | Valeo Systemes Thermiques | High/low temperature water cooling system and a four port valve for such a system |
EP2037097A2 (en) * | 2007-09-11 | 2009-03-18 | Scania CV AB | Cooling system and thermostat device for motor vehicle |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2015060768A1 (en) * | 2013-10-24 | 2015-04-30 | Scania Cv Ab | Cooling system in a vehicle |
RU2628689C1 (en) * | 2013-10-24 | 2017-08-21 | Сканиа Св Аб | Cooling system for vehicles |
US10156181B2 (en) | 2013-10-24 | 2018-12-18 | Scania Cv Ab | Cooling system in a vehicle |
EP3137747A4 (en) * | 2014-04-30 | 2017-12-13 | Cummins, Inc. | System and method for optimizing the integration of engines and vehicle driveline retarders |
WO2016026903A1 (en) * | 2014-08-21 | 2016-02-25 | Bayerische Motoren Werke Aktiengesellschaft | Method for operating a cooling system of an internal combustion engine and protection system in a cooling system |
US10174666B2 (en) | 2014-08-21 | 2019-01-08 | Bayerische Motoren Werke Aktiengesellschaft | Method for operating a cooling system of an internal combustion engine and protection system in a cooling system |
EP3078827A1 (en) * | 2015-04-09 | 2016-10-12 | Renault S.A.S. | Method for diagnosing a zero flow rate of a motor vehicle coolant |
FR3034809A1 (en) * | 2015-04-09 | 2016-10-14 | Renault Sa | SYSTEM FOR DIAGNOSING A NULL FLOW OF A COOLING FLUID OF A VEHICLE ENGINE |
EP3260679A1 (en) * | 2016-06-20 | 2017-12-27 | Hyundai Motor Company | Diagnostic apparatus and method for coolant control valve |
US9951676B2 (en) | 2016-06-20 | 2018-04-24 | Hyundai Motor Company | Diagnostic apparatus and method for coolant control valve |
Also Published As
Publication number | Publication date |
---|---|
BR102012027058B1 (en) | 2021-04-27 |
CN103075239A (en) | 2013-05-01 |
US20140230758A9 (en) | 2014-08-21 |
US20140083376A1 (en) | 2014-03-27 |
RU2012143562A (en) | 2014-04-20 |
DE102011116933A1 (en) | 2013-05-02 |
BR102012027058A2 (en) | 2014-04-22 |
EP2587017B1 (en) | 2015-05-13 |
US8800503B2 (en) | 2014-08-12 |
RU2599882C2 (en) | 2016-10-20 |
CN103075239B (en) | 2017-07-11 |
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