EP3453855A1 - Method and device for cooling and/or lubrication of a piston and/or a path of travel of a cylinder in a reciprocating piston engine - Google Patents
Method and device for cooling and/or lubrication of a piston and/or a path of travel of a cylinder in a reciprocating piston engine Download PDFInfo
- Publication number
- EP3453855A1 EP3453855A1 EP18187887.7A EP18187887A EP3453855A1 EP 3453855 A1 EP3453855 A1 EP 3453855A1 EP 18187887 A EP18187887 A EP 18187887A EP 3453855 A1 EP3453855 A1 EP 3453855A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- lubricant
- internal combustion
- combustion engine
- stroke
- 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
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 37
- 238000000034 method Methods 0.000 title claims abstract description 23
- 238000005461 lubrication Methods 0.000 title description 3
- 239000000314 lubricant Substances 0.000 claims abstract description 87
- 238000002485 combustion reaction Methods 0.000 claims abstract description 42
- 230000001050 lubricating effect Effects 0.000 claims abstract description 7
- 230000001419 dependent effect Effects 0.000 claims description 9
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- 239000003921 oil Substances 0.000 description 84
- 239000007921 spray Substances 0.000 description 26
- 238000010586 diagram Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 8
- 230000008901 benefit Effects 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000009849 deactivation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006735 deficit Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000007704 transition Effects 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
- 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
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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
- 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
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
Definitions
- the invention relates to a method for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine.
- the invention further relates to a device for cooling and / or lubrication of a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine.
- the invention further relates to a motor vehicle, in particular a commercial vehicle, with such a device.
- a method for operating a reciprocating internal combustion engine having a piston cooling device in which a switching valve for controlling the amount of oil for cooling a piston by means of a device driven by a control unit and the oil flow by means of said device, for example an oil spray nozzle, operating point dependent is controlled.
- the switching valve is closed when a temporarily increased oil requirement is detected by the control unit at another point of the reciprocating internal combustion engine.
- FIG. 6 illustrates, by way of example, a device 1 known from the prior art for piston cooling.
- the internal combustion engine is shown reduced to features essential to the invention and has a piston 2, a connecting rod 3, a crankshaft 4, a nozzle device (oil spray nozzle) 5, a switching valve 6 and a control unit 7.
- the oil spray nozzle 5 is arranged in a crankcase, not shown, and injects oil from below to the underside of the piston 2 to cool it at high load.
- the oil is conveyed by a pump not shown in the main oil passage 8. From there, a subset is passed via a first line 9 to the crankshaft 4 in order to lubricate the bearing of the crankshaft and the connecting rod 3.
- a further subset of the oil pumped by the pump is conveyed via a second line 10 to the oil spray nozzle 5.
- the remaining amount of oil is conveyed through the extended main oil passage 8 in the direction of the cylinder head, not shown.
- the flow of oil through the second conduit 10 is controlled by a switching valve 6.
- the switching valve 6 in turn is controlled by a control unit 7, which calculates the opening time of the switching valve 6 with the input values of various operating parameters.
- the opening time of the switching valve is calculated in particular independently of the angle of rotation of the crankshaft.
- the invention has for its object to provide an improved method and an improved device of the type mentioned, by means of which an internal combustion engine, in particular as regards their cooling, low-consumption and environmentally friendly operation can be.
- a method for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, wherein the piston is supplied via a nozzle device lubricant, in particular injected, is.
- the nozzle device is also referred to as a piston cooling nozzle or piston nozzle.
- the lubricant can be oil.
- the lubricant is commonly referred to as oil, although today it is often no longer oil. Accordingly, the nozzle device is also referred to as an oil spray nozzle. All designs in this document that use oil as a highlighted lubricant example also apply to other lubricants.
- the nozzle device is preferably designed in a manner known per se, to inject lubricant to the underside of the piston, wherein the outlet opening of the nozzle device is arranged below the piston.
- the method is characterized in that during the Gartaktigen duty cycle of the reciprocating internal combustion engine, at least one interruption phase is provided, during which a supply of lubricant to the piston via the nozzle device is interrupted.
- the reciprocating internal combustion engine is a four-stroke reciprocating internal combustion engine with the four-stroke gas exchange or duty cycle suction - compression - burning - ejection.
- a supply of lubricant to the piston via the nozzle device of the reciprocating internal combustion engine is temporarily interrupted during the four-stroke gas exchange or duty cycle, for example by switching off and on of the lubricant flow to the oil spray nozzle.
- the reciprocating internal combustion engine can also be designed as a two-stroke reciprocating internal combustion engine.
- the interruption phase is thus shorter than the duration of the four-stroke gas change.
- a significant saving in lubricant consumption can be achieved.
- the lubricant pump can thus be designed smaller or with a lower ratio compared to known from the prior art lubricant pumps, which reduces the total fuel consumption of the vehicle.
- the interruption phase is only within a piston upward movement.
- the interruption phase may in particular begin and end during a piston upward movement.
- the supply of lubricant to the piston via the nozzle means or the injection of the piston with lubricant during the piston down movement is not interrupted, but interrupted during a piston upward movement or during a portion of the piston upward movement.
- the interruption of the lubricant supply during the piston upward movement is particularly advantageous because the adverse effects on the piston cooling due to the interrupted supply of lubricant are particularly low here. The reason is that the piston moves away from the oil spray nozzle during the piston upward movement and thus the impact velocity of the lubricant on the piston is lower than in the piston downward movement. Accordingly, the cooling performance of the impinging lubricant is reduced.
- the at least one interruption phase comprises a first interruption phase, that of the compression phase or part of the compression phase of the four-stroke cycle.
- the at least one interruption phase may comprise a second interruption phase corresponding to the ejection phase or a part of the ejection phase of the four-stroke cycle.
- the interruption phase may include that phase of piston up movement during which a piston speed exceeds a predetermined threshold and / or during which a rotational angle of the crankshaft is within a predetermined range selected such that the piston speed is above the threshold.
- This choice of the interruption phase is also particularly advantageous because the adverse effects on the piston cooling due to the interrupted supply of lubricant are also particularly low here.
- the speed of the piston continuously changes during the multi-stroke cycle. The piston speed is zero at both top dead center (TDC) and bottom dead center (TDC) and reaches a maximum in magnitude in a middle range between TDC and TDC.
- the interruption phase comprises angular positions of the crankshaft at which a relative speed (v_rel) between the lubricant and the piston falls below a predetermined threshold value.
- the interruption phase comprises rotational angular positions of the crankshaft, at which a relative speed between the lubricant and the piston is negative (v_rel ⁇ 0). This corresponds to rotational angles during the upward movement of the piston at which the piston speed is faster than the mean flow velocity of the injected lubricant, in particular at the point where the lubricant would hit or hit the piston underside. The piston thus "runs" away from the lubricant when v_rel ⁇ 0.
- the relative speed as a function of the rotational angular position of the crankshaft is defined as a difference between an average flow velocity of the lubricant at a distance from the nozzle device, which corresponds to the rotational angle-dependent distance of the piston to the nozzle device, and a Piston speed, which is dependent on the angle of rotation and depends on the push rod ratio.
- the aforesaid flow velocity corresponds to the mean flow velocity with which the injected lubricant would strike or hit the piston.
- the flow speed of the lubricant decreases as a result of beam widening effects with increasing distance from the outlet opening of the nozzle device.
- the mean flow velocity (v_ ⁇ l) with which the lubricant would hit or hit the underside of the piston or the oil inlet bore of the piston thus depends on the instantaneous distance of the piston underside from the outlet opening of the nozzle device, which is minimal in the UT and maximum in the OT is. Accordingly, the mean flow velocity (v_ ⁇ l) is highest in UT and lowest in TDC.
- the relative speed depending on the rotational angular position of the crankshaft is set as a difference of an average flow velocity of the lubricant at a distance from the nozzle device corresponding to the rotational angle-dependent distance of the piston to the nozzle device, and a rotational angle-dependent piston speed.
- the relative speed can be determined experimentally. For example, each rotational angular position of the piston is associated with a distance of the piston underside and the oil inlet bore of the piston from the outlet opening of the nozzle device. The average flow velocity of the injected lubricant for each rotational angular position or for each piston position can then z. B. be measured experimentally.
- both the instantaneous piston velocity and the flow rate at which the lubricant would strike or hit the underside of the piston or the oil inlet bore of the piston are dependent on the instantaneous rotational angular position of the crankshaft.
- the relative speed of lubricant and piston, v_rel v_ ⁇ l -v_Kolben, depending on the current Kolbenhub- and / or rotational angular position of the crankshaft.
- an electrically controllable solenoid valve is provided, by means of which the lubricant supply of the nozzle device during the Purtaktigen, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine temporarily deactivated, that is interruptible.
- a rotating rotary valve may be provided, by means of which the lubricant supply of the nozzle device during the multi-bar, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine is temporarily deactivated.
- an apparatus for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine comprises at least one piston guided in a cylinder of the reciprocating internal combustion engine, a nozzle device for supplying lubricant to the piston, and a control device which is designed to supply lubricant to the piston via the nozzle device during the multi-stroke, in particular four-stroke, cycle of the reciprocating internal combustion engine to interrupt during at least one interruption phase.
- the device and / or the control device may comprise an electrically controllable solenoid valve, by means of which the lubricant supply of the nozzle device is temporarily deactivated.
- This embodiment has the advantage that by the electrical control a freely programmable connection and disconnection of the lubricant supply in dependence on other operating parameters, such. As a load, speed, oil temperature, etc., in a simple manner can be realized.
- a fail-safe can be realized by a provision of the solenoid valve via the lubricant pressure.
- a coil of the solenoid valve may be arranged on the outside of a crankcase of the reciprocating internal combustion engine.
- the device and / or the control device may comprise a rotating rotary slide, by means of which the lubricant supply of the nozzle device during the Digitaktigen, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine is temporarily deactivated.
- the rotary valve can be arranged perpendicular to the crankshaft.
- This embodiment also has the advantage that by the electrical control of the rotating rotary valve, a freely programmable connection and disconnection of the lubricant supply in dependence on other operating parameters, such. As a load, speed, oil temperature, etc., in a simple manner can be realized.
- a fail-safe by a provision of the Solenoid valve be realized via the lubricant pressure.
- a rotation angle sensor for detecting the opening state of the rotary valve is provided.
- the electric motor for driving the rotary valve can be arranged on the outside of the crankcase.
- the rotary valve may be arranged parallel to the crankshaft.
- the drive of the rotary valve can be done electrically via an electric motor, in particular an electric motor for all cylinders, or mechanically by a gear drive of the internal combustion engine.
- the connection and disconnection of the rotary valve can be done analogously to the control of the camshaft, z. B. means of camshaft actuator or axial displacement, etc.
- a rotation angle sensor for detecting the opening state of the rotary valve is provided.
- the control device may include a control device for controlling the solenoid valve or the rotating rotary valve.
- the invention further relates to a motor vehicle, in particular a utility vehicle, comprising a device for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, as described in this document.
- FIG. 1 shows a diagram 15 for illustrating the dependence of the flow rate of the lubricant in dependence on the piston stroke of a commercial vehicle.
- FIG. 1 By way of example only, a reciprocating piston with a stroke of 170 mm is used, an oil nozzle with a diameter of the outlet opening of 3.1 mm, an oil pressure of 3.5 bar and a volume flow at an output speed of 9.5 l / min.
- the straight line 11 denotes the diameter of the oil inlet bore in the piston, which in the present example is 11 mm.
- the oil jet from oil spray nozzle 5 has an increasing distance of the beam diameter (beam expansion). This is in FIG. 1 illustrated by the curve 12.
- the oil spray nozzle has, for example, an outlet opening with a diameter of 3.1 mm.
- the simplifying assumption has been made that the distance of the oil spray nozzle 5 at UT to the piston is zero mm. Accordingly, the exiting lubricant jet at the outlet opening or at the UT has a diameter of 3.1 mm, which subsequently widens up to 11 mm at the TDC. If the piston is thus at UT, an oil jet with a diameter of 3.1 mm strikes the oil inlet bore of the piston. If the piston is at the TDC, an oil jet with a diameter of 11 mm strikes the oil inlet bore of the piston. If the piston is between UT and TDC, the curve 12 indicates the beam diameter.
- FIG. 2 shows a diagram 20 for illustrating the dependence of the relative velocity between the lubricant and the piston in dependence on the piston stroke.
- FIG. 2 also serves to illustrate a method of piston cooling according to an embodiment of the invention.
- the curve 21 of the upper diagram indicates the piston speed (v_volts) in m / s each angular position from 0 ° to 360 ° of the crankshaft, where 0 ° and 360 ° correspond to the TDC and 180 ° to the UT.
- the range from 0 ° to 180 ° thus corresponds to a downward piston movement with negative speed.
- the range of 180 ° to 360 ° thus corresponds to a piston upward movement with positive speed.
- the piston speed in each case has a maximum in a middle range between UT and TDC.
- the mean flow velocity of the injected oil (v_ ⁇ l) at the piston inlet, ie at the oil inlet bore on the piston, is represented by the curve 22.
- the flow rate is lowest due to the beam expansion effects at TDC (0 ° and 360 °) and greatest at BDC (180 °), as described above with reference to FIG. 1 was explained.
- the curve 23 indicates the relative speed (v_rel) between the lubricant and the piston (difference between lubricant speed 22 and piston speed 21). This is greatest during the piston down movement, since the piston 3 moves toward the oil spray nozzle 5 and thus towards the oil ejected by the latter, and during the piston upward movement the lowest since the piston 3 moves away from the oil spray nozzle 5.
- the oil speed in the example shown is lower than the piston speed. Consequently, in this range, the relative speed (v_rel) between the lubricant speed 22 and the piston speed 21 even becomes negative, which is indicated by the area 23a. It is emphasized that in other embodiments or motors in the range of the maximum piston speed, the oil speed must not be less than the piston speed, but also here the relative speed assumes its minimum value.
- the oil supply of the oil spray nozzle 5 can be deactivated in these time periods.
- the oil supply to the oil spray nozzle 5 may be activated during the four-stroke duty cycle during the piston down movement and deactivated during the piston up movement.
- the deactivation in the region 23a of the piston upward movement ie when the relative speed 23 is negative. This interruption phase is identified by the reference symbol P.
- the lubricant supply 25 to the piston underside is selectively activated or interrupted.
- the lubricant supply 25 is switched on.
- the lubricant supply 25 is interrupted.
- the invention is not limited to this embodiment.
- the lubricant supply may be interrupted during the complete upstroke of the piston.
- the region P may also include positive relative velocity regions.
- the crankshaft of the sum oil consumption of the oil spray nozzles by the same number of up and down movements is constant. Despite switching off the oil supply to the individual oil spray nozzles on the upstroke, the pressure pulsations in this embodiment are therefore low.
- FIG. 3 shows a schematic representation of a device 30 according to an embodiment of the invention.
- FIG. 3 again shows a connecting rod 3, at the end of which the piston is no longer shown.
- the internal combustion engine is shown reduced to features essential to the invention.
- Lubricant oil
- Oil spray nozzle 5 is released during the downward stroke of the piston and is interrupted during the upstroke (or in a portion of the upstroke) of the piston.
- the stroke of the solenoid valve is about 6 mm.
- the control can be superimposed by a known per se control of the oil spray nozzle, wherein the oil spray nozzle on the input side of the control unit by signal lines 34 is controlled on the basis of further operating parameters, such as load, speed, oil temperature, etc., is controlled.
- FIG. 4 shows a schematic representation of a device 40 for piston cooling according to another embodiment of the invention.
- the peculiarity of this embodiment is that instead of a solenoid valve, a rotating rotary valve 41 is used to enable and interrupt the supply of lubricant to the piston.
- the use of rotating rotary valves offers the advantage that higher switching frequencies and a lower noise level are possible.
- the rotating rotary valve 41 according to FIG. 4 is arranged perpendicular to the crankshaft.
- a rotation angle sensor is provided (not shown).
- the drive of the rotating rotary valve 41 via an electric motor 42 which is arranged externally on the crankcase. Again, an electrical control of the connection and disconnection of the lubricant supply by driving the electric motor in response to the upward movement or downward movement of the piston and in dependence on other operating parameters is possible.
- FIG. 5 shows a schematic representation of a device 50 for piston cooling according to another embodiment of the invention.
- the peculiarity of this embodiment is that the rotary valve 51 is now arranged parallel to the crankshaft axis.
- the drive of the rotary valve can be provided via an electric motor for all cylinders or alternatively via a gear drive of the internal combustion engine.
- the connection and disconnection is analogous to the mechanical control of the camshaft, for example via a camshaft actuator.
- the reference numeral 52 designates a lenticular opening which can be released or closed by the rotary rotary valve and which is connected to the oil supply via the upper channel.
- Reference numeral 53 denotes the rotational movement of the rotary rotary valve 51.
Abstract
Die Erfindung betrifft ein Verfahren und eine Vorrichtung zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine, wobei dem Kolben über eine Düseneinrichtung Schmiermittel zugeführt, insbesondere zugespritzt, wird. Die Erfindung betrifft ferner ein Kraftfahrzeug, insbesondere ein Nutzfahrzeug, mit einer derartigen Vorrichtung. Erfindungsgemäß ist während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine mindestens eine Unterbrechungsphase (P) vorgesehen, während derer eine Zufuhr von Schmiermittel zum Kolben über die Düseneinrichtung (5) unterbrochen ist. The invention relates to a method and a device for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, wherein the piston is supplied via a nozzle device lubricant, in particular injected, is. The invention further relates to a motor vehicle, in particular a commercial vehicle, with such a device. According to the invention, at least one interruption phase (P) is provided during the multi-stroke, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine, during which a supply of lubricant to the piston via the nozzle device (5) is interrupted.
Description
Die Erfindung betrifft ein Verfahren zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine. Die Erfindung betrifft ferner eine Vorrichtung zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine. Die Erfindung betrifft ferner ein Kraftfahrzeug, insbesondere ein Nutzfahrzeug, mit einer derartigen Vorrichtung.The invention relates to a method for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine. The invention further relates to a device for cooling and / or lubrication of a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine. The invention further relates to a motor vehicle, in particular a commercial vehicle, with such a device.
Aus der
Aus der
Aus der
Der Erfindung liegt die Aufgabe zugrunde, ein verbessertes Verfahren und eine verbesserte Vorrichtung der eingangs genannten Art bereitzustellen, mittels deren eine Brennkraftmaschine, insbesondere was deren Kühlung betrifft, verbrauchsärmer und umweltschonender betrieben werden kann.The invention has for its object to provide an improved method and an improved device of the type mentioned, by means of which an internal combustion engine, in particular as regards their cooling, low-consumption and environmentally friendly operation can be.
Diese Aufgaben werden durch Vorrichtungen und Verfahren mit den Merkmalen der unabhängigen Ansprüche gelöst. Vorteilhafte Ausführungsformen und Anwendungen der Erfindung ergeben sich aus den abhängigen Ansprüchen und werden in der folgenden Beschreibung unter teilweiser Bezugnahme auf die Figuren näher erläutert.These objects are achieved by devices and methods having the features of the independent claims. Advantageous embodiments and applications of the invention will become apparent from the dependent claims and are explained in more detail in the following description with partial reference to the figures.
Gemäß einem ersten allgemeinen Gesichtspunkt der Erfindung wird ein Verfahren zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine bereitgestellt, wobei dem Kolben über eine Düseneinrichtung Schmiermittel zugeführt, insbesondere zugespritzt, wird.According to a first general aspect of the invention, a method is provided for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, wherein the piston is supplied via a nozzle device lubricant, in particular injected, is.
Die Düseneinrichtung wird auch als Kolbenkühldüse oder Kolbenspritzdüse bezeichnet. Das Schmiermittel kann Öl sein. Das Schmiermittel wird üblicherweise auch als Öl bezeichnet, auch wenn dies heute häufig kein Öl mehr ist. Entsprechend wird die Düseneinrichtung auch als Ölspritzdüse bezeichnet. Alle Ausführungen in diesem Dokument, bei dem Öl als hervorgehobenes Schmiermittelbeispiel verwendet wird, gelten auch für andere Schmiermittel. Hierbei ist die Düseneinrichtung vorzugsweise in an sich bekannter Weise ausgebildet, Schmiermittel an die Unterseite des Kolbens zu spritzen, wobei die Austrittsöffnung der Düseneinrichtung unterhalb des Kolbens angeordnet ist.The nozzle device is also referred to as a piston cooling nozzle or piston nozzle. The lubricant can be oil. The lubricant is commonly referred to as oil, although today it is often no longer oil. Accordingly, the nozzle device is also referred to as an oil spray nozzle. All designs in this document that use oil as a highlighted lubricant example also apply to other lubricants. In this case, the nozzle device is preferably designed in a manner known per se, to inject lubricant to the underside of the piston, wherein the outlet opening of the nozzle device is arranged below the piston.
Erfindungsgemäß zeichnet sich das Verfahren dadurch aus, dass während des mehrtaktigen Arbeitszyklus der Hubkolbenbrennkraftmaschine mindestens eine Unterbrechungsphase vorgesehen ist, während derer eine Zufuhr von Schmiermittel zum Kolben über die Düseneinrichtung unterbrochen ist. Vorzugsweise ist die Hubkolbenbrennkraftmaschine eine Viertakt-Hubkolbenbrennkraftmaschine mit dem viertaktigen Gaswechsel bzw. Arbeitszyklus Ansaugen - Verdichten - Verbrennen - Ausstoßen. Mit anderen Worten wird im Falle eines Viertakt-Hubkolbenmotors eine Zufuhr von Schmiermittel zum Kolben über die Düseneinrichtung der Hubkolbenbrennkraftmaschine während des viertaktigen Gaswechsels bzw. Arbeitszyklus zeitweise unterbrochen, beispielsweise durch Ab- und Zuschalten des Schmiermittelstroms an der Ölspritzdüse. Prinzipiell kann die Hubkolbenbrennkraftmaschine auch als Zweitakt-Hubkolbenbrennkraftmaschine ausgeführt sein.According to the invention, the method is characterized in that during the mehrtaktigen duty cycle of the reciprocating internal combustion engine, at least one interruption phase is provided, during which a supply of lubricant to the piston via the nozzle device is interrupted. Preferably, the reciprocating internal combustion engine is a four-stroke reciprocating internal combustion engine with the four-stroke gas exchange or duty cycle suction - compression - burning - ejection. In other words, in the case of a four-stroke reciprocating engine, a supply of lubricant to the piston via the nozzle device of the reciprocating internal combustion engine is temporarily interrupted during the four-stroke gas exchange or duty cycle, for example by switching off and on of the lubricant flow to the oil spray nozzle. In principle, the reciprocating internal combustion engine can also be designed as a two-stroke reciprocating internal combustion engine.
Die Unterbrechungsphase ist somit kürzer als die Dauer des viertaktigen Gaswechsels. Hierdurch kann eine signifikante Einsparung des Schmiermittelverbrauchs erzielt werden. Entsprechend ist die erforderliche Antriebsleistung für die Schmiermittelpumpe zur Versorgung der Düseneinrichtung mit Schmiermittel reduziert. Die Schmiermittelpumpe kann somit im Vergleich zu aus dem Stand der Technik bekannten Schmiermittelpumpen kleiner bzw. mit geringerer Übersetzung ausgelegt werden, was den Gesamtkraftstoffverbrauch des Fahrzeugs verringert.The interruption phase is thus shorter than the duration of the four-stroke gas change. As a result, a significant saving in lubricant consumption can be achieved. Accordingly, the required drive power for the lubricant pump for supplying the nozzle device is reduced with lubricant. The lubricant pump can thus be designed smaller or with a lower ratio compared to known from the prior art lubricant pumps, which reduces the total fuel consumption of the vehicle.
Gemäß einer besonders bevorzugten Ausführungsform liegt die Unterbrechungsphase nur innerhalb einer Kolbenaufwärtsbewegung. Die Unterbrechungsphase kann insbesondere während einer Kolbenaufwärtsbewegung beginnen und enden. Gemäß dieser Ausführungsform ist die Zufuhr von Schmiermittel zum Kolben über die Düseneinrichtung bzw. das Anspritzen des Kolbens mit Schmiermittel während der Kolbenabwärtsbewegung nicht unterbrochen, jedoch unterbrochen während einer Kolbenaufwärtsbewegung oder während einer Teildauer der Kolbenaufwärtsbewegung. Die Unterbrechung der Schmiermittelzufuhr während der Kolbenaufwärtsbewegung ist besonders vorteilhaft, da hier die nachteiligen Effekte auf die Kolbenkühlung aufgrund der unterbrochenen Schmiermittelzufuhr besonders gering sind. Der Grund ist, dass sich der Kolben bei der Kolbenaufwärtsbewegung von der Ölspritzdüse wegbewegt und somit die Auftreffgeschwindigkeit des Schmiermittels auf den Kolben geringer ist als bei der Kolbenabwärtsbewegung. Entsprechend ist die Kühlleistung des auftreffenden Schmiermittels verringert.According to a particularly preferred embodiment, the interruption phase is only within a piston upward movement. The interruption phase may in particular begin and end during a piston upward movement. According to this embodiment, the supply of lubricant to the piston via the nozzle means or the injection of the piston with lubricant during the piston down movement is not interrupted, but interrupted during a piston upward movement or during a portion of the piston upward movement. The interruption of the lubricant supply during the piston upward movement is particularly advantageous because the adverse effects on the piston cooling due to the interrupted supply of lubricant are particularly low here. The reason is that the piston moves away from the oil spray nozzle during the piston upward movement and thus the impact velocity of the lubricant on the piston is lower than in the piston downward movement. Accordingly, the cooling performance of the impinging lubricant is reduced.
Eine besonders vorteilhafte Variante der Ausführungsform sieht vor, dass die mindestens eine Unterbrechungsphase eine erste Unterbrechungsphase umfasst, die der Verdichtungsphase oder einem Teil der Verdichtungsphase des viertaktigen Arbeitszyklus entspricht. Alternativ oder vorzugsweise zusätzlich kann die mindestens eine Unterbrechungsphase eine zweite Unterbrechungsphase umfassen, die der Ausstoßphase oder einem Teil der Ausstoßphase des viertaktigen Arbeitszyklus entspricht.A particularly advantageous variant of the embodiment provides that the at least one interruption phase comprises a first interruption phase, that of the compression phase or part of the compression phase of the four-stroke cycle. Alternatively or preferably additionally, the at least one interruption phase may comprise a second interruption phase corresponding to the ejection phase or a part of the ejection phase of the four-stroke cycle.
Gemäß einem weiteren Aspekt kann die Unterbrechungsphase diejenige Phase der Kolbenaufwärtsbewegung umfassen, während derer eine Kolbengeschwindigkeit einen vorbestimmten Schwellenwert überschreitet und/oder während derer ein Drehwinkel der Kurbelwelle in einem vorbestimmten Bereich liegt, der so gewählt ist, dass die Kolbengeschwindigkeit über dem Schwellenwert liegt. Diese Wahl der Unterbrechungsphase ist ebenfalls besonders vorteilhaft, da hier die nachteiligen Effekte auf die Kolbenkühlung aufgrund der unterbrochenen Schmiermittelzufuhr ebenfalls besonders gering sind. Hierbei ist zu beachten, dass sich die Geschwindigkeit des Kolbens während des mehrtaktigen Arbeitszyklus fortlaufend ändert. Die Kolbengeschwindigkeit beträgt null sowohl im oberen Totpunkt (OT) als auch im unteren Totpunkt (UT) und erreicht betragsmäßig ein Maximum in einem mittleren Bereich zwischen dem OT und dem UT.In another aspect, the interruption phase may include that phase of piston up movement during which a piston speed exceeds a predetermined threshold and / or during which a rotational angle of the crankshaft is within a predetermined range selected such that the piston speed is above the threshold. This choice of the interruption phase is also particularly advantageous because the adverse effects on the piston cooling due to the interrupted supply of lubricant are also particularly low here. It should be noted that the speed of the piston continuously changes during the multi-stroke cycle. The piston speed is zero at both top dead center (TDC) and bottom dead center (TDC) and reaches a maximum in magnitude in a middle range between TDC and TDC.
Gemäß einem weiteren Aspekt der Erfindung ist es besonders vorteilhaft, die Festlegung der Unterbrechungsphase während der Aufwärtsbewegung des Kolbens ferner in Abhängigkeit von der Relativgeschwindigkeit zwischen Schmiermittel und Kolben vorzunehmen.According to a further aspect of the invention, it is particularly advantageous to further define the interruption phase during the upward movement of the piston as a function of the relative speed between the lubricant and the piston.
So ist gemäß einer weiteren Ausführungsform besonders vorteilhaft, falls die Unterbrechungsphase Drehwinkelpositionen der Kurbelwelle umfasst, an denen eine Relativgeschwindigkeit (v_rel) zwischen dem Schmiermittel und dem Kolben einen vorbestimmten Schwellenwert unterschreitet. Gemäß einer besonders vorteilhaften Variante umfasst die Unterbrechungsphase Drehwinkelpositionen der Kurbelwelle, an denen eine Relativgeschwindigkeit zwischen dem Schmiermittel und dem Kolben negativ ist (v_rel < 0). Dies entspricht Drehwinkeln während der Aufwärtsbewegung des Kolbens, an denen die Kolbengeschwindigkeit schneller ist als die mittlere Strömungsgeschwindigkeit des eingespritzten Schmiermittels, insbesondere an der Stelle, an der das Schmiermittel auf die Kolbenunterseite trifft oder treffen würde. Der Kolben "läuft" somit dem Schmiermittel "weg", wenn v_rel < 0. Es wird betont, dass auch bei positiven Relativgeschwindigkeiten eine Unterbrechungsphase vorgesehen sein kann. Bei einer vorteilhaften Variante dieser Ausgestaltungsform ist die Relativgeschwindigkeit in Abhängigkeit von der Drehwinkelposition der Kurbelwelle festgelegt als eine Differenz einer mittleren Strömungsgeschwindigkeit des Schmiermittels in einem Abstand von der Düseneinrichtung, der dem drehwinkelabhängigen Abstand des Kolbens zur Düseneinrichtung entspricht, und einer Kolbengeschwindigkeit, die drehwinkelabhängig ist und vom Schubstangenverhältnis abhängig ist. Die vorgenannte Strömungsgeschwindigkeit entspricht insbesondere der mittleren Strömungsgeschwindigkeit, mit der das eingespritzte Schmiermittel auf den Kolben trifft oder treffen würde.Thus, according to a further embodiment, it is particularly advantageous if the interruption phase comprises angular positions of the crankshaft at which a relative speed (v_rel) between the lubricant and the piston falls below a predetermined threshold value. According to a particularly advantageous variant, the interruption phase comprises rotational angular positions of the crankshaft, at which a relative speed between the lubricant and the piston is negative (v_rel <0). This corresponds to rotational angles during the upward movement of the piston at which the piston speed is faster than the mean flow velocity of the injected lubricant, in particular at the point where the lubricant would hit or hit the piston underside. The piston thus "runs" away from the lubricant when v_rel <0. It is emphasized that even at positive relative speeds an interruption phase can be provided. In an advantageous variant of this embodiment, the relative speed as a function of the rotational angular position of the crankshaft is defined as a difference between an average flow velocity of the lubricant at a distance from the nozzle device, which corresponds to the rotational angle-dependent distance of the piston to the nozzle device, and a Piston speed, which is dependent on the angle of rotation and depends on the push rod ratio. In particular, the aforesaid flow velocity corresponds to the mean flow velocity with which the injected lubricant would strike or hit the piston.
Diesem Aspekt liegt die technische Erkenntnis zugrunde, dass der Kühleffekt des auf den Kolben treffenden Schmiermittels maßgeblich von der Relativgeschwindigkeit von eingespritztem Schmiermittel und Kolben abhängt. Hierbei ist, wie vorstehend bereits erwähnt, einerseits zu berücksichtigen, dass sich die Geschwindigkeit des Kolbens während des mehrtaktigen Arbeitszyklus fortlaufend ändert. Die Geschwindigkeit beträgt null sowohl im oberen Totpunkt (OT) als auch im unteren Totpunkt (UT) und erreicht betragsmäßig ein Maximum in einem mittleren Bereich zwischen dem OT und dem UT. Wenn die Kolbenunterseite mit Schmiermittel von der Düseneinrichtung angespritzt wird, bewegt sich der Kolben bei der Abwärtsbewegung (Ansaugtakt oder Arbeitstakt) auf das entgegenkommende Schmiermittel zu, das von unten an die Kolbenunterseite gespritzt wird, d. h., die Strömungsgeschwindigkeit des Schmiermittels (v_Öl) und die Geschwindigkeiten des Kolbens (v_Kolben) haben unterschiedliche Vorzeichen.This aspect is based on the technical knowledge that the cooling effect of the lubricant striking the piston depends significantly on the relative speed of injected lubricant and piston. Here, as already mentioned above, on the one hand to take into account that the speed of the piston changes continuously during the multi-stroke cycle. The speed is zero at both top dead center (TDC) and bottom dead center (TDC) and reaches a maximum in terms of magnitude in a middle range between the TDC and TDC. When the piston bottom is sprayed with lubricant from the nozzle means, the piston moves in the downward movement (intake stroke or power stroke) to the oncoming lubricant, which is injected from below to the piston bottom, d. h., The flow rate of the lubricant (v_Öl) and the speeds of the piston (v_Kolben) have different signs.
Daher addieren sich bei der Abwärtsbewegung des Kolbens die Strömungsgeschwindigkeit des Schmiermittels (v_Öl) und die Geschwindigkeiten des Kolben (v_Kolben) betragsmäßig zur Ermittlung der Relativgeschwindigkeit, v_rel = v_Öl - v_Kolben = |v_Öl |+ |v_Kolben|. Bei der Aufwärtsbewegung des Kolbens werden die Strömungsgeschwindigkeit des Schmiermittels (v_Öl) und die Kolbengeschwindigkeit (v_Kolben) zur Ermittlung der Relativgeschwindigkeit v_rel= v_Öl- v_Kolben = |v_Öl | - |v_Kolben| betragsmäßig voneinander abgezogen. Es kann zu einer negativen Relativgeschwindigkeit kommen, d. h., der Kolben ist schneller als das Schmiermittel. In diesen Situationen ist der Kühleffekt besonders gering, da der Kolben dem eingespritzten Schmiermittel quasi "wegläuft". Insbesondere gilt, dass je kleiner die Relativgeschwindigkeit (v_rel), desto kleiner der Kühleffekt.Therefore, in the downward movement of the piston, the flow speed of the lubricant (v_Öl) and the speeds of the piston (v_Kolben) amount to the relative velocity, v_rel = v_Öl - v_Kolben = | v_Öl | + | v_Kolben |. During the upward movement of the piston, the flow speed of the lubricant (v_Öl) and the piston speed (v_Kolben) for determining the relative velocity v_rel = v_Öl- v_Kolben = | v_Öl | - | v_Kolben | subtracted from each other in amount. It can come to a negative relative speed, d. h., the piston is faster than the lubricant. In these situations, the cooling effect is particularly low because the piston virtually "runs away" from the injected lubricant. In particular, the smaller the relative velocity (v_rel), the smaller the cooling effect.
Bei der Ermittlung der Relativgeschwindigkeit ist ferner zu beachten, dass die Strömungsgeschwindigkeit des Schmiermittels durch Strahlaufweitungseffekte mit zunehmenden Abstand von der Austrittsöffnung der Düseneinrichtung abnimmt. Die mittlere Strömungsgeschwindigkeit (v_Öl), mit der das Schmiermittel auf die Unterseite des Kolbens bzw. auf die Ölzulaufbohrung des Kolbens trifft oder treffen würde, hängt somit vom momentanen Abstand der Kolbenunterseite von der Austrittsöffnung der Düseneinrichtung ab, der minimal im UT ist und maximal im OT ist. Entsprechend ist die mittlere Strömungsgeschwindigkeit (v_Öl) im UT am größten und im OT am geringsten.When determining the relative speed, it should also be noted that the flow speed of the lubricant decreases as a result of beam widening effects with increasing distance from the outlet opening of the nozzle device. The mean flow velocity (v_Öl), with which the lubricant would hit or hit the underside of the piston or the oil inlet bore of the piston thus depends on the instantaneous distance of the piston underside from the outlet opening of the nozzle device, which is minimal in the UT and maximum in the OT is. Accordingly, the mean flow velocity (v_Öl) is highest in UT and lowest in TDC.
Daher ist bei der vorstehend genannten vorteilhaften Variante die Relativgeschwindigkeit in Abhängigkeit von der Drehwinkelposition der Kurbelwelle festgelegt als eine Differenz einer mittleren Strömungsgeschwindigkeit des Schmiermittels in einem Abstand von der Düseneinrichtung, der dem drehwinkelabhängigen Abstand des Kolbens zur Düseneinrichtung entspricht, und einer drehwinkelabhängigen Kolbengeschwindigkeit.Therefore, in the aforementioned advantageous variant, the relative speed depending on the rotational angular position of the crankshaft is set as a difference of an average flow velocity of the lubricant at a distance from the nozzle device corresponding to the rotational angle-dependent distance of the piston to the nozzle device, and a rotational angle-dependent piston speed.
Die Relativgeschwindigkeit kann experimentell bestimmt werden. Beispielsweise ist jeder Drehwinkelposition des Kolbens ein Abstand der Kolbenunterseite bzw. der Ölzulaufbohrung des Kolbens von der Austrittsöffnung der Düseneinrichtung zugeordnet. Die mittlere Strömungsgeschwindigkeit des eingespritzten Schmiermittels für jede Drehwinkelposition bzw. für jede Kolbenposition kann dann z. B. experimentell gemessen werden. Zusammengefasst sind somit sowohl die momentane Kolbengeschwindigkeit als auch die Strömungsgeschwindigkeit, mit der das Schmiermittels auf die Unterseite des Kolbens bzw. auf die Ölzulaufbohrung des Kolbens trifft oder treffen würde, abhängig von der momentanen Drehwinkelposition der Kurbelwelle. Entsprechend ist die Relativgeschwindigkeit von Schmiermittel und Kolben, v_rel = v_Öl -v_Kolben, abhängig von der momentanen Kolbenhub- und/oder Drehwinkelposition der Kurbelwelle.The relative speed can be determined experimentally. For example, each rotational angular position of the piston is associated with a distance of the piston underside and the oil inlet bore of the piston from the outlet opening of the nozzle device. The average flow velocity of the injected lubricant for each rotational angular position or for each piston position can then z. B. be measured experimentally. Thus, in summary, both the instantaneous piston velocity and the flow rate at which the lubricant would strike or hit the underside of the piston or the oil inlet bore of the piston are dependent on the instantaneous rotational angular position of the crankshaft. Accordingly, the relative speed of lubricant and piston, v_rel = v_Öl -v_Kolben, depending on the current Kolbenhub- and / or rotational angular position of the crankshaft.
Wenn somit in Betriebsphasen, in denen die Relativgeschwindigkeit klein ist, z. B. einen vorbestimmten Schwellenwert unterschreitet, die Schmiermittelversorgung temporär unterbrochen wird, ist die Beeinträchtigung der Kolbenkühlung gering. Gleichzeitig kann der Schmiermittelverbrauch jedoch signifikant gesenkt werden, verbunden mit der Möglichkeit, die Schmiermittelpumpe kleiner auszulegen und dadurch den Kraftstoffverbrauch zu senken. Bei mehrzylindrigen Motoren mit zueinander phasenverschobenen Taktzeitpunkten wird der Summenölverbrauch nur sehr wenig bedingt durch Rückkopplungseffekte pulsieren.Thus, if in operating phases in which the relative speed is small, z. B. falls below a predetermined threshold, the lubricant supply is temporarily interrupted, the impairment of the piston cooling is low. At the same time, however, the lubricant consumption can be significantly reduced, combined with the ability to make the lubricant pump smaller and thereby reduce fuel consumption. In multi-cylinder engines with mutually phase-shifted clock times, the total oil consumption will pulsate only very little due to feedback effects.
Gemäß einem weiteren Aspekt der Erfindung ist ein elektrisch ansteuerbares Magnetventil vorgesehen, mittels dessen die Schmiermittelversorgung der Düseneinrichtung während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine zeitweise deaktivierbar, d. h. unterbrechbar ist.According to another aspect of the invention, an electrically controllable solenoid valve is provided, by means of which the lubricant supply of the nozzle device during the mehrtaktigen, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine temporarily deactivated, that is interruptible.
Gemäß einer alternativen Ausführungsform kann ein rotierender Drehschieber vorgesehen sein, mittels dessen die Schmiermittelversorgung der Düseneinrichtung während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine zeitweise deaktivierbar ist.According to an alternative embodiment, a rotating rotary valve may be provided, by means of which the lubricant supply of the nozzle device during the multi-bar, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine is temporarily deactivated.
Gemäß einem zweiten allgemeinen Gesichtspunkt der Erfindung wird eine Vorrichtung zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine bereitgestellt. Die Vorrichtung umfasst mindestens einen in einem Zylinder der Hubkolbenbrennkraftmaschine geführten Kolben, eine Düseneinrichtung zur Zuführung von Schmiermittel zu dem Kolben und eine Steuereinrichtung, die ausgebildet ist, während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine eine Zufuhr von Schmiermittel zum Kolben über die Düseneinrichtung während mindestens einer Unterbrechungsphase zu unterbrechen.According to a second general aspect of the invention, there is provided an apparatus for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine. The device comprises at least one piston guided in a cylinder of the reciprocating internal combustion engine, a nozzle device for supplying lubricant to the piston, and a control device which is designed to supply lubricant to the piston via the nozzle device during the multi-stroke, in particular four-stroke, cycle of the reciprocating internal combustion engine to interrupt during at least one interruption phase.
Die Vorrichtung und/oder die Steuereinrichtung kann ein elektrisch ansteuerbares Magnetventil umfassen, mittels dessen die Schmiermittelversorgung der Düseneinrichtung zeitweise deaktivierbar ist. Diese Ausführungsform bietet den Vorzug, dass durch die elektrische Ansteuerung eine frei programmierbare Zu- und Abschaltung der Schmiermittelversorgung in Abhängigkeit von weiteren Betriebsparametern, wie z. B. einer Last, Drehzahl, Öltemperatur etc., auf einfache Weise realisierbar ist. Ferner kann optional eine Ausfallsicherung (engl. fail safe) durch eine Rückstellung des Magnetventils über den Schmiermitteldruck realisiert sein.The device and / or the control device may comprise an electrically controllable solenoid valve, by means of which the lubricant supply of the nozzle device is temporarily deactivated. This embodiment has the advantage that by the electrical control a freely programmable connection and disconnection of the lubricant supply in dependence on other operating parameters, such. As a load, speed, oil temperature, etc., in a simple manner can be realized. Furthermore, optionally a fail-safe (fail safe) can be realized by a provision of the solenoid valve via the lubricant pressure.
Gemäß einer vorteilhaften Variante dieser Ausführungsform kann eine Spule des Magnetventils außen an einem Kurbelgehäuse der Hubkolbenbrennkraftmaschine angeordnet sein.According to an advantageous variant of this embodiment, a coil of the solenoid valve may be arranged on the outside of a crankcase of the reciprocating internal combustion engine.
Gemäß einer weiteren Ausführungsform kann die Vorrichtung und/oder die Steuereinrichtung einen rotierenden Drehschieber umfassen, mittels dessen die Schmiermittelversorgung der Düseneinrichtung während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine zeitweise deaktivierbar ist. Der Drehschieber kann senkrecht zur Kurbelwelle angeordnet sein. Diese Ausführungsform bietet ebenfalls den Vorzug, dass durch die elektrische Ansteuerung des rotierenden Drehschiebers eine frei programmierbare Zu- und Abschaltung der Schmiermittelversorgung in Abhängigkeit von weiteren Betriebsparametern, wie z. B. einer Last, Drehzahl, Öltemperatur etc., auf einfache Weise realisierbar ist. Ferner kann optional eine Ausfallsicherung (engl. fail safe) durch eine Rückstellung des Magnetventils über den Schmiermitteldruck realisiert sein. Vorzugsweise ist ein Drehwinkelsensor zur Erkennung des Öffnungszustands des Drehschiebers vorgesehen. Der Elektromotor zum Antrieb des Drehschiebers kann außen am Kurbelgehäuse angeordnet sein.According to a further embodiment, the device and / or the control device may comprise a rotating rotary slide, by means of which the lubricant supply of the nozzle device during the mehrtaktigen, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine is temporarily deactivated. The rotary valve can be arranged perpendicular to the crankshaft. This embodiment also has the advantage that by the electrical control of the rotating rotary valve, a freely programmable connection and disconnection of the lubricant supply in dependence on other operating parameters, such. As a load, speed, oil temperature, etc., in a simple manner can be realized. Furthermore, optionally a fail-safe (fail safe) by a provision of the Solenoid valve be realized via the lubricant pressure. Preferably, a rotation angle sensor for detecting the opening state of the rotary valve is provided. The electric motor for driving the rotary valve can be arranged on the outside of the crankcase.
Alternativ kann der Drehschieber parallel zur Kurbelwelle angeordnet sein. Der Antrieb des Drehschiebers kann elektrisch über einen Elektromotor, insbesondere einen Elektromotor für alle Zylinder, erfolgen oder mechanisch durch einen Rädertrieb der Brennkraftmaschine. Bei einem mechanischen Antrieb kann die Zu- und Abschaltung des Drehschiebers analog der Steuerung der Nockenwelle erfolgen, z. B. mittels Nockenwellen-Steller oder Axialverschiebung etc. Vorzugsweise ist ein Drehwinkelsensor zur Erkennung des Öffnungszustands des Drehschiebers vorgesehen. Die Steuereinrichtung kann ein Steuergerät zur Ansteuerung des Magnetventils oder des rotierenden Drehschiebers umfassen.Alternatively, the rotary valve may be arranged parallel to the crankshaft. The drive of the rotary valve can be done electrically via an electric motor, in particular an electric motor for all cylinders, or mechanically by a gear drive of the internal combustion engine. In a mechanical drive, the connection and disconnection of the rotary valve can be done analogously to the control of the camshaft, z. B. means of camshaft actuator or axial displacement, etc. Preferably, a rotation angle sensor for detecting the opening state of the rotary valve is provided. The control device may include a control device for controlling the solenoid valve or the rotating rotary valve.
Zur Vermeidung von Wiederholungen sollen rein vorrichtungsgemäß offenbarte Merkmale auch als verfahrensgemäß offenbart gelten und beanspruchbar sein und vice versa.To avoid repetition, features disclosed purely in accordance with the device should also be regarded as disclosed according to the method and be able to be claimed and vice versa.
Die Erfindung betrifft ferner ein Kraftfahrzeug, insbesondere ein Nutzfahrzeug, umfassend eine Vorrichtung zur Kühlung und/oder Schmierung eines Kolbens und/oder der Laufbahn eines Zylinders einer Hubkolbenbrennkraftmaschine, wie in diesem Dokument beschrieben.The invention further relates to a motor vehicle, in particular a utility vehicle, comprising a device for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, as described in this document.
Die zuvor beschriebenen bevorzugten Ausführungsformen und Merkmale der Erfindung sind beliebig miteinander kombinierbar. Weitere Einzelheiten und Vorteile der Erfindung werden im Folgenden unter Bezug auf die beigefügten Zeichnungen beschrieben. Es zeigen:
Figur 1- eine Diagramm zur Illustration der Abhängigkeit der Strömungsgeschwindigkeit des Schmiermittels in Abhängigkeit vom Kolbenhub;
Figur 2- ein Diagramm zur Illustration eines Verfahrens gemäß einer Ausführungsform der Erfindung; und
Figur 3- eine schematische Darstellung einer Vorrichtung gemäß einer Ausführungsform der Erfindung;
- Figur 4
- eine schematische Darstellung einer Vorrichtung zur Kolbenkühlung gemäß einer weiteren Ausführungsform der Erfindung; und
Figur 5- eine schematische Darstellung einer Vorrichtung zur Kolbenkühlung gemäß einer weiteren Ausführungsform der Erfindung; und
Figur 6- eine schematische Darstellung einer aus dem Stand der Technik bekannten Vorrichtung zur Kolbenkühlung.
- FIG. 1
- a diagram illustrating the dependence of the flow velocity of the lubricant as a function of the piston stroke;
- FIG. 2
- a diagram illustrating a method according to an embodiment of the invention; and
- FIG. 3
- a schematic representation of an apparatus according to an embodiment of the invention;
- FIG. 4
- a schematic representation of a device for piston cooling according to another embodiment of the invention; and
- FIG. 5
- a schematic representation of a device for piston cooling according to another embodiment of the invention; and
- FIG. 6
- a schematic representation of a known from the prior art device for piston cooling.
Gleiche oder funktional äquivalente Elemente sind in allen Figuren mit denselben Bezugszeichen bezeichnet und zum Teil nicht gesondert beschrieben.Identical or functionally equivalent elements are denoted in all figures with the same reference numerals and partly not described separately.
Dem Diagramm der
Der Ölstrahl aus Ölspritzdüse 5 besitzt mit steigendem Abstand eine Vergrößerung des Strahldurchmessers (Strahlaufweitung). Dies ist in
Je nach Zusammensetzung des aufgeweiteten Ölstrahls reduziert sich dessen Strömungsgeschwindigkeit durch die Aufweitung mit zunehmendem Abstand. Der Verlauf kann experimentell oder simulativ bestimmt werden und ist in
Die mittlere Strömungsgeschwindigkeit des eingespritzten Öls (v_Öl) am Kolbeneintritt, d. h. an der Ölzulaufbohrung am Kolben, ist durch die Kurve 22 dargestellt. Die Strömungsgeschwindigkeit ist aufgrund der Strahlaufweitungseffekte am OT (0° und 360°) am geringsten und am UT (180°) am größten, wie vorstehend anhand von
Die Kurve 23 bezeichnet die Relativgeschwindigkeit (v_rel) zwischen dem Schmiermittel und dem Kolben (Differenz aus Schmiermittelgeschwindigkeit 22 und Kolbengeschwindigkeit 21). Diese ist während der Kolbenabwärtsbewegung am größten, da der Kolben 3 sich auf die Ölspritzdüse 5 und damit auf das von dieser ausgespritzte Öl zubewegt, und während der Kolbenaufwärtsbewegung am geringsten, da der Kolben 3 sich von der Ölspritzdüse 5 wegbewegt. Im Bereich der maximalen Kolbengeschwindigkeit ist die Ölgeschwindigkeit in dem gezeigten Beispiel geringer als die Kolbengeschwindigkeit. Folglich wird in diesem Bereich die Relativgeschwindigkeit (v_rel) zwischen der Schmiermittelgeschwindigkeit 22 und der Kolbengeschwindigkeit 21 sogar negativ, was durch den Bereich 23a gekennzeichnet ist. Es wird betont, dass bei anderen Ausführungsbeispielen bzw. Motoren im Bereich der maximalen Kolbengeschwindigkeit die Ölgeschwindigkeit nicht geringer als die Kolbengeschwindigkeit sein muss, aber auch hier nimmt die Relativgeschwindigkeit ihren Minimalwert an.The
Durch die geringe und zum Teil negative Relativgeschwindigkeit 23a während der Kolbenaufwärtsbewegung findet in diesen Zeitbereichen wenig bis keine Anspritzung des Kolbens mit Schmiermittel aus der Ölspritzdüse statt. Bei ausreichender Schmierung der umliegenden Bauteile kann die Ölversorgung der Ölspritzdüse 5 in diesen Zeitbereichen deaktiviert werden. Beispielsweise kann die Ölversorgung der Ölspritzdüse 5 während des Viertakt-Arbeitszyklus während der Kolbenabwärtsbewegung aktiviert sein und während der Kolbenaufwärtsbewegung deaktiviert sein. Besonders vorteilhaft ist die Deaktivierung im Bereich 23a der Kolbenaufwärtsbewegung, d. h. wenn die Relativgeschwindigkeit 23 negativ ist. Diese Unterbrechungsphase ist mit dem Bezugszeichen P gekennzeichnet.Due to the low and sometimes negative
Durch Abschaltung der Ölspritzdüse 5 im Aufwärtshub oder lediglich in Teilphasen P des Aufwärtshubs kann der Ölverbrauch und damit die Ölpumpenantriebsleistung reduziert werden, was wiederum zu einem reduzierten Kraftstoffverbrauch führt.By switching off the
Im unteren Diagramm ist entsprechend eine Ausführungsform des Verfahrens illustriert. In Abhängigkeit von der Relativgeschwindigkeit 23 wird die Schmiermittelzufuhr 25 zur Kolbenunterseite wahlweise aktiviert oder unterbrochen. Bei Kolbenhubpositionen, die einer positiven Relativgeschwindigkeit entsprechen, hier beispielhaft von 0° bis 220°, ist die Schmiermittelzufuhr 25 angeschaltet. Bei Kolbenhubpositionen, die einer negativen Relativgeschwindigkeit 23a entsprechen, hier beispielhaft von 220° bis 350° (Bereich P), ist die Schmiermittelzufuhr 25 unterbrochen.In the lower diagram, an embodiment of the method is illustrated accordingly. Depending on the
Es wird betont, dass die Erfindung nicht auf diese Ausführungsform beschränkt ist. Beispielsweise kann die Schmiermittelversorgung während des kompletten Aufwärtshubs des Kolbens unterbrochen sein. Beispielsweise kann der Bereich P auch Bereiche mit positiver Relativgeschwindigkeit umfassen.It is emphasized that the invention is not limited to this embodiment. For example, the lubricant supply may be interrupted during the complete upstroke of the piston. For example, the region P may also include positive relative velocity regions.
Wenn beispielsweise die Ölspritzdüse im kompletten Aufwärtshub, d. h. sowohl während des Verdichtungstakts als auch während des Ausschiebetakts, abgeschaltet wird, d. h. die Ölzufuhr unterbrochen wird, kann der Ölverbrauch der Ölspritzdüse um 50 % reduziert werden. Insbesondere bei einer 6-zylindrischen Hubkolbenbrennkraftmaschine mit 120°-Kropfung der Kurbelwelle ist der Summenölverbrauch der Ölspritzdüsen durch die gleiche Anzahl an Auf- und Abwärtsbewegungen konstant. Trotz Abschaltung der Ölzufuhr bei den einzelnen Ölspritzdüsen beim Aufwärtshub sind die Druckpulsationen bei dieser Ausführung daher gering.For example, if the oil spray nozzle in the complete upstroke, d. H. both during the compression stroke and during the exhaust stroke, is turned off, d. H. the oil supply is interrupted, the oil consumption of the oil spray nozzle can be reduced by 50%. In particular, in a 6-cylinder reciprocating internal combustion engine with 120 ° -Kropfung the crankshaft of the sum oil consumption of the oil spray nozzles by the same number of up and down movements is constant. Despite switching off the oil supply to the individual oil spray nozzles on the upstroke, the pressure pulsations in this embodiment are therefore low.
Dies kann mit einem elektrisch ansteuerbaren Magnetventil 31 realisiert werden, mittels dessen die Zufuhr von Öl zur Ölspritzdüse 5 wahlweise freigegeben oder unterbrochen werden kann. Aus Bauraumgründen ist die Spule 32 des Magnetventils 31 außen am Kurbelgehäuse angeordnet. Ein Steuergerät 37 steuert über eine Signalleitung 33 den Betrieb des Magnetventils 31. Das Steuergerät 37 steuert das Ventil 31 so an, dass die Schmiermittelzufuhr derThis can be realized with an electrically
Ölspritzdüse 5 während des Abwärtshubs des Kolbens freigegeben ist und während des Aufwärtshubs (oder in einem Teilabschnitt des Aufwärtshubs) des Kolbens unterbrochen ist. Lediglich beispielhaft beträgt der Hub des Magnetventils hierbei ca. 6 mm.
Die Steuerung kann durch eine an sich bekannte Steuerung der Ölspritzdüse überlagert werden, wobei die Ölspritzdüse anhand weiterer Betriebsparameter, wie Last, Drehzahl, Öltemperatur etc., die eingangsseitig von dem Steuergerät durch Signalleitungen 34 empfangen werden, gesteuert wird.The control can be superimposed by a known per se control of the oil spray nozzle, wherein the oil spray nozzle on the input side of the control unit by
Der rotierende Drehschieber 41 gemäß
Das Bezugszeichen 52 bezeichnet eine linsenförmige Öffnung, die von dem rotierenden Drehschieber freigegeben oder verschlossen werden kann und die an die Ölversorgung über den oberen Kanal angeschlossen ist. Das Bezugszeichen 53 bezeichnet die Rotationsbewegung des rotierenden Drehschiebers 51.The
Obwohl die Erfindung unter Bezugnahme auf bestimmte Ausführungsbeispiele beschrieben worden ist, ist es für einen Fachmann ersichtlich, dass verschiedene Änderungen ausgeführt werden können und Äquivalente als Ersatz verwendet werden können, ohne den Bereich der Erfindung zu verlassen. Folglich soll die Erfindung nicht auf die offenbarten Ausführungsbeispiele begrenzt sein, sondern soll alle Ausführungsbeispiele umfassen, die in den Bereich der beigefügten Patentansprüche fallen. Insbesondere beansprucht die Erfindung auch Schutz für den Gegenstand und die Merkmale der Unteransprüche unabhängig von den in Bezug genommenen Ansprüchen.Although the invention has been described with reference to particular embodiments, it will be apparent to those skilled in the art that various changes may be made and equivalents may be substituted for without departing from the scope of the invention. Accordingly, the invention should not be limited to the disclosed embodiments, but should include all embodiments which fall within the scope of the appended claims. In particular, the invention also claims protection of the subject matter and the features of the subclaims independently of the claims referred to.
- 11
- Vorrichtung zur Kolbenkühlung aus dem Stand der TechnikApparatus for piston cooling of the prior art
- 22
- Kolbenpiston
- 33
- Pleuelstangeconnecting rod
- 44
- Kurbelwellecrankshaft
- 55
- Düseneinrichtung, ÖlspritzdüseNozzle device, oil spray nozzle
- 66
- Schaltventilswitching valve
- 77
- Steuergerätcontrol unit
- 88th
- HauptölkanalMain oil
- 99
- Ölleitungoil line
- 1010
- Ölleitungoil line
- 1111
- Durchmesser Ölzulaufbohrung am KolbenDiameter oil inlet hole on the piston
- 1212
- Strahldurchmesser ÖlstrahlBeam diameter oil jet
- 1313
- Geschwindigkeit des eingespritzten Öls am KolbeneintrittSpeed of injected oil at the piston inlet
- 1515
- Diagrammdiagram
- 2020
- Diagrammdiagram
- 2121
- Kolbengeschwindigkeitpiston speed
- 2222
- Geschwindigkeit des eingespritzten Öls am KolbeneintrittSpeed of injected oil at the piston inlet
- 2323
- Relativgeschwindigkeit v_rel = v_Öl- v_KolbenRelative speed v_rel = v_Öl- v_Kolben
- 23a23a
- Bereich mit negativer RelativgeschwindigkeitRange with negative relative speed
- 2525
- Schmiermittelzufuhr zur KolbenunterseiteLubricant supply to the piston underside
- 3030
- Vorrichtung zur KolbenkühlungApparatus for piston cooling
- 3131
- Magnetventilmagnetic valve
- 3232
- SpuleKitchen sink
- 3333
- Signalleitungsignal line
- 3434
- Signalleitungsignal line
- 3737
- Steuergerätcontrol unit
- 4040
- Vorrichtung zur KolbenkühlungApparatus for piston cooling
- 4141
- Rotierender DrehschieberRotary rotary valve
- 4242
- Elektromotorelectric motor
- 5050
- Vorrichtung zur KolbenkühlungApparatus for piston cooling
- 5151
- Rotierender DrehschieberRotary rotary valve
- 5252
- Linsenförmige ÖffnungLenticular opening
- 5353
- Rotationsrichtungen des rotierenden DrehschiebersRotation directions of the rotating rotary valve
- PP
- Unterbrechungsphaseinterruption phase
Claims (14)
dadurch gekennzeichnet, dass während des mehrtaktigen, insbesondere des viertaktigen, Arbeitszyklus der Hubkolbenbrennkraftmaschine mindestens eine Unterbrechungsphase (P) vorgesehen ist, während derer eine Zufuhr (25) von Schmiermittel zum Kolben über die Düseneinrichtung (5) unterbrochen ist.Method for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine, the lubricant being supplied, in particular injected, to the piston via a nozzle device,
characterized in that during the mehrtaktigen, in particular the four-stroke, duty cycle of the reciprocating internal combustion engine at least one interruption phase (P) is provided, during which a supply (25) of lubricant to the piston via the nozzle means (5) is interrupted.
Applications Claiming Priority (1)
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DE102017120727.9A DE102017120727A1 (en) | 2017-09-08 | 2017-09-08 | Method and device for cooling and / or lubricating a piston and / or the raceway of a cylinder of a reciprocating internal combustion engine |
Publications (2)
Publication Number | Publication Date |
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EP3453855A1 true EP3453855A1 (en) | 2019-03-13 |
EP3453855B1 EP3453855B1 (en) | 2020-04-01 |
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Application Number | Title | Priority Date | Filing Date |
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EP18187887.7A Active EP3453855B1 (en) | 2017-09-08 | 2018-08-08 | Method and device for cooling and/or lubrication of a piston and/or a path of travel of a cylinder in a reciprocating piston engine |
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EP (1) | EP3453855B1 (en) |
DE (1) | DE102017120727A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN115443371A (en) * | 2020-04-22 | 2022-12-06 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
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DE3543084A1 (en) * | 1984-12-07 | 1986-06-12 | Toyota Jidosha K.K., Toyota, Aichi | CONTROL SYSTEM FOR FUEL EVAPORATION SPEED IN AN ENGINE WITH DIRECT FUEL INJECTION |
DE3821302C1 (en) * | 1988-06-24 | 1989-06-01 | Mtu Friedrichshafen Gmbh | |
DE102005010234A1 (en) * | 2005-03-05 | 2006-09-14 | Daimlerchrysler Ag | Piston cooling for internal combustion engine has oil spraying nozzle which is connected to oil dispenser channel whereby connection between oil dispenser channel and lubricating oil channel is formed for receiving hole of on-off valve |
DE102008033294A1 (en) * | 2008-07-15 | 2010-01-21 | Mtu Friedrichshafen Gmbh | Internal combustion engine comprises crankshaft, which is supported in crank housing by main bearing, and spray nozzle is provided for piston cooling |
DE102009057549A1 (en) * | 2009-12-09 | 2011-06-16 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Method for cooling or lubricating piston or path in cylinder of internal-combustion engine, involves feeding piston by nozzle device under pressure standing oil |
DE102015107078A1 (en) * | 2014-05-13 | 2015-11-19 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Single piston injector changeover with crank angle resolved control |
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JP4599785B2 (en) | 2001-09-25 | 2010-12-15 | トヨタ自動車株式会社 | Piston temperature control device for internal combustion engine |
DE102005006054A1 (en) | 2005-02-10 | 2006-08-31 | Daimlerchrysler Ag | Method for operation of reciprocating internal combustion engine involves closing of switching valve when higher requirement of oil load is recorded from control unit at another position in reciprocating internal combustion engine |
DE102015009568B4 (en) * | 2015-07-23 | 2021-02-11 | Audi Ag | Internal combustion engine with a control device for the targeted control of a piston cooling nozzle or a piston cooling duct and a method for operating an internal combustion engine |
-
2017
- 2017-09-08 DE DE102017120727.9A patent/DE102017120727A1/en not_active Withdrawn
-
2018
- 2018-08-08 EP EP18187887.7A patent/EP3453855B1/en active Active
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Publication number | Priority date | Publication date | Assignee | Title |
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DE3543084A1 (en) * | 1984-12-07 | 1986-06-12 | Toyota Jidosha K.K., Toyota, Aichi | CONTROL SYSTEM FOR FUEL EVAPORATION SPEED IN AN ENGINE WITH DIRECT FUEL INJECTION |
DE3821302C1 (en) * | 1988-06-24 | 1989-06-01 | Mtu Friedrichshafen Gmbh | |
DE102005010234A1 (en) * | 2005-03-05 | 2006-09-14 | Daimlerchrysler Ag | Piston cooling for internal combustion engine has oil spraying nozzle which is connected to oil dispenser channel whereby connection between oil dispenser channel and lubricating oil channel is formed for receiving hole of on-off valve |
DE102008033294A1 (en) * | 2008-07-15 | 2010-01-21 | Mtu Friedrichshafen Gmbh | Internal combustion engine comprises crankshaft, which is supported in crank housing by main bearing, and spray nozzle is provided for piston cooling |
DE102009057549A1 (en) * | 2009-12-09 | 2011-06-16 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Method for cooling or lubricating piston or path in cylinder of internal-combustion engine, involves feeding piston by nozzle device under pressure standing oil |
DE102015107078A1 (en) * | 2014-05-13 | 2015-11-19 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Single piston injector changeover with crank angle resolved control |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN115443371A (en) * | 2020-04-22 | 2022-12-06 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
Also Published As
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DE102017120727A1 (en) | 2019-03-14 |
EP3453855B1 (en) | 2020-04-01 |
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