EP1929130A1 - Valve for piston cooling nozzles - Google Patents

Valve for piston cooling nozzles

Info

Publication number
EP1929130A1
EP1929130A1 EP06775712A EP06775712A EP1929130A1 EP 1929130 A1 EP1929130 A1 EP 1929130A1 EP 06775712 A EP06775712 A EP 06775712A EP 06775712 A EP06775712 A EP 06775712A EP 1929130 A1 EP1929130 A1 EP 1929130A1
Authority
EP
European Patent Office
Prior art keywords
valve
oil
cooling nozzles
piston cooling
valve according
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
EP06775712A
Other languages
German (de)
French (fr)
Other versions
EP1929130B1 (en
Inventor
Heiko Schulz-Andres
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.)
Magna Powertrain Hueckeswagen GmbH
Original Assignee
Ixetic Hueckeswagen GmbH
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 Ixetic Hueckeswagen GmbH filed Critical Ixetic Hueckeswagen GmbH
Publication of EP1929130A1 publication Critical patent/EP1929130A1/en
Application granted granted Critical
Publication of EP1929130B1 publication Critical patent/EP1929130B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/08—Cooling of piston exterior only, e.g. by jets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means

Definitions

  • the invention relates to a valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine.
  • valves are known.
  • a type of pressure limiting valves is used for this, so that the volume flow, which is to flow through the piston cooling nozzles, only above a certain pressure (usually 2 bar) flows.
  • a certain pressure usually 2 bar
  • the disadvantage of this solution is that at very high temperatures in conjunction with low speeds, the pistons are not cooled because at low speeds, these pressures are not achieved by low pump performance and high leaks. Cooling at high temperatures and low rotational speeds would also be particularly helpful after high engine loads, since the pistons heat up in this reheating phase, although no further energy is supplied thermodynamically.
  • Piston cooling nozzles are used today in internal combustion engines, where due to the high power density overheating of the reciprocating piston can occur. To do this, the piston cooling nozzles inject engine oil from below onto the pistons. In order to achieve the required cooling capacity, a correspondingly large volume flow of the oil is necessary. At low speeds, this can lead to the total volume flow of the lubricating oil pump being insufficient to cover all these consumers.
  • a new, additional application for the piston cooling nozzles is to use them for oil heating in cold oil.
  • the ⁇ lericarmung generated via the pressure relief valve of the piston cooling nozzles is Another possibility.
  • electrically controlled valves which, however, is cost-intensive and space-intensive.
  • the object is achieved by a valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine, wherein the valve produces an oil flow to the piston cooling nozzles at low oil temperatures Interrupting oil flow to the piston cooling nozzles at medium oil temperatures and in turn produces an oil flow to the piston cooling nozzles at high oil temperatures.
  • a valve is preferred which adjusts the oil flow to the piston cooling nozzles depending on the temperature. This has the advantage that the oil flow is regulated independently of pressure, so that, especially in hot running at low speeds by low pressures, a still sufficient flow of oil can be provided by the pump. In addition, at low temperatures, no additional pressure loss is built up by interposing a pressure limiting valve, so that power is saved at the pump at this operating point.
  • a valve is preferred, which is adjustable by a temperature-dependent adjustable actuator (against a return spring).
  • a temperature-dependent adjustable actuator for example, has the advantage that no electromagnet and the necessary control circuit are necessary.
  • Another valve according to the invention is characterized in that an adjustable opening cross section for low oil temperatures is greater than the opening cross section for high oil temperatures. This has the advantage that viscosity-compliant oil flow metering is possible both for the cold operating condition and for the hot running operating condition, since with hot running the oil viscosity can be lower by a factor of 1000 than at low temperatures. In addition, a smaller flow area allows less space for the valve.
  • valve which has one inlet opening and two outlet openings, or two inlet openings and one outlet opening.
  • This has the advantage that, depending on the operating state (cold start or hot run) each have a different drain opening can be connected to the inlet or vice versa.
  • Another valve according to the invention is characterized in that the valve is designed as a slide valve (directional control valve).
  • a valve is preferred in which above the oil temperature of the slide path is adjusted continuously. The continuous adjustment has the advantage that the oil flows can be controlled slowly larger or smaller and no pressure peaks caused by the opening and closing of the opening cross-sections.
  • valve which is integrated in a cartridge sleeve. This has the advantage that the valve can be used as a preassembled, set and tested unit in the engine block.
  • valve is preferred in which the valve components are fixed in the cartridge by a retaining ring. This has the advantage of ease of manufacture and assembly (no thread necessary) and a quick assembly and disassembly of the components as needed. Furthermore, a valve is preferred in which the temperature-dependent adjustable actuator is designed as DehnMechelement or as a bimetallic element. Also preferred is a valve in which the valve is represented by a combination of poppet valves rather than a slide valve.
  • Figure 1 shows a first variant of a control valve according to the invention for
  • FIG. 2 shows another variant of a control valve for piston cooling nozzles in three control positions.
  • FIG. 1 shows a first variant 1 of a control valve for piston cooling nozzles.
  • the three representations of Figure 1a, Figure 1 b and Figure 1c shows the three possible switching positions of this control valve.
  • a valve housing 3 is a continuously displaceable piston 5 between a temperature-dependent adjustable actuator 7, for example, an expansion element, and a coil spring 9 clamped.
  • FIG. 1 a shows the position of the expansion element 7 at a low oil temperature, that is to say in a cold start.
  • the valve housing 1 further has an inlet opening 11 from the lubricating oil circuit of the engine and two drain openings 13 and 15, wherein the two drain openings 13 and 15 lead to the piston cooling nozzles.
  • the oil inlet 11 is connected via an annular groove 17 of the valve piston 5 to the drain 13 so that oil is supplied to the piston cooling nozzles in the cold state via this control valve and thereby after the start of the engine heating of the lubricating oil on the warming piston and the oil sprayed on it takes place.
  • the valve piston 17, the compression spring 9 and the temperature-dependent adjustable actuator 7 are housed in an opening 19 of the valve housing 3 and closed by an end plug 21, with which, if appropriate, the position of the valve piston can be adjusted.
  • the temperature-dependent adjustable expansion element When exceeding the 40 degrees Celsius oil temperature threshold, with a tolerance of + 5 degrees Celsius is sufficient for driving the valve piston in a different position, the temperature-dependent adjustable expansion element, as shown in Figure 1 b, by expansion of the expansion material, such as a wax filling , Extend a corresponding punch 23 within the element and thus move the piston 5 against the spring 9, so that the valve piston 5 now both the outflow 13 to the piston cooling nozzles closes and still closed the drain 15 to the piston cooling nozzles.
  • the expansion material such as a wax filling
  • the directional control valve 1 is used so that at low oil temperatures, a connection is generated from the lubricating oil supply area to the piston cooling nozzles.
  • This connection is generated with the largest possible cross-sections (opening cross-section for the line 13) in order to allow a large volume flow, which can flow off in the cold state via the piston cooling nozzles.
  • the actuator 7 closes this connection and then opens it again only at high temperatures (hot run). This also has the advantage that a possible pre-throttling can prevent the outflow of an impermissibly high volume flow.
  • connection is only opened again at very high temperatures, as shown in FIG. 1 c.
  • the openings 11 and 15 are connected to each other by the further extension of the actuator 7.
  • the hot run is cooled very well.
  • no pressure relief valves with, for example, a necessary opening pressure of 2 bar must be used.
  • oil is injected through the piston cooling nozzles.
  • oil will flow through the piston cooling nozzles only at engine speeds of 4000 rpm in the hot run because of the high leakage.
  • a control valve variant of Figure 2 can be used in which the control valve 28 is integrated into a cartridge sleeve 30 and now only as a pre-assembled, set and tested unit in the engine block 32 must be used.
  • Various solutions are available for fixing the valve components in the cartridge 30. Shown is a fuse by means of a retaining ring 34, which allows quick assembly and, if necessary, disassembly of the valve parts.
  • a solution is shown here in Figure 2, in which only two holes 36 and 38 are needed, which extend at an angle of 90 degrees in the engine block 32. The feed of the lubricating oil through the bore 36, the bore 38 is connected to the piston cooling nozzles. Through two bores 40 and 42 in the piston 44 and through two control openings 46 and 48 in the carton. ridge 30, the control function can now be realized again.
  • Figures 2a, 2b and 2c show again the three different positions.
  • FIG. 2a the cold start position is shown.
  • the temperature-dependent adjustable actuator 50 is retracted.
  • the control piston 44 is pressed against the actuator 50 by the compression spring 52, which is supported on the securing ring 34.
  • the supply line 36 is connected via the control port 46 of the cartridge 30, the radial bore 40 and the axial bore 42 of the piston 44 to the drain 38 to the piston cooling nozzles, so that now in the cold start lubricating oil is injected under the piston for heating.
  • the actuator 50 extended by a certain range, here to recognize the extended punch 54, which is supported in this valve variant 28 against the screw plug 56.
  • the radial transverse bore 40 of the piston is connected in this position neither with the radial inflow bore 46 of the sleeve 30 nor with the radial inflow bore 48 of the sleeve 30, so that via the drain 38 no lubricating oil can flow to the piston cooling nozzles.
  • the hot-running position is reached.
  • the actuator 50 has the punch 54 completely extended.
  • the radial transverse bore 40 of the piston 44 is now connected to the radial hot-flow inlet opening 48 of the sleeve 30, so that the lubricating oil inlet 36 is connected to the drain 38 to the piston cooling nozzles.
  • the opening cross-section 48 that is to say the inlet for the hot-running state of the internal combustion engine, can be decidedly smaller in cross section than the cold running inlet cross section 46, which, however, is not shown to scale in this picture.
  • the invention thus uses the principle with a single control valve, which is also controlled by a temperature-dependent actuator and does not have a pressure limiting function, an oil volume flow above the rising Tempe- first pass, then switch off and then let it through again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Nozzles (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Compressor (AREA)

Abstract

The invention relates to a valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine, said valve (1,28) being characterized in that it produces a throughflow of oil to the piston cooling nozzles at low temperatures, blocks a throughflow of oil to the piston cooling nozzles at medium temperatures, and produces a throughflow of oil to the piston cooling nozzles again at high oil temperatures.

Description

Ventil für Kolbenkühldüsen Valve for piston cooling nozzles
Die Erfindung betrifft ein Ventil zur Regelung eines Ölstromes für Kolbenkühldüsen im Schmierölkreislauf eines Verbrennungsmotors.The invention relates to a valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine.
Derartige Ventile sind bekannt. Im Stand der Technik wird dafür eine Art von Druckbegrenzungsventilen eingesetzt, damit der Volumenstrom, der über die Kolbenkühldüsen fließen soll, erst oberhalb eines bestimmten Druckes (in der Regel 2 bar) abfließt. Der Nachteil dieser Lösung ist, dass bei sehr hohen Temperaturen in Verbindung mit niedrigen Drehzahlen die Kolben nicht gekühlt werden, da bei niedrigen Drehzahlen diese Drücke durch niedrige Pumpenleistung und hohe Leckagen nicht erreicht werden. Dabei wäre das Kühlen bei hohen Temperaturen und niedrigen Drehzahlen auch besonders hilfreich nach hohen Motorbeiastungen, da in dieser Nachheizphase sich die Kolben erhitzen, obwohl thermodynamisch keine weitere Energie zugeführt wird.Such valves are known. In the prior art, a type of pressure limiting valves is used for this, so that the volume flow, which is to flow through the piston cooling nozzles, only above a certain pressure (usually 2 bar) flows. The disadvantage of this solution is that at very high temperatures in conjunction with low speeds, the pistons are not cooled because at low speeds, these pressures are not achieved by low pump performance and high leaks. Cooling at high temperatures and low rotational speeds would also be particularly helpful after high engine loads, since the pistons heat up in this reheating phase, although no further energy is supplied thermodynamically.
Kolbenkühldüsen werden heutzutage in Verbrennungsmotoren eingesetzt, bei denen aufgrund der hohen Leistungsdichte eine Überhitzung des Hubkolbens auftreten kann. Hierzu spritzen die Kolbenkühldüsen Motoröl von unten an die Kolben. Um die erforderliche Kühlleistung zu bewirken, ist ein entsprechend großer Volumenstrom des Öls notwendig. Dies kann bei niedrigen Drehzahlen dazu führen, dass der Gesamtvolumenstrom der Schmierölpumpe nicht ausreichend ist, um alle diese Verbraucher abzudecken.Piston cooling nozzles are used today in internal combustion engines, where due to the high power density overheating of the reciprocating piston can occur. To do this, the piston cooling nozzles inject engine oil from below onto the pistons. In order to achieve the required cooling capacity, a correspondingly large volume flow of the oil is necessary. At low speeds, this can lead to the total volume flow of the lubricating oil pump being insufficient to cover all these consumers.
Ein neuer, zusätzlicher Einsatz für die Kolbenkühldüsen besteht darin, diese auch zur Öler- wärmung bei kaltem Öl einzusetzen. Dazu wird im Stand der Technik die Ölerwärmung über das Druckbegrenzungsventil der Kolbenkühldüsen erzeugt. Eine andere Möglichkeit besteht darin, elektrisch angesteuerte Ventile einzusetzen, was allerdings kostenintensiv und bau- raumintensiv ist.A new, additional application for the piston cooling nozzles is to use them for oil heating in cold oil. For this purpose, in the prior art, the Ölerwärmung generated via the pressure relief valve of the piston cooling nozzles. Another possibility is to use electrically controlled valves, which, however, is cost-intensive and space-intensive.
Es ist daher Aufgabe der Erfindung, ein Regelventil für Kolbenkühldüsen zu finden, welches diese Nachteile nicht aufweist.It is therefore an object of the invention to find a control valve for piston cooling nozzles, which does not have these disadvantages.
Die Aufgabe wird gelöst durch ein Ventil zur Regelung eines Ölstromes für Kolbenkühldüsen im Schmierölkreislauf eines Verbrennungsmotors, wobei das Ventil bei niedrigen Öltemperaturen einen Öldurchfluss zu den Kolbenkühldüsen herstellt, bei mittleren Öltemperaturen einen Öldurchfluss zu den Kolbenkühldüsen unterbricht und bei hohen Öltemperaturen wiederum einen Öldurchfluss zu den Kolbenkühldüsen herstellt. Das hat den Vorteil, dass mit einem einzigen Ventil eine zusätzliche Ölerwär- mung bei kaltem Motor als auch eine Kolbenkühlung bei hohen Öltemperaturen, also bei Heißlauf des Motors, möglich ist.The object is achieved by a valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine, wherein the valve produces an oil flow to the piston cooling nozzles at low oil temperatures Interrupting oil flow to the piston cooling nozzles at medium oil temperatures and in turn produces an oil flow to the piston cooling nozzles at high oil temperatures. This has the advantage that with a single valve an additional oil heating with a cold engine as well as a piston cooling with high oil temperatures, ie with hot running of the engine, is possible.
Es wird ein Ventil bevorzugt, welches temperaturabhängig den Ölstrom zu den Kolbenkühldüsen einstellt/regelt. Das hat den Vorteil, dass der Ölstrom druckunabhängig geregelt wird, so dass vor allem bei Heißlauf mit niedrigen Drehzahlen durch niedrige Drücke ein noch hinreichender Ölstrom von der Pumpe zur Verfügung gestellt werden kann. Außerdem wird bei niedrigen Temperaturen nicht ein zusätzlicher Druckverlust durch Zwischenschalten eines Druckbegrenzungsventils aufgebaut, so dass in diesem Betriebspunkt Leistung an der Pumpe eingespart wird.A valve is preferred which adjusts the oil flow to the piston cooling nozzles depending on the temperature. This has the advantage that the oil flow is regulated independently of pressure, so that, especially in hot running at low speeds by low pressures, a still sufficient flow of oil can be provided by the pump. In addition, at low temperatures, no additional pressure loss is built up by interposing a pressure limiting valve, so that power is saved at the pump at this operating point.
Auch wird ein Ventil bevorzugt, welches durch einen temperaturabhängig verstellbaren Aktor (gegen eine Rückstellfeder) verstellbar ist. Der Einsatz eines temperaturabhängig verstellbaren Aktors hat zum Beispiel den Vorteil, dass keine Elektromagneten und der dazu notwendige Ansteuerschaltkreis notwendig sind.Also, a valve is preferred, which is adjustable by a temperature-dependent adjustable actuator (against a return spring). The use of a temperature-dependent adjustable actuator, for example, has the advantage that no electromagnet and the necessary control circuit are necessary.
Ein weiteres erfindungsgemäßes Ventil zeichnet sich dadurch aus, dass ein einstellbarer Öffnungsquerschnitt für niedrige Öltemperaturen größer ist als der Öffnungsquerschnitt für hohe Öltemperaturen. Das hat den Vorteil, dass eine viskositätsgerechte Ölstromdosierung sowohl für den kalten Betriebszustand als auch für den Heißlauf- Betriebszustand möglich ist, da bei Heißlauf die Ölviskosität um den Faktor 1000 niedriger sein kann als bei niedrigen Temperaturen. Außerdem ermöglicht ein kleinerer Durchflussquerschnitt weniger Bauraum für das Ventil.Another valve according to the invention is characterized in that an adjustable opening cross section for low oil temperatures is greater than the opening cross section for high oil temperatures. This has the advantage that viscosity-compliant oil flow metering is possible both for the cold operating condition and for the hot running operating condition, since with hot running the oil viscosity can be lower by a factor of 1000 than at low temperatures. In addition, a smaller flow area allows less space for the valve.
Auch wird ein Ventil bevorzugt, welches eine Zulauföffnung und zwei Ablauföffnungen aufweist, oder zwei Zulauföffnungen und eine Ablauföffnung. Das hat den Vorteil, dass je nach Betriebszustand (Kaltstart oder Heißlauf) jeweils eine andere Ablauföffnung mit dem Zulauf verbunden werden kann oder umgekehrt. Ein weiteres erfindungsgemäßes Ventil zeichnet sich dadurch aus, dass das Ventil als Schieberventil (Wegeventil) ausgeführt ist. Auch wird ein Ventil bevorzugt, bei welchem über der Öltemperatur der Schieberweg stufenlos verstellt wird. Die stufenlose Verstellung hat den Vorteil, dass die Ölströme langsam größer oder kleiner geregelt werden können und keine Druckspitzen durch das Öffnen und Schließen der Öffnungsquerschnitte entstehen.Also preferred is a valve which has one inlet opening and two outlet openings, or two inlet openings and one outlet opening. This has the advantage that, depending on the operating state (cold start or hot run) each have a different drain opening can be connected to the inlet or vice versa. Another valve according to the invention is characterized in that the valve is designed as a slide valve (directional control valve). Also, a valve is preferred in which above the oil temperature of the slide path is adjusted continuously. The continuous adjustment has the advantage that the oil flows can be controlled slowly larger or smaller and no pressure peaks caused by the opening and closing of the opening cross-sections.
Auch wird ein Ventil bevorzugt, welches in einer Cartridge-Hülse integriert ist. Das hat den Vorteil, dass das Ventil als vormontierte, eingestellte und geprüfte Einheit in den Motorblock eingesetzt werden kann.Also preferred is a valve which is integrated in a cartridge sleeve. This has the advantage that the valve can be used as a preassembled, set and tested unit in the engine block.
Weiterhin wird ein Ventil bevorzugt, bei welchem die Ventilbauteile im Cartridge durch einen Sicherungsring fixiert sind. Das hat den Vorteil einer einfachen Fertigung und Montage (kein Gewinde notwendig) und einer schnellen Montage und Demontage der Bauteile bei Bedarf. Weiterhin wird ein Ventil bevorzugt, bei welchem der temperaturabhängig verstellbare Aktor als Dehnkörperelement oder als Bimetallelement ausgeführt ist. Auch wird ein Ventil bevorzugt, bei welchem das Ventil statt als Schieberventil durch eine Kombination von Sitzventilen dargestellt ist.Furthermore, a valve is preferred in which the valve components are fixed in the cartridge by a retaining ring. This has the advantage of ease of manufacture and assembly (no thread necessary) and a quick assembly and disassembly of the components as needed. Furthermore, a valve is preferred in which the temperature-dependent adjustable actuator is designed as Dehnkörperelement or as a bimetallic element. Also preferred is a valve in which the valve is represented by a combination of poppet valves rather than a slide valve.
Die Erfindung wird nun anhand der Figuren beschrieben:The invention will now be described with reference to the figures:
Figur 1 zeigt eine erste Variante eines erfindungsgemäßen Regelventils fürFigure 1 shows a first variant of a control valve according to the invention for
Kolbenkühldüsen in drei Regelpositionen,Piston cooling nozzles in three control positions,
Figur 2 zeigt eine andere Variante eines Regelventils für Kolbenkühldüsen in drei Regelpositionen.FIG. 2 shows another variant of a control valve for piston cooling nozzles in three control positions.
In Figur 1 ist eine erste Variante 1 eines Regelventils für Kolbenkühldüsen dargestellt. Dabei zeigen die drei Darstellungen der Figur 1a, Figur 1 b und Figur 1c die drei möglichen Schaltstellungen dieses Regelventils. In einem Ventilgehäuse 3 ist ein stufenlos verschiebbarer Kolben 5 zwischen einem temperaturabhängig verstellbaren Aktor 7, beispielsweise einem Dehnstoffelement, und einer Schraubenfeder 9 eingespannt. In der Figur 1 a ist dabei die Stellung des Dehnstoffelementes 7 bei niedriger Öltempera- tur, also im Kaltstart, dargestellt. Das Ventilgehäuse 1 weist ferner eine Zulauföffnung 11 aus dem Schmierölkreislauf des Motors sowie zwei Ablauföffnungen 13 und 15 auf, wobei die beiden Ablauföffnungen 13 und 15 zu den Kolbenkühldüsen führen. Im hier dargestellten Kaltstart-Zustand ist der Ölzulauf 11 über eine Ringnut 17 des Ventilkolbens 5 mit dem Ablauf 13 verbunden, so dass im kalten Zustand Öl über dieses Regelventil den Kolbenkühldüsen zugeführt wird und dadurch nach dem Start des Motors eine Erwärmung des Schmieröls über die sich erwärmenden Kolben und das daran angespritzte Öl stattfindet. Der Ventilkolben 17, die Druckfeder 9 und der temperaturabhängig verstellbare Aktor 7 sind in einer Öffnung 19 des Ventilgehäuses 3 untergebracht und durch einen Abschlussstopfen 21 verschlossen, mit dem gegebenenfalls die Position des Ventilkolbens einjustiert werden kann. Die Kaltstartposition wird in diesem Falle für Öltemperaturen < = 40 Grad Celsius eingenommen.FIG. 1 shows a first variant 1 of a control valve for piston cooling nozzles. In this case, the three representations of Figure 1a, Figure 1 b and Figure 1c shows the three possible switching positions of this control valve. In a valve housing 3 is a continuously displaceable piston 5 between a temperature-dependent adjustable actuator 7, for example, an expansion element, and a coil spring 9 clamped. FIG. 1 a shows the position of the expansion element 7 at a low oil temperature, that is to say in a cold start. The valve housing 1 further has an inlet opening 11 from the lubricating oil circuit of the engine and two drain openings 13 and 15, wherein the two drain openings 13 and 15 lead to the piston cooling nozzles. In the cold start state illustrated here, the oil inlet 11 is connected via an annular groove 17 of the valve piston 5 to the drain 13 so that oil is supplied to the piston cooling nozzles in the cold state via this control valve and thereby after the start of the engine heating of the lubricating oil on the warming piston and the oil sprayed on it takes place. The valve piston 17, the compression spring 9 and the temperature-dependent adjustable actuator 7 are housed in an opening 19 of the valve housing 3 and closed by an end plug 21, with which, if appropriate, the position of the valve piston can be adjusted. The cold start position is taken in this case for oil temperatures <= 40 degrees Celsius.
Beim Überschreiten der 40 Grad Celsius-Öltemperaturschwelle, wobei eine Toleranz von + 5 Grad Celsius hinreichend ist für das Fahren des Ventilkolbens in eine andere Position, wird das temperaturabhängig verstellbare Dehnelement, wie in Figur 1 b gezeigt, durch Ausdehnung des Dehnstoffes, beispielsweise einer Wachsfüllung, innerhalb des Elementes einen entsprechenden Stempel 23 ausfahren und damit den Kolben 5 gegen die Feder 9 verfahren, so dass der Ventilkolben 5 jetzt sowohl den Ab- fluss 13 zu den Kolbenkühldüsen verschließt als auch noch den Abfluss 15 zu den Kolbenkühldüsen verschlossen hält. Durch entsprechende Überdeckung des Kolbens 5 und entsprechende Gestaltung der umlaufenden Nut 17 und der Abstände der Öffnungen 13 und 15 wird dieser geschlossene Zustand bei weiterem Ausfahren des Dehnstoffelementes 7 bis etwa 120 Grad Celsius Öltemperatur beibehalten.When exceeding the 40 degrees Celsius oil temperature threshold, with a tolerance of + 5 degrees Celsius is sufficient for driving the valve piston in a different position, the temperature-dependent adjustable expansion element, as shown in Figure 1 b, by expansion of the expansion material, such as a wax filling , Extend a corresponding punch 23 within the element and thus move the piston 5 against the spring 9, so that the valve piston 5 now both the outflow 13 to the piston cooling nozzles closes and still closed the drain 15 to the piston cooling nozzles. By appropriate overlap of the piston 5 and corresponding design of the circumferential groove 17 and the distances of the openings 13 and 15, this closed state is maintained at further extension of the expansion element 7 to about 120 degrees Celsius oil temperature.
Bei Überschreiten dieser Öltemperatur, also bei Eintreten des so genannten Heißlaufes, wird dann die Kolbenposition in Figur 1c erreicht. Der Stempel 23 des Dehnstoffelementes 7 ist nun so weit ausgefahren, dass die umlaufende Nut 17 des Regelkolbens 5 den Zufluss 11 mit dem zweiten Abfluss 15 zu den Kolbenkühldüsen verbindet, so dass jetzt das Schmieröl zur Kühlung der Kolben an deren Unterseite gespritzt werden kann. Dabei kann der Ablaufquerschnitt der Öffnung 15 wesentlich kleiner gestaltet werden als der Ablaufquerschnitt der Öffnung 13 für den Kaltstart, da jetzt das durch hohe Temperaturen viel dünnflüssigere Öl eine entschieden kleinere Öffnung benötigt, damit der gleiche Volumenstrom unter die Kolben gefördert werden kann.When this oil temperature is exceeded, ie when the so-called hot run occurs, the piston position in FIG. 1c is then reached. The punch 23 of the expansion element 7 is now extended so far that the circumferential groove 17 of the control piston 5 connects the inflow 11 with the second outflow 15 to the piston cooling nozzles, so that now the lubricating oil for cooling the piston can be injected at the bottom. In this case, the flow area of the opening 15 can be made substantially smaller than the flow area of the opening 13 for the cold start, since now the much higher viscosity by high temperatures oil requires a decidedly smaller opening so that the same volume flow can be promoted under the piston.
Durch den Einsatz dieses temperaturgesteuerten Wegeventils 1 kann also die gewünschte Funktion zur doppelten Verwendung der Kolbenkühldüsen beim Kaltstart und beim Heißlauf kostengünstig erzeugt werden, wobei das Ventil bei niedrigen Öl- temperaturen (< = 40 Grad Celsius) ein Abspritzen des Öls über die Kolbenkühldüsen zum Zwecke der Ölerwärmung zulässt, ohne hohe Öldrücke zu erzeugen, in einem Zwischenbereich (40 Grad Celsius bis 120 Grad Celsius) keinen Ölstrom zu den Kolbenkühldüsen zuführt und dann im Hochtemperaturbereich (> = 120 Grad Celsius) wieder den Durchlass zu den Kolbenkühldüsen öffnet. Dabei wird das Wegeventil 1 so eingesetzt, dass bei niedrigen Öltemperaturen eine Verbindung vom Schmierölversorgungsbereich zu den Kolbenkühldüsen erzeugt wird. Diese Verbindung wird mit möglichst großen Querschnitten generiert (Öffnungsquerschnitt für die Leitung 13), um einen großen Volumenstrom zu ermöglichen, der im kalten Zustand über die Kolbenkühldüsen abfließen kann. Bei steigenden Öltemperaturen verschließt der Aktor 7 diese Verbindung und öffnet sie dann erst wieder bei hohen Temperaturen (Heißlauf). Dies hat auch den Vorteil, dass eine mögliche Vordrosselung das Abfließen eines unzulässig hohen Volumenstromes verhindern kann.By using this temperature-controlled directional control valve 1 so the desired function for double use of the piston cooling nozzles during cold start and hot running can be produced inexpensively, the valve at low oil temperatures (<= 40 degrees Celsius), a spray of the oil through the piston cooling nozzles for the purpose oil heating allows, without producing high oil pressures, in an intermediate range (40 degrees Celsius to 120 degrees Celsius) no oil flow to the piston cooling nozzles supplies and then in the high temperature range (> = 120 degrees Celsius) again opens the passage to the piston cooling nozzles. In this case, the directional control valve 1 is used so that at low oil temperatures, a connection is generated from the lubricating oil supply area to the piston cooling nozzles. This connection is generated with the largest possible cross-sections (opening cross-section for the line 13) in order to allow a large volume flow, which can flow off in the cold state via the piston cooling nozzles. With increasing oil temperatures, the actuator 7 closes this connection and then opens it again only at high temperatures (hot run). This also has the advantage that a possible pre-throttling can prevent the outflow of an impermissibly high volume flow.
Da im Kaltstart der Verbrennungsmotor nur einen geringen Ölbedarf hat, bauen sich üblicherweise in diesem Betriebspunkt die höchsten Drücke auf. Durch eine geschickte Auslegung der Öffnungsquerschnitte und des Öffnungsdrucks der Kolbenkühldüsen kann der Druck im Ölkreislauf abgesenkt werden. Dies führt zusätzlich zu einer leichten Reduzierung der Pumpenleistung und damit der Antriebsleistung. Mit zunehmender Ölerwärmung fährt der Aktor 7 weiter aus und verschließt dann die Verbindung von der Zulaufleitung 11 zu den Kolbenkühldüsen. Die Genauigkeit für den Schaltpunkt ist mit ± 5 Grad Celsius ausreichend. Da das Schließen der Verbindung zu keinen dynamischen Druckspitzen führt und auch nicht absolut dicht sein muss, ist eine Ausführung des Ventils 1 als Schieberventil die richtige Wahl.Since the internal combustion engine only requires a small amount of oil during a cold start, the highest pressures usually build up at this operating point. By skillfully designing the opening cross sections and the opening pressure of the piston cooling nozzles, the pressure in the oil circuit can be lowered. This leads in addition to a slight reduction of the pump power and thus the drive power. With increasing oil heating, the actuator 7 moves on and then closes the connection from the supply line 11 to the piston cooling nozzles. The accuracy for the switching point is sufficient at ± 5 degrees Celsius. Since the closing of the connection leads to no dynamic pressure peaks and also does not have to be absolutely tight, a design of the valve 1 as a slide valve is the right choice.
Geöffnet wird die Verbindung erst wieder bei sehr hohen Temperaturen, wie in Figur 1 c dargestellt. In diesem Fall werden durch das weitere Ausfahren des Aktors 7 die Öffnungen 11 und 15 miteinander verbunden. Hierdurch wird der Heißlauf sehr gut gekühlt. Durch die Schaltfunktion bzw. Regelfunktion ist es möglich, den Öffnungsdruck zu reduzieren, da hier keine Druckbegrenzungsventile mit beispielsweise einem notwendigen Öffnungsdruck von 2 Bar eingesetzt werden müssen. Damit lässt sich insbesondere der kritische Heißlauf bei niedrigen Motordrehzahlen viel besser abdecken, da dann wirklich Öl durch die Kolbenkühldüsen gespritzt wird. Im Stand der Technik mit einem Öffnungsdruck der Druckbegrenzungsventile von beispielsweise mehr als 2 bar wird im Heißlauf wegen der hohen Leckagen Öl erst ab Motordrehzahlen von 4000 U/min durch die Kolbenkühldüsen fließen.The connection is only opened again at very high temperatures, as shown in FIG. 1 c. In this case, the openings 11 and 15 are connected to each other by the further extension of the actuator 7. As a result, the hot run is cooled very well. By switching function or control function, it is possible to reduce the opening pressure, since here no pressure relief valves with, for example, a necessary opening pressure of 2 bar must be used. Thus, in particular the critical hot run at low engine speeds much better cover, since then really oil is injected through the piston cooling nozzles. In the prior art with an opening pressure of the pressure relief valves of, for example, more than 2 bar, oil will flow through the piston cooling nozzles only at engine speeds of 4000 rpm in the hot run because of the high leakage.
Zur Reduzierung des Montageaufwandes, beispielsweise im Motormontageband, kann eine Regelventilvariante nach Figur 2 eingesetzt werden, bei welcher das Regelventil 28 in eine Cartridge-Hülse 30 integriert ist und nun nur noch als vormontierte, eingestellte und geprüfte Einheit in den Motorblock 32 eingesetzt werden muss. Zur Fixierung der Ventilbauteile im Cartridge 30 bieten sich verschiedene Lösungen an. Dargestellt ist eine Sicherung mittels eines Sicherungsringes 34, welcher eine schnelle Montage und gegebenenfalls Demontage der Ventileinzelteile ermöglicht. Zur Reduzierung des Herstellaufwandes für den Motorenhersteller wird hier in Figur 2 eine Lösung gezeigt, bei der nur zwei Bohrungen 36 und 38 benötigt werden, die im Winkel von 90 Grad im Motorblock 32 verlaufen. Der Zulauf des Schmieröls erfolgt durch die Bohrung 36, die Bohrung 38 ist mit den Kolbenkühldüsen verbunden. Durch zwei Bohrungen 40 und 42 im Kolben 44 und durch zwei Steueröffnungen 46 und 48 im Cart- ridge 30 kann nun wieder die Regelfunktion realisiert werden. Die Figuren 2a, 2b und 2c zeigen wieder die drei unterschiedlichen Positionen.To reduce the installation effort, for example in the motor assembly tape, a control valve variant of Figure 2 can be used in which the control valve 28 is integrated into a cartridge sleeve 30 and now only as a pre-assembled, set and tested unit in the engine block 32 must be used. Various solutions are available for fixing the valve components in the cartridge 30. Shown is a fuse by means of a retaining ring 34, which allows quick assembly and, if necessary, disassembly of the valve parts. To reduce the manufacturing effort for the engine manufacturer, a solution is shown here in Figure 2, in which only two holes 36 and 38 are needed, which extend at an angle of 90 degrees in the engine block 32. The feed of the lubricating oil through the bore 36, the bore 38 is connected to the piston cooling nozzles. Through two bores 40 and 42 in the piston 44 and through two control openings 46 and 48 in the carton. ridge 30, the control function can now be realized again. Figures 2a, 2b and 2c show again the three different positions.
In Figur 2a ist die Kaltstartposition dargestellt. Der temperaturabhängig verstellbare Aktor 50 ist eingefahren. Der Regelkolben 44 wird durch die Druckfeder 52, welche sich auf dem Sicherungsring 34 abstützt, gegen den Aktor 50 gedrückt. Die Zulaufleitung 36 ist über die Steueröffnung 46 des Cartridge 30, die radiale Bohrung 40 und über die axiale Bohrung 42 des Kolbens 44 mit dem Ablauf 38 zu den Kolbenkühldüsen verbunden, so dass jetzt im Kaltstart Schmieröl unter die Kolben zur Erwärmung gespritzt wird.In Figure 2a, the cold start position is shown. The temperature-dependent adjustable actuator 50 is retracted. The control piston 44 is pressed against the actuator 50 by the compression spring 52, which is supported on the securing ring 34. The supply line 36 is connected via the control port 46 of the cartridge 30, the radial bore 40 and the axial bore 42 of the piston 44 to the drain 38 to the piston cooling nozzles, so that now in the cold start lubricating oil is injected under the piston for heating.
In der Figur 2b ist bei mittleren Öltemperaturen der Aktor 50 um einen gewissen Bereich ausgefahren, hier an dem ausgefahrenen Stempel 54 zu erkennen, welcher sich in dieser Ventilvariante 28 gegen die Verschlussschraube 56 abstützt. Die radiale Querbohrung 40 des Kolbens ist in dieser Position weder mit der radialen Zuflussbohrung 46 der Hülse 30 noch mit der radialen Zuflussbohrung 48 der Hülse 30 verbunden, so dass über den Ablauf 38 kein Schmieröl zu den Kolbenkühldüsen strömen kann.In the figure 2b is at average oil temperatures, the actuator 50 extended by a certain range, here to recognize the extended punch 54, which is supported in this valve variant 28 against the screw plug 56. The radial transverse bore 40 of the piston is connected in this position neither with the radial inflow bore 46 of the sleeve 30 nor with the radial inflow bore 48 of the sleeve 30, so that via the drain 38 no lubricating oil can flow to the piston cooling nozzles.
In Figur 2c ist schließlich bei dieser Ventilvariante 28die Heißlaufposition erreicht. Der Aktor 50 hat den Stempel 54 ganz ausgefahren. Die radiale Querbohrung 40 des Kolbens 44 ist nun mit der radialen Heißlaufzuflussöffnung 48 der Hülse 30 verbunden, so dass der Schmierölzulauf 36 mit dem Ablauf 38 zu den Kolbenkühldüsen verbunden ist. Wie vorab schon erwähnt, kann der Öffnungsquerschnitt 48, also der Zulauf für den Heißlaufzustand des Verbrennungsmotors, im Querschnitt entschieden kleiner gestaltet werden als der Kaltlaufzulaufquerschnitt 46, was in diesem Bild allerdings nicht maßstäblich dargestellt ist.Finally, in FIG. 2c, in this valve variant 28, the hot-running position is reached. The actuator 50 has the punch 54 completely extended. The radial transverse bore 40 of the piston 44 is now connected to the radial hot-flow inlet opening 48 of the sleeve 30, so that the lubricating oil inlet 36 is connected to the drain 38 to the piston cooling nozzles. As already mentioned above, the opening cross-section 48, that is to say the inlet for the hot-running state of the internal combustion engine, can be decidedly smaller in cross section than the cold running inlet cross section 46, which, however, is not shown to scale in this picture.
Die Erfindung verwendet also das Prinzip, mit einem einzigen Regelventil, welches außerdem durch einen temperaturabhängigen Aktor gesteuert wird und nicht über eine Druckbegrenzungsfunktion, einen Ölvolumenstrom über der ansteigenden Tempe- ratur erst durchzulassen, danach abzuschalten und anschließend wieder durchzulassen. The invention thus uses the principle with a single control valve, which is also controlled by a temperature-dependent actuator and does not have a pressure limiting function, an oil volume flow above the rising Tempe- first pass, then switch off and then let it through again.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
I Regelventil für Kolbenkühldüsen (Variante 1) 3 VentilgehäuseI Control valve for piston cooling nozzles (Variant 1) 3 Valve body
5 Kolben5 pistons
7 temperaturabhängig verstellbarer Aktor7 temperature-dependent adjustable actuator
9 Schraubenfeder9 coil spring
I 1 ZulauföffnungI 1 inlet opening
13 Ablauföffnung Kaltstart13 Drain opening cold start
15 Ablauföffnung Heißlauf15 Drain opening of the hot runner
17 Ringnut des Ventilkolbens 517 annular groove of the valve piston 5
19 Öffnung des Ventilgehäuses 319 opening of the valve housing 3rd
21 Abschlussstopfen21 stopper
23 Stempel des Aktors 723 Stamp of the actuator 7
28 Regelventil für Kolbenkühldosen (Variante 2)28 Control valve for piston cooling cans (variant 2)
30 Cartridge-Hülse (Ventilhülse)30 Cartridge Sleeve (Valve Sleeve)
32 Motorblock32 engine block
34 Sicherungsring34 circlip
36 Bohrung im Motorblock36 hole in the engine block
38 Bohrung im Motorblock38 hole in the engine block
40 radiale Bohrung im Kolben 4440 radial bore in the piston 44th
42 axiale Bohrung im Kolben 4442 axial bore in the piston 44th
44 Ventilkolben44 valve piston
46 Steueröffnung für Kaltstart in der Cartridge-Hülse 3046 Control opening for cold start in the cartridge sleeve 30
48 Steueröffnung für Heißlauf in der Cartridge-Hülse 3048 control opening for hot run in the cartridge sleeve 30th
50 temperaturabhängig verstellbarer Aktor50 temperature-dependent adjustable actuator
52 Druckfeder52 compression spring
54 Stempel des Aktors 4054 punch of the actuator 40th
56 Verschlussschraube der Ventilvariante 28 56 Screw plug of valve variant 28

Claims

Patentansprüche claims
1. Ventil zur Regelung eines Ölstroms für Kolbenkühldüsen im Schmierölkreislauf eines Verbrennungsmotors, dadurch gekennzeichnet, dass das Ventil (1 , 28) bei niedrigen Temperaturen einen Öldurchfluss zu den Kolbenkühldüsen herstellt, bei mittleren Temperaturen einen Öldurchfluss zu den Kolbenkühldüsen unterbricht und bei hohen Öl- temperaturen wiederum einen Öldurchfluss zu den Kolbenkühldüsen herstellt.Valve for controlling an oil flow for piston cooling nozzles in the lubricating oil circuit of an internal combustion engine, characterized in that the valve (1, 28) at low temperatures produces an oil flow to the piston cooling nozzles, at medium temperatures an oil flow to the piston cooling nozzles interrupts and at high oil temperatures in turn produces an oil flow to the piston cooling nozzles.
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, dass das Ventil (1 , 28) temperaturabhängig den Ölstrom zu den Kolbenkühldüsen regelt.2. Valve according to claim 1, characterized in that the valve (1, 28) temperature-dependent controls the flow of oil to the piston cooling nozzles.
3. Ventil nach Anspruch 1 oder Anspruch 2, dadurch gekennzeichnet, dass das Ventil (1 , 28) durch einen temperaturabhängig verstellbaren Aktor (7, 50) gegen eine Rückstellfeder (9, 32) verstellbar ist.3. Valve according to claim 1 or claim 2, characterized in that the valve (1, 28) by a temperature-dependent adjustable actuator (7, 50) against a return spring (9, 32) is adjustable.
4. Ventil nach Anspruch 1 bis Anspruch 3, dadurch gekennzeichnet, dass ein einstellbarer Öffnungsquerschnitt (13, 46) für niedrige Öltemperaturen größer ist als der Öffnungsquerschnitt (15, 48) für hohe Öltemperaturen.4. Valve according to claim 1 to claim 3, characterized in that an adjustable opening cross-section (13, 46) for low oil temperatures is greater than the opening cross-section (15, 48) for high oil temperatures.
5. Ventil nach Anspruch 1 bis Anspruch 4, dadurch gekennzeichnet, dass das Ventil (1 , 28) eine Zulauföffnung (11) und zwei Ablauföffnungen (13, 15) aufweist oder zwei Zulauföffnungen (46, 48) und eine Ablauföffnung (42).5. Valve according to claim 1 to claim 4, characterized in that the valve (1, 28) has an inlet opening (11) and two drain openings (13, 15) or two inlet openings (46, 48) and a drain opening (42).
6. Ventil nach Anspruch 1 bis Anspruch 5, dadurch gekennzeichnet, dass das Ventil (1, 28) als Schieberventil (Wegeventil) ausgeführt ist.6. Valve according to claim 1 to claim 5, characterized in that the valve (1, 28) is designed as a slide valve (directional control valve).
7. Ventil nach Anspruch 6, dadurch gekennzeichnet, dass über der Temperatur der Schieberweg stufenlos verstellt wird.7. Valve according to claim 6, characterized in that above the temperature of the slide path is adjusted continuously.
8. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ventil in einer Cartridge-Hülse (30) integriert ist.8. Valve according to one of the preceding claims, characterized in that the valve is integrated in a cartridge sleeve (30).
9. Ventil nach Anspruch 8, dadurch gekennzeichnet, dass die einzelnen Ventilbauteile im Cartridge (30) durch einen Sicherungsring (34) fixiert sind. 9. Valve according to claim 8, characterized in that the individual valve components in the cartridge (30) by a securing ring (34) are fixed.
10. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der temperaturabhängig verstellbare Aktor (7, 50) als Dehnkörperelement oder als Bimetallelement ausgeführt ist.10. Valve according to one of the preceding claims, characterized in that the temperature-dependent adjustable actuator (7, 50) is designed as Dehnkörperelement or as a bimetallic element.
11. Ventil nach Anspruch 1 bis Anspruch 5 und Anspruch 8 bis Anspruch 10, dadurch gekennzeichnet, dass das Ventil statt als Schieberventil durch eine Kombination von Sitzventilen dargestellt ist. 11. Valve according to claim 1 to claim 5 and claim 8 to claim 10, characterized in that the valve is shown instead of a slide valve by a combination of seat valves.
EP06775712A 2005-09-16 2006-07-20 Valve for piston cooling nozzles Not-in-force EP1929130B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005044302 2005-09-16
PCT/DE2006/001255 WO2007031047A1 (en) 2005-09-16 2006-07-20 Valve for piston cooling nozzles

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EP1929130A1 true EP1929130A1 (en) 2008-06-11
EP1929130B1 EP1929130B1 (en) 2010-10-06

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AT (1) ATE483895T1 (en)
DE (2) DE502006008042D1 (en)
WO (1) WO2007031047A1 (en)

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DE102017223465A1 (en) * 2017-12-20 2019-06-27 Volkswagen Aktiengesellschaft piston cooling

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DE2546273C2 (en) * 1975-10-16 1984-11-22 Audi Nsu Auto Union Ag, 7107 Neckarsulm Device for regulating piston oil cooling for a piston internal combustion engine
JPS61244820A (en) * 1985-04-23 1986-10-31 Yanmar Diesel Engine Co Ltd Cooling device for piston
US5819692A (en) * 1997-05-01 1998-10-13 Schafer; Timothy Vernon Piston cooling oil control valve
DE10261180A1 (en) * 2002-12-20 2004-07-01 Daimlerchrysler Ag Temperature-controlled oil spray nozzle for piston cooling

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Publication number Priority date Publication date Assignee Title
DE102017002729A1 (en) 2016-03-29 2017-10-05 Scania Cv Ab System and method for controlling the cooling of an internal combustion engine

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DE502006008042D1 (en) 2010-11-18
WO2007031047A1 (en) 2007-03-22
EP1929130B1 (en) 2010-10-06
ATE483895T1 (en) 2010-10-15

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