KR102557509B1 - Reciprocating piston internal combustion engine, in particular 2-stroke large diesel engine, and mixing section, in particular mixing pipe line - Google Patents

Abstract

The present invention relates to a reciprocating piston internal combustion engine (1), in particular to a longitudinally cleaned two-stroke-large diesel engine, each having a combustion chamber (2) and a respective discharge valve (3) respectively. It includes a cylinder group (GZ) made up of a plurality of cylinder liners (GZ1, GZ2), and each combustion chamber of the cylinder group (GZ) made up of the cylinder liners (GZ1, GZ2) has one common exhaust gas collection pipe (4). In an operating state, the exhaust gas 5 from each combustion chamber of the cylinder group GZ made up of cylinder liners GZ1 and GZ2 passes through the corresponding discharge valve 3 to the exhaust gas collecting pipe 4. ), and in the washing mode, the exhaust gas 5 from the exhaust gas collection pipe 4 can be supplied into the exhaust gas reactor 6 for treatment. Also provided are supercharging units (7, 71, 72) comprising a first supercharging group (71) for compressing air (80), the exhaust gas (5) from the exhaust gas reactor (6) being cleaned in the cleaning mode. can be supplied to the supercharger unit, so that consequently the air 80 compressed by the first supercharger group 71 is directed to one or a plurality of cylinder liners Z and/or through respective corresponding cleaning air openings. Alternatively, it may be supplied as cleaning air to one or a plurality of cylinder liners of the cylinder liners GZ1 and GZ2 of the cylinder group GZ. According to the invention, the mixing section 12 is, on the one hand, adjacent to the first charging group 71, so that the exhaust gas 5 can be supplied to the exhaust gas reactor 6 via this mixing section 12. and, on the other hand, substantially parallel to the collection tube section 401 of the exhaust gas collection tube 4 at least in a section-wise manner. The invention also relates to a mixing section 12, in particular a mixing pipe line, for a reciprocating piston internal combustion engine 1.

Description

Reciprocating piston internal combustion engines, especially two-stroke large diesel engines, and mixing sections, especially mixing pipe lines

The present invention relates to a reciprocating piston internal combustion engine according to the preamble of the independent claims, in particular to a longitudinally cleaned two-stroke-large diesel engine, and to a mixing section, in particular to a mixing pipe line.

[0002] Large diesel engines of a cross-head construction, such as those used, preferably in ship construction or in stationary installations, for example to generate electrical energy, comprise three large housing segments forming the frame of the engine. On a bottom plate with bearing saddles with crankshaft main bearings for accommodating the crankshaft, a so-called stator separated by this bottom plate is arranged. Known stators face each other, each having one vertically running sliding surface for guiding two neighboring cross heads connected with a crankshaft through a connecting rod, corresponding to the number of cylinders of a large diesel engine. It includes a plurality of support bodies disposed thereon. At this time, each of the two supporting bodies, which run vertically facing each other and have a sliding surface, is further supported by one intermediate wall. The individual support bodies are generally connected to each other by means of a common cover sheet. Then, at the top of the stator, the cover sheet is arranged with a cylinder section, often referred to as a cylinder jacket, which cylinder section is suitable for accommodating a plurality of cylinder liners. At this time, in the stator area, tension anchors, which usually extend inside the supporting body, are screwed in or on the bottom plate under a fairly high prestress, so that the stator and the cylinder section are connected to each other by means of the tension anchor. Connected.

At this time, various types of stators are known which cause different problems with respect to stability and wear, in which case correspondingly optimized solutions are proposed in the prior art.

In order to increase the output of a reciprocating piston internal combustion engine, but not just for this purpose, but in particular for a stator of the type described above, fresh air after the combustion stroke usually contains one or more exhaust gas turbochargers. It is injected into the combustion chamber of the cylinder liner under increased pressure by the supercharged group. At this time, a portion of the thermal energy of the exhaust gas leaving the combustion chamber of the cylinder liner after the combustion stroke can be used. For this purpose, the hot exhaust gases are guided out from the combustion chamber of the cylinder liner of the supercharged group by, for example, opening of a discharge valve provided in the cylinder cover of the cylinder liner. In this case, the supercharge group consists essentially of a turbine driven by heated exhaust gas flowing into the supercharge group under pressure. The turbine drives a compressor on its side, whereby fresh air is drawn in and compressed. Compressor with turbine, i.e. an assembly which, in addition to the designation exhaust gas turbocharger, is frequently also simply referred to as a turbocharger, in particular, but not only so named, but also, in the case of two-stroke-large diesel engines, also embodied as a centrifugal compressor. Behind is connected a so-called diffuser, charge air cooler, water separator and inlet receiver, from which compressed fresh air, also called charge air or scrubbing air, is finally fed into the individual combustion chambers of the cylinder liners of large diesel engines. do. Thus, by using such a supercharging group, the supply of fresh air is increased and the efficiency of the combustion process in the cylinder combustion chamber is increased.

In the case of large diesel engines, the air supply is made at different points in the cylinder liner depending on the type. Thus, in a two-stroke engine with longitudinal cleaning, for example, air is injected into the combustion chamber of the cylinder liner through a cleaning slot arranged inside the running surface in the lower region of the cylinder liner. In small four-stroke engines, charge air is usually injected into the combustion chamber of the cylinder through one or more inlet valves, for example arranged in the cylinder head. In this case, a fully two-stroke engine is also known which is equipped with an inlet valve arranged above the cylinder liner, at the point of the cleaning slot in the lower region of the cylinder liner.

1 is designed as a two-stroke-heavy diesel engine with a longitudinal scrubber, heretofore known in the prior art, in order to facilitate the understanding of the invention, which will be further explained later, hereinafter generally designated by reference numeral 1'. The basic structure of the exhaust gas turbocharger system of a large diesel engine, denoted by , is shown in a schematic diagram to explain the interaction of the different components.

In order to better distinguish the present invention from the prior art, reference numerals for features of examples known in the prior art are each provided with an apostrophe ('), while features of embodiments according to the present invention and Relevant reference numbers do not have an apostrophe.

A large diesel engine 1' basically comprises, in a known manner, usually a cylinder group GZ', which cylinder group has a plurality of cylinder liners GZ1 with discharge valves 3' arranged in a cylinder cover. '), and within this cylinder liner GZ1', the piston K' is arranged such that it can reciprocate between the bottom dead center UT' and the top dead center OT' along the working surface.

The cylinder walls of the cylinder liner GZ1' with cylinder cover and the piston K' limit the combustion chamber 2' of the cylinder liner GZ1' in a known manner.

For reasons of clarifying the overview of the drawing, only one cylinder liner GZ1' is shown as an example in FIG. 1 . It is self-evident that in practice the cylinder group G' comprises a plurality, generally a number of cylinder liners GZ1'.

In the lower region of the cylinder liner GZ1', a plurality of cleaning air openings 9' embodied as cleaning slots are provided. Depending on the position of the piston K', the cleaning slot is either covered or exposed by the piston. Through the cleaning air opening 9', charge air, designated as cleaning air 81', can be introduced into the combustion chamber 2' of the cylinder liner GZ1'. Through the discharge valve 3' disposed in the cylinder cover, the exhaust gas 5' generated during combustion passes through the discharge valve 3' in the open state to the individual combustion chamber 2'. Through the exhaust gas collection pipe 4' coupled with the flow, the exhaust gas flows into the supercharged group 71' formed as a turbocharger.

The exhaust gas turbocharger of the supercharging group 71' is the main component as described above, basically in a known manner, a compressor with a compressor impeller 711' for compressing the air 80' , and a turbine having a turbine impeller 712' for driving a compressor impeller 711', wherein the compressor impeller is operatively rigidly coupled to the turbine impeller 712' in a known manner by means of a shaft. . The turbine and compressor are arranged in one housing, thereby forming an exhaust gas turbocharger, mostly designed as a centrifugal compressor. The turbine is driven in a known manner by the heated exhaust gas 5' entering from the combustion chamber 2' of the cylinder liner GZ1'.

In order to fill the combustion chamber 2' of the cylinder liner GZ1' with the cleaning air 81', the air 80' is sucked in from the surroundings through the suction nozzle by the compressor impeller 711', and the exhaust gas turbocharger compressed within From the exhaust gas turbocharger, the compressed air 80' reaches the inside of the inlet receiver 750' via the water separator 740' by the diffuser 720' and charge air cooler 730' connected thereafter. and, from there, the compressed air 80' is finally passed through the cleaning air opening 9' formed as a cleaning slot, into the combustion chamber 2' of the cylinder liner GZ1' under increased pressure, the cleaning air ( 81').

This principle of charging the engine with charge air by means of one or more turbochargers has been known for a long time for all possible types of engines, and correspondingly also in large two-stroke-long diesel engines with longitudinal cleaning, it has been used for dozens of applications. It has been used successfully for years. In this case, as the development progressed, the geometry and arrangement of the exhaust gas system consisting of the above-mentioned turbocharger system with diffuser, charge air cooler and water separator and the exhaust gas collection pipe were continuously optimized, as a result of which the known The modified exhaust gas system is now also inserted into the entire geometry of the engine in an optimally space-saving form. This fact is particularly decisive for two-stroke-large diesel engines installed inside ships and longitudinally cleaned, since there is basically little space provided in the hull, thereby saving space for the engine components. This is because the decisive role is given to the arrangement state.

However, precisely at this point, recently, a fairly large problem has arisen, which can be traced, among other things, to the increasingly sharpening of exhaust gas regulations, a situation like this that was not at all expected at first.

Due to increasingly stringent exhaust gas regulations, the requirements for exhaust gas quality have been increasing more and more since several years ago, in which case not only the exhaust gas quality, but also the concentration of nitrogen oxides in the exhaust gas in particular are subject to the emission regulations. It is in focus. In this regard, the statutory regulations and limit values for the corresponding exhaust gas limit values are also becoming more and more sharp. This fact has resulted in the combustion of traditional heavy oil containing high levels of hazardous substances, but also of diesel oil or other fuels, is becoming increasingly problematic, especially in two-stroke-heavy diesel engines. This may be because maintaining emission limit values is becoming increasingly difficult, technically more complex and therefore more expensive, or even that maintaining such limit values may ultimately no longer be sensible. Because of fear.

That is why, in practice, for several years now, a great deal of effort has been made in relation to exhaust gas cleaning, the catchword "exhaust gas catalytic converter" and alternative fuels. That is why, in addition or alternatively, for the same reasons, there has long been a need for so-called "dual fuel engines", more specifically for engines that can run on two different fuels. exist. In gas mode, gas, such as natural gas such as liquefied natural gas (LNG), or gas in the form of LP gas (autogas) or other gas suitable for driving an internal combustion engine is burned, while in liquid mode Suitable liquid fuels such as gasoline, diesel, heavy oil or other suitable liquid fuels may be combusted in the same engine. At this time, the engine may be a two-stroke-engine or a four-stroke-engine, in which case a small engine, a medium-to-large engine, but also a large engine, particularly a two-stroke-large diesel engine that is cleaned in the longitudinal direction may also be used.

Therefore, within the framework of the present application, the term "heavy duty diesel engine" means, in addition to traditional two-stroke-heavy duty diesel engines operating on heavy oil or diesel oil, which can operate in diesel mode, characterized by self-ignition of the fuel, as well as fuel Even large engines that can be operated in otto mode, featuring external ignition, or a hybrid of the two. The term heavy-duty diesel engine also includes in particular the aforementioned dual-fuel engines, as well as heavy-duty engines in which ignition of fuel is initiated by external ignition with another fuel.

In liquid mode, fuel is usually injected directly into the combustion chamber of the cylinder by means of an injection nozzle, where it burns according to the self-ignition principle. In the gas mode, it is known to mix a gaseous gas with purge air according to the Otto principle in order to form an ignitable mixture in the combustion chamber of the cylinder. In such a low-pressure method, ignition of the mixture in the cylinder is usually carried out at the exact moment when a small amount of liquid fuel is injected into the combustion chamber of the cylinder or into a pre-chamber which subsequently leads to ignition of the air-gas-mixture. . A dual-fuel engine can switch from gas mode to liquid mode and vice versa during frequent operation.

However, in particular where high emission standards are required which can be maintained economically and rationally with reasonable technical costs only by means of gas combustion, which likewise may be the subject of the present invention described further below, pure gas engines , ie engines which can only be operated on gas, and alternatively cannot be operated on diesel, heavy fuel oil or other fuels.

Regardless of whether it is a twin-fuel engine, a pure gas engine, or an engine that runs on liquid fuel such as gasoline, diesel or heavy fuel oil, or a mixture of the above engine types, in the future, exhaust gases will be emitted to the environment. It will be necessary to clean or treat the exhaust gas with suitable equipment and methods beforehand.

It is known to use an exhaust gas reactor, in particular a so-called "SCR-reactor", in particular to reduce nitrogen oxides contained in the exhaust gas.

At this time, the term SCR is an English abbreviation for "Selective Catalytic Reduction", and as an everyday term, it can be named as a catalytic converter that reduces nitrogen oxides in exhaust gas. However, this catalytic converter does not function as in automobiles, for example with platinum-catalytic converter materials, but rather, as in SCR-reactors, the catalytic converter element is made of ceramic or metal, for example, which catalytic converter element is provided with a special reactive coating. However, the reduction reaction takes place in conjunction with the coating only if the exhaust gases have previously been mixed with suitable chemical substances, such as urea or ammonia, which must be vaporized to ammonia in the exhaust gases, for example.

For such mixing and vaporization, it is known in the prior art to provide a mixing section of a certain length formed as a mixing- and vaporizing tube for mixing and vaporizing the exhaust gases and reactants, such as urea, before the inlet into the SCR-reactor. has been In order to ensure reliable mixing and vaporization, this mixing section has hitherto been arranged in the form of a mixing pipe line between the collection pipe of the exhaust gas pipe and the SCR-reactor with a certain minimum length. However, in solutions known from the prior art, the mixer pipe line of large engines known in the prior art is very much within the hull, since the mixer pipe line extends away from the engine, as will be described more schematically with reference to FIG. 2 below. It occupies a lot of installation space, which hinders compact construction methods.

However, the mixing pipe line itself is not alone in requiring a significant amount of expensive installation space. In large diesel engines with none other than a number of cylinder liners, e.g. 6, 8, 10, 12 or even 14 cylinder liners, often instead of just one supercharged group, two or even two with turbochargers It is absolutely necessary to provide the above supercharged group, and in this case, in the prior art, the entire assembly consisting of the mixing pipe line and the exhaust gas reactor is separately provided for each turbocharger, and this separate provision naturally reduces the installation space. cause excessive additional consumption.

The above problems are addressed with reference to Figure 2, which shows a schematic diagram of a large diesel engine known from the prior art with an exhaust gas collection tube, a mixing tube line, an SCR-reactor and a charge group for the case where there is only one turbocharger. shown as an example. If a plurality of turbochargers is present, the prior art has hitherto provided for each individual turbocharger a separate assembly consisting of a corresponding mixing tube line and an SCR reactor, respectively. This illustration with a plurality of turbochargers has been abandoned herein for spatial reasons, and the entire assembly with a plurality of turbochargers is presented in a simplified form from FIG. 2 , especially for the person skilled in the art.

Figure 2 shows a known large diesel engine 1' with a mixing section 12' in the form of an exhaust gas collecting pipe 4' and a mixing pipe line 121', in this case in this mixing pipe line. In, for example, urea vaporized into ammonia in the exhaust gas 5' and the exhaust gas 5' are mixed. As already mentioned above, for reliable mixing and vaporization of exhaust gas 5' and urea, as shown in the drawing, in front of the inlet into the SCR-reactor, the mixing section formed as a mixing- and vaporization tube ( 12') and together with this a constant minimum length of the mixing pipe line 121' must be ensured. In order to be able to maintain a minimum length of such a mixing pipe line 121' between the exhaust gas collecting pipe 4' and the SCR-reactor 6', in the large diesel engine according to FIG. 2 known in the prior art, Mixer pipe line 121' initially extends away from the engine through connecting member 122', so that, as a result, there is sufficient space to maintain the requisite minimum length of mixer pipe line 121'.

The fact that can be immediately seen from schematic FIG. 2 without further explanation is that the exhaust gas 5' flowing into the mixing pipe line 121' from the exhaust gas collection pipe 4' by this structure and the reliability of the elements That is, adequate mixing and vaporization were ensured. But, on the other hand, a structure like this requires, among other things, a space of basically unacceptable size, which is not provided in the hull or could otherwise be better utilized.

At the same time, such a structure also has other problematic properties, which a person skilled in the art can recognize without much difficulty. In other words, one major problem known is that when operating very large engines such as those above, which can often have powers up to 10,000 KW per cylinder, or even more than 10,000 KWs, they are induced to the periphery or such engines Vibration induced into installed attachment components. In this case, recently known marine engines often have, for example, 12 or even up to 14 cylinders, which in working condition are directed into the hull and, among other things, also exhaust-, catalytic converter-with supercharged groups. and powerful vibrations can be induced even inside components installed in the engine, such as a turbocharger system, resulting in large-scale damage to the hull and such components if suitable countermeasures, such as vibration compensators, are not provided. It can be damaged or even destroyed. However, in such a freely supported structure of the SCR-catalytic converter system according to FIG. 2 , known vibration compensators are often no longer sufficient to permanently prevent damage to such a structure.

However, by means of additional pipe line members, and for example a connecting member 122' or in the large diesel engine of FIG. 2, for example between the mixing pipe line 121' and the SCR-reactor 6' and between the A longer exhaust gas flow path connected to the pipe line members by other additional connecting members, such as those provided between (6') and the charge group 71', is also basically undesirable and results in unnecessary material consumption. In addition to this, other negative technical effects arise, such as, for example, a temperature and/or pressure drop of the exhaust gases 5' in the pipe line system, which in turn reduces the output of the turbocharger and is known to the person skilled in the art. Naturally undesirable, it leads to a series of other negative technical impacts that should be avoided wherever possible.

The object of the present invention, departing from the prior art, is to provide an improved engine, in particular a crosshead-heavy diesel engine with an exhaust gas catalytic converter system, in particular an SCR-reactor, in this case a diesel engine known in the prior art. Disadvantages are avoided, in particular a maximum space-saving arrangement of the exhaust gas system and a shortening of the flow path length between the discharge valve of the cylinder liner and the charge group with the turbocharger are achieved. Another object of the present invention is to provide a reciprocating piston internal combustion engine, in particular a two-stroke heavy-duty diesel engine, in which propellant savings can be achieved under comparable load conditions and exhaust emissions can be reduced overall.

The objects of the invention which solve the above problems are characterized by having the features of the independent claims.

The dependent claims relate to particularly preferred embodiments of the invention.

The dependent claims relate to particularly preferred embodiments of the invention.

Accordingly, the present invention relates to a reciprocating piston internal combustion engine, in particular a two-stroke-large diesel engine with longitudinal cleaning, comprising a cylinder group consisting of a plurality of cylinder liners, each with one combustion chamber and each with a corresponding discharge valve, In this case, each combustion chamber of the cylinder group of cylinder liners is fluidly coupled with one common exhaust gas collection pipe, so that in the operating state the exhaust gases from each combustion chamber of the cylinder group of cylinder liners open each corresponding discharge valve. It can be supplied to the exhaust gas collection pipe through the exhaust gas collection pipe, and in the cleaning mode, the exhaust gas from the exhaust gas collection pipe can be supplied to the inside of the exhaust gas reactor for treatment. Furthermore, there is provided a supercharging unit comprising a first supercharging group for compressing air, wherein the exhaust gas from the exhaust gas reactor can be supplied to the supercharging unit in a cleaning mode, whereby the first supercharging group Air compressed by the cleaning air can be supplied as cleaning air to one or a plurality of cylinder liners and/or to one or a plurality of cylinder liners of the cylinder liners of the cylinder group through respective corresponding cleaning air openings. According to the invention, the mixing section extends on the one hand in a region adjacent to the first supercharging group, and on the other hand in the exhaust gas collecting pipe, so that exhaust gases can be supplied to the exhaust gas reactor via this mixing section. It extends substantially parallel to the collection tube section, at least in section fashion.

An important fact for the present invention is therefore that the mixing section extends on the one hand in a region adjacent to the first supercharging group, and on the other hand, so that the exhaust gas can be supplied to the exhaust gas reactor through the mixing section. that it extends substantially parallel, at least in a sectional fashion, with the collecting duct section of the duct.

To put it more simply, between the exhaust gas turbocharger of the supercharging group and the exhaust gas collection tube, a mixing section is provided according to the invention, particularly preferably in the form of a mixing pipe line, in which the exhaust gas Exhaust gas coming from the collection tube is mixed or vaporized with the reactants, in particular urea or ammonia, and then passed to the exhaust gas reactor.

Unlike engines hitherto known from the prior art, in which at least one mixing section had to be provided separately for each exhaust gas reactor, which even caused excessive additional consumption of installation space as described above, in the present invention by, especially large diesel engines with multiple cylinder liners, for example 6, 8, 10, 12 or even 14 cylinder liners, operated by two or more supercharged groups each with one exhaust gas turbocharger In a particularly preferred embodiment, it is possible for the first time to provide only one exhaust gas reactor and only one mixing pipe line, to which the treated exhaust gases are then distributed to the supercharging groups.

At this time, even in one particular embodiment in which a plurality of mixing sections or mixing pipe lines must be provided for a specific reason, it is obvious that much more installation space is secured by the present invention, because under the exhaust gas collection pipe or This is because hitherto unused space under the collector section is utilized according to the present invention for at least part of the length of the mixing section.

In other words, in a special case, in an engine according to the invention, first of all in an engine with a plurality of cylinder liners, naturally, for a specific reason, for example, two or more exhaust gas reactors or two or more exhaust gas reactors consisting of a mixing tube line and an exhaust gas reactor. It is also possible that an assembly is provided.

Thus, according to the present invention, since the number of exhaust gas reactors or the number of assemblies composed of mixing tube lines and exhaust gas reactors can be reduced to an absolute minimum on the one hand, not only can a great deal of installation space be saved, but also the most In an advantageous case, only another exhaust gas reactor or just another assembly consisting of a mixing tube line and an exhaust gas reactor need only be provided. Rather, significant savings in installation space are achieved only if the mixing pipe section, in particular the mixing pipe line, is arranged according to the invention very compactly between the supercharger group with the turbocharger and the exhaust gas collecting pipe.

However, furthermore, a series of other above-mentioned problems known in the prior art are further and simultaneously eliminated by the present invention.

Thus, in the assembly according to the invention, the above-mentioned problems associated with vibrations induced by the engine in operation are significantly reduced, and this situation results, among other things, from the compact design. Thus, according to the present invention, due to the structure based on the compact arrangement and compact configuration of the entire exhaust gas system, the exhaust gas collection pipe, the exhaust gas reactor with the mixing pipe line, the supercharging group and the exhaust gas distributor line are The risk that the exhaust system, including the equipped turbocharger system, is damaged by induced vibrations is significantly reduced, as a result of which in the engine according to the invention, vibrations induced in the components of the exhaust system or the entire exhaust In order to reduce the vibrations induced in the gas system, it is no longer necessary to take additional measures, since such a situation is already reached automatically, so to speak, due to structural conditions.

The compact arrangement and structure of the exhaust gas system according to the invention, among other things, also has another positive result, that the aforementioned additional pipe line elements are no longer needed in the exhaust system and can therefore be saved. In this way, the longer path of the exhaust gas flow, which is known in the prior art and which is naturally undesirable, is avoided by the present invention. This not only saves material for additional tube line elements that are no longer needed, but also reliably avoids other negative technical effects resulting from unnecessarily long paths in the exhaust gas system known from the prior art. . Thus, for example, the temperature and/or pressure drop of the exhaust gases in the exhaust system is significantly reduced, which improves the output of the turbocharger, which in turn also saves propellant, for example under comparable load conditions. emissions are also reduced overall, which ultimately has positive effects for the surrounding environment.

At this time, the fact that there are no additional pipe line members also improves the vibration characteristics as well, because the absence of additional pipe line members makes the overall structure and arrangement of the exhaust gas system more compact and, in turn, vibration technically is also stronger, as a result of which the induced vibrations are better compensated or even cannot be absorbed at all by the exhaust system or its components, further reducing the possibility of damage.

In one particularly preferred embodiment to be practiced, the reciprocating piston internal combustion engine is a large engine, in particular a longitudinally cleaned two-stroke-large diesel engine, wherein the mixing section or mixing tube line is at least in a sectional manner generally directly below the exhaust gas collection tube. To be more specific, between the first supercharge group and the second supercharger group on the one hand and between the first supercharge group and the exhaust gas collection pipe on the other hand, and adjacent to one of the cylinder liners in the vertical direction are placed appropriately.

In this way, the length of the supply line leading to the exhaust gas turbochargers, in particular of the supercharging group, has been significantly shortened, providing for a horizontal gallery in the engine, through which later, for example, service personnel and other persons can move on the engine; Valuable space provided for service work or other duties is saved. Besides, at least part of the pressure loss is avoided by the shortened pipe line, and also the natural frequency of the exhaust gas installation, in particular of the exhaust gas collection pipe, is positively influenced, whereby the material for these components is Savings are made and costs are reduced only by this.

In one embodiment that is important for implementation, the exhaust gas collection tube is supported by a guide element in the form of a guide box and is fixed to the reciprocating piston internal combustion engine.

At this time, the guide box,

It is formed as a connecting section and fluidly coupled with the mixing section so that the exhaust gas can be supplied to the mixing section through this guide box in the cleaning mode. Particularly preferably, the guide box or the connecting section additionally comprises a connecting valve, so that in bypass mode, that is to say in a mode other than cleaning mode, the exhaust gas flow from the exhaust gas collecting tube into the mixing section is interrupted. do.

In this case, the mixing section is integrated at least in a section manner, preferably completely into the exhaust gas collection pipe, preferably parallel to the exhaust gas collection pipe as a mixing pipe line parallel to the collection pipe section and/or exhaust Since the gas collection pipe itself is formed as a mixing section, even more valuable installation space can be secured. Thereby, as mentioned above, much more valuable space is of course reserved, and consequently material consumption and cost can be further minimized.

In this case, in practice, one or more second charge groups are provided for compressing the air in addition to the first charge group, and exhaust gases from the exhaust gas reactor can be supplied to the charge groups in cleaning mode, so that consequently air compressed by the first charge group and the second charge group as cleaning air to one or a plurality of cylinder liners and/or to one or a plurality of cylinder liners of the cylinder liners of the cylinder group through respective corresponding cleaning air openings. can be supplied.

In another embodiment of the present invention which is particularly important for implementation, the exhaust gas distribution line is such that the exhaust gas from the exhaust gas reactor can be supplied to the first and second supercharging groups through the exhaust gas distributor line. , adjacent to one cylinder liner in the region between the first and second supercharge groups on the one hand and between the first supercharge group and the exhaust gas collection pipe on the other hand, and the internal combustion engine is substantially connected to the crankshaft. are placed parallel to each other. Expressed more simply, between the exhaust gas turbocharger of the supercharging group and the exhaust gas collection tube, according to the invention, an exhaust gas distributor line can be provided which distributes the treated exhaust gas coming from the exhaust gas reactor to the turbocharger. Thereby, even in large engines, particularly two-stroke-large diesel engines with longitudinal cleaning, it is advantageous to distribute the treated exhaust gas coming from the same exhaust gas reactor to a plurality of supercharging groups or to the exhaust gas turbochargers of these supercharging groups. efficient for the first time.

In another embodiment of the invention, which is better matched to stationary internal combustion engines depending on the circumstances, the exhaust gas distributor line is also placed before the turbochargers, more specifically, in the vertical direction, the first and second supercharging groups. It can be arranged at the height of the group, in which case the first charge group and the second charge group are arranged between the exhaust gas distributor lines and adjacent to one of the cylinder liners.

Preferably, the length of the exhaust gas distributor line at this time is such that, relative to the exhaust gas collection pipe, the exhaust gas distributor line can be flowably connected to all corresponding exhaust gas turbochargers in a straight line, but otherwise the length of the exhaust gas distributor line is It can be shortened so as not to exceed the limits of the assembly of turbochargers.

In another embodiment, it is also possible that the mixing section is integrated at least in a sectional manner, but preferably also completely into the exhaust gas reactor, or the exhaust gas reactor and the exhaust gas distributor line form one common integral component. Formation is also possible.

In this case, the exhaust gas collection pipe, the mixing section, the exhaust gas reactor and the exhaust gas distributor line can in particular or even be embodied in the form of a common integrated component, which component preferably comprises on the one hand the first supercharger group and on the other hand. It extends substantially parallel to the crankshaft of the internal combustion engine in a region adjacent to the second supercharged group and on the other hand in a region adjacent to the cylinder liners.

Of course, in practice, for example, when a vessel equipped with an engine according to the invention is sailing in an area where correspondingly strict exhaust gas regulations do not apply, the exhaust gas reactor often does not need to be continuously operated, so that consequential Alternatively, it may be desirable to temporarily disable the exhaust gas reactor, eg for economic reasons or eg for the purpose of carrying out maintenance work.

As such, preferably, the exhaust gases can be supplied to the corresponding charge group or turbocharger for delivery bypassing the exhaust gas reactor of the exhaust gas distributor line, that is to say that the exhaust gases pass through the bypass line to the exhaust gas reactor A bypass line can be arranged and provided so that the exhaust gas no longer flows through the exhaust gas reactor as a result. For this purpose, a bypass line can be provided, for example, between the exhaust gas collection pipe and the exhaust gas distributor line.

The bypass line itself may be provided to be blocked by, for example, a bypass valve. In this case, the bypass line itself may be preferably formed as a bypass valve, although this is not necessarily the case. In other words, the bypass valve functions as a bypass line, a situation such as this may be particularly advantageous if, for example, the exhaust gas distributor line is arranged in the immediate vicinity of the exhaust gas collection pipe, for example parallel to the exhaust gas collection pipe. .

At this time, of course, the exhaust gas collection pipe can also be blocked by the exhaust gas collection pipe valve, and in this case, the blocking of the exhaust gas collection pipe is not necessary, as described above, in this operating state. It is made so that the exhaust gases from can no longer be supplied to the exhaust gas reactor. Also for this purpose, the exhaust gas distributor line can be blocked by means of an exhaust gas distributor valve, so that exhaust gases from the exhaust gas reactor can no longer be supplied to the exhaust gas distributor line.

In another embodiment of the present invention, the exhaust gas collection pipe is such that the exhaust gas from the first assembly of cylinder liners can be directly supplied only to the first exhaust gas collection chamber, and the second assembly of cylinder liners It may include a first exhaust gas collection chamber and a second exhaust gas collection chamber fluidly coupled with the first exhaust gas collection chamber so that exhaust gas from the exhaust gas can be directly supplied only to the second exhaust gas collection chamber, Compensating elements for compensating mechanical and/or thermal stresses and/or expansions are particularly preferably provided between the first exhaust gas collecting chamber and the second exhaust gas collecting chamber.

In this way, not only can eg thermal expansion or other types of mechanical stresses, eg vibrations, be better compensated, but also the distribution of the exhaust gas flow in the exhaust gas collecting pipe can be optimized thereby, Mutual influences of the exhaust gas streams from the various cylinder liners simultaneously connected to the gas collecting pipe can also be prevented or minimized at least as a whole.

Very similarly, the exhaust gas distributor line may also include a first exhaust gas distributor chamber and a second exhaust gas distributor chamber in flow coupling with the first exhaust gas distributor chamber, wherein the exhaust gas from the exhaust gas collection tube is passed through the first exhaust gas distributor chamber. Through the bypass line or the first bypass valve, only the first exhaust gas distributor chamber can be supplied directly, and the exhaust gas from the exhaust gas collection pipe is only supplied through the second bypass line or the second bypass valve. It can be fluidly coupled with the exhaust gas collection pipe so that it can be directly supplied only to the second exhaust gas distributor chamber.

In one particularly preferred variant of the embodiment according to the present invention introduced above, the exhaust gas from the first exhaust gas collection chamber of the exhaust gas collection pipe passes through the first bypass line or through the first bypass valve only to the first It is directly supplied only to the exhaust gas distributor chamber, and the exhaust gas from the second exhaust gas collection chamber of the exhaust gas collection pipe is directly supplied only to the second exhaust gas distributor chamber through the second bypass line or through the second bypass valve. do.

At this time, in each corresponding embodiment, a compensating connection may be provided between the first exhaust gas distributor chamber and the second exhaust gas distributor chamber, preferably for compensating for mechanical and/or thermal stress and/or expansion. As a result, not only eg thermal expansion or other types of mechanical stresses, eg vibrations, can be better compensated, but also the distribution of the exhaust gas flow in the exhaust gas distributor line can be optimized as a result, Mutual influences of the exhaust gas streams from the various exhaust gas collecting tubes simultaneously connected to the distributor line can also be prevented or minimized at least as a whole.

At this time, naturally, in a similar way, also the mixing section, in particular the mixing tube line, may include a first mixing chamber and a second mixing chamber, and between the first mixing chamber and the second mixing chamber, mechanical and/or thermal Compensation lines may be provided to compensate for stress and/or expansion.

that the connection valve and/or the bypass valve, in particular the first bypass valve and/or the second bypass valve and/or the exhaust gas collector valve and/or the exhaust gas distributor valve, can also be controlled or adjusted; It is self-evident that it can be controlled or adjusted according to the predetermined operating parameters of the reciprocating piston internal combustion engine, in particular electrically or hydraulically or pneumatically, particularly preferably by means of a computer-controlled installation. do.

For this purpose, in particular, for example, in a known manner, a sensor, in particular an exhaust gas sensor, a temperature sensor, a pressure sensor, or a bypass valve, in particular a first bypass valve and/or a second bypass valve and/or an exhaust gas collecting pipe It is also possible that other sensors suitable for controlling or regulating the valve and/or the exhaust gas distributor valve are suitably provided.

In order to further optimize the flow of the exhaust gas, an exhaust gas collection pipe, in particular the first exhaust gas collection chamber and/or the second exhaust gas collection chamber, is provided in a line device, in particular for guiding and distributing the exhaust gas within the exhaust gas collection pipe. It may comprise a line sheet, in particular for the purpose of distributing the exhaust gas to different sections of the exhaust gas distributor line, in particular for the purpose of distributing the exhaust gas to the first exhaust gas distributor chamber and the second exhaust gas distributor chamber of the exhaust gas distributor line. Sheets may be included.

Very similarly and with a similar purpose, an exhaust gas distributor line, in particular a first exhaust gas distributor chamber and/or a second exhaust gas distributor chamber, is of course also a redirecting device, in particular for redirecting and distributing exhaust gases within the exhaust gas distributor line. diverting seats for the purpose of distributing the exhaust gases to the different exhaust gas turbochargers of the charging unit, in particular to the first and second charging groups of the charging unit; , in this case also a blind, in particular a controllable or adjustable blind, can be provided in the discharge line as shown, so that the gas flow can be controlled or regulated by means of this blind.

For fastening, the exhaust gas collecting pipe and/or the mixing section, in particular the mixing pipe line and/or the exhaust gas distributor line, is preferably, but need not, supported and/or guided by one common guide element. , in which case this guide element is preferably a guide plate, guide box or other suitable guide- or fixing device for fixing and guiding the exhaust gas collection pipe and the exhaust gas distributor line.

In this case, it is very particularly advantageous in practice to guide elements such that even mechanically and/or thermally induced stresses and/or expansions or vibrations of the exhaust gas collection tube and the exhaust gas distributor line or other mechanical components can be at least partially compensated for. is formed, and an exhaust gas collection pipe and/or a mixing section, in particular a mixing pipe line and/or an exhaust gas distributor line, is arranged in this guide element.

Particularly preferably, guide elements, in particular guide plates and/or for compensating and/or equalizing mechanically and/or thermally induced stresses and/or expansions and/or vibrations of the exhaust gas collecting pipe and the exhaust gas distributor line, and/or Alternatively, the guide box may be movably disposed inside a sliding shoe.

The present invention also relates to a mixing section, in particular a mixing pipe line, for a reciprocating piston internal combustion engine according to the invention described in this application, in which case the mixing pipe section of the present invention is in one particular embodiment an exhaust gas collection pipe and/or or a combined mixing section that may include an exhaust gas distributor line and/or an exhaust gas reactor.

The invention is explained in detail below with reference to the drawings. In the schematic drawing:

1 schematically shows an exhaust gas turbocharger system known from the prior art for two-stroke-heavy diesel engines;
2 shows a known large diesel engine with an SCR-reactor for treating exhaust gases;
Fig. 3a shows a first embodiment of a two-stroke-large diesel engine according to the present invention in a perspective view with a mixing pipe line under the exhaust gas collecting pipe;
Fig. 3b shows a side view of the embodiment according to Fig. 3a;
Fig. 3c shows a third view of the embodiment according to Fig. 3a;
Figure 4 shows a schematic second embodiment of a two-stroke-large diesel engine according to the present invention having a guide box formed of a connecting section with connecting valves;
Fig. 5 shows a second embodiment according to Fig. 4;
6 shows an embodiment of a two-stroke-heavy duty diesel engine according to the present invention with a mixing tube line under the collector tube section;
7 shows an exhaust gas collecting pipe or an exhaust gas distributor line and a compensating element or compensating connection;
Fig. 8a shows a first embodiment of an exhaust gas collecting pipe with a blind and a line device for exhaust gas;
Fig. 8b shows another embodiment according to Fig. 8a;
Fig. 8c shows a third embodiment according to Fig. 8a;
FIG. 9a shows a first embodiment of an exhaust gas distributor line with a blind and a diverting device for the exhaust gas; FIG.
Fig. 9b shows another embodiment according to Fig. 9a;
Fig. 9c shows a third embodiment according to Fig. 9a;
10 shows a guide element with a sliding shoe, an exhaust gas collection tube and a mixing tube section.

1 and 2 relate to examples known from the prior art, which need not be discussed again in this part, since they have already been described in detail in the introduction.

The reciprocating piston internal combustion engine according to the present invention, designated hereinafter as a whole by reference numeral (1), is designed in particular as a two-stroke, longitudinally-cleaned, heavy-duty diesel engine, such as is widely used, for example, in ship construction.

Referring to Figures 3a, 3b and 3c, a first embodiment of a two-stroke-large diesel engine according to the present invention with a mixing tube line under the exhaust gas collection tube is shown in a perspective view in Figure 3a, these drawings Important to the present invention of a reciprocating piston internal combustion engine according to the present invention, in the particular embodiment of a two-stroke-heavy diesel engine with a plurality of cylinder liners and longitudinally cleaned, for use on a ship, for example a container ship, show the parts At this time, FIG. 3B is only a side view of the engine according to FIG. 3A to help understanding the interaction of the main components, and FIG. 3C is only a front view.

The reciprocating piston internal combustion engine according to the present invention shown in FIG. 3a or FIGS. 3b and 3c is a longitudinally cleaned two-stroke-large diesel engine, which engine has in a known manner each one combustion chamber 2 and each one a cylinder group (GZ) of a plurality of cylinder liners (GZ1, GZ2) with corresponding discharge valves (3) of which, in this case, each combustion chamber (2) of the cylinder group (GZ) of cylinder liners (GZ1, GZ2) In the operating state, the exhaust gas 5 coming out of each combustion chamber 2 of the cylinder group GZ of the cylinder liners GZ1 and GZ2 passes through each corresponding discharge valve 3 to the exhaust gas collection pipe 4 It is fluidly coupled with one common exhaust gas collection pipe 4 so that it can be supplied to the For treatment or cleaning, that is to say in practice to remove hazardous nitrogen oxides from the exhaust gas 5, the exhaust gas 5 from the exhaust gas collection tube 4 is transported, in cleaning mode, to a mixture formed by the mixing tube line. Exhaust gas may be supplied into the reactor 6 via section 12.

In addition, a first supercharged group 71 and a second supercharged group 72 for compressing the air 80 sucked from the surroundings by one turbocharger of the supercharged group 71 and the supercharged group 72, respectively. In this case, the exhaust gas 5 from the exhaust gas reactor 6 is compressed by the first supercharger group 71 and the second supercharger group 72 in the washing mode. Supercharge group so that air 80 can be supplied as cleaning air to cylinder liner Z or cylinder liners GZ1 and GZ2 of cylinder group GZ through corresponding cleaning air openings not shown in FIGS. 3A to 3C , respectively. (71, 72) can be supplied.

At this time, in the example of FIGS. 3A to 3C, two assemblies consisting of a mixing tube line 121, an exhaust gas reactor 6 and a supercharger group 7, 71, 72 are shown as an example, and these are shown for efficient operation. It is absolutely necessary in this case because of the number of cylinder liners (Z) for

According to the invention, the mixing section 12 is, on the one hand, adjacent to the first supercharging group 71, so that the exhaust gas 5 can be supplied to the exhaust gas reactor 6 via said mixing section 12. and, on the other hand, substantially parallel to the collection tube section 401 of the exhaust gas collection tube 4 at least in a section-wise manner.

At this time, the mixing section 12 is based on the vertical direction VR of the reciprocating piston internal combustion engine 1 on the one hand the exhaust gas collection pipe 4 and on the other hand the crankshaft of the reciprocating piston internal combustion engine 1 ( 11), it extends substantially parallel to the exhaust gas collection pipe 4 at least in a section manner. At this time, the mixing section 12 is arranged so that the exhaust gas 5 can be supplied to the exhaust gas reactor 6 via the mixing section 12 and is provided inside the exhaust gas facility, in which case the mixing section ( 12) is formed in the form of a mixing pipe line 121 between the exhaust gas collection pipe 4 and the exhaust gas reactor 6.

4 and 5, a schematic second embodiment of a two-stroke-large diesel engine according to the present invention having a guide box 142 formed as a connection section 130 with a connection valve V130 is provided below. are discussed

4 and 5 show a guide box 142 formed as a connecting section 130 hereinafter, and these guide boxes are respectively formed as a mixing pipe line 121 and a mixing section 121 and the exhaust gas collection pipe 4 A connection valve (V130) is included therebetween. In this embodiment, which is particularly preferred to be implemented, the mixing pipe line 121 is disposed directly below the exhaust gas collection pipe 4 of the guide box 142, and in this case, the connection valve V130 is simultaneously connected to the guide box 142. ) in the connection section 130, and this formation is particularly space-saving, since additional connection lines are thereby essentially eliminated. At this time, the exhaust gas collection pipe 4 has an exhaust gas collection pipe valve ( 40) can be blocked.

In addition, the exhaust gas distributor line 10 is connected to the exhaust gas distributor valve 100 so that the exhaust gas 5 from the exhaust gas collecting pipe 4 can no longer be supplied directly to the exhaust gas distributor line 10. can be blocked by In other words, if the exhaust gas reactor 6 is not needed in one specific operating state of the reciprocating piston internal combustion engine 1 or is shut down for other reasons, the exhaust gas collector valve 40 is closed simultaneously with the exhaust gas distributor valve. By opening (10), the exhaust gas reactor (6) and the mixing section (12) can be separated from the exhaust gas system, so that the exhaust gas (5) is drawn directly from the exhaust gas collection tube (4) into the guide box (142). ) and the exhaust gas distributor line 10 to the turbochargers of the supercharged groups 7, 71, 72, which are likewise not shown in FIG. 5 for the purpose of clarifying the drawing.

In the particular embodiment shown in FIG. 6 , the mixing section 12 is integrated in the form of a mixing pipe line 121 into the exhaust gas collecting pipe 4 below the collecting pipe section 401 . At this time, the exhaust gas 5 can be supplied directly to the mixing section 12 via the flow-through valve DV, or by closing the flow-through valve DV during the bypass mode and the exhaust gas collecting pipe valve 40 ) can be supplied to the charge groups 7, 71, 72 directly through the exhaust gas distributor line 10, if present.

7 shows in a schematic way an exhaust gas distributor line 10 and an exhaust gas collection tube 4 with a compensating element 400 or a compensating connection 500, in this case in order to clarify the overview of the drawing. For this reason, the mixing section 12 , 121 , which can run eg parallel to the exhaust gas collecting pipe 4 and/or parallel to the exhaust gas distributor line 10 , is not clearly shown.

At this time, the exhaust gas distributor line 10 passes the exhaust gas 5 from the exhaust gas reactor 6 to the first supercharged group 71 and the second supercharged group 72 through the exhaust gas distributor line 10. The crankshaft of the internal combustion engine 1 (not shown in FIG. 11), and on the other hand, in the lower portion of the exhaust gas collection pipe 4, the exhaust gas collection pipe 4 and the crankshaft (with respect to the vertical direction VR of the reciprocating piston internal combustion engine 1) 11) is placed between them. In a particular embodiment, the exhaust gas distributor line 10 is directed in the vertical direction VR between the first charging group 71 and the second charging group 72 on the one hand and the first charging group on the other hand. It is disposed between the group 71 and the exhaust gas collection pipe 4 and adjacent to one of the cylinder liners Z, GZ1, GZ2.

In this particularly preferred embodiment, according to FIG. 7 , an exhaust gas collection pipe 4 and an exhaust gas distributor line 10 are provided, in which case the exhaust gas collection pipe 4 and the exhaust gas distributor line 10 are provided. ) has one compensating member 400 or one compensating connector 500 for compensating for mechanical or thermal stress or other failures. At this time, in the exhaust gas collection pipe 4, the exhaust gas 5 from the first combination EZ1 of the cylinder liner Z can be directly supplied only to the first exhaust gas collection chamber 41, and the cylinder liner The first exhaust gas collection chamber 41 and this first exhaust gas so that the exhaust gas 5 from the second combination EZ2 of (Z) can be directly supplied only to the second exhaust gas collection chamber 42. and a second exhaust gas collection chamber 42 fluidly coupled with the collection chamber 41 .

At this time, as already mentioned above, between the first exhaust gas collecting chamber 41 and the second exhaust gas collecting chamber 42, mechanical and/or thermal stress and/or expansion and/or vibration or other mechanical Alternatively, a compensating member 400 for compensating for thermal failure is provided.

In addition, the exhaust gas distributor line 10 includes a first exhaust gas distributor chamber 101 and a second exhaust gas distributor chamber 102 fluidly coupled with the first exhaust gas distributor chamber 101, and collects exhaust gases. The exhaust gas 5 from the pipe 4 can be directly supplied only to the first exhaust gas distributor chamber 101 through the first bypass valve 1311, and the exhaust gas from the exhaust gas collecting pipe 4 can be supplied directly. It is fluidly connected to the exhaust gas collecting tube 4 so that the gas 5 can be directly supplied only to the second exhaust gas distributor chamber 102 via the second bypass valve 1312 . At this time, the exhaust gas 5 from the first exhaust gas collection chamber 41 of the exhaust gas collection pipe 4 is directly supplied only to the first exhaust gas distributor chamber 101 through the first bypass valve 1311. The exhaust gas 5 from the second exhaust gas collection chamber 42 of the exhaust gas collection pipe 4 passes through the second bypass valve 1312 only to the second exhaust gas distributor chamber 102. can be supplied directly. Similar to the exhaust gas collection pipe 4, between the first exhaust gas distributor chamber 101 and the second exhaust gas distributor chamber 102 there is mechanical and/or thermal stress and/or expansion and/or vibration and/or Alternatively, a compensating connection 500 is provided to compensate for other mechanical or thermal disturbances.

At this time, the bypass valve 131, the first bypass valve 1311 and / or the second bypass valve 1312 in this embodiment and / or the exhaust gas collection pipe valve 40 not clearly shown in the drawing and/or the exhaust gas distributor valve 100, which is likewise not explicitly shown in the drawing, is particularly preferably controllable or adjustable, in particular electrically or hydraulically or pneumatically controllable or embodied to be adjustable. For this purpose also sensors, in particular exhaust gas sensors, temperature sensors or pressure sensors, or bypass valves 131, in particular first bypass valves 1311 and/or second bypass valves 1312 and/or exhaust Other sensors suitable for controlling or regulating the gas collection pipe valve 40 and/or the exhaust gas distributor valve 100 may suitably be provided.

Referring to FIG. 8a , another particularly advantageous first embodiment of an exhaust gas collecting pipe 4 with a line device 15 , 151 for the exhaust gas 5 is schematically shown, in this case controllable. As a result, the gas flow can be controlled or regulated by means of this blind B. FIG. 8B shows another embodiment according to FIG. 8A, while referring to FIG. 8C, a third embodiment according to FIG. 8A is illustrated.

As can be seen from FIGS. 8A to 8C , the exhaust gas collection pipe 4 , in particular the first exhaust gas collection chamber 41 and/or the second exhaust gas collection chamber 42 is a line device 15 , 151 , in particular a line sheet 151 for guiding and distributing the exhaust gases 5 within the exhaust gas collecting pipe 4, in particular for distributing the exhaust gases 5 to different sections of the exhaust gas distributor line 10. For this purpose, it includes a line sheet specifically for distribution to the first exhaust gas distributor chamber 101 and the second exhaust gas distributor chamber 102 of the exhaust gas distributor line. A person skilled in the art will know which of the embodiments according to FIGS. 7a to 7c can be used for practice, or whether simple non-inventive improvements of these embodiments can be used for practice, as the case may be. It can be simply determined from one's own expertise and can be applied to specific real-world situations.

Here, FIG. 9a shows a first embodiment of an exhaust gas distributor line 10 with diverter devices 16 , 161 for the exhaust gases 5 , in this case a controllable or adjustable blind B is provided, consequently the gas flow can be controlled or regulated by means of this blind (B).

FIG. 9B shows another embodiment according to FIG. 9A, while referring to FIG. 9C, a third embodiment according to FIG. 9A is illustrated. At this time, the exhaust gas distributor line 10, in particular the first exhaust gas distributor chamber 101 and/or the second exhaust gas distributor chamber 102, the redirection device 16, 161, in particular the exhaust gas distributor line 10 for redirecting and distributing the exhaust gases 5 in the vehicle, in particular to the different exhaust gas turbochargers of the charging unit 7, i.e. the first charging group 71 of the charging unit 7 and a direction turning sheet 161 for distributing to the second supercharging group 72. A person skilled in the art will know which of the embodiments according to FIGS. 9a to 9c can be used for practice, or whether simple non-inventive improvements of these embodiments can be used for practice, as the case may be. It can be simply determined from one's own expertise and can be applied to specific real-world situations.

FIG. 10 shows by way of example a special embodiment of a guide element 14 , 141 , which is particularly important for the last implementation, by means of which the exhaust gas collector 4 as well as the exhaust gas distributor line 10 can also preferably be jointly fixed to the engine, in which case the exhaust gas collection pipe 4 and the exhaust gas distributor line 10 are supported and/or supported by one common guide element 14, 141. be a guide By means of additional guide elements 14 , 141 the exhaust gas collection pipe 4 is better secured to the engine together with the exhaust gas distributor line 10 , eg thermal expansion is better compensated and the vibration characteristics are better are markedly improved under the action of vibration.

In this case, the guide elements 14 , 141 according to FIG. 10 can occur not only in the thermal expansion of the exhaust gas collection pipe and/or the exhaust gas collection line 10 , but also in a very wide range, for example in operating conditions of a reciprocating piston internal combustion engine. It is formed in the form of a guide plate 141 that is particularly well suited to absorbing or compensating for other mechanical loads or disturbances, such as mechanical vibrations. In this case, not only the thermal expansion or vibration of the exhaust gas collection pipe 4 or the exhaust gas collection line 10 in the longitudinal direction, but also the thermal expansion or vibration in the direction perpendicular to this direction can be compensated. This compensation is possible in particular by realizing the guide plate as a relatively thin plate and by means of a special geometrical shape that can be matched to the individual situation. At this time, mechanically and/or thermally induced stress and/or expansion and/or vibration of the exhaust gas collection pipe 4 and the exhaust gas distributor line 10 shown in FIG. 10 are compensated for and/or evenly. The guide elements 14 and 141, in particular, the guide plate 141 and/or the guide box 142 may be movably disposed inside the sliding shoe 1400.

A person skilled in the art understands that the present invention is not limited to the explicitly discussed embodiments, but rather that corresponding refinements are likewise covered by the present invention. In particular, the invention pertains to all suitable combinations of the discussed embodiments as well.

Claims (36)

As a reciprocating piston internal combustion engine,
a cylinder group (GZ) consisting of a plurality of cylinder liners (GZ1, GZ2), each having a combustion chamber (2) and a corresponding discharge valve (3), each comprising a cylinder consisting of said cylinder liners (GZ1, GZ2); Each combustion chamber 2 of the group GZ is fluidly coupled with one common exhaust gas collection pipe 4, so that in the operating state each combustion chamber 2 of the cylinder group GZ consists of cylinder liners GZ1 and GZ2. ) is supplied to the exhaust gas collecting pipe (4) through the respective discharge valve (3), and in the cleaning mode, the exhaust gas (5) from the exhaust gas collecting pipe (4) is discharged for treatment. is supplied into the exhaust gas reactor 6, and a supercharging unit 7, 71, 72 including a first supercharging group 71 for compressing air 80 is provided, and the exhaust gas reactor 6 ) is supplied to the supercharger unit in the cleaning mode, so that the air 80 compressed by the first supercharger group 71 passes through each corresponding cleaning air opening to one or a plurality of cylinder liners. supplied as cleaning air to (Z) and/or to one or a plurality of cylinder liners of the cylinder liners (GZ1, GZ2) of the cylinder group (GZ);
The mixing section 12 extends in a region adjacent to the first supercharging group 71 so that the exhaust gas 5 is supplied to the exhaust gas reactor 6 via the mixing section 12, and the exhaust gas collecting pipe ( extends at least partially parallel to the collecting tube section 401 of 4);
The mixing section 12 is at least partially between the exhaust gas collecting pipe 4 and the crankshaft 11 of the reciprocating piston internal combustion engine in the vertical direction VR of the reciprocating piston internal combustion engine. A reciprocating piston internal combustion engine, characterized in that it extends parallel to (4). delete According to claim 1,
The reciprocating piston internal combustion engine, wherein the mixing section (12) is formed as a mixing pipe line (121). According to claim 1,
The exhaust gas collecting pipe 4 is supported by guide elements 14, 142 in the form of a guide box 142 and is fixed to the reciprocating piston internal combustion engine, the guide box 142 having the exhaust gas 5 ) is formed as a connecting section (130) and fluidly connected with the mixing section (12), so that the mixing section (12) is supplied through the guide box (142) in the cleaning mode. According to claim 4,
By the guide box 142 or the connection section 130 including the connection valve V130, the exhaust gas flow from the exhaust gas collection pipe 4 into the mixing section 12 is stopped in the bypass mode, Reciprocating piston internal combustion engine. delete According to claim 1,
In addition to the first charge group 71, at least one second charge group 72 is provided for compressing the air 80, the exhaust gas 5 from the exhaust gas reactor 6 is directed to the above-mentioned charge group in the cleaning mode. By being supplied to the charge groups, the air 80 compressed by the first charge group 71 and the second charge group 72 passes through respective cleaning air openings to one or a plurality of cylinder liners Z , and supplied as cleaning air to at least one of one or a plurality of cylinder liners of cylinder liners GZ1 and GZ2 of cylinder group GZ. According to claim 1,
The exhaust gas distributor line 10 is such that the exhaust gas 5 from the exhaust gas reactor 6 is supplied to the first supercharge group 71 and the second supercharge group 72 through the exhaust gas distributor line 10. , which extends parallel to the crankshaft 11 of the reciprocating piston internal combustion engine in an area at least partially adjacent to the first supercharged group 71 and the second supercharged group 72 and follows the vertical direction VR of the reciprocating piston internal combustion engine. A reciprocating piston internal combustion engine, extending between the exhaust gas collecting tubes (4) as a reference. According to claim 8,
The exhaust gas distributor line 10 is disposed between the supercharger unit including the first supercharger group 71 and the second supercharger group 72 and the exhaust gas collection pipe 4 based on the vertical direction VR, A reciprocating piston internal combustion engine. According to claim 8,
The exhaust gas distributor line 10 is disposed at the height of the first supercharging group 71 and the second supercharging group 72 based on the vertical direction VR, and the first supercharging group 71 and the A reciprocating piston internal combustion engine in which two charge groups (72) are disposed between the exhaust gas distributor lines (10) and adjacent to the cylinder liners (Z, GZ1, GZ2). According to claim 1,
The reciprocating piston internal combustion engine, wherein the mixing section (12) and the exhaust gas reactor (6) at least partially form one integral unit. According to claim 8,
The reciprocating piston internal combustion engine, wherein the exhaust gas reactor (6) and the exhaust gas distributor line (10) form one common integral component. According to claim 8,
The exhaust gas collecting pipe 4, the mixing section 12, the exhaust gas reactor 6 and the exhaust gas distributor line 10 are provided in the form of one common integrated component, and the integrated component extends parallel to the crankshaft 11 of the internal combustion engine in a region adjacent to the first supercharged group 71 and the second supercharged group 72 and to one of the cylinder liners GZ1, GZ2, Z. , a reciprocating piston internal combustion engine. According to claim 1,
A reciprocating piston internal combustion engine in which a bypass line (13) is arranged and provided so that the exhaust gas (5) bypasses the exhaust gas reactor (6) and is supplied to the supercharging unit (7, 71, 72). According to claim 14,
The bypass line (13) is provided between the exhaust gas collection pipe (4) and the exhaust gas distributor line (10). According to claim 14,
A reciprocating piston internal combustion engine, wherein the bypass line (13) is blocked by a bypass valve (131). According to claim 16,
The reciprocating piston internal combustion engine, wherein the bypass line (13) is formed as a bypass valve (131). According to claim 1,
The exhaust gas collection pipe (4) is blocked by the exhaust gas collection pipe valve (40) so that the exhaust gas (5) from the exhaust gas collection pipe (4) is no longer supplied to the exhaust gas reactor (6). Reciprocating piston internal combustion engine. According to claim 1,
The reciprocating exhaust gas distributor line 10 is blocked by the exhaust gas distributor valve 100 so that the exhaust gas 5 from the exhaust gas reactor 6 is no longer supplied to the exhaust gas distributor line 10. piston internal combustion engine. According to claim 8,
The exhaust gas collecting pipe 4 is such that the exhaust gas 5 from the first combination EZ1 of cylinder liners Z is directly supplied only to the first exhaust gas collecting chamber 41, and the cylinder liner Z the first exhaust gas collecting chamber 41 and the first exhaust gas collecting chamber 41 so that the exhaust gas 5 from the second combination of EZ2 is directly supplied only to the second exhaust gas collecting chamber 42 A reciprocating piston internal combustion engine comprising a second exhaust gas collecting chamber (42) fluidly coupled with a second exhaust gas collection chamber (42). According to claim 20,
A compensating member 400 is provided between the first exhaust gas collecting chamber 41 and the second exhaust gas collecting chamber 42 to compensate for at least one of mechanical, thermal, mechanical and thermal stress and expansion. A reciprocating piston internal combustion engine. According to claim 20,
The exhaust gas distributor line 10 includes a first exhaust gas distributor chamber 101 and a second exhaust gas distributor chamber 102 fluidly coupled with the first exhaust gas distributor chamber 101, and collects exhaust gas. The exhaust gas 5 from the pipe 4 is directly supplied only to the first exhaust gas distributor chamber 101 through the first bypass valve 1311, and the exhaust gas 5 from the exhaust gas collection pipe is A reciprocating piston internal combustion engine, fluidly coupled with the exhaust gas collecting pipe (4), so that it is directly supplied only to the second exhaust gas distributor chamber (102) through two bypass valves (1312). The method of claim 22,
Exhaust gas 5 from the first exhaust gas collection chamber 41 of the exhaust gas collection pipe is directly supplied only to the first exhaust gas distributor chamber 101 through the first bypass valve 1311, and the exhaust gas 5 A reciprocating piston internal combustion engine in which the exhaust gas 5 from the second exhaust gas collection chamber 42 of the gas collection tube is directly supplied only to the second exhaust gas distributor chamber 102 through the second bypass valve 1312 . The method of claim 22,
A compensation connection 500 is provided between the first exhaust gas distributor chamber 101 and the second exhaust gas distributor chamber 102 to compensate for at least one of mechanical, thermal, mechanical and thermal stress and expansion. A reciprocating piston internal combustion engine. According to claim 1,
The mixing section 12 includes a first mixing chamber 1201 and a second mixing chamber 1202, and between the first mixing chamber 1201 and the second mixing chamber 1202, mechanical or thermal A reciprocating piston internal combustion engine, wherein a compensation line (600) is provided for compensating at least one of mechanical and thermal stress and expansion. According to claim 16,
A reciprocating piston internal combustion engine in which the connection valve (V130) and/or the bypass valve (131) is regulated. The method of claim 26,
The reciprocating piston internal combustion engine is provided with a sensor for regulating the connection valve (V130) and/or the bypass valve (131). According to claim 1,
The reciprocating piston internal combustion engine, wherein the exhaust gas collecting pipe (4) comprises a line device (15, 151) for guiding and distributing the exhaust gas (5) within the exhaust gas collecting pipe (4). According to claim 8,
A reciprocating piston internal combustion engine, wherein the exhaust gas distributor line (10) comprises a redirecting device (16, 161) for redirecting and distributing exhaust gas (5) within the exhaust gas distributor line (10). According to claim 28,
A reciprocating piston internal combustion engine, wherein an adjustable blind (B) is provided, such that the gas flow is regulated by means of the blind (B). According to claim 8,
A reciprocating piston internal combustion engine, wherein the exhaust gas collection pipe (4) and/or the mixing section (12) are supported and/or guided by one common guide element (14, 141). According to claim 31,
The reciprocating piston internal combustion engine, wherein the guide element (14, 141) is a guide plate (141) or a guide box (142). According to claim 31,
the guide element (14, 141) such that at least one of the mechanical, thermal or mechanically and thermally induced stresses and expansions of the exhaust gas collecting pipe (4) and the exhaust gas distributor line (10) are at least partially compensated. ) is formed, and the exhaust gas collection pipe (4) and the mixing section (12) are arranged on the guide element. According to claim 31,
At least one of mechanical, thermal, mechanical and thermally induced stress, expansion and vibration of the exhaust gas collection pipe 4 and the exhaust gas distributor line 10 is compensated, equalized, compensated and equalized. A reciprocating piston internal combustion engine in which guide elements (14, 141) for driving are movably disposed inside a sliding shoe (1400). delete delete

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