EP3502453B1 - Piston for a reciprocating piston combustion engine - Google Patents
Piston for a reciprocating piston combustion engine Download PDFInfo
- Publication number
- EP3502453B1 EP3502453B1 EP18209823.6A EP18209823A EP3502453B1 EP 3502453 B1 EP3502453 B1 EP 3502453B1 EP 18209823 A EP18209823 A EP 18209823A EP 3502453 B1 EP3502453 B1 EP 3502453B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- cooling channel
- wall
- skirt
- section
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 238000002485 combustion reaction Methods 0.000 title claims description 28
- 238000001816 cooling Methods 0.000 claims description 139
- 239000000314 lubricant Substances 0.000 claims description 33
- 239000007921 spray Substances 0.000 claims description 18
- 230000007704 transition Effects 0.000 claims description 12
- 230000004323 axial length Effects 0.000 claims description 6
- 230000001419 dependent effect Effects 0.000 claims description 3
- 239000003921 oil Substances 0.000 description 29
- 239000012809 cooling fluid Substances 0.000 description 10
- 239000012530 fluid Substances 0.000 description 10
- 230000008901 benefit Effects 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000003466 welding Methods 0.000 description 2
- DGAQECJNVWCQMB-PUAWFVPOSA-M Ilexoside XXIX Chemical compound C[C@@H]1CC[C@@]2(CC[C@@]3(C(=CC[C@H]4[C@]3(CC[C@@H]5[C@@]4(CC[C@@H](C5(C)C)OS(=O)(=O)[O-])C)C)[C@@H]2[C@]1(C)O)C)C(=O)O[C@H]6[C@@H]([C@H]([C@@H]([C@H](O6)CO)O)O)O.[Na+] DGAQECJNVWCQMB-PUAWFVPOSA-M 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000004069 differentiation Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000011734 sodium Substances 0.000 description 1
- 229910052708 sodium Inorganic materials 0.000 description 1
- 238000009736 wetting Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/06—Arrangements for cooling pistons
- F01P3/10—Cooling by flow of coolant through pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/18—Pistons having cooling means the means being a liquid or solid coolant, e.g. sodium, in a closed chamber in piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
- F02F3/225—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid the liquid being directed into blind holes
Definitions
- the invention relates to a piston for a reciprocating internal combustion engine.
- pistons for a reciprocating internal combustion engine are known.
- Such a piston is usually arranged in a cylinder of a reciprocating internal combustion engine.
- the piston has a piston skirt, which is usually also referred to as a “skirt” or “piston skirt”. In English, the piston skirt is called the “piston skirt”.
- the piston has a ring belt adjoining the piston skirt in the axial direction of the piston, with at least one ring groove for a piston ring.
- the ring belt is part of the piston head.
- the friction of an internal combustion engine is made up of the friction of the basic engine (bearing, piston group) and the drive power of the auxiliary units.
- the piston group accounts for about 30% of the total friction, with the piston skirt causing about 2/3 of the friction of the piston group.
- the piston skirt friction is influenced by various influencing factors.
- the piston skirt friction depends on the engine speed, the engine load, the gap between the liner and the piston skirt and the shape of the piston skirt.
- a piston which has a circumferential cooling channel in the area of the ring belt 6 which extends from the ring belt in the axial direction along an inner surface of the wall of the piston skirt.
- an oil film temperature of the oil film in the cylinder liner between the piston skirt and cylinder can be increased in order to reduce the piston skirt friction.
- lubricant heated in the upper section of the cooling channel also reaches the inner surface of the wall of the piston skirt in order to enable an energy transfer for heating the piston skirt GB493126 A and US 2013/206084 A1 reveal further pistons.
- the object of the invention is in particular to provide a piston for to provide a reciprocating internal combustion engine with which piston skirt friction can be reduced.
- a piston for a reciprocating piston internal combustion engine which is slidably guided in a liner of a cylinder of the internal combustion engine and comprises, in a manner known per se, a piston head and a piston skirt.
- the piston skirt is used to guide the piston in the cylinder barrel.
- the piston skirt adjoins the ring belt in the axial direction of the piston.
- the axial direction corresponds to the direction of movement of the piston in the cylinder. It was already stated above that the piston skirt is also referred to as the piston skirt.
- the piston head is also known as the piston crown.
- the piston head has a circumferential ring belt with at least one ring groove for a piston ring.
- the piston has a fluid channel, having an upper section arranged in the area of the ring belt and a lower section starting from the upper section and extending along an inner surface of the wall of the piston skirt, in particular such that when the piston moves back and forth in the upper section Of the fluid channel heated lubricant also reaches the inner surface of the wall of the piston skirt and is guided through this in order to enable an energy transfer for heating the piston skirt.
- the fluid channel is referred to as a cooling channel and is also referred to as a first cooling channel, for better differentiation from a second cooling channel, which will be described below.
- the upper section of the cooling channel can be formed circumferentially in the ring belt.
- the first cooling channel is designed to be filled with a medium, for example with a cooling fluid, e.g. B. a cooling liquid or sodium, which has a melting point of about 98 ° C, or a lubricant, especially oil, to be filled.
- the upper section is used to cool the combustion bowl, which is also known as the piston bowl.
- the combustion bowl heated by the combustion process heats the medium, e.g. B. that Lubricant.
- the first cooling channel is not only arranged in the area of the ring belt or the piston head, but also extends down into the area of the piston skirt, so that cooling fluid is guided along at least a partial area of the inner wall of the piston skirt.
- Cooling channel which extends to the wall of the piston skirt, offers the advantage that the cooling fluid heated in the cooling channel in the area of the ring belt is guided in the lower section along the inner surface of the wall of the piston skirt, which enables energy to be transferred to heat the piston skirt.
- the lower section preferably runs parallel to the axial direction. The additional heating of the piston skirt achieved in this way increases the oil film temperature between the piston skirt and the cylinder liner, thereby reducing the piston skirt friction.
- the capacity of the lower section of the first cooling channel running in the area of the piston skirt can be at least 30% of the capacity of the upper section running in the area of the ring belt.
- the capacity of the lower section is preferably at least as large as the capacity of the upper section.
- the lower section of this fluid channel extending according to the invention to the wall of the piston skirt is also referred to as part of the cooling channel, although this section serves to supply the lubricant heated in the upper area of the cooling channel to the piston skirt and to heat it , and thus actually serves as a "heat channel”.
- the first cooling channel is characterized in that it is closed and permanently filled with a medium, in particular a cooling fluid.
- the degree of filling of the cooling channel with cooling fluid is constant, that is to say, the amount of cooling fluid in the first cooling channel is preferably introduced into the piston for a lifetime and does not change.
- the first cooling channel thus has no inlet and no outlet via which cooling fluid can enter or exit during operation of the piston.
- An inlet can only be provided for the first filling of the first cooling channel, which, however, is closed after filling, e.g. B. by welding or closing with a plug or a screw cap.
- the amount of medium in the first cooling channel does not change to conventional cooling channels with spray oil filling, in which the degree of filling fluctuates depending on the engine speed and the oil pressure at the oil spray nozzle. This can reduce the amount of piston cooling oil required. Furthermore, the optimal cooling in the oil channel is ensured, since the filling level of the first cooling channel remains constant. In combination with the above-described configuration of the first cooling channel with an upper and a lower section, an optimal distribution of the heat from the upper region of the piston to the piston rings and the piston skirt takes place.
- a particular advantage of the closed first cooling channel is that the temperature of the cooling fluid in the first cooling channel increases more than in the case of an open cooling channel. This increases the temperature of the piston skirt significantly, which significantly increases the heat flow from the piston to the liner.
- the oil spray nozzles can be completely dispensed with. In this case, there is also no load-dependent heat input into the engine oil. This means that there is no need to install an oil cooler, as the interaction of the oil with the engine is sufficient for cooling.
- the piston has a further fluid channel which, in contrast to the first fluid channel, is, however, designed to be open.
- This further fluid channel is referred to below as the second cooling channel.
- the second cooling channel is not fluidly connected to the first cooling channel.
- the second cooling channel is designed so that a lubricant, in particular oil, can flow through it. All statements in this document in which oil is used as a highlighted lubricant example also apply to other lubricants.
- the provision of the second fluid channel is particularly advantageous in engines with a very high specific power in order to increase the cooling power in the ring belt by combining the first cooling channel with a closed cooling channel and the second open cooling channel.
- the open second cooling channel thus serves as an additionally usable cooling channel, which is supplied with lubricant when required.
- the second cooling channel can for example be arranged in the piston head, in particular below the piston bowl.
- the second cooling channel is used for additional cooling of the combustion bowl.
- the second cooling channel can have at least one inlet opening through which the lubricant can flow into the second cooling channel, and can furthermore have at least one outlet opening through which the lubricant can exit from the second cooling channel.
- the inlet opening can be arranged in the area of the piston interior on the underside of the piston head. This is advantageous for filling the second cooling channel with spray oil with an oil spray nozzle.
- the inlet opening can be designed as an inlet bore. Accordingly, the outlet opening can be designed as a drain hole.
- a capacity of the first cooling channel can be greater than a capacity of the second cooling channel.
- the first cooling channel extends as far as a wall of the piston skirt arranged below the ring belt.
- the first cooling channel preferably extends at least to below the ring belt.
- the piston skirt can have a pin eye for receiving a piston pin.
- the first cooling channel can be designed circumferentially in the area of the ring part, d. That is, the cooling channel extends in the circumferential direction of the piston, preferably around 360 °, so that the cooling channel runs in a ring shape in the ring belt.
- the lower part of the first cooling channel i. H. that part which, starting from the upper section of the first cooling channel in the area of the ring belt as far as a wall of the piston skirt, does not extend around 360 °.
- the first cooling channel extends along the inner surface of the wall of the piston skirt to a lower end region of the wall of the piston skirt facing away from the ring belt, in order to be able to heat the piston skirt over its entire axial length.
- the cooling channel can extend along at least 50% of the axial length of the piston skirt along the inner surface of the wall of the piston skirt, more preferably along at least 2/3 of the axial length or further preferably along at least 4/5 of the axial length of the piston skirt.
- the lower section of the cooling channel runs parallel to the axial direction and is delimited on the outside by the inner surface of the wall of the piston skirt.
- the piston skirt has at least one pin eye for receiving a piston pin.
- the cooling channel can extend in the axial direction of the piston up to the level of the at least one bolt eye along the inner surface of the wall of the piston skirt. It is particularly advantageous if the cooling channel extends in the axial direction of the piston as far as a lower end of the bolt eye.
- the lower end of the bolt eye is that which faces a connecting rod engaging the piston.
- the wall of the piston skirt can have a profile on a side facing the first cooling channel, the profile preferably being formed by a groove structure.
- the profiling increases the surface area of the wall of the cooling channel on the side of the piston skirt, as a result of which the heat transfer to the piston skirt is increased by the lubricant that adheres to the profiling.
- a wall section of the first cooling channel which connects an upper area of the first cooling channel, which is designed circumferentially in the area of the ring belt, with a lower area of the cooling channel, which adjoins the wall of the piston skirt, is designed such that the lubricant is thrown against the wall of the piston skirt.
- This part of the wall of the cooling channel is referred to below as the transition wall section.
- the transition wall section of the cooling channel is designed in such a way that it has a section which runs obliquely downwards towards the piston skirt, on which in the lower region of the cooling channel there is a wall of the cooling channel that runs more steeply downwards in comparison and is arranged opposite the piston skirt, connects.
- the section of the transition wall section running obliquely downward can, for example, have the shape of a lateral surface of a truncated cone.
- the lubricant is thrown particularly efficiently against the wall of the piston skirt when shaking, so that the heat transfer is improved.
- an arrangement is provided with a piston which comprises both the first cooling channel and the second cooling channel, as described above.
- the arrangement or device further comprises an oil spray nozzle which is provided for supplying the piston with lubricant and is arranged such that a piston interior and an inlet opening of the second cooling channel can be sprayed with lubricant from the lubricant pump.
- the arrangement or device further comprises a control device of the oil spray nozzle, which is designed to selectively switch the lubricant pump on or off as a function of an operating parameter of an internal combustion engine, from which the current engine load can be derived.
- control device can be designed to operate the reciprocating internal combustion engine in wide partial load ranges without spray cooling and to switch on the oil spray nozzles only at operating points close to full load.
- a reciprocating piston internal combustion engine comprising a piston which comprises the first cooling channel, but not an open second cooling channel, as described above.
- the reciprocating internal combustion engine cannot have an oil spray nozzle for supplying the piston with lubricant and / or no oil cooler for cooling the lubricant for the reciprocating internal combustion engine, so that the heat exchange of the medium in the closed first cooling channel with the internal combustion engine is sufficient for cooling.
- a motor vehicle is provided with a piston as described in this document.
- the motor vehicle can be a utility vehicle, for example a truck or bus.
- FIG. 1 shows a partial section of an example.
- the piston 10 comprises a piston head 5 which has a circumferential ring belt 6.
- the ring belt 6 comprises several ring grooves 6a for a piston ring.
- the piston skirt 1 adjoins the ring belt 6 downwards, which, in contrast to the ring belt 6, does not is carried out completely circumferentially.
- the piston 10 is therefore not designed as a full skirt piston.
- the piston skirt 1 is slidingly mounted in the cylinder liner, a wall 10 of the piston skirt sliding back and forth along the liner when the piston moves.
- the piston 10 is mounted in a corresponding cylinder (not shown) of a cylinder piston housing (not shown) of a reciprocating internal combustion engine.
- the piston skirt 1 has at least one pin eye 8 for receiving a piston pin.
- a connecting rod (not shown) mounted on the crankshaft is articulated to the piston 10 via such a piston pin in order to convert the translational movements of the piston 10 in the cylinder into rotational movements of the crankshaft about its axis of rotation as a result of this articulated coupling.
- the piston 10 also has a piston bowl 7, also referred to as a combustion chamber bowl.
- the piston bowl 7 is designed as a so-called omega bowl. This means that the piston bowl 7 has a cross section which is at least essentially the shape of a "
- the piston 10 further comprises a first cooling channel 2, with an upper section 3 arranged in the area of the ring belt 6 and a lower section 4 starting from the upper section and extending along an inner surface 12 of the wall 11 of the piston skirt 1.
- the upper section 3 of the cooling channel 2 which is designed to run around 360 °
- the lower section 4 of the The cooling channel 2 is not completely circumferential, due to the running surface of the piston 10 which is not completely circumferential.
- the lower region of the section 4 of the cooling channel 2 extends in the axial direction A of the piston to the lower end 8 of the bolt eye or essentially almost along the entire axial length of the piston skirt 1. Both the upper section 3 and the lower Section 4 of the cooling channel 2 extend circumferentially along the outer wall of the piston 10.
- the first cooling channel 2 is closed and permanently filled with a medium 15, ie the amount of the medium 15 (eg lubricant, cooling fluid) in the first cooling channel is constant and does not change.
- the first cooling channel 2 thus has no inlet and no outlet via which cooling fluid could enter or exit during operation of the piston.
- An inlet can only be provided for the first filling of the first cooling channel, the after filling, however, is closed, e.g. B. by welding or closing with a plug or a screw cap.
- the example of Figure 1 has the advantage that the medium 15, which cools the piston head 5 in the upper region 3 of the cooling channel 2 and is heated in the process, is thrown back and forth between a bottom dead center and an upper dead center in the cooling channel 2 by the reciprocating movement of the piston ( "Shaken"), so that the medium 15 heated in the upper cooling channel region 3 also reaches the inner surface of the wall 10 of the piston skirt 1 and thus heats it.
- the oil film which is located between the outside 13 of the piston skirt and the cylinder liner is also heated, whereby its friction effect is reduced.
- an effective reduction in piston skirt friction can be achieved.
- the wall of the lower section 4 of the first cooling channel 2, which is located opposite the wall 10 of the piston skirt is designated by the reference numeral 14.
- transition between the upper area 3 of the cooling channel 2 and the lower area 4 of the cooling channel 2 is designed such that the medium is guided along a transition wall section 9 of the cooling channel 2.
- the transition wall section 9 is arranged on the side of the cooling channel 2 facing the inside of the piston and connects the upper area 3 of the cooling channel to the lower area 4 of the cooling channel.
- the transition wall section 9 runs straight downwards, with a strong downward curvature or also an edge being formed at the end of the transition wall section 9 at the transition to the lower wall section 4 of the cooling channel.
- the oil flowing along the transition wall section 9 is thrown at this bend like a jump against the inner surface 11 of the wall 10 of the piston skirt 1, so that an effective wetting of the wall 10 of the piston skirt with lubricant is made possible.
- the peculiarity of the embodiment of the Figure 2 lies in the fact that, in addition to the closed cooling channel 2, a second cooling channel 22 is provided, which, in contrast to the first cooling channel 2, is, however, open.
- the second cooling channel 22 is not fluidly connected to the first cooling channel.
- the second cooling channel 22 is arranged here, for example, below the piston recess 7 and extends only in the piston head 5.
- the second cooling channel 22 has an inlet bore 21 through which the lubricant can flow into the second cooling channel.
- the second cooling channel 22 also has one or more outlet openings, via which lubricant can exit again from the second cooling channel 22.
- the inlet bore 21 is arranged in the area of the piston interior on the underside of the piston head 5.
- An oil spray nozzle 23 is arranged below the piston skirt 1 in such a way that lubricant 24 emerging from the oil spray nozzle 23 is sprayed onto the inlet bore 21.
- the provision of the second fluid channel is particularly advantageous in engines with a very high specific power in order to increase the cooling power in the ring belt by combining the first cooling channel with a closed cooling channel and the second open cooling channel.
- the open second cooling channel can thus serve as an optionally additionally usable cooling channel, which is supplied with lubricant when required.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Description
Die Erfindung betrifft einen Kolben für eine Hubkolben-Verbrennungskraftmaschine.The invention relates to a piston for a reciprocating internal combustion engine.
Aus dem Stand der Technik, beispielsweise aus der Offenlegungsschrift
Die Reibung eines Verbrennungsmotors setzt sich aus der Reibung des Grundmotors (Lager, Kolbengruppe) und der Antriebsleistung der Nebenaggregate zusammen. Auf die Kolbengruppe entfallen hierbei in etwa 30 % der gesamten Reibung, wobei das Kolbenhemd in etwa 2/3 der Reibung der Kolbengruppe verursacht.The friction of an internal combustion engine is made up of the friction of the basic engine (bearing, piston group) and the drive power of the auxiliary units. The piston group accounts for about 30% of the total friction, with the piston skirt causing about 2/3 of the friction of the piston group.
Die Kolbenhemdreibung wird durch verschiedene Einflussgrößen beeinflusst. Beispielsweise hängt die Kolbenhemdreibung von der Motordrehzahl, der Motorlast, dem Spalt zwischen Laufbuchse und Kolbenhemd sowie der Form des Kolbenhemds ab.The piston skirt friction is influenced by various influencing factors. For example, the piston skirt friction depends on the engine speed, the engine load, the gap between the liner and the piston skirt and the shape of the piston skirt.
Aus der
Es ist eine Aufgabe der Erfindung, einen verbesserten Kolben für eine Hubkolben-Verbrennungskraftmaschine bereitzustellen, mit dem Nachteile herkömmlicher Kolben vermieden werden können. Die Aufgabe der Erfindung ist es insbesondere, einen Kolben für eine Hubkolben-Verbrennungskraftmaschine bereitzustellen, mit dem eine Kolbenhemdreibung reduziert werden kann.It is an object of the invention to provide an improved piston for a reciprocating piston internal combustion engine with which the disadvantages of conventional pistons can be avoided. The object of the invention is in particular to provide a piston for to provide a reciprocating internal combustion engine with which piston skirt friction can be reduced.
Diese Aufgaben werden durch einen Kolben für eine Hubkolben-Verbrennungskraftmaschine mit den Merkmalen des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen und Anwendungen der Erfindung sind Gegenstand der abhängigen Ansprüche und werden in der folgenden Beschreibung unter teilweiser Bezugnahme auf die Figuren näher erläutert. Erfindungsgemäß wird ein Kolben für eine Hubkolben-Verbrennungskraftmaschine bereitgestellt, der in einer Laufbuchse eines Zylinders der Verbrennungskraftmaschine gleitbeweglich geführt ist und in an sich bekannter Weise einen Kolbenkopf und ein Kolbenhemd umfasst. Das Kolbenhemd dient zur Führung des Kolbens im Zylinderrohr. Das Kolbenhemd schließt sich in axialer Richtung des Kolbens an die Ringpartie an. Hierbei entspricht die Axialrichtung der Bewegungsrichtung des Kolbens im Zylinder. Vorstehend wurde bereits festgestellt, dass das Kolbenhemd auch als Kolbenschaft bezeichnet wird. Der Kolbenkopf wird auch als Kolbenboden bezeichnet. Der Kolbenkopf weist eine umlaufende Ringpartie mit wenigstens einer Ringnut für einen Kolbenring auf.These objects are achieved by a piston for a reciprocating internal combustion engine with the features of the independent claim. Advantageous embodiments and applications of the invention are the subject matter of the dependent claims and are explained in more detail in the following description with partial reference to the figures. According to the invention, a piston for a reciprocating piston internal combustion engine is provided, which is slidably guided in a liner of a cylinder of the internal combustion engine and comprises, in a manner known per se, a piston head and a piston skirt. The piston skirt is used to guide the piston in the cylinder barrel. The piston skirt adjoins the ring belt in the axial direction of the piston. The axial direction corresponds to the direction of movement of the piston in the cylinder. It was already stated above that the piston skirt is also referred to as the piston skirt. The piston head is also known as the piston crown. The piston head has a circumferential ring belt with at least one ring groove for a piston ring.
Der Kolben weist einen Fluidkanal auf, aufweisend einen im Bereich der Ringpartie angeordneten oberen Abschnitt und einen vom oberen Abschnitt ausgehenden, sich entlang einer Innenfläche der Wandung des Kolbenhemds erstreckenden unteren Abschnitt, insbesondere derart, dass bei einer Hin- und Herbewegung des Kolbens im oberen Abschnitt des Fluidkanals erwärmtes Schmiermittel auch die Innenfläche der Wandung des Kolbenhemds erreicht und durch diese geführt wird, um einen Energietransfer zum Erwärmen des Kolbenhemds zu ermöglichen.The piston has a fluid channel, having an upper section arranged in the area of the ring belt and a lower section starting from the upper section and extending along an inner surface of the wall of the piston skirt, in particular such that when the piston moves back and forth in the upper section Of the fluid channel heated lubricant also reaches the inner surface of the wall of the piston skirt and is guided through this in order to enable an energy transfer for heating the piston skirt.
Der Fluidkanal wird in diesem Dokument als Kühlkanal bezeichnet und auch als erster Kühlkanal bezeichnet, zum besseren Unterscheiden von einem nachfolgend noch beschriebenen zweiten Kühlkanal.In this document, the fluid channel is referred to as a cooling channel and is also referred to as a first cooling channel, for better differentiation from a second cooling channel, which will be described below.
Der obere Abschnitt des Kühlkanals kann in der Ringpartie umlaufend ausgebildet sein. Der erste Kühlkanal ist ausgeführt, um mit einem Medium, beispielsweise mit einem Kühlfluid, z. B. einer Kühlflüssigkeit oder Natrium, welches einen Schmelzpunkt von ca. 98° C aufweist, oder einem Schmiermittel, insbesondere Öl, befüllt zu werden. Der obere Abschnitt dient zur Kühlung der Brennraummulde, die auch als Kolbenmulde bezeichnet wird. Die durch den Verbrennungsprozess erwärmte Brennraummulde erwärmt dabei das Medium, z. B. das Schmiermittel. Der erste Kühlkanal ist nicht nur im Bereich der Ringpartie bzw. des Kolbenkopfs angeordnet, sondern erstreckt sich ferner nach unten bis in den Bereich des Kolbenhemds, so dass Kühlfluid entlang zumindest eines Teilbereichs der Innenwandung des Kolbenhemds geführt ist. "Nach unten" bedeutet hier weg vom Kolbenkopf in Richtung Kurbelwellenpleuel bzw. in Richtung Kolbenbolzen. Dieser sich bis zur Wandung des Kolbenhemds erstreckende Kühlkanal bietet den Vorteil, dass das im Kühlkanal im Bereich der Ringpartie erwärmte Kühlfluid im unteren Abschnitt entlang der Innenfläche der Wandung des Kolbenhemds geführt wird, wodurch ein Energietransfer zum Erwärmen des Kolbenhemds ermöglicht wird. Der untere Abschnitt verläuft vorzugsweise parallel zur Axialrichtung. Die auf diese Weise erzielte zusätzliche Erwärmung des Kolbenhemds erhöht die Ölfilmtemperatur zwischen Kolbenhemd und Laufbuchse des Zylinders, wodurch eine Reduzierung der Kolbenhemdreibung erreicht wird. Das Fassungsvolumen des im Bereich des Kolbenhemds verlaufenden unteren Abschnitts des ersten Kühlkanals kann mindestens 30 % des Fassungsvolumens des im Bereich der Ringpartie verlaufenden oberen Abschnitts aufweisen. Vorzugsweise ist das Fassungsvolumen des unteren Abschnitts mindestens so groß wie das Fassungsvolumen des oberen Abschnitts.The upper section of the cooling channel can be formed circumferentially in the ring belt. The first cooling channel is designed to be filled with a medium, for example with a cooling fluid, e.g. B. a cooling liquid or sodium, which has a melting point of about 98 ° C, or a lubricant, especially oil, to be filled. The upper section is used to cool the combustion bowl, which is also known as the piston bowl. The combustion bowl heated by the combustion process heats the medium, e.g. B. that Lubricant. The first cooling channel is not only arranged in the area of the ring belt or the piston head, but also extends down into the area of the piston skirt, so that cooling fluid is guided along at least a partial area of the inner wall of the piston skirt. "Down" here means away from the piston head in the direction of the crankshaft connecting rod or in the direction of the piston pin. This cooling channel, which extends to the wall of the piston skirt, offers the advantage that the cooling fluid heated in the cooling channel in the area of the ring belt is guided in the lower section along the inner surface of the wall of the piston skirt, which enables energy to be transferred to heat the piston skirt. The lower section preferably runs parallel to the axial direction. The additional heating of the piston skirt achieved in this way increases the oil film temperature between the piston skirt and the cylinder liner, thereby reducing the piston skirt friction. The capacity of the lower section of the first cooling channel running in the area of the piston skirt can be at least 30% of the capacity of the upper section running in the area of the ring belt. The capacity of the lower section is preferably at least as large as the capacity of the upper section.
Je höher die Temperatur des Ölfilms zwischen Kolbenhemd und Laufbuchse, desto niedriger ist die Kolbenhemdreibung. Entsprechend dieser üblichen Bezeichnung des Fluidkanals als Kühlkanal wird auch der sich bis zur Wandung des Kolbenhemds erfindungsgemäß erstreckende untere Abschnitt dieses Fluidkanals als Teil des Kühlkanals bezeichnet, obwohl dieser Abschnitt dazu dient, das im oberen Bereich des Kühlkanals erwärmte Schmiermittel dem Kolbenhemd zuzuführen und dieses zu erwärmen, und somit eigentlich als "Wärmekanal" dient.The higher the temperature of the oil film between the piston skirt and the liner, the lower the piston skirt friction. Corresponding to this usual designation of the fluid channel as a cooling channel, the lower section of this fluid channel extending according to the invention to the wall of the piston skirt is also referred to as part of the cooling channel, although this section serves to supply the lubricant heated in the upper area of the cooling channel to the piston skirt and to heat it , and thus actually serves as a "heat channel".
Der erste Kühlkanal zeichnet sich dadurch aus, dass er verschlossen und mit einem Medium, insbesondere einem Kühlfluid, dauerhaft befüllt ist. Anders ausgedrückt ist der Befüllungsgrad des Kühlkanals mit Kühlfluid konstant, d. h., die Menge an Kühlfluid im ersten Kühlkanal ist vorzugsweise auf Lebensdauer in den Kolben eingebracht und ändert sich nicht. Der erste Kühlkanal hat somit keinen Einlass und keinen Auslass, über die Kühlfluid im Betrieb des Kolbens ein- bzw. austreten kann. Ein Einlass kann lediglich zur erstmaligen Befüllung des ersten Kühlkanals vorgesehen sein, der nach Befüllung jedoch verschlossen wird, z. B. durch Verschweißen oder Verschließen mit einem Stöpsel oder einem Schraubverschluss. Die Menge des Mediums im ersten Kühlkanals ändert sich somit nicht, im Gegensatz zu konventionellen Kühlkanälen mit Spritzölbefüllung, bei denen der Füllungsgrad in Abhängigkeit von der Motordrehzahl und des Öldrucks an der Ölspritzdüse schwankt. Hierdurch kann die benötigte Kolbenkühlölmenge reduziert werden. Ferner wird die optimale Kühlung im Ölkanal sichergestellt, da der Füllungsgrad des ersten Kühlkanals konstant bleibt. In Kombination mit der vorstehend beschriebenen Ausgestaltung des ersten Kühlkanals mit oberem und unterem Abschnitt findet eine optimale Verteilung der Wärme aus dem oberen Bereich des Kolbens zu den Kolbenringen und dem Kolbenhemd statt.The first cooling channel is characterized in that it is closed and permanently filled with a medium, in particular a cooling fluid. In other words, the degree of filling of the cooling channel with cooling fluid is constant, that is to say, the amount of cooling fluid in the first cooling channel is preferably introduced into the piston for a lifetime and does not change. The first cooling channel thus has no inlet and no outlet via which cooling fluid can enter or exit during operation of the piston. An inlet can only be provided for the first filling of the first cooling channel, which, however, is closed after filling, e.g. B. by welding or closing with a plug or a screw cap. In contrast, the amount of medium in the first cooling channel does not change to conventional cooling channels with spray oil filling, in which the degree of filling fluctuates depending on the engine speed and the oil pressure at the oil spray nozzle. This can reduce the amount of piston cooling oil required. Furthermore, the optimal cooling in the oil channel is ensured, since the filling level of the first cooling channel remains constant. In combination with the above-described configuration of the first cooling channel with an upper and a lower section, an optimal distribution of the heat from the upper region of the piston to the piston rings and the piston skirt takes place.
Ein besonderer Vorzug des geschlossenen ersten Kühlkanals liegt darin, dass sich die Temperatur des Kühlfluids im ersten Kühlkanal stärker als bei einem offenen Kühlkanal erhöht. Dadurch steigt die Temperatur des Kolbenhemds deutlich, wodurch der Wärmestrom vom Kolben an die Laufbuchse deutlich erhöht wird.A particular advantage of the closed first cooling channel is that the temperature of the cooling fluid in the first cooling channel increases more than in the case of an open cooling channel. This increases the temperature of the piston skirt significantly, which significantly increases the heat flow from the piston to the liner.
Stand der Technik bei Verbrennungsmotoren ist, dass im Leerlauf und bei niedrigen Lasten die Ölspritzdüsen abgeschalten werden. Durch den erhöhten Wärmestrom vom Kolben an die Laufbuchse kann der Bereich, in dem ohne Ölspritzdüsen gefahren wird, deutlich vergrößert werden.The state of the art in internal combustion engines is that the oil spray nozzles are switched off when idling and at low loads. Due to the increased heat flow from the piston to the liner, the area in which the vehicle is driven without oil spray nozzles can be significantly enlarged.
Ein weiterer Vorzug ist, dass bei zweckmäßig geeigneter Auslegung des ersten Kühlkanals (Fassungsvolumen, Länge etc.) die Ölspritzdüsen komplett entfallen können. In diesem Fall entfällt auch der lastabhängige Wärmeeintrag in das Motoröl. Hierdurch kann auf den Verbau eines Ölkühlers verzichtet werden, da die Interaktion des Öls mit dem Motor für die Kühlung ausreicht.Another advantage is that if the first cooling channel is suitably designed (capacity, length, etc.), the oil spray nozzles can be completely dispensed with. In this case, there is also no load-dependent heat input into the engine oil. This means that there is no need to install an oil cooler, as the interaction of the oil with the engine is sufficient for cooling.
Erfindungsgemäß weist der Kolben einen weiteren Fluidkanal auf, der im Unterschied zum ersten Fluidkanal jedoch offen ausgeführt ist. Dieser weitere Fluidkanal wird nachfolgend als zweiter Kühlkanal bezeichnet. Der zweite Kühlkanal steht mit dem ersten Kühlkanal fluidisch nicht in Verbindung. Der zweite Kühlkanal ist ausgebildet, um von einem Schmiermittel, insbesondere Öl, durchströmt zu werden. Alle Ausführungen in diesem Dokument, bei dem Öl als hervorgehobenes Schmiermittelbeispiel verwendet wird, gelten auch für andere Schmiermittel.According to the invention, the piston has a further fluid channel which, in contrast to the first fluid channel, is, however, designed to be open. This further fluid channel is referred to below as the second cooling channel. The second cooling channel is not fluidly connected to the first cooling channel. The second cooling channel is designed so that a lubricant, in particular oil, can flow through it. All statements in this document in which oil is used as a highlighted lubricant example also apply to other lubricants.
Das Vorsehen des zweiten Fluidkanals ist besonders bei Motoren mit sehr hoher spezifischer Leistung vorteilhaft, um durch Kombination des ersten Kühlkanals mit geschlossenem Kühlkanal und des zweiten offenen Kühlkanals die Kühlleistung in der Ringpartie zu erhöhen.The provision of the second fluid channel is particularly advantageous in engines with a very high specific power in order to increase the cooling power in the ring belt by combining the first cooling channel with a closed cooling channel and the second open cooling channel.
Der offene zweite Kühlkanal dient somit als zusätzlich nutzbarer Kühlkanal, der bei Bedarf mit Schmiermittel versorgt wird.The open second cooling channel thus serves as an additionally usable cooling channel, which is supplied with lubricant when required.
Der zweite Kühlkanal kann beispielsweise im Kolbenkopf angeordnet sein, insbesondere unterhalb der Kolbenmulde. Der zweite Kühlkanal dient so zur zusätzlichen Kühlung der Brennraummulde.The second cooling channel can for example be arranged in the piston head, in particular below the piston bowl. The second cooling channel is used for additional cooling of the combustion bowl.
Der zweite Kühlkanal kann mindestens eine Zulauföffnung aufweisen, über die das Schmiermittel in den zweiten Kühlkanal einströmen kann, und kann ferner mindestens eine Austrittsöffnung aufweisen, über die Schmiermittel aus dem zweiten Kühlkanal austreten kann. Die Zulauföffnung kann im Bereich des Kolbeninnenraums an der Unterseite des Kolbenkopfs angeordnet sein. Dies ist vorteilhaft für eine Spritzölbefüllung des zweiten Kühlkanals mit Ölspritzdüse. Die Zulauföffnung kann als Zulaufbohrung ausgeführt sein. Entsprechend kann die Austrittsöffnung als Ablaufbohrung ausgeführt sein.The second cooling channel can have at least one inlet opening through which the lubricant can flow into the second cooling channel, and can furthermore have at least one outlet opening through which the lubricant can exit from the second cooling channel. The inlet opening can be arranged in the area of the piston interior on the underside of the piston head. This is advantageous for filling the second cooling channel with spray oil with an oil spray nozzle. The inlet opening can be designed as an inlet bore. Accordingly, the outlet opening can be designed as a drain hole.
Gemäß einem weiteren Aspekt kann ein Fassungsvolumen des ersten Kühlkanals größer sein als ein Fassungsvolumen des zweiten Kühlkanals.According to a further aspect, a capacity of the first cooling channel can be greater than a capacity of the second cooling channel.
Der erste Kühlkanal erstreckt sich bis zu einer unterhalb der Ringpartie angeordneten Wandung des Kolbenhemds. Der erste Kühlkanal erstreckt sich vorzugsweise mindestens bis unterhalb der Ringpartie. Das Kolbenhemd kann ein Bolzenauge zur Aufnahme eines Kolbenbolzens aufweisen. Der erste Kühlkanal kann im Bereich der Ringpartei umlaufend ausgebildet sein, d. h., der Kühlkanal erstreckt sich in Umfangsrichtung des Kolbens, vorzugsweise um 360° umlaufend, so dass der Kühlkanal in der Ringpartie ringförmig verläuft. Vorzugsweise ist der untere Teil des ersten Kühlkanals, d. h. derjenige Teil, der sich ausgehend vom oberen Abschnitt des ersten Kühlkanals im Bereich der Ringpartie bis zu einer Wandung des Kolbenhemds erstreckt, nicht um 360° umlaufend ausgebildet.The first cooling channel extends as far as a wall of the piston skirt arranged below the ring belt. The first cooling channel preferably extends at least to below the ring belt. The piston skirt can have a pin eye for receiving a piston pin. The first cooling channel can be designed circumferentially in the area of the ring part, d. That is, the cooling channel extends in the circumferential direction of the piston, preferably around 360 °, so that the cooling channel runs in a ring shape in the ring belt. Preferably the lower part of the first cooling channel, i. H. that part which, starting from the upper section of the first cooling channel in the area of the ring belt as far as a wall of the piston skirt, does not extend around 360 °.
Gemäß einer besonders vorteilhaften Ausführungsform erstreckt sich der erste Kühlkanal entlang der Innenfläche der Wandung des Kolbenhemds bis zu einem unteren, der Ringpartie abgewandten Endbereich der Wandung des Kolbenhemds, um auf diese Weise das Kolbenhemd über seine ganze axiale Länge erwärmen zu können. Alternativ kann sich der Kühlkanal entlang mindestens 50 % der axialen Länge des Kolbenhemds entlang der Innenfläche der Wandung des Kolbenhemds erstrecken, weiter vorzugsweise entlang mindestens 2/3 der axialen Länge oder ferner vorzugsweise mindestens entlang 4/5 der axialen Länge des Kolbenhemds. Der untere Abschnitt des Kühlkanals verläuft dabei parallel zur Axialrichtung und wird außenseitig von der Innenfläche der Wandung des Kolbenhemds begrenzt.According to a particularly advantageous embodiment, the first cooling channel extends along the inner surface of the wall of the piston skirt to a lower end region of the wall of the piston skirt facing away from the ring belt, in order to be able to heat the piston skirt over its entire axial length. Alternatively, the cooling channel can extend along at least 50% of the axial length of the piston skirt along the inner surface of the wall of the piston skirt, more preferably along at least 2/3 of the axial length or further preferably along at least 4/5 of the axial length of the piston skirt. The lower section of the cooling channel runs parallel to the axial direction and is delimited on the outside by the inner surface of the wall of the piston skirt.
Vorstehend wurde bereits erwähnt, dass das Kolbenhemd mindestens ein Bolzenauge zur Aufnahme eines Kolbenbolzens aufweist. Gemäß einer weiteren Ausführungsform kann sich der Kühlkanal in axialer Richtung des Kolbens bis auf Höhe des mindestens einen Bolzenauges entlang der Innenfläche der Wandung des Kolbenhemds erstrecken. Besonders vorteilhaft ist, wenn sich der Kühlkanal in axialer Richtung des Kolbens bis zu einem unteren Ende des Bolzenauges erstreckt. Hierbei ist das untere Ende des Bolzenauges dasjenige, das einem am Kolben angreifenden Pleuel zugewandt ist.It was already mentioned above that the piston skirt has at least one pin eye for receiving a piston pin. According to a further embodiment, the cooling channel can extend in the axial direction of the piston up to the level of the at least one bolt eye along the inner surface of the wall of the piston skirt. It is particularly advantageous if the cooling channel extends in the axial direction of the piston as far as a lower end of the bolt eye. Here, the lower end of the bolt eye is that which faces a connecting rod engaging the piston.
Gemäß einer weiteren bevorzugten Ausführungsform kann die Wandung des Kolbenhemds auf einer dem ersten Kühlkanal zugewandten Seite eine Profilierung aufweisen, wobei die Profilierung vorzugsweise durch eine Rillenstruktur gebildet ist. Die Profilierung vergrößert die Oberfläche der Wandung des Kühlkanals auf der Seite des Kolbenhemds, wodurch der Wärmeübergang zum Kolbenhemd durch das an der Profilierung hängenbleibende Schmiermittel vergrößert wird.According to a further preferred embodiment, the wall of the piston skirt can have a profile on a side facing the first cooling channel, the profile preferably being formed by a groove structure. The profiling increases the surface area of the wall of the cooling channel on the side of the piston skirt, as a result of which the heat transfer to the piston skirt is increased by the lubricant that adheres to the profiling.
Gemäß einer weiteren vorteilhaften Ausführungsform ist ein Wandungsabschnitt des ersten Kühlkanals, der einen oberen Bereich des ersten Kühlkanals, der im Bereich der Ringpartie umlaufend ausgeführt ist, mit einem unteren Bereich des Kühlkanals, der an die Wandung des Kolbenhemds angrenzt, verbindet, so ausgeführt, dass das Schmiermittel gegen die Wandung des Kolbenhemds geschleudert wird. Dieser Teil der Wandung des Kühlkanals wird nachfolgend als Übergangswandungsabschnitt bezeichnet. Beispielsweise ist der Übergangswandungsabschnitt des Kühlkanals so ausgeführt, dass er einen schräg nach unten hin zum Kolbenhemd verlaufenden Abschnitt aufweist, an den sich im unteren Bereich des Kühlkanals eine sich im Vergleich hierzu steiler nach unten verlaufende Wandung des Kühlkanals, die zum Kolbenhemd gegenüberliegend angeordnet ist, anschließt. Der schräg nach unten verlaufende Abschnitt des Übergangswandungsabschnitts kann beispielsweise die Form einer Mantelfläche eines Kegelstumpfes aufweisen. Bei dieser Ausführungsform wird somit das Schmiermittel besonders effizient beim Shakern gegen die Wandung des Kolbenhemds geschleudert, so dass der Wärmeübertrag verbessert wird.According to a further advantageous embodiment, a wall section of the first cooling channel, which connects an upper area of the first cooling channel, which is designed circumferentially in the area of the ring belt, with a lower area of the cooling channel, which adjoins the wall of the piston skirt, is designed such that the lubricant is thrown against the wall of the piston skirt. This part of the wall of the cooling channel is referred to below as the transition wall section. For example, the transition wall section of the cooling channel is designed in such a way that it has a section which runs obliquely downwards towards the piston skirt, on which in the lower region of the cooling channel there is a wall of the cooling channel that runs more steeply downwards in comparison and is arranged opposite the piston skirt, connects. The section of the transition wall section running obliquely downward can, for example, have the shape of a lateral surface of a truncated cone. In this embodiment, the lubricant is thrown particularly efficiently against the wall of the piston skirt when shaking, so that the heat transfer is improved.
Gemäß einem weiteren Aspekt wird eine Anordnung (Vorrichtung) bereitgestellt, mit einem Kolben, der sowohl den ersten Kühlkanal als auch den zweiten Kühlkanal, wie vorstehend beschrieben, umfasst. Die Anordnung bzw. Vorrichtung umfasst ferner eine Ölspritzdüse, die zur Versorgung des Kolbens mit Schmiermittel vorgesehen ist und so angeordnet ist, dass ein Kolbeninnenraum und eine Zulauföffnung des zweiten Kühlkanals mit Schmiermittel von der Schmiermittelpumpe bespritzbar sind. Die Anordnung bzw. Vorrichtung umfasst ferner eine Steuereinrichtung der Ölspritzdüse, die ausgebildet ist, in Abhängigkeit von einem Betriebsparameter eines Verbrennungsmotors, aus dem die aktuelle Motorlast ableitbar ist, die Schmiermittelpumpe wahlweise einzuschalten oder abzuschalten.According to a further aspect, an arrangement (device) is provided with a piston which comprises both the first cooling channel and the second cooling channel, as described above. The arrangement or device further comprises an oil spray nozzle which is provided for supplying the piston with lubricant and is arranged such that a piston interior and an inlet opening of the second cooling channel can be sprayed with lubricant from the lubricant pump. The arrangement or device further comprises a control device of the oil spray nozzle, which is designed to selectively switch the lubricant pump on or off as a function of an operating parameter of an internal combustion engine, from which the current engine load can be derived.
Beispielsweise kann die Steuereinrichtung ausgebildet sein, die Hubkolben-Verbrennungskraftmaschine in weiten Teillastbereichen ohne Spritzkühlung zu betreiben und nur in volllastnahen Betriebspunkten die Ölspritzdüsen zuzuschalten.For example, the control device can be designed to operate the reciprocating internal combustion engine in wide partial load ranges without spray cooling and to switch on the oil spray nozzles only at operating points close to full load.
Gemäß einem weiteren Aspekt wird eine Hubkolben-Verbrennungskraftmaschine bereitgestellt, umfassend einen Kolben, der den ersten Kühlkanal umfasst, jedoch keinen offenen zweiten Kühlkanal, wie vorstehend beschrieben. Gemäß diesem Aspekt kann die Hubkolben-Verbrennungskraftmaschine keine Ölspritzdüse zur Versorgung des Kolbens mit Schmiermittel und/oder keinen Ölkühler zur Kühlung des Schmiermittels für die Hubkolben-Verbrennungskraftmaschine aufweisen, so dass der Wärmeaustausch des Mediums im geschlossenen ersten Kühlkanal mit der Brennkraftmaschine für die Kühlung ausreicht.According to a further aspect, a reciprocating piston internal combustion engine is provided, comprising a piston which comprises the first cooling channel, but not an open second cooling channel, as described above. According to this aspect, the reciprocating internal combustion engine cannot have an oil spray nozzle for supplying the piston with lubricant and / or no oil cooler for cooling the lubricant for the reciprocating internal combustion engine, so that the heat exchange of the medium in the closed first cooling channel with the internal combustion engine is sufficient for cooling.
Ferner wird ein Kraftfahrzeug bereitgestellt, mit einem Kolben, wie in diesem Dokument beschrieben. Das Kraftfahrzeug kann ein Nutzfahrzeug sein, beispielsweise ein Lastkraftwagen oder Omnibus.Furthermore, a motor vehicle is provided with a piston as described in this document. The motor vehicle can be a utility vehicle, for example a truck or bus.
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:
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einen Teilschnitt eines Kolbens gemäß eines Beispiels;Figur 1
und -
einen Teilschnitt eines Kolbens gemäß einer ersten Ausführungsform.Figur 2
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Figure 1 a partial section of a piston according to an example;
and -
Figure 2 a partial section of a piston according to a first embodiment.
Gleiche oder funktional äquivalente Elemente sind in allen Figuren mit denselben Bezugszeichen bezeichnet und werden zum Teil nicht gesondert beschrieben.Identical or functionally equivalent elements are denoted by the same reference symbols in all figures and in some cases are not described separately.
Der Kolben 10 weist ferner eine Kolbenmulde 7 auf, auch als Brennraummulde bezeichnet. Die Kolbenmulde 7 ist als sogenannte Omega-Mulde ausgebildet. Dies bedeutet, dass die Kolbenmulde 7 einen Querschnitt aufweist, welcher zumindest im Wesentlichen die Form eines "" aufweist. Der Kolben 10 umfasst ferner einen ersten Kühlkanal 2, mit einem im Bereich der Ringpartie 6 angeordneten oberen Abschnitt 3 und einen vom oberen Abschnitt ausgehenden, sich entlang einer Innenfläche 12 der Wandung 11 des Kolbenhemds 1 erstreckenden unteren Abschnitt 4. Der untere Abschnitt 4, der sich im Bereich des Kolbenhemds 1 befindet, grenzt an die Wandung 10 des Kolbenhemds 1 an und ist entlang dieser geführt. Im Gegensatz zum oberen Abschnitt 3 des Kühlkanals 2, der um 360° umlaufend ausgeführt ist, ist der untere Abschnitt 4 des Kühlkanals 2 nicht vollständig umlaufend ausgeführt, bedingt durch die nicht vollständig umlaufend ausgeführte Lauffläche des Kolbens 10.The
Im gezeigten Beispiel erstreckt sich der untere Bereich des Abschnitts 4 des Kühlkanals 2 in axialer Richtung A des Kolbens bis zum unteren Ende 8 des Bolzenauges bzw. im Wesentlichen fast entlang der ganzen axialen Länge des Kolbenhemds 1. Sowohl der obere Abschnitt 3 als auch der untere Abschnitt 4 des Kühlkanals 2 erstrecken sich umfangsseitig entlang der äußeren Wandung des Kolbens 10.In the example shown, the lower region of the
Erfindungsgemäß ist der erste Kühlkanal 2 verschlossen und mit einem Medium 15 dauerhaft befüllt, d. h., die Menge des Mediums 15 (z. B. Schmiermittel, Kühlfluid) im ersten Kühlkanal ist konstant und ändert sich nicht. Der erste Kühlkanal 2 hat somit keinen Einlass und keinen Auslass, über die Kühlfluid im Betrieb des Kolben ein- bzw. austreten könnte. Ein Einlass kann lediglich zur erstmaligen Befüllung des ersten Kühlkanals vorgesehen sein, der nach Befüllung jedoch verschlossen wird, z. B. durch Verschweißen oder Verschließen mit einem Stöpsel oder einem Schraubverschluss.According to the invention, the
Das Beispiel der
Im Vergleich zu einem offenen Kühlkanal wird bei dem geschlossenen Kühlkanal 2 das Medium im Kühlkanal 2 stärker erwärmt und dadurch der Wärmestrom vom Kolben an die Laufbuchse deutlich erhöht, da sich die Temperatur des Kolbenhemds deutlich steigert.Compared to an open cooling channel, with the
In
In
Die Besonderheit der Ausführungsform der
Das Vorsehen des zweiten Fluidkanals ist besonders bei Motoren mit sehr hoher spezifischer Leistung vorteilhaft, um durch Kombination des ersten Kühlkanals mit geschlossenem Kühlkanal und des zweiten offenen Kühlkanals die Kühlleistung in der Ringpartie zu erhöhen. Der offene zweite Kühlkanal kann somit als optional zusätzlich nutzbarer Kühlkanal dienen, der bei Bedarf mit Schmiermittel versorgt wird.The provision of the second fluid channel is particularly advantageous in engines with a very high specific power in order to increase the cooling power in the ring belt by combining the first cooling channel with a closed cooling channel and the second open cooling channel. The open second cooling channel can thus serve as an optionally additionally usable cooling channel, which is supplied with lubricant when required.
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.Although the invention has been described with reference to particular exemplary embodiments, it will be apparent to a person skilled in the art that various changes can be made and equivalents used as replacements without departing from the scope of the invention. Accordingly, it is intended that the invention not be limited to the disclosed embodiments, but that it encompass all embodiments that fall within the scope of the appended claims.
- 11
- KolbenhemdPiston skirt
- 22
- Erster KühlkanalFirst cooling channel
- 33
- Oberer AbschnittUpper section
- 44th
- Unterer AbschnittLower section
- 55
- KolbenkopfPiston head
- 66th
- RingpartieRing game
- 6a6a
- RingnutRing groove
- 77th
- KolbenmuldePiston recess
- 88th
- BolzenaugeBolt eye
- 99
- ÜbergangswandungsabschnittTransition wall section
- 1010
- Kolbenpiston
- 1111
- Wandung des KolbenhemdsWall of the piston skirt
- 1212th
- Innenfläche der Wandung des KolbenhemdsInner surface of the wall of the piston skirt
- 1313th
- Außenfläche des KolbenhemdsOuter surface of the piston skirt
- 1414th
- WandungWall
- 1515th
- Medium im ersten KühlkanalMedium in the first cooling channel
- 2020th
- Kolbenpiston
- 2121
- Zulauföffnung, insbesondere ZulaufbohrungInlet opening, in particular inlet bore
- 2222nd
- Zweiter KühlkanalSecond cooling channel
- 2323
- ÖlspritzdüseOil spray nozzle
- 2424
- Gespritztes SchmiermittelSplashed lubricant
- AA.
- Axiale RichtungAxial direction
Claims (11)
- A piston (10; 20) for a reciprocating-piston internal combustion engine, comprising
a piston crown (5), having an encircling ring section (6) with at least one ring groove for a piston ring;
a piston skirt (1); and
a first cooling channel (2), having an upper section (3) arranged in the region of the ring section (6) and a lower section (4) which proceeds from the upper section and which extends along an inner surface (12) of the wall (11) of the piston skirt (1);
wherein the first cooling channel (2) is closed and is permanently filled with a medium (15); characterized by an open second cooling channel (22) . - The piston (20) according to Claim 1, characterized in that the second cooling channel (22) is arranged in the piston crown, in particular below the piston depression (7).
- The piston (20) according to Claim 1 or 2, characterized in that the second cooling channel (22) has an inflow opening which is arranged in the region of the piston interior space at the underside of the piston crown.
- The piston (20) according to any of the preceding claims, characterized in that a volume of the first cooling channel (2) is greater than a volume of the second cooling channel (22).
- The piston according to any of the preceding claims, characterized in that the piston skirt (1) has at least one pin bore (8) for receiving a piston pin; and
b1) in that the lower section (4) of the first cooling channel (2) extends in an axial direction of the piston along the inner surface of the wall (11) of the piston skirt (1) at least to the level of the at least one pin bore (8); and/or
b2) in that the cooling channel extends in an axial direction of the piston along the inner surface of the wall (11) of the piston skirt (2) at least to a lower end of the pin bore (8). - The piston according to any of the preceding claims, characterized in that the first cooling channel (2) extends along the inner surface of the wall (11) of the piston skirt (2) along at least 2/3 of the axial length of the piston skirt, preferably to a lower end region (4), averted from the ring section (6), of the wall (11) of the piston skirt (1).
- The piston according to any of the preceding claims, characterized in that the inner surface (12) of the wall (11) of the piston skirt (2) has a profiling (61), wherein the profiling (61) is formed preferably by a groove structure.
- The piston according to any of the preceding claims, characterized in thata) a transition wall section of the first cooling channel (2) is provided,a1) which is arranged on the side of the first cooling channel (2) facing towards the piston inner side anda2) which connects the upper region (3) of the first cooling channel (2), which is of encircling form in the region of the ring section (6), to the lower region (4) of the first cooling channel (2) anda3) which has a section (9) running obliquely downwards towards the piston skirt (1), which section is adjoined in the lower region (4) of the first cooling channel (2) by a wall (14) of the first cooling channel (2), which wall runs more steeply downwards in relation to said section and is arranged opposite the piston skirt (1).
- An arrangement, comprisinga) a piston according to any of the preceding claims, andb) an oil spray nozzle which is provided for supplying lubricant to the piston and which is arranged such that a piston interior space and an inflow opening of the second cooling channel can be sprayed with lubricant by the lubricant pump, andc) a control device of the oil spray nozzle, wherein the control device is designed to selectively activate or deactivate the lubricant pump in a manner dependent on an operating parameter of an internal combustion engine, from which operating parameter the present engine load can be derived.
- A reciprocating-piston internal combustion engine comprising a piston according to any of Claims 1 to 8, characterized in that the reciprocating-piston internal combustion engine has no oil spray nozzle for supplying lubricant to the piston and/or has no oil cooler for cooling the lubricant for the reciprocating-piston internal combustion engine.
- A motor vehicle, in particular utility vehicle, having a piston according to any of Claims 1 to 8.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017130961.6A DE102017130961A1 (en) | 2017-12-21 | 2017-12-21 | Piston for a reciprocating internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3502453A1 EP3502453A1 (en) | 2019-06-26 |
EP3502453B1 true EP3502453B1 (en) | 2021-04-21 |
Family
ID=64572213
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18209823.6A Active EP3502453B1 (en) | 2017-12-21 | 2018-12-03 | Piston for a reciprocating piston combustion engine |
Country Status (2)
Country | Link |
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EP (1) | EP3502453B1 (en) |
DE (1) | DE102017130961A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102020133122B3 (en) | 2020-12-11 | 2022-03-17 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Pistons for an internal combustion engine and method of manufacturing a piston for an internal combustion engine |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB493126A (en) * | 1936-07-23 | 1938-09-30 | Louis Birkigt | Improvements in and relating to liquid circulating means |
DE663733C (en) * | 1937-01-26 | 1938-08-12 | Fried Krupp Germaniawerft Akt | Cooled working piston, especially for compressorless internal combustion engines |
DE726685C (en) * | 1939-09-01 | 1942-10-19 | Versuchsanstalt Fuer Luftfahrt | Pistons for internal combustion engines |
DE102011106559A1 (en) * | 2011-07-05 | 2013-01-10 | Mahle International Gmbh | Piston for an internal combustion engine |
DE102011111319A1 (en) * | 2011-08-26 | 2013-02-28 | Mahle International Gmbh | Piston for an internal combustion engine |
US8662026B2 (en) * | 2012-02-10 | 2014-03-04 | Federal-Mogul Corporation | Piston with supplemental cooling gallery and internal combustion engine therewith |
US9284876B2 (en) * | 2013-03-07 | 2016-03-15 | Ford Global Technologies, Llc | System and method for cooling engine pistons |
JP6171644B2 (en) | 2013-07-12 | 2017-08-02 | マツダ株式会社 | Vehicle control device |
US10202936B2 (en) * | 2015-04-09 | 2019-02-12 | Tenneco Inc. | Zero oil cooled (ZOC) piston incorporating heat pipe technology |
DE102016001926A1 (en) | 2016-02-18 | 2017-08-24 | Man Truck & Bus Ag | Piston for a reciprocating internal combustion engine |
-
2017
- 2017-12-21 DE DE102017130961.6A patent/DE102017130961A1/en not_active Withdrawn
-
2018
- 2018-12-03 EP EP18209823.6A patent/EP3502453B1/en active Active
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DE102017130961A1 (en) | 2019-06-27 |
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