KR20160041821A - 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), and more specifically, two-stroke large diesel engine. The engine comprises a cylinder group (GZ) composed of a plurality of cylinder liners (GZ1, GZ2) having one combustion chamber (2) and one corresponding discharge valve (3) individually. Exhaust gas (5) discharged from an exhaust gas collection pipe (4) can be supplied into an exhaust gas reactor (6) in a washing mode. Moreover, provided is supercharging units (7, 71, 72) comprising a first supercharging group (71) and a second supercharging group (72) for compressing air.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating piston internal combustion engine, particularly a two-stroke large-size diesel engine, and a mixing section, particularly a mixing pipe line.

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

A large diesel engine of the crosshead configuration, such as is used for generating electrical energy, for example in a ship structure or in a stationary facility, comprises three large housing segments forming the frame of the engine. A so-called stator, separated by the bottom plate, is disposed on a bottom plate having bearing saddles with crankshaft main bearings for receiving crankshafts. Known stator assemblies have a number of sliding surfaces, each corresponding to the number of cylinders of a large diesel engine, each of which has one sliding surface that advances vertically to guide two adjacent crosshead heads connected to the crankshaft via a connecting rod, And a plurality of support bodies disposed. At this time, the two support bodies each having the sliding surface proceed vertically while facing each other are further supported by one intermediate wall. The individual support bodies are generally connected to one another by a common cover sheet. Next, the cover sheet at the top of the stator is provided with a cylinder section which is also frequently referred to as a cylinder jacket, which cylinder section is suitable for accommodating a plurality of cylinder liners. At this time, a tension anchor, which is very generally in the stator area extending inside the support body, is screwed in the bottom plate or under a considerably large pre-stress in the bottom plate, so that the stator and cylinder sections .

At this time, various types of stator 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 the reciprocating piston internal combustion engine, but not only for this purpose but also for the stator of the type described above in particular, fresh air after the combustion stroke generally comprises one or more exhaust gas turbochargers Lt; RTI ID = 0.0 > liner < / RTI > At this time, a part 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, hot exhaust gases are guided out of the combustion chamber of the cylinder liner of the supercharging group, for example by opening of the discharge valve provided in the cylinder cover of the cylinder liner. Wherein the supercharging group consists essentially of a turbine driven by the heated exhaust gas entering the supercharging group under pressure. The turbine drives the compressor on its side, so that fresh air is sucked and compressed. In addition to the name of a compressor with a turbine, that is to say an exhaust gas turbocharger, it is often named as a turbocharger simply and in particular, but also in the case of a two-stroke-large diesel engine as well as a centrifugal compressor A so-called diffuser, a supercharging air cooler, a water separator and an inlet receiver are connected, from which compressed fresh air, also referred to as supercharging air or cleaning air, is finally fed into the individual combustion chambers of the cylinder liners of large diesel engines do. Therefore, 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, air is supplied at different points in the cylinder liners depending on the type. Thus, for example, in a two-stroke engine that is cleaned in the longitudinal direction, air is injected into the combustion chamber of the cylinder liner through a cleaning slot disposed in the working surface in the lower region of the cylinder liner. In a small four stroke engine, boost air is typically injected into the combustion chamber of the cylinder through one or more inlet valves, for example, disposed in the cylinder head. In this case, a fully two-stroke-engine with an inlet valve arranged above the cylinder liner at the point of the clearing slot in the lower region of the cylinder liner is also known.

1 is formed as a two-stroke-large diesel engine with longitudinal decanter so far known in the prior art to facilitate further understanding of the invention to be described in the following, The basic structure of an exhaust gas turbocharger system of a large diesel engine is shown in a schematic view for explaining the interaction of different components.

In order to better distinguish the present invention from the prior art, apostrophe (') is provided for each of the features of the examples known in the prior art, while the features of the embodiments according to the present invention Related references do not have apostrophes.

The large diesel engine 1 'basically includes a cylinder group GZ' in a known manner, and this cylinder group is divided into a plurality of cylinder liner GZ1 'having a discharge valve 3' The piston K 'is arranged in the cylinder liner GZ1' so as to reciprocate between the bottom dead center UT 'and the top dead center OT' along the operating surface.

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

For the sake of clarity of the drawing, only one cylinder liner GZ1 'is shown in Fig. 1 as an example. In practice, it is clear that the cylinder group G 'includes a plurality of, generally, a plurality of cylinder liners GZ1'.

In the lower region of the cylinder liner GZ1 ', a plurality of cleaning air openings 9' implemented as cleaning slots are provided. Depending on the position of the piston (K '), the cleansing slot is covered or exposed by the piston. Through the cleaning air opening 9 ', the supercharging air, which is referred to as the cleaning air 81', can be introduced into the combustion chamber 2 'of the cylinder liner GZ1'. The exhaust gas 5 'generated at the time of combustion is discharged from the individual combustion chamber 2' through the discharge valve 3 'while the discharge valve 3' is opened through the discharge valve 3 ' Into the supercharging group 71 'formed as an exhaust gas turbocharger through the exhaust gas collecting pipe 4' which is fluidly coupled with the exhaust gas collecting pipe 4 '.

The exhaust gas turbocharger of the supercharging group 71 'is a main component, as described above, in a manner known per se in the art, including a compressor impeller 711' for compressing the air 80 ' And a turbine impeller 712 'for driving the compressor impeller 711', wherein the compressor impeller is operatively tightly connected to the turbine impeller 712 'in a manner known by the shaft . The turbine and the compressor are arranged in one housing, thereby forming an exhaust gas turbocharger, which is mostly formed as a centrifugal compressor. The turbine is driven in a known manner by the heated exhaust gas 5 'flowing from the combustion chamber 2' of the cylinder liner GZ1 '.

The air 80 'is sucked from the periphery through the suction nozzle by the compressor impeller 711' to fill the combustion chamber 2 'of the cylinder liner GZ1' with the cleaning air 81 ' Lt; / RTI > From the exhaust gas turbocharger the compressed air 80 'is introduced into the inlet receiver 750' via the water separator 740 'by the diffuser 720' and the boost air cooler 730 ' From which the compressed air 80 'is introduced into the combustion chamber 2' of the cylinder liner GZ1 'under the increased pressure through the clean air opening 9', which is finally formed into the cleansing slot, 81 '.

This principle of supercharging the supercharged air to the engine using one or more turbochargers has long been known for all possible types of engines and correspondingly also in the longitudinally cleaned two-stroke-heavy diesel engines, It has been successfully used for years. In this case, as the development progresses, the geometry and arrangement of the exhaust gas system comprising the turbocharger system and the exhaust gas collecting tube described above, with the diffuser, the supercharging air cooler and the water separator, have been continuously optimized, Exhaust system is now also inserted into the entire geometry of the engine in a very space-saving and optimal form. This is particularly crucial in a two-stroke-large diesel engine, which is installed inside the ship and is cleaned in the longitudinal direction, because essentially little space is provided in the hull and thus space- This is because a decisive role is given to the arrangement state.

But precisely in this regard, there has been a considerable amount of difficulty in finding the cause in recent years, especially in the fact that exhaust gas regulations become increasingly more acute than anything else, and this situation was unexpected at first.

Due to increasingly stringent exhaust gas regulations, the requirements for exhaust gas quality have been increasing steadily over the years, in which case the concentration of nitrogen oxides in the exhaust gas, notably the exhaust gas quality, It is in focus. At this point, legal regulations and limit values for the corresponding exhaust gas limits are also becoming increasingly acute. This fact has resulted in the burning of traditional heavy oil, which contains a high level of harmful substances, but also the combustion of diesel oil or other fuels increasingly problematic, especially in two-stroke-heavy diesel engines The reason is that maintaining the exhaust gas limit becomes increasingly difficult, technologically more complicated, and therefore pricing becomes more expensive, or that even maintaining such a limit will ultimately no longer be reasonable It is because of fear.

For this reason, a great deal of effort related to exhaust gas cleaning, namely the "exhaust gas catalytic converter" catchword and alternative fuels, have been practiced for several years in practice. That is to say, in other words, additionally or alternatively, for the same reason, the need for an engine which has long been already known as a so-called "dual fuel engine ", in more detail, exist. In the gas mode, gases such as natural gas such as LNG (liquefied natural gas) or LP gas (autogas) or other gases suitable for driving an internal combustion engine are 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-sized engine, but also a large engine, especially a two-stroke-large diesel engine that is cleaned in the longitudinal direction may also be used.

Thus, in the framework of the present application, the term "large diesel engine" not only can be operated in diesel mode, which is characterized by the self-ignition of the fuel, in addition to the traditional two stroke- Or even a large engine that can be operated in an otto mode or a mixture of two such modes. In addition, the term large-size diesel engine also encompasses especially the above-described dual-fuel engine, and large engines in which ignition of the fuel is initiated by external ignition by other fuels.

In the liquid mode, fuel is usually injected directly into the combustion chamber of the cylinder by the injection nozzle, where it is burned in accordance with the principle of self-ignition. In the gas mode, it is known to mix gaseous gases with clean air in accordance with the auto principle in order to form a combustible mixture in the combustion chamber of the cylinder. In such a low-pressure method, ignition of the mixture in the cylinder is typically injected into the interior of the combustion chamber of the cylinder at a precise moment, or into the interior of the reserve chamber, which in turn leads to ignition of the air-gas mixture . The dual fuel engine can be switched from gas mode to liquid mode and vice versa during frequent operation.

However, particularly when a high exhaust gas standard, which can be economically and reasonably maintained at reasonable technical costs solely by gas combustion, and which can likewise be the object of the present invention, which is likewise described further below, is desired, , That is, engines that can only be operated with gas only, or alternatively can not be operated with diesel, heavy oil or other fuels.

Whether it is a dual fuel engine, a pure gas engine, or an engine that operates with liquid fuel such as gasoline, diesel or heavy oil, or whatever mixed type of engine types described above, in the future, The process of cleaning or treating the exhaust gas with suitable equipment and methods will be necessary before.

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

At this time, the term SCR is an English abbreviation for " Selective Catalytic Reduction ", and as a usual term, it can be named as a catalytic converter for reducing nitrogen oxides in the exhaust gas. However, this catalytic converter does not function as, for example, in a car with a platinum-catalytic converter material, rather, as in an SCR-reactor, the catalytic converter element is made of, for example, ceramic or metal, A special reactive coating is provided. However, the reduction reaction occurs in association with the coating only when the exhaust gas has previously been mixed with a suitable chemical substance such as ammonia or an element that must be vaporized with ammonia in the exhaust gas in advance.

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 gas with reactants such as urea in front of the inlet to the SCR- . In order to ensure reliable mixing and vaporization, so far this mixing section has been arranged with a predetermined minimum length between the exhaust gas collection tube and the SCR-reactor in the form of a mixing tube line. However, in the solution known in the prior art, the mixing line of the large engine, as known in the prior art, is very close in the hull because the mixing tube line extends away from the engine as will be described in greater detail below with reference to FIG. Occupies a large amount of installation space, thereby hindering a compact configuration method.

However, the mixing line alone does not require a significant amount of expensive installation space. In a large number of cylinder liners, for example large diesel engines with six, eight, ten, twelve or even fourteen cylinder liners, there are often two or even two with a turbocharger instead of one supercharging group It is necessary to provide the above-mentioned supercharging groups. In this case, in the prior art, for the respective turbochargers, the entire assembly consisting of the mixing line and the exhaust gas reactor is provided separately, Causing excessive additional consumption.

The above-mentioned problems can be solved by referring to the schematic FIG. 2 showing a prior art large diesel engine with an exhaust gas collection line, mixing line, SCR-reactor and supercharging group for the case where only one turbocharger is present Is shown as an example. In the case of a plurality of turbochargers, in the prior art, one separate assembly of the mixing line and the SCR-reactor has been provided for each individual turbocharger to date. Such a city with a plurality of turbochargers has been abandoned here for spatial reasons, and in particular a complete assembly with a plurality of turbochargers for those skilled in the art is schematically illustrated in FIG.

Figure 2 shows a known large diesel engine 1 'with a mixing section 12' in the form of an exhaust gas collecting tube 4 'and a mixing tube line 121' The exhaust gas 5 'is mixed with the exhaust gas 5', for example, an element which is vaporized by ammonia in the exhaust gas 5 '. As already mentioned above, in order to reliably mix and vaporize the exhaust gas 5 'and the elements, it is necessary to introduce a mixing section (as shown in the figure) in front of the inlet into the SCR- 12 'and a certain minimum length of the mixing tube line 121' must be ensured. In the large diesel engine according to FIG. 2 known in the prior art, in order to be able to maintain the minimum length of such mixing line 121 'between the exhaust gas collection pipe 4' and the SCR-reactor 6 ' There is sufficient space to maintain the essential minimum length of the mixing tube line 121 'as a result of the mixing tube line 121' initially extending through the connecting member 122 'and away from the engine.

2, the exhaust gas 5 'flowing into the mixing pipe line 121' from the exhaust gas collecting pipe 4 'and the exhaust gas 5' flowing into the mixing pipe line 121 ' It is guaranteed to be mixed and vaporized. On the other hand, however, such a structure requires a space of essentially unacceptable size, which is not provided in the hull, among other things, or can be utilized better in other ways.

At this time, such a structure also has other problematic characteristics that can be recognized by a person skilled in the art without difficulty. In other words, one major problem known is that the engine can be driven to the periphery when operating such a very large engine, which can have an output of up to 10,000 KW per cylinder or even an output of more than 10,000 KW, It is the vibration that is induced into the installed attachment components. In this case, recently known marine engines have, for example, up to 12 or even up to 14 cylinders, which, in the operating state, are connected to the inside of the hull and, above all, And turbocharger systems, the result is that even if appropriate countermeasures such as, for example, vibration compensators are not provided, the hull and such components can be used in large scale It can be damaged or even destroyed. However, in the structure of the SCR-catalytic converter system according to FIG. 2, which is freely supported as described above, the known vibration compensating air is often no longer sufficient to permanently prevent damage of such a structure.

However, additional tube line members and, for example, a connecting member 122 'or in a large diesel engine of FIG. 2, for example between mixing line 121' and SCR-reactor 6 ' A longer exhaust gas flow path connected to the tube line members by other additional connecting members such as those provided between the heating element 6 'and the supercharging group 71' is basically undesirable and unnecessary material consumption As well as other negative technical effects such as, for example, temperature and / or pressure drop of the exhaust gas 5 'in the line system, which eventually reduces the output of the turbocharger and is known to those skilled in the art Which, of course, leads to a series of other negative technical effects that should be avoided as much as possible.

It is an object of the present invention, starting from the prior art, to provide an improved engine, particularly a crosshead-heavy diesel engine with an exhaust gas catalytic converter system, in particular an SCR-reactor, The disadvantages are avoided, in particular the maximum space saving arrangement of the exhaust system, and the reduction of the flow path length between the supercharging group with the turbocharger and the discharge valve of the cylinder liner is achieved. A further object of the present invention is to provide a reciprocating piston internal combustion engine, especially a two stroke-large diesel engine, which can save propellant under equivalent load conditions and overall reduce exhaust emissions.

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 present invention.

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

Accordingly, the present invention relates to a reciprocating piston internal combustion engine, particularly a longitudinally cleaned two-stroke-large diesel engine, comprising a cylinder group consisting of a plurality of cylinder liners each having one combustion chamber and one respective corresponding discharge valve, In this case, each of the combustion chambers of the cylinder group made of the cylinder liner is fluidly coupled with one common exhaust gas collecting pipe, so that the exhaust gas from each combustion chamber of the cylinder group made up of the cylinder liner in the operating state, And in the cleaning mode, the exhaust gas from the exhaust gas collection tube can be supplied into the exhaust gas reactor for processing. Further, there is provided a supercharging unit including a first supercharging group for compressing air, and exhaust gas from the exhaust gas reactor can be supplied to the supercharging unit in the cleaning mode, The compressed air can be supplied to one or a plurality of cylinder liners through respective respective cleaning air openings and / or as clean air to one or more cylinder liners of the cylinder liners of the cylinder group. According to the present invention, the mixing section extends in the region adjacent to the first supercharging group, on the one hand, so that the exhaust gas can be supplied to the exhaust gas reactor via this mixing section, and on the other hand, Extends substantially parallel to the collection tube section at least in section fashion.

Therefore, an important fact of the present invention is that the mixing section extends in the region adjacent to the first supercharging group on the one hand so that the exhaust gas can be supplied to the exhaust gas reactor through the mixing section, Extends substantially parallel to the collection tube section of the tube at least in section fashion.

More concretely, a mixing section in the form of a mixing section, particularly preferably a mixing tube line, is provided between the exhaust turbocharger of the supercharging group and the exhaust gas collecting tube according to the invention, in which the exhaust gas The exhaust gas from the collection tube is mixed with the reactants, in particular urea or ammonia, or vaporized and then delivered to the exhaust gas reactor.

Unlike the engines so far known in the prior art, which had to be provided separately at least one mixing section for each exhaust gas reactor, which caused excessive additional consumption of the installation space as described above, A large number of cylinder liners, for example six, eight, ten, twelve or even fourteen cylinder liners, operated by two or more supercharging groups, each with one exhaust gas turbocharger, It is for the first time possible to provide only one exhaust gas reactor and a single mixing line which are distributed to the supercharging group after the treated exhaust gas has exited in a particularly preferred embodiment.

It will be appreciated that, in certain embodiments, much more space is provided by the present invention, as long as a plurality of mixing sections or mixing tube lines must be provided, even for a particular reason, The unused space below the collection tube section is utilized according to the present invention because at least a portion of the mixing section length is utilized.

In other words, in a special case, in an engine according to the present invention, among others, an engine with a plurality of cylinder liners will naturally have, for a certain reason, two or more, for example two or more exhaust gas reactors or mixing line and exhaust gas reactors It is also possible that an assembly is provided.

As a result, according to the present invention, the number of exhaust gas reactors or the number of assemblies constituted by the mixing pipe line and the exhaust gas reactor can be reduced to an absolute minimum value, so that not only a great amount of installation space can be saved, If advantageous, only one further assembly of exhaust gas reactors or mixing line and exhaust gas reactors need be provided. Rather, the installation space is significantly saved, even if the mixing tube sections are arranged very compactly according to the invention, in particular between the supercharging group with the turbocharger and the exhaust gas collecting tube.

Yet further, the above-described series of other problems known in the prior art are additionally removed simultaneously by the present invention.

Therefore, in the assembly according to the present invention, the above-mentioned problems associated with the vibration induced by the engine in the operating state have been remarkably reduced, and this situation is ultimately due to a more compact construction method than anything else. Thus, according to the present invention, an exhaust gas collecting tube, an exhaust gas reactor with a mixing tube line, a supercharging group and an exhaust gas distributor line The risk of damage to the exhaust system including the turbocharger system equipped with the turbocharger is greatly reduced and consequently in the engine according to the present invention the vibration induced in the components of the exhaust system or the total exhaust In order to reduce the vibrations induced in the gas system, there is no need to take any further action, because structural conditions already exist and are automatically reached in this situation.

The compact arrangement and construction of the exhaust system according to the invention also results in another positive result that, among other things, the additional tube line members described above can be saved in the exhaust gas system, which is no longer necessary. Thereby, a longer path of the exhaust gas flow known in the prior art and of course not desirable is avoided by the present invention. This not only saves material for additional tube line members that are no longer needed, but also other negative technical effects that result from unnecessarily long paths in the exhaust gas system known in the prior art are reliably avoided . Thus, for example, the temperature- and / or pressure drop of the exhaust gas occurring in the exhaust gas system is significantly reduced, and this situation improves the output of the turbocharger, thereby eventually saving the propulsion system, And exhaust emissions are reduced overall, and this situation ultimately has positive effects for the surrounding environment.

At this time, the fact that there are no additional pipe line members likewise improves the vibration characteristics, because the absence of additional pipe line members makes the overall structure and arrangement of the exhaust gas system more compact and, eventually, Is further strengthened and as a result the induced vibration can be compensated for even better, or even less, by the inability to be absorbed at all by the exhaust gas system or the components of the exhaust gas system.

In one embodiment which is particularly preferred in the practice, the reciprocating piston internal combustion engine is a large engine, in particular a two-stroke-large diesel engine which is cleaned in the longitudinal direction, and the mixing section or mixing line is at least sectioned, On the one hand, between the first supercharging group and the second supercharging group on the one hand, and between the first supercharging group and the exhaust collecting tube on the one hand, and between the first supercharging group and the second supercharging group on the other, Respectively.

Thereby, the length of the supply line, which extends to the exhaust turbocharger of the supercharging group in particular, has been significantly shortened and is later provided for a horizontal gallery in the engine, for example a service staff and others can be moved on the engine, Important space provided for service work or other tasks is saved. In addition, at least a portion of the pressure loss is avoided by the shortened tube line, and the natural frequency of the exhaust system, in particular the natural frequency of the exhaust gas collection tube, is also positively influenced thereby providing a material for such components Only the cost is reduced by this.

In one embodiment 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,

In order to supply the exhaust gas to the mixing section through the guide box in the cleaning mode, it is a type of connection section and is fluidly coupled with the mixing section. Particularly preferably, the guide box or connection section further includes a connection valve, so that in the bypass mode, that is, in the non-cleaning mode, the exhaust gas flow from the exhaust gas collection tube into the mixing section is interrupted do.

At this time, the mixing section is integrated in parallel at least in a section manner, preferably entirely inside the exhaust gas collection tube, preferably in the mixing tube line parallel to the collection tube section and / Since the gas collecting tube itself is formed as a mixing section, a much more valuable installation space can be secured. Thereby, as mentioned above, a much more valuable space is naturally secured, and eventually the material consumption and cost can be further minimized.

At this time, in fact, in addition to the first supercharging group, at least one second supercharging group is provided for compressing the air, and the exhaust gas from the exhaust gas reactor can be supplied to the supercharging groups in the cleaning mode, Air compressed by the first supercharging group and the second supercharging group is supplied to one or more cylinder liners through respective corresponding cleaning air openings and / or to the one or more cylinder liners of the cylinder liners of the cylinder group Can be supplied.

In another embodiment of the present invention that is particularly important for implementation, the exhaust gas distribution line may be such that the exhaust gas from the exhaust gas reactor is supplied to the first supercharging group and the second supercharging group through the exhaust gas distributor line On the one hand, in a region between the first supercharging group and the second supercharging group, and on the other hand in the region between the first supercharging group and the exhaust gas collecting tube, adjacent to one cylinder liner and with the internal combustion engine substantially in contact with the crankshaft And are arranged in parallel. Briefly stated, an exhaust gas distributor line may be provided between the turbocharger and the exhaust gas collecting tube of the supercharging group, according to the present invention, for distributing the treated exhaust gas from the exhaust gas reactor to the turbocharger. Thus, even in a large engine, especially a two-stroke-large diesel engine that is cleaned in the longitudinal direction, it is advantageous to distribute the treated exhaust gas, which is discharged from the same exhaust gas reactor, to a plurality of supercharging groups or exhaust turbochargers of these supercharging groups It is efficient for the first time.

In another embodiment of the present invention, where the situation is better matched to a fixed internal combustion engine, the exhaust gas distributor line is also placed in front of the turbocharger, more specifically, in the vertical direction with respect to the first supercharging group and the second supercharging Group, where the first supercharging group and the second supercharging group are disposed between the exhaust gas distributor lines and next to one of the cylinder liners.

Preferably, the length of the exhaust gas distributor line here is such that the exhaust gas distributor line can be in flow connection with all corresponding exhaust turbochargers in a straight line, relative to the exhaust gas collection tube, but otherwise the length of the exhaust gas distributor line May be shortened so as not to exceed the limit of the assembly of turbochargers.

In yet another embodiment, it is also possible that the mixing section is integrated at least in a section manner, but preferably also entirely inside the exhaust gas reactor, or that the exhaust gas reactor and the exhaust gas distributor line have a common integrated component It is of course possible to form.

At this time, the exhaust gas collection tube, the mixing section, the exhaust gas reactor, and the exhaust gas distributor line may be particularly implemented in the form of one common integrated component, which preferably comprises a first supercharging group Extends substantially parallel to the crankshaft of the internal combustion engine in the region adjacent to the second supercharging group and on the other hand in the region adjacent to the cylinder liners.

Of course, in practice, for example, when a ship equipped with an engine according to the present invention is navigating an area to which the corresponding strict exhaust gas regulations do not apply, it is often the case that the exhaust gas reactor does not need to continue to operate, It may be desirable not to operate the exhaust gas reactors temporarily, for example for economic reasons or for the purpose of carrying out, for example, management operations.

Therefore, preferably, the exhaust gas can be supplied to the corresponding supercharging group or the turbocharger for transfer by bypassing the exhaust gas reactor of the exhaust gas distributor line, that is, the exhaust gas is supplied to the exhaust gas reactor The bypass line can be arranged and provided so that the exhaust gas no longer flows through the exhaust gas reactor. For this purpose, a bypass line may be provided, for example, between the exhaust gas collection line and the exhaust gas distributor line.

The bypass line itself may be provided, for example, to be blocked by a bypass valve, in which case the bypass line itself is not necessarily required but may be formed as a bypass valve, preferably according to an embodiment. In other words, the bypass valve functions as a bypass line, and this situation may be preferable in particular when, for example, the exhaust gas distributor line is disposed in the immediate vicinity of the exhaust gas collecting tube, for example in parallel with the exhaust gas collecting tube .

At this time, of course, the exhaust gas collecting pipe can also be blocked by the exhaust gas collecting pipe valve. In this case, when the exhaust gas cleaning or the treatment of the exhaust gas is not necessarily required in this operating state, So that the exhaust gas from the exhaust gas can no longer be supplied to the exhaust gas reactor. Also for this purpose, the exhaust gas distributor line may be blocked by an exhaust gas distributor valve so that the exhaust gas 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 tube may be configured such that the exhaust gas from the first assembly (Ensemble) of the cylinder liners can be fed directly into only the first exhaust gas collection chamber, The first exhaust gas collection chamber and the second exhaust gas collection chamber in fluid communication with the first exhaust gas collection chamber so that the exhaust gas from the second exhaust gas collection chamber can be directly supplied only to the second exhaust gas collection chamber, A compensation member is provided between the first exhaust gas collection chamber and the second exhaust gas collection chamber for compensating for particularly favorable mechanical and / or thermal stresses and / or expansion.

Thereby, not only can thermal expansion or other types of mechanical stresses, such as vibrations, be compensated for better, but also the distribution of the exhaust gas flow in the exhaust gas collecting tube can be optimized, The mutual influence of the exhaust gas streams from the various cylinder liners simultaneously connected to the gas collecting tube can also be at least generally prevented or minimized.

Quite similarly, the exhaust gas distributor line may also include a first exhaust gas distributor chamber and a second exhaust gas distributor chamber in fluid communication with the first exhaust gas distributor chamber, and the exhaust gas from the exhaust gas collecting duct may comprise a first The exhaust gas can be supplied directly to the first exhaust gas distributor chamber only through the bypass line or the first bypass valve and the exhaust gas from the exhaust gas collecting pipe can be supplied only through the second bypass line or the second bypass valve Can be flow coupled with the exhaust gas collection tube, such that it can be fed directly into the second exhaust gas distributor chamber.

In a particularly preferred variant of the embodiment according to the invention introduced above, the exhaust gas from the first exhaust gas collecting chamber of the exhaust gas collecting tube flows through the first bypass line or through the first bypass valve, The exhaust gas from the second exhaust gas collecting chamber of the exhaust gas collecting tube is directly supplied only to the second exhaust gas distributor chamber through the second bypass line or through the second bypass valve, do.

Here, in each corresponding embodiment, a compensating connection may be provided between the first exhaust gas distributor chamber and the second exhaust gas distributor chamber to compensate for preferably mechanical and / or thermal stresses and / or expansion. As a result, not only can thermal expansion or other types of mechanical stresses, such as vibrations, be compensated for better, but also the distribution of the exhaust gas flow in the exhaust gas distributor line can be optimized, The mutual influence of the exhaust gas streams from the various exhaust gas collecting tubes simultaneously connected to the distributor lines can also be at least generally prevented or minimized.

In this case, of course, also in a similar manner, also a mixing section, in particular a mixing tube line, may comprise a first mixing chamber and a second mixing chamber in which a mechanical and / A compensation line may be provided to compensate for stress and / or expansion.

It will be appreciated that the connecting valve and / or the bypass valve, in particular the first bypass valve and / or the second bypass valve and / or the exhaust gas collection pipe valve and / or the exhaust gas distributor valve can also be controlled or adjusted, Which can be controlled or adjusted in accordance with the operational parameters of the reciprocating piston internal combustion engine, in particular by means of an electric or hydraulic or pneumatic, particularly preferably by means of a computer-controlled device, Do.

For this purpose, it is possible in particular to carry out, for example in a known manner, sensors, in particular exhaust sensors, temperature sensors, pressure sensors or bypass valves, in particular a first bypass valve and / or a second bypass valve and / It is also possible that other sensors suitable for controlling or regulating valves and / or exhaust gas distributor valves are suitably provided.

In order to further optimize the flow of the exhaust gas, an exhaust gas collection tube, in particular a first exhaust gas collection chamber and / or a second exhaust gas collection chamber, is provided for guiding and distributing the exhaust gas in a line device, Line sheet, and in particular for the purpose of distributing the exhaust gases to different sections of the exhaust gas distributor line, particularly for distributing to the first exhaust gas distributor chamber and the second exhaust gas distributor chamber of the exhaust gas distributor line, Sheet.

For very similar and similar purposes, the exhaust gas distributor line, especially the first exhaust gas distributor chamber and / or the second exhaust gas distributor chamber, is of course also capable of directing and distributing the exhaust gas in the diverting device, in particular in the exhaust gas distributor line , And may in particular comprise a redirecting sheet for the purpose of distributing the exhaust gases to different exhaust gas turbochargers of the supercharging unit, in particular to the first supercharging group and the second supercharging group of the supercharging unit , In which case blinds, especially controllable or adjustable blinds, may also be provided within the discharge line as shown, so that the gas flow can be controlled or adjusted by this blind.

For fixing, the exhaust gas collection tube and / or the mixing section, in particular the mixing tube line and / or the exhaust gas distributor line, are particularly preferably, but not necessarily, supported and / or guided by one common guide element In which case the guide element is preferably a guide plate, guide box or other suitable guide- or locking device for fixing and guiding the exhaust gas collection tube and the exhaust gas distributor line.

At this time it is very particularly advantageous that the mechanical and / or thermally induced stresses and / or the expansion or vibrations of the exhaust gas collection tube and of the exhaust gas distributor line or other mechanical components can also be compensated at least in part, And an exhaust gas collecting tube and / or a mixing section, in particular a mixing tube line and / or an exhaust gas distributor line, are arranged in the guide element.

Particularly preferably, the guide elements and / or the guide plates for compensating and / or equalizing the mechanical and / or thermally induced stress and / or expansion and / or vibration of the exhaust gas collection tube and the exhaust gas distributor line, Or the guide box may be movably disposed within a sliding shoe.

The present invention also relates to a mixing section for a reciprocating piston internal combustion engine according to the present invention, in particular a mixing line, in which case the mixing section of the present invention is in one particular embodiment an exhaust gas collection tube and / Or an exhaust gas distributor line and / or an exhaust gas reactor.

The present invention is described 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 of a two stroke-large diesel engine;
Figure 2 shows a known large diesel engine with an SCR-reactor for treating exhaust gases;
3A shows a first embodiment of a two-stroke-large diesel engine according to the present invention in a perspective view with a mixing tube line below the exhaust gas collection tube;
Figure 3b shows a side view of the embodiment according to Figure 3a;
Figure 3c shows a third view of the embodiment according to Figure 3a;
Fig. 4 shows a schematic second embodiment of a two-stroke-large diesel engine according to the present invention having a guide box formed with a connecting section with a connecting valve;
Figure 5 shows a second embodiment according to Figure 4;
Figure 6 shows an embodiment of a two stroke-large diesel engine according to the present invention with a mixing tube line below the collection tube section;
Figure 7 shows an exhaust gas collection tube or exhaust gas distributor line and a compensation member or compensation connection;
8A shows a first embodiment of an exhaust gas collection tube with a line device and a blind for exhaust gas;
Figure 8b shows another embodiment according to Figure 8a;
Figure 8c shows a third embodiment according to Figure 8a;
Figure 9a shows a first embodiment of an exhaust gas distributor line with a directional switch for exhaust gas and a blind;
FIG. 9B shows another embodiment according to FIG. 9A; FIG.
Figure 9c shows a third embodiment according to Figure 9a;
10 shows a guide element with a sliding shoe, an exhaust gas collection tube and a mixing tube section.

Figures 1 and 2 relate to examples known in the prior art which have not been discussed in this section because they have already been described in detail at the introduction.

The reciprocating piston internal combustion engine according to the present invention, hereinafter denoted generally by the numeral 1, is designed in particular as a two-stroke-large diesel engine that is cleaned in the longitudinal direction, for example as widely used in ship structures.

3a, 3b and 3c, a first embodiment of a two stroke-large diesel engine according to the present invention with a mixing line below the exhaust gas collection tube is shown in perspective view in Figure 3a, In a particular embodiment of a two-stroke-large diesel engine comprising a plurality of cylinder liners and being vertically cleaned, for use in a vessel, for example a container vessel, the reciprocating piston internal combustion engine according to the invention, Show the parts. Here, FIG. 3B is a side view of the engine according to FIG. 3A to help understand the interaction of the main components, and FIG. 3C is a front view only.

The reciprocating piston internal combustion engine according to the present invention shown in Fig. 3a or 3b and 3c is a two-stroke-large diesel engine that is cleaned in the longitudinal direction, which is connected to a single combustion chamber 2 and one GZ2 of the cylinder liner GZ1 and GZ2 in the combustion chamber 2 of each of the cylinder groups GZ of the cylinder liners GZ1 and GZ2, The exhaust gas 5 coming from each combustion chamber 2 of the cylinder group GZ of the cylinder liner GZ1 and GZ2 in the operating state is supplied to the exhaust gas collection pipe 4 through each corresponding discharge valve 3, And is in fluid communication with a common exhaust gas collection pipe 4 so that it can be supplied to the exhaust gas collecting pipe 4. The exhaust gas 5 from the exhaust gas collecting tube 4 is discharged from the exhaust gas collecting tube 4 in the washing mode in order to remove dangerous nitrogen oxides from the exhaust gas 5, Section 12 to the inside of the exhaust gas reactor 6.

In addition, the first supercharging group 71 and the second supercharging group 72 for compressing the air 80 sucked from the periphery by the turbocharger of one of the supercharging group 71 and the supercharging group 72 are included The exhaust gas 5 from the exhaust gas reactor 6 is compressed in the cleaning mode by the first supercharging group 71 and the second supercharging group 72 So that the air 80 can be supplied as clean air to the cylinder liner ZZ or the cylinder liner GZ1 or GZ2 of the cylinder group GZ through the respective cleaning air openings not shown in Figs. 3A to 3C, (71, 72).

3A to 3C show as an example two assemblies consisting of the mixing tube line 121, the exhaust gas reactor 6 and the supercharging group 7, 71 and 72, Which is necessary in the case of a plurality of cylinder liners (Z).

According to the invention, the mixing section 12 is arranged in such a way that the exhaust gas 5 can be supplied to the exhaust gas reactor 6 via the mixing section 12, And on the other hand extends substantially parallel to the collection tube section 401 of the exhaust gas collection tube 4 at least in a section manner.

At this time, the mixing section 12 is connected to the exhaust gas collecting pipe 4 on the one hand and to the crankshaft (not shown) of the reciprocating piston internal combustion engine 1 on the one hand based on the vertical direction VR of the reciprocating piston internal combustion engine 1 11), at least in a section manner, substantially parallel to the exhaust gas collection pipe (4). 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 this case, 12 are formed in the form of a mixing pipe line 121 between the exhaust gas collecting 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 connecting section 130 with a connecting valve V130 Is discussed.

4 and 5 show a guide box 142 formed as a connection section 130 which is composed of a mixing section 121 formed as a mixing tube line 121 and a mixing section 121 formed as an exhaust gas collecting tube 4, And a connection valve V130. In this embodiment, which is particularly preferred in practice, the mixing line 121 is arranged directly below the exhaust gas collection tube 4 of the guide box 142, in which case the connection valve V130 is simultaneously connected to the guide box 142 ), And this formation is particularly space-saving because the additional connection lines are basically unnecessary hereby. The exhaust gas collecting pipe 4 is connected to the exhaust gas collecting pipe valve 4 so that the exhaust gas 5 from the exhaust gas collecting pipe 4 can no longer be supplied to the exhaust gas reactor 6 in the bypass mode. 40).

The exhaust gas distributor line 10 is also connected to the exhaust gas distributor valve 100 such that the exhaust gas 5 from the exhaust gas collection pipe 4 can no longer be supplied directly to the exhaust gas distributor line 10. [ . In other words, in the case where the exhaust gas reactor 6 is not needed or is shut down for another reason in one specific operating state of the reciprocating piston internal combustion engine 1, the exhaust gas collection pipe valve 40 is closed and the exhaust gas distributor valve 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 immediately discharged from the exhaust gas collecting pipe 4 to the guide box 142 And turbocharger of the supercharging group 7, 71, 72, not shown in Fig. 5, for the purpose of clarifying the outline of the figure, through the exhaust gas distributor line 10 and the exhaust gas distributor line 10 as well.

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

7 shows in a schematic manner the exhaust gas distributor line 10 and the exhaust gas collection pipe 4 with the compensating member 400 or the compensating connection 500 and in this case to clarify the overview of the drawing For reasons, it is not clearly shown, for example, that the mixing sections 12, 121, which may extend parallel to the exhaust gas collection tube 4 and / or in parallel with the exhaust gas distributor line 10, are not clearly shown.

At this time, the exhaust gas distributor line 10 is arranged so that the exhaust gas 5 from the exhaust gas reactor 6 flows through the exhaust gas distributor line 10 into the first supercharging group 71 and the second supercharging group 72 In the region adjacent to the first supercharging group 71 and the second supercharging group 72, the crankshaft (not shown in Fig. 7) of the internal combustion engine 1 And on the other hand at the lower portion of the exhaust gas collecting pipe 4 is disposed an exhaust gas collecting pipe 4 and a crankshaft (hereinafter, referred to as a crankshaft) 11 based on the vertical direction VR of the reciprocating piston internal combustion engine 1 11). In a particular embodiment, the exhaust gas distributor line 10 is arranged on the basis of the vertical direction (VR), on the one hand between the first supercharging group 71 and the second supercharging group 72 and, on the other hand, Is disposed between the group 71 and the exhaust gas collecting pipe 4 and adjacent to one of the cylinder liners Z, GZ1 and GZ2

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 Each have one compensating member 400 or compensating connecting portion 500 for compensating for mechanical or thermal stresses or other obstacles. At this time, the exhaust gas collecting pipe 4 is arranged such that the exhaust gas 5 from the first combination EZ1 of the cylinder liner Z can be supplied directly to only the first exhaust gas collecting chamber 41, So that the exhaust gas 5 from the second combination EZ2 of the first exhaust gas collecting chamber Z can be directly supplied only to the second exhaust gas collecting chamber 42, And a second exhaust gas collection chamber (42) fluidly coupled to the collection chamber (41).

At this time, as already mentioned above, mechanical and / or thermal stresses and / or expansion and / or vibrations or other mechanical effects between the first exhaust gas collection chamber 41 and the second exhaust gas collection chamber 42 Or a compensating member 400 for compensating for a thermal obstacle is provided.

The exhaust gas distributor line 10 also includes a first exhaust gas distributor chamber 101 and a second exhaust gas distributor chamber 102 in fluid communication with the first exhaust gas distributor chamber 101, The exhaust gas 5 from the pipe 4 can be supplied directly to only the first exhaust gas distributor chamber 101 through the first bypass valve 1311 and the exhaust gas 5 from the exhaust gas collecting pipe 4 And is in fluid communication with the exhaust gas collection tube 4 such that the gas 5 can be supplied directly to the second exhaust gas distributor chamber 102 only through the second bypass valve 1312. [ At this time, the exhaust gas 5 from the first exhaust gas collecting chamber 41 of the exhaust gas collecting 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 second exhaust gas collecting chamber 42 of the exhaust gas collecting pipe 4 flows only through the second bypass valve 1312 but only to the second exhaust gas distributor chamber 102 Can be supplied directly. Similar to the exhaust gas collection pipe 4, mechanical and / or thermal stresses and / or expansion and / or vibrations and / or vibrations may occur between the first exhaust gas distributor chamber 101 and the second exhaust gas distributor chamber 102. [ Or compensating for other mechanical or thermal obstacles is provided.

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, which is not explicitly shown in the figure, And / or the exhaust gas distributor valve 100, which is likewise not explicitly shown in the figures, are particularly preferably controllable or adjustable, in particular electrically or hydraulically or pneumatically controlled or adjustably implemented. For this purpose, a sensor, in particular an exhaust gas sensor, a temperature sensor or a pressure sensor, or a bypass valve 131, in particular a first bypass valve 1311 and / or a second bypass valve 1312 and / Other sensors suitable for controlling or regulating the gas collection line valve 40 and / or the exhaust gas distributor valve 100 may be suitably provided.

8A, there is shown schematically another further preferred embodiment of an exhaust gas collection pipe 4 with line devices 15, 151 for exhaust gas 5, in which case controllable Or the adjustable blind B is provided, so that the gas flow can be controlled or adjusted by this blind B as a result. FIG. 8B shows another embodiment according to FIG. 8A, while referring to FIG. 8C, a third embodiment according to FIG. 8A is shown.

8A to 8C, the exhaust gas collecting pipe 4, particularly the first exhaust gas collecting chamber 41 and / or the second exhaust gas collecting chamber 42 are connected to the line devices 15 and 151, In particular a line sheet 151 for guiding and distributing the exhaust gas 5 within the exhaust gas collection pipe 4 and in particular for distributing the exhaust gas 5 to different sections of the exhaust gas distributor line 10 For distribution to the first exhaust gas distributor chamber 101 and the second exhaust gas distributor chamber 102 of the exhaust gas distributor line. Those skilled in the art will appreciate that any of the embodiments according to Figs. 7A-7C may be used for implementation, or, in some cases, simple non-inventive improvements of these embodiments may be used for implementation, You can easily determine from your own expertise and apply it to specific real-world situations.

9A shows a first embodiment of an exhaust gas distributor line 10 with a directional switch 16,161 for the exhaust gas 5, in this case a controllable or adjustable blind B, The gas flow can be controlled or adjusted by this blind B as a result.

FIG. 9B shows another embodiment according to FIG. 9A, while FIG. 9C shows a third embodiment according to FIG. 9A. At this time, the exhaust gas distributor line 10, particularly the first exhaust gas distributor chamber 101 and / or the second exhaust gas distributor chamber 102, the redirection devices 16 and 161, in particular the exhaust gas distributor line 10, In particular the exhaust gas 5 to the different exhaust gas turbochargers of the supercharging unit 7, that is to say the first supercharging group 71 of the supercharging unit 7, And a redirecting sheet (161) for distributing to the second supercharging group (72). Those skilled in the art will appreciate whether any of the embodiments according to Figs. 9A-9C can be used for implementation, or, in some cases, simple non-inventive improvements of these embodiments can be used for implementation, You can easily determine from your own expertise and apply it to specific real-world situations.

Figure 10 shows, by way of example, one particular embodiment of the guide elements 14, 141, which is particularly important for the final implementation, by means of which the exhaust gas collecting tube 4 as well as the exhaust gas distributor line 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, Guided. The additional guide elements 14 and 141 allow the exhaust gas collection tube 4 to be better secured to the engine together with the exhaust gas distributor line 10 and to compensate for the thermal expansion better, Are significantly improved under vibration.

At this time, the guide elements 14 and 141 according to Fig. 10 can be used not only for the thermal expansion of the exhaust gas collecting tube and / or the exhaust gas collecting line 10, but also for a very wide range, for example in the operating state of a reciprocating piston internal combustion engine Which is particularly well suited for absorbing or compensating for other mechanical loads or disturbances, such as mechanical vibrations. In this case, not only thermal expansion or vibration in the longitudinal direction of the exhaust gas collecting pipe 4 or the exhaust gas collecting line 10, but also thermal expansion or vibration in the direction perpendicular to this direction can be compensated Such compensation is possible, in particular, by implementing the guide plate in a relatively thin plate and by special geometric molding which can be matched to individual situations. At this time, the mechanical and / or thermally induced stresses and / or expansion and / or vibrations of the exhaust gas collection pipe 4 and the exhaust gas distributor line 10, particularly shown in FIG. 10, are compensated and / The guide element 141 and / or the guide box 142 may be movably disposed within the sliding shoes 1400. The guide elements 141,

Skilled artisans appreciate that the invention is not limited to the explicitly discussed embodiments, but rather that corresponding improvements are likewise covered by the present invention. In particular, the present invention is of course also relevant to all suitable combinations of the embodiments discussed.

Claims (36)

A reciprocating piston internal combustion engine, in particular a two-stroke-large diesel engine,
And a cylinder group GZ made up of a plurality of cylinder liners GZ1 and GZ2 each having one combustion chamber 2 and one corresponding discharge valve 3 and the cylinder group GZ including the cylinder liners GZ1 and GZ2 Each of the combustion chambers 2 of the group GZ is in fluid communication with one common exhaust gas collecting pipe 4 so that the respective combustion chambers 2 of the cylinder group GZ made up of the cylinder liner GZ1 and GZ2 Exhaust gas 5 from the exhaust gas collecting pipe 4 can be supplied to the exhaust gas collecting pipe 4 through the respective corresponding discharge valve 3 and the exhaust gas from the exhaust gas collecting pipe 4 5 and 7 are provided in the exhaust gas reactor 6 and also include a supercharging unit 7, 71 and 72 including a first supercharging group 71 for compressing the air 80, The exhaust gas (5) from the gas reactor (6) So that the air 80 compressed by the first supercharging group 71 can be supplied to one or a plurality of cylinder liner Z and / Can be supplied as cleaning air to one or a plurality of cylinder liners of the cylinder liner (GZ1, GZ2) of the cylinder (GZ)
The mixing section 12 is arranged to extend in the region adjacent to the first power group 71 so that the exhaust gas 5 can be supplied to the exhaust gas reactor 6 via the mixing section 12, , And on the other hand extends substantially parallel to the collection tube section (401) of the exhaust gas collection tube (4) at least in a section manner. The method according to claim 1,
The mixing section 12 is provided between the exhaust gas collecting pipe 4 on the one hand and the crankshaft 11 of the reciprocating piston internal combustion engine on the one hand based on the vertical direction VR of the reciprocating piston internal combustion engine, Extending substantially parallel to the exhaust gas collection pipe (4) in a manner that the exhaust gas collecting pipe (4) and the exhaust gas collecting pipe (4) are connected to each other. 3. The method according to claim 1 or 2,
And the mixing section (12) is formed as a mixing pipe line (121). 4. The method according to any one of claims 1 to 3,
The exhaust gas collecting pipe 4 is supported by the guide elements 14 and 142 in the form of a guide box 142 and is fixed to the reciprocating piston internal combustion engine and the guide box 142 is connected to the exhaust gas 5 Is formed as a connection section (130) and is in fluid communication with the mixing section (12) so that the mixing section (12) can be supplied to the mixing section (12) through the guide box (142) in the cleaning mode. 5. The method of claim 4,
As a result, in the bypass mode, the flow of exhaust gas from the exhaust gas collecting pipe 4 into the mixing section 12 is interrupted due to the guide box 142 or the connection section 130 including the connection valve V130. Of the internal combustion engine. 6. The method according to any one of claims 1 to 5,
The mixing section 12 is at least sectioned and preferably entirely inside the exhaust gas collection tube 4 and preferably in the mixing tube line 121 parallel to the collection tube section 401, 4) and / or said exhaust gas collection pipe (4) itself is formed as a mixing section (12). 7. The method according to any one of claims 1 to 6,
Wherein at least one second supercharging group 72 is provided for compressing the air 80 in addition to the first supercharging group 71 and the exhaust gas 5 from the exhaust gas reactor 6 is supplied in the washing mode So that the air 80 compressed by the first and the second supercharging groups 71 and 72 can be supplied to the supercharging groups through one or more And can be supplied as clean air to the cylinder liner (Z) and / or to one or more cylinder liners of the cylinder liner (GZ1, GZ2) of the cylinder group (GZ). 8. The method according to any one of claims 1 to 7,
The exhaust gas distributor line 10 supplies the exhaust gas 5 from the exhaust gas reactor 6 to the first supercharging group 71 and the second supercharging group 72 via the exhaust gas distributor line 10 And extends substantially parallel to the crankshaft 11 of the reciprocating piston internal combustion engine in the region adjacent to the first supercharging group 71 and the second supercharging group 72 on the one hand at least in section, On the one hand, between the exhaust gas collecting tubes 4, preferably between the mixing section 12 and the crankshaft 11, with reference to the vertical direction VR of the reciprocating piston internal combustion engine. 9. The method of claim 8,
The exhaust gas distributor line 10 is arranged between the first and the second supercharging group 71 and 72 on the one hand and the first supercharging group 71 on the other hand on the basis of the vertical direction VR, And between the second supercharging group (72) and the exhaust gas collecting pipe (4), preferably adjacent to one of the cylinder liners (Z, GZ1, GZ2). 10. The method according to claim 8 or 9,
The exhaust gas distributor lines 10 are arranged at the heights of the first supercharging group 71 and the second supercharging group 72 with respect to the vertical direction VR, 2 supercharging group (72) is disposed between the exhaust gas distributor lines (10) and adjacent to the cylinder liners (Z, GZ1, GZ2). 11. The method according to any one of claims 1 to 10,
Wherein said mixing section (12) and said exhaust gas reactor (6) form at least one integrated unit, preferably in a completely sectioned manner. The method according to any one of claims 8 to 11,
Wherein the exhaust gas reactor (6) and the exhaust gas distributor line (10) form one common integrated component. 13. The method according to any one of claims 1 to 12,
Wherein the exhaust gas collection tube 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, On the one hand, in the region adjacent to the first and second supercharging groups 71 and 72 and on the other hand in the region adjacent to one of the cylinder liners GZ1, GZ2 and Z, (11) of the internal combustion engine. 14. The method according to any one of claims 1 to 13,
So that the exhaust gas 5 bypasses the exhaust gas reactor 6 and can be supplied to the supercharging units 7, 71 and 72, particularly to the first supercharging group 71 and / or the second supercharging group 72, Wherein the bypass line (13) is arranged and provided so that it can be supplied to the supercharging unit (7, 71, 72), in particular via the exhaust gas distributor line (10). 15. The method of claim 14,
Wherein said bypass line (13) is provided between an exhaust gas collection pipe (4) and an exhaust gas distributor line (10). 16. The method according to claim 14 or 15,
And the bypass line (13) can be shut off by the bypass valve (131). 17. The method of claim 16,
And the bypass line (13) is formed as a bypass valve (131). 18. The method according to any one of claims 1 to 17,
The exhaust gas collecting tube 4, particularly the collecting tube section 401, is arranged so that the exhaust gas 5 from the exhaust gas collecting tube 4 can no longer be supplied to the exhaust gas reactor 6, And can be shut off by the pipe valve (40). 19. The method according to any one of claims 1 to 18,
The exhaust gas distributor line 10 can be blocked by the exhaust gas distributor valve 100 so that the exhaust gas 5 from the exhaust gas reactor 6 can no longer be supplied to the exhaust gas distributor line 10. [ Reciprocating piston internal combustion engine. 20. The method according to any one of claims 1 to 19,
The exhaust gas collecting pipe 4 can be formed such that the exhaust gas 5 from the first combination EZ1 of the cylinder liner Z can be supplied directly to only the first exhaust gas collecting chamber 41, The first exhaust gas collecting chamber 41 and the first exhaust gas collecting chamber 42 are arranged such that the exhaust gas 5 from the second combination EZ2 of the first exhaust gas collecting chamber 42 and the second exhaust gas collecting chamber 42 can be directly supplied only to the second exhaust gas collecting chamber 42, And a second exhaust gas collection chamber (42) fluidly coupled to the chamber (41). 21. The method of claim 20,
Wherein a compensating member (400) is provided between the first exhaust gas collecting chamber (41) and the second exhaust gas collecting chamber (42) for compensating mechanical and / or thermal stress and / Piston internal combustion engine. 22. The method according to any one of claims 1 to 21,
The exhaust gas distributor line (10) includes a first exhaust gas distributor chamber (101) and a second exhaust gas distributor chamber (102) in fluid communication with the first exhaust gas distributor chamber (101) The exhaust gas 5 from the pipe 4 can be supplied directly to the first exhaust gas distributor chamber 101 only through the first bypass valve 1311 and the exhaust gas 5 from the exhaust gas collecting pipe Is fluidly coupled with the exhaust gas collection tube (4) such that the exhaust gas can be directly supplied only to the second exhaust gas distributor chamber (102) through the second bypass valve (1312). 23. The method of claim 22,
The exhaust gas 5 from the first exhaust gas collecting chamber 41 of the exhaust gas collecting tube can be supplied directly to only 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 tube can be supplied directly to the second exhaust gas distributor chamber 102 only through the second bypass valve 1312, Reciprocating piston internal combustion engine. 24. The method according to claim 22 or 23,
Wherein a compensating connection (500) is provided for compensating mechanical and / or thermal stress and / or expansion between said first exhaust gas distributor chamber (101) and said second exhaust gas distributor chamber (102) Piston internal combustion engine. 25. The method according to any one of claims 1 to 24,
The mixing section 12 and in particular the mixing tube line 121 includes a first mixing chamber 1201 and a second mixing chamber 1202 and the first mixing chamber 1201 and the second mixing chamber 1201 1202) is provided with a compensating line (600) for compensating mechanical and / or thermal stresses and / or expansion. 26. The method according to any one of claims 5 to 25,
The connection valve V130 and / or the bypass valve 131, particularly the first bypass valve 1311 and / or the second bypass valve 1312 and / or the exhaust gas collection pipe valve 40 and / Or the exhaust gas distributor valve 100 can be controlled or adjusted, and in particular, can be controlled or adjusted electrically or hydraulically or pneumatically. 27. The method of claim 26,
The connection valve V130 and / or the bypass valve 131, particularly the first bypass valve 1311 and / or the second bypass valve 1312 and / or the exhaust gas collection pipe valve 40 And / or a sensor, in particular an exhaust gas sensor, a temperature sensor or a pressure sensor, for controlling or regulating the exhaust gas distributor valve (100) is suitably provided. 28. The method according to any one of claims 1 to 27,
The exhaust gas collection pipe 4 and particularly the first exhaust gas collection chamber 41 and / or the second exhaust gas collection chamber 42 are arranged in the line devices 15 and 151, in particular in the exhaust gas collection pipe 4 A line sheet 151 for guiding and distributing the exhaust gas 5 and in particular for the purpose of distributing the exhaust gas 5 to different sections of the exhaust gas distributor line 10, 1 exhaust gas distributor chamber (101) and a second exhaust gas distributor chamber (102). 29. The method according to any one of claims 8 to 28,
The exhaust gas distributor line 10 and in particular the first exhaust gas distributor chamber 101 and / or the second exhaust gas distributor chamber 102 are connected to the diversion devices 16 and 161, in particular the exhaust gas distributor line 10, In particular the exhaust gas 5 to a different exhaust gas turbocharger of the supercharger unit 7 and in particular to the supercharger unit 7, And a redirecting sheet for distribution to a first supercharging group (71) and a second supercharging group (72) of the internal combustion engine. 30. The method of claim 28 or 29,
A controllable or adjustable blind (B) can be provided whereby the gas flow can be controlled or adjusted by the blind (B). 31. The method according to any one of claims 1 to 30,
The exhaust gas collection tube 4 and / or the mixing section 12, in particular the mixing tube line 121 and / or the exhaust gas distributor line 10, are connected by a common guide element 14, 141 Supported and / or guided. 32. The method of claim 31,
Wherein the guide element (14, 141) is a guide plate (141) or a guide box (142). 33. The method according to claim 31 or 32,
The guide element (14, 141) is arranged such that the mechanically and / or thermally induced stress and / or expansion of the exhaust gas collection tube (4) and the exhaust gas distributor line (10) can be at least partially compensated And wherein the exhaust gas collection pipe (4) and the mixing section (12), in particular the mixing line (121) and / or the exhaust gas distributor line (10) Internal combustion engine. 34. The method according to any one of claims 31 to 33,
Guide elements 14, 15 for compensating and / or equalizing the mechanical 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, 141), in particular the guide plate (141) and / or the guide box, are movably disposed within the sliding shoe (1400). 34. A mixing line for a reciprocating piston internal combustion engine (1) according to any one of claims 1 to 34. 36. The method of claim 35,
Wherein the mixing section is a combined mixing section including an exhaust gas collecting tube (4) and / or an exhaust gas distributor line (10) and / or an exhaust gas reactor (6).

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