JP2016075282A - Reciprocation internal combustion engine, in particular, two-cycle large diesel engine, and mixing flow channel, in particular, mixing pipe conduit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an improved engine achieving arrangement of an exhaust gas system capable of saving a space as much as possible, and shortening of a length of a flow channel between a cylinder liner and a supercharge assembly with turbo charger.SOLUTION: This invention relates to a reciprocation type internal combustion engine 1 including a cylinder assembly GZ of a plurality of cylinder liners GZ1, GZ2 respectively provided with one combustion chamber 2 and one exhaust gas valve 3, in particular, a uniflow scavenging two-cycle large diesel engine. Flows of the combustion chambers 2 of the cylinder assembly GZ of the cylinder liners GZ1, GZ2 are connected by a common exhaust gas collection pipe 4, and an exhaust gas 5 can be supplied to an exhaust gas reactor 6 from the exhaust gas collection pipe 4 for treatment in a purification mode.SELECTED DRAWING: Figure 3a

Description

  The present invention relates to a reciprocating internal combustion engine, in particular a uniflow scavenging two-cycle large diesel engine, and a mixing channel, in particular a mixing line according to the superordinate concept of the independent claims.

  A large diesel engine with a crosshead structure preferably has three large housing parts that are mounted, for example, for power generation, such as in a shipbuilding or stationary device, and form the framework of the engine. A so-called stand is arranged on the base plate which clearly shows the lateral support elements for mounting the crankshaft in the vicinity of the bearing base with the crankshaft main bearing and is partitioned by a floor plate. The known stand has a plurality of opposed supports according to the number of cylinders of a large diesel engine, which supports two adjacent crossheads connected to the crankshaft via a connecting rod. For each, specify one vertical running slide surface. Here, each of the two opposing vertical extending supports having sliding surfaces is additionally supported by a partition wall. Each support is typically interconnected by a common closing panel. Next, in many cases, a cylinder portion, also called a cylinder jacket, is disposed on the closing panel on the upper side of the stand, and this cylinder portion is adapted for mounting a plurality of cylinder liners. The base plate, stand and cylinder part here are usually interconnected by tie rods which extend into the interior of the support in the area of the stand part, which means that the tie rods are in or on the base plate. This is done by applying a significant preload and bolting.

  Here, various types of stands are known which deal with different problems relating to stability and wear, and in the background art optimal solutions are proposed as appropriate.

  In order to improve the output of reciprocating internal combustion engines, not only that, but especially in the case of the above-mentioned type, after the combustion stroke, the fresh air is usually increased by a supercharging assembly equipped with at least one exhaust gas turbocharger. It is sent to the combustion chamber of the cylinder liner under a given pressure. Here, a part of the thermal energy of the exhaust gas exiting from the combustion chamber of the cylinder liner after the combustion stroke can be utilized. For this purpose, hot exhaust gas is supplied from the combustion chamber of the cylinder liner to the supercharging assembly, for example by opening an exhaust gas valve attached to the cylinder cover of the cylinder liner. The supercharging assembly here mainly consists of a turbine driven by heated exhaust gas that is pressurized and enters the supercharging assembly. The turbine drives the compressor on its own side, whereby fresh air is drawn and compressed. Along with the name exhaust gas turbocharger for classification, it is often referred to simply as a turbocharger, but not only with a turbine, which is usually implemented as a radial compressor, especially in the case of two-cycle large diesel engines The compressor is followed by a so-called diffuser, charge air cooler, water separator and intake receiver, from which the compressed fresh air, also known as charge air or scavenging, eventually becomes a large diesel It is sent to each combustion chamber of the engine cylinder liner. Thus, the use of such a supercharging assembly can improve the fresh air supply and increase the efficiency of the combustion process in the combustion chamber of the cylinder.

  In the case of a large diesel engine, air is supplied to different locations on the cylinder liner depending on the type. Thus, for example, in the case of a uniflow scavenging two-cycle engine, air is fed into the combustion chamber of the cylinder liner via a scavenging slot located on the sliding surface in the area below the cylinder liner. In a small four-cycle engine, charge air is typically fed into the cylinder's combustion chamber, for example, via one or more intake valves located in the cylinder head. Here, as is well known for two-cycle engines, these two-cycle engines are equipped with an intake valve which is arranged on the cylinder liner at the location of the scavenging slot in the area below the cylinder liner.

  FIG. 1 is developed as a two-cycle large diesel engine with uniflow scavenging and is generally indicated by the reference 1 'below and is known from the background art to date for large diesel engine exhaust gas turbochargers. The principle structure of the system is shown in a schematic diagram illustrating the interaction of the different components in order to make it easier to understand the invention which will be described later.

  In order to make it easy to distinguish between the background art and the present invention, the reference numerals for the example indices known from the background art are each marked with a dash. There is no dash.

  A large diesel engine 1 'has a cylinder assembly GZ' having a plurality of cylinder liners GZ1 'with exhaust valves 3' arranged in a cylinder cover in a known manner, and the cylinder In the liner GZ1 ′, the piston K ′ is disposed so as to move back and forth along the sliding surface between the bottom dead center UT ′ and the top dead center OT ′. The cylinder wall of the cylinder liner GZ1 'with the cylinder cover and piston K' limits the combustion chamber 2 'of the cylinder liner GZ1' in a known manner.

  For the sake of clarity, only the cylinder liner GZ1 'is illustrated in FIG. 1 by way of example. In practice, the cylinder assembly G 'is understood to comprise a plurality, usually a large number of cylinder liners GZ1'.

  A plurality of scavenging openings 9 ', which are implemented as scavenging slots, are attached to the lower region of the cylinder liner GZ1'. Depending on the position of the piston K ', the scavenging slot is covered or opened by this piston. The scavenging opening 9 'allows charge air, called scavenging 81', to flow into the combustion chamber 2 'of the cylinder liner GZ1'. Exhaust gas 5 ′ generated during combustion through the exhaust gas valve 3 ′ disposed in the cylinder cover is connected to each combustion chamber 2 ′ via the open exhaust gas valve 3 ′. It flows from the exhaust gas collecting pipe 4 'into a supercharging assembly 71' developed as an exhaust gas / turbocharger.

  As described above, the exhaust gas / turbocharger of the supercharging assembly 71 ′ is a known method as an important component as described above, and a compressor with an air 80 ′ compressor, a compressor with a flywheel 711 ′, and a shaft in a known manner. It includes a turbine with a turbine flywheel 712 'for driving a compressor flywheel 711' that is positively connected to the turbine flywheel 712 '. The turbine and compressor are arranged in a housing, thus forming an exhaust gas turbocharger which is usually formed as a radial compressor. The turbine is driven in a known manner by heated exhaust gas 5 'flowing from the combustion chamber 2' of the cylinder liner GZ1 '.

  In order to feed the scavenging air 81 'into the combustion chamber 2' of the cylinder liner GZ1 ', air 80' is drawn from the surroundings via the intake nozzle by the compressor / flywheel 711 'and compressed in the exhaust gas / turbocharger. . From the exhaust gas turbocharger, the compressed air 80 'reaches the intake receiver 750' via the water separator 740 'by the diffuser 720' and the charge air cooler 730 'connected downstream. The compressed air 80 'is finally applied with a pressure increased by a scavenging opening 9' developed as a scavenging slot and reaches the combustion chamber 2 'of the cylinder liner GZ1' as scavenging 81 '.

  This principle of engine charge by charge air using one or more turbochargers has long been known in all conceivable forms of the engine, in the case of uniflow scavenged two-cycle large diesel engines But it has been used successfully for decades. In the meantime, in the process of development, the shape and arrangement of the exhaust gas system consisting of the above-mentioned turbocharger system with exhaust gas collecting pipe and diffuser, charge air cooler and water separator is always further optimized As a result, known exhaust gas systems have been optimized with significant space savings between them and incorporated into the overall shape of the engine. This is especially true for uniflow scavenged two-cycle large diesel engines installed on ships, where little space can be used in the hull as a rule, which determines the space-saving arrangement of engine components. This is a crucial point because it plays a vital role.

  However, in this regard, a great number of problems have recently occurred, the cause of which has been identified, among other things, in exhaust gas standards that are becoming more stringent and was not initially anticipated.

  Based on exhaust gas regulations, which have become stricter, requirements for exhaust gas quality have been constantly increasing for several years. Not only that, but also the concentration of nitrogen oxides in exhaust gas has become the focus of exhaust gas standards. Here, the legal standard value and the regulation value regarding the applicable exhaust gas regulation value are always becoming more and more strict. For this reason, especially in the case of two-cycle large diesel engines, it is always more difficult to comply with emission regulations, which is technically expensive and therefore expensive, or even finally, compliance is no longer quite reasonable. Combustion of high-load conventional heavy oil containing toxic substances, as well as combustion of diesel fuel or other fuels, is constantly becoming an issue.

  Therefore, in recent years, great efforts have been made regarding exhaust gas purification, the key word “exhaust gas catalyst” and alternative fuels. Thus, additionally or alternatively, there has long been a need for so-called “dual fuel engines”, ie engines that can be driven by two types of fuel, for the same reason. In the gas mode, a gas, for example a natural gas such as LNG (liquefied natural gas), or a gas in the form of a liquefied gasoline gas or another gas adapted for driving an internal combustion engine is burned, while in liquid mode Sometimes benzine, diesel, heavy oil or other adapted liquid fuel can be combusted in the same engine. The engine here can be a two-cycle engine or a four-cycle engine, where it can be a small engine, a medium-sized engine, even a large engine, in particular a uniflow scavenged two-cycle large diesel engine.

  Thus, a diesel engine characterized by self-ignition of fuel alongside the conventional two-cycle large diesel engine driven by heavy oil or diesel fuel within the framework of this application by the concept of “large diesel engine”. In addition to mode, large engines are also understood that can be driven in gasoline mode, characterized by external ignition of fuel, or in a mixed form of both. Furthermore, the concept of a large diesel engine includes, inter alia, the dual fuel engine described above, as well as a large engine in which fuel ignition is initiated by external ignition with another fuel.

  In the liquid mode, the fuel is generally fed directly into the combustion chamber of the cylinder by the injection nozzle and burned there by the self-ignition principle. In the gas mode, it is known that an air-fuel mixture that can be ignited in a combustion chamber of a cylinder is generated by mixing gas in a gas state with scavenging gas based on the Otto principle. In such a low pressure process, a small amount of liquid fuel is generally injected at a proper moment into the combustion chamber or pre-combustion chamber of the cylinder, so that the mixture is ignited in the cylinder. Ignition of the gas mixture is triggered. Dual fuel engines can often be switched from gas mode to liquid mode and vice versa during operation.

  However, pure gas engines, which can only be driven by gas and instead cannot be driven by diesel fuel, heavy oil or other fuels, are notable for economic reasons, especially because of the technical cost they can accept. There is a demand when a high exhaust gas reference value is required which can only be observed by combustion, and can therefore also be the subject of the following invention which will be described further below.

  Whether it is a dual fuel engine, a pure gas engine, or an engine driven by a liquid fuel such as benzine, diesel fuel, or heavy oil, or a mixed type engine of the type mentioned above. Similarly, it will be absolutely necessary in the future to purify or treat the exhaust gas with suitable equipment and methods before it is discharged to the environment.

  It is known to use exhaust gas reactors, especially so-called “SCR reactors”, in particular for the reduction of nitrogen oxides in exhaust gases.

  The concept of SCR is an English abbreviation “Selective Catalytic Reduction”, which can be colloquially referred to as a catalyst, and reduces nitrogen oxides in exhaust gas. This does not work, for example, in the case of an automobile with platinum catalyst material, and in the SCR reactor, the catalytic element is made of ceramic or metal, for example, and has a special reaction layer. However, the reduction reaction takes place in combination with the coating only when the exhaust gas is premixed with a suitable chemical, for example urea or ammonia, and urea must be vaporized in the exhaust gas to become ammonia. .

  For this mixing and vaporization, before entering the SCR reactor, a mixing channel of a certain length developed as a reaction material with exhaust gas, for example, a mixing and vaporizing tube for mixing and vaporizing urea is provided. Are known from the background art. In order to ensure reliable mixing and vaporization, the mixing flow path is conventionally arranged in the form of a mixing line between the exhaust gas and pipe collecting pipe and a specific minimum length SCR reactor. However, in the case of a solution known from the background art, the mixing line of the large engine known from the background art is in the hull because the mixing line extends from the engine, as will be further illustrated below in FIG. Requires an extremely large installation space, thereby obstructing a compact structure.

  It should be noted that only the mixing line does not require a significant amount of useful installation space as such. In a very large diesel engine with a large number of cylinder liners, for example 6, 8, 10, 12, or even 14 cylinder liners, often two or more than just one supercharged assembly On the contrary, it is necessary to provide three or more supercharging assemblies together with the turbocharger, and in the conventional background art, each turbocharger has a separate arrangement of mixing lines and exhaust gas reactors. Limit the huge use of additional installation space.

  The above problem is illustrated by a schematic diagram 2 showing a large diesel engine known from the background art with exhaust gas collecting pipe, mixing line, SCR reactor and supercharging assembly when only one turbocharger is installed. Is illustrated. If a plurality of turbochargers are installed, the background art conventionally provides a separate arrangement of mixing lines and SCR reactors, one for each individual turbocharger. Such a diagram with multiple turbochargers is abandoned here for space reasons, but the overall arrangement with multiple turbochargers is freely provided from FIG. 2 especially for those skilled in the art. ing.

  FIG. 2 shows a known large diesel engine with a mixing channel 12 ′ in the form of a mixing channel 121 ′ in which, for example, urea that vaporizes into ammonia in the exhaust gas 5 ′ is mixed into the exhaust gas collecting pipe 4 ′ and the exhaust gas 5 ′. -Shows engine 1 '. As already mentioned, regarding the reliable mixing and vaporization of urea with the exhaust gas 5 ′ before entering the SCR reactor 6 ′, as shown, the mixing channel 12 ′ developed as a mixing and vaporizing tube, as shown, and this A certain minimum length of the mixing line 121 'needs to be guaranteed. In order to be able to comply with this minimum length of the mixing line 121 'between the exhaust gas collecting pipe 4' and the SCR reactor 6 ', in the case of a large diesel engine known from the background art according to FIG. The conduit 121 ′ first extends from the engine via the connection 122 ′, so that there is sufficient space to comply with the required minimum length of the mixing conduit 121 ′.

  Without further explanation, it is directly from the schematic FIG. 2 that this structure guarantees reliable vaporization and mixing of urea from the exhaust gas collecting pipe 4 ′ into the exhaust gas 5 ′ entering the mixing pipe 121 ′. I can read it. But on the other hand, this structure requires a large amount of unacceptable space at the root, and such space cannot be secured, especially in the hull, or could be better used otherwise. Is.

  There are other problematic features in the structure, as will be readily appreciated by those skilled in the art. An important, per se known problem is that, in operation, a huge engine, often with a maximum output per cylinder or even exceeding 10,000 KW, to the surroundings and the components to which such an engine is mounted. This is the vibration that occurs. Marine engines known today are, for example, usually equipped with up to 12 cylinders, or even 14 cylinders, so that during operation so much vibration is attached to the hull and above all to the engine. Components, and even in exhaust gas systems, catalyst systems and turbocharger systems with supercharging assemblies, these can be used without appropriate countermeasures, for example vibration compensators. It can be severely damaged or otherwise destroyed. However, with such a free-supporting structure of the SCR catalyst system according to FIG. 2, in many cases even known vibration compensators are no longer sufficient to continually avoid such structural damage.

  However, for example in the case of the large diesel engine of FIG. 2, the additional line part and the longer path of the exhaust gas stream connected to it by means of the connection part 122 ′ or by other additional connections may also be used, for example in the case of a mixing line. In addition to the consumption of waste material, which is not desired at the root, as it is mounted between 121 ′ and the SCR reactor 6 ′ and between the SCR reactor 6 ′ and the supercharging assembly 71 ′, for example, Other negative technical effects, such as temperature and / or pressure drop of the exhaust gas 5 'in the pipeline system, which ultimately reduce the output of the turbocharger and are known per se to those skilled in the art. , Of course, which is undesirable and thus has its own set of other negative technical impacts that need to be avoided as much as possible.

  Therefore, according to the background art, the object of the present invention is to avoid the disadvantages known from the background art, in particular the arrangement of the exhaust gas system as space-saving as possible, and of the supercharged assembly with exhaust valves, cylinder liner and turbocharger. The aim is to propose an improved engine, in particular an exhaust gas catalyst system, in particular a crosshead large diesel engine with an SCR reactor, in which a shortening of the flow path between them is achieved. Another object of the present invention is to produce a reciprocating internal combustion engine, particularly a two-cycle large diesel engine, which can improve fuel efficiency at the same load and can reduce exhaust gas emissions comprehensively. It is to be.

  The object of the invention to solve these problems is characterized by the indicators of the independent claims.

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

  The present invention thus relates to a reciprocating internal combustion engine comprising a cylinder assembly of a plurality of cylinders and liners, each with one combustion chamber and one exhaust valve, in particular a two-flow large diesel engine with uniflow scavenging. The combustion chambers of the cylinder assembly of the cylinder / liner are connected to each other by a common exhaust gas collecting pipe, so that the exhaust gas from each combustion chamber of the cylinder assembly of the cylinder / liner is arranged in the respective operation during operation. The exhaust gas can be supplied to the exhaust gas collecting pipe through the exhaust gas valve, and the exhaust gas can be supplied from the exhaust gas collecting pipe to the exhaust gas / reactor in the purification mode for processing. Further, a supercharging unit including a first supercharging assembly for air compression is attached, and in the purification mode, exhaust gas can be supplied from the exhaust gas reactor so that air compressed by the first supercharging assembly can be supplied. May be supplied as scavenging to one or more cylinder liners and / or to one or more cylinder liners of a cylinder assembly via a scavenging opening, one for each. According to the invention, the mixing channel extends on the one hand to the region adjacent to the first supercharging assembly and on the other hand mainly through the mixing channel by extending at least partly in parallel with the collecting tube part of the exhaust gas collecting tube. The exhaust gas can be supplied to the exhaust gas reactor.

  Thus, what is important with the present invention is that the mixing flow path extends at least partially on the one hand in the region adjacent to the first supercharging assembly and on the other hand mainly parallel to the collecting pipe part of the exhaust gas collecting pipe, The exhaust gas can be supplied to the exhaust gas / reactor via the mixing channel.

  More clearly, between the exhaust gas collecting pipe and the exhaust gas turbocharger of the supercharging assembly, according to the invention, the exhaust gas coming from the exhaust gas collecting pipe is mixed or vaporized with the reactants, in particular urea or ammonia. Thereafter, a mixing channel, which is further fed into the exhaust gas reactor, is installed, particularly preferably in the form of a mixing line.

  Unlike the known engine according to the prior art, which has to add at least one mixing channel to each exhaust gas reactor individually, resulting in the additional consumption of the large installation space mentioned above, according to the present invention, For the first time, especially in the case of large diesel engines with a large number of cylinder liners, for example 6, 8, 10, 12 or even 14 cylinder liners, usually one each of two or more supercharging assemblies In a particularly preferred embodiment, it is possible to have only one mixing line and only one exhaust gas reactor, in which the exhaust gas treated from the exhaust gas reactor is Distributed to the feeder assembly. Here, in one particular embodiment where it is necessary to install a plurality of mixing channels or mixing lines for a specific reason, a previously unused space under the exhaust gas collecting pipe or under the collecting pipe part is included in the present invention. Thus, it will be appreciated that the present invention can still save a great deal of installation space because it is used by at least a portion of the length of the mixing channel.

  That is, in a special case of the engine according to the invention, especially in an engine with a large number of cylinder liners, for a specific reason, for example, two or more exhaust gas reactors or two or more exhaust lines and mixing lines and exhaust gas reactors are arranged. Of course, it is also possible to be attached.

  For this reason, for the first time according to the present invention, the number of exhaust gas reactors or the number of mixing lines and exhaust gas reactors can be reduced to an absolute minimum. It is only necessary to install one additional arrangement or one arrangement of the mixing line and the exhaust gas reactor, so that a great installation space is reduced. Not only that, the installation space can be reduced extensively only by the very compact arrangement of the mixing pipe flow path according to the invention, in particular the mixing pipe line between the exhaust gas collecting pipe and the turbocharged supercharging assembly.

  Furthermore, at the same time, the present invention solves the problems known from the above series of other background arts.

  Thus, in the case of the arrangement according to the invention, the above problems due to vibrations generated by the engine during operation are significantly reduced, which are ultimately limited by a particularly compact structure. Therefore, according to the present invention, the exhaust gas system is limited to a compact arrangement and a structure based on a compact structure, and an exhaust gas collecting pipe, an exhaust gas reactor with a mixing pipe, a turbocharger with an exhaust gas distribution pipe, In the case of the engine according to the invention, therefore, it is often realized automatically if already constrained to the structure, since the risk of damage from the generated vibrations of the exhaust system including the system is significantly reduced. There is no longer any need to take additional measures to reduce vibrations in the exhaust system components or in the exhaust system as a whole.

  The compact arrangement and structure of the exhaust gas system of the present invention also has another positive result, in particular that the above-mentioned additional conduits in the exhaust gas system are no longer necessary and can therefore be saved. Thereby, the longer path of the exhaust gas flow known from the background is naturally not desirable and is avoided by the present invention. This not only saves additional pipe material that is no longer needed, but also reliably avoids other negative technical effects originating from wasteful long paths in the known exhaust gas system due to the background art. The Thus, for example, the temperature and / or pressure drop of the exhaust gas in the exhaust gas system is significantly reduced, thereby improving the output of the turbocharger, which ultimately saves fuel, for example, at equivalent loads. And overall exhaust emissions are reduced, resulting in a positive impact on the environment.

  Here, the elimination of the additional pipelines will also improve the vibration characteristics as well, but the elimination of the additional pipelines will make the overall structure and arrangement of the exhaust gas system more compact and the final. In particular, the vibration technology is robust, so that the compensation of the generated vibrations can be improved, or the vibrations cannot be absorbed at all by the exhaust gas system or its components, resulting in additional damage. This is because the possibility of this is further reduced.

  In fact, in a particularly preferred embodiment, the reciprocating internal combustion engine is a large engine, in particular a uniflow scavenging two-cycle large diesel engine, and the mixing flow path or mixing line is at least partly more or less directly connected to the exhaust gas collection. Below the pipe, and therefore in the vertical direction, is arranged between the first supercharging assembly and on the one hand the second supercharging assembly and on the other hand the exhaust gas collecting pipe and adjacent to one cylinder liner.

  This, in particular, significantly shortens the supply line of the turbocharger to the exhaust gas and turbocharger and saves significant space, which can be used by service mechanics or other staff on the engine. Provided for gallery of engines that can be moved and for service work or other work. In addition, the shortening of the pipeline avoids at least some pressure loss, and the natural frequency of the exhaust gas equipment, especially also the exhaust gas collecting pipe, is positively influenced, thereby saving the material of those components. Can thus reduce costs.

  In one practically important embodiment, the exhaust gas collecting pipe is supported by a guide element in the form of a guide box and is fixed to a reciprocating internal combustion engine. Here, the guide box is formed as a connection flow path, and the flow is connected to the mixing flow path. Therefore, in the purification mode, the exhaust gas can be supplied to the mixing flow path via the guide box. Particularly preferably, the guide box or the connection flow path is further provided with a connection valve so that the exhaust gas flow from the exhaust gas collecting pipe to the mixing flow path is interrupted in the bypass mode, and therefore in the non-purification mode.

  Further important installation space here is that the mixing flow path is at least partly integrated, preferably completely in the exhaust gas collecting pipe, preferably parallel to the mixing pipe and parallel to the collecting pipe section, and in the exhaust gas collecting pipe, and This can be saved by forming the exhaust gas collecting pipe itself as a mixing channel. This, of course, saves more and more important space, as described above, and ultimately can further minimize material consumption and costs.

  In practice, in many cases, in addition to the first supercharging assembly, in addition to the first supercharging assembly, at least one second supercharging assembly for air compression is attached, which can supply exhaust gas from the exhaust gas reactor in the purification mode. Preferably, the air compressed by the first supercharging assembly and the second supercharging assembly is one for each of the one or more cylinder liners and / or one or more cylinder liners of the cylinder assembly. It can supply as scavenging via the arranged scavenging opening.

  In another embodiment of the present invention, which is of particular importance, the exhaust gas distribution pipe can supply exhaust gas from the exhaust gas reactor via the exhaust gas distribution pipes of the first and second supercharging assemblies. In the region adjacent to the cylinder liner and mainly parallel to the crankshaft of the internal combustion engine, between the first supercharging assembly and on the one hand the second supercharging assembly and on the other hand to the exhaust gas collecting pipe Is done. More simply, according to the present invention, an exhaust gas distribution pipe for distributing the exhaust gas sent from the exhaust gas / reactor to the turbocharger is installed between the exhaust gas collecting pipe and the exhaust gas / turbocharger of the supercharging assembly. Can do. This is the first time that a large engine, especially in the case of a uniflow scavenged two-cycle large diesel engine, discharges the treated exhaust gas from one and the same exhaust gas reactor into multiple supercharging assemblies or exhaust gas turbochargers. It becomes possible to distribute efficiently.

  In another embodiment of the invention, which is even better adapted in some cases to a specific internal combustion engine, the first supercharging assembly and the It can be arranged at the height of two supercharging assemblies, wherein the first supercharging assembly and the second supercharging assembly are arranged between the exhaust gas distribution pipe and any one adjacent cylinder liner.

  Preferably, the length of the exhaust gas distribution pipe can be shorter than that of the exhaust gas collecting pipe so that the flow can be connected to all exhaust gas turbochargers where the exhaust gas distribution pipe is just arranged. In addition, when not shortening length, it will protrude from a turbocharger, without being restrict | limited to arrangement | positioning.

  In another embodiment, it is possible that the mixing flow path is at least partially, but preferably fully integrated into the exhaust gas reactor, or an integrated assembly in which the exhaust gas reactor and the exhaust gas distribution pipe are in common Of course, it is also possible to form.

  Here, the exhaust gas collecting pipe, the mixing channel, the exhaust gas reactor and the exhaust gas distribution pipe can even be implemented in the form of a common integrated assembly in special cases, which is mainly parallel to the crankshaft of the internal combustion engine. Extending on the one hand in the region adjacent to the first and second supercharging assemblies and on the other hand adjacent to the cylinder liner.

  Of course, in practice, for example, when a vessel equipped with an engine according to the present invention is navigating an area where there are no strict exhaust emission regulations, the exhaust gas reactor does not need to be operated continuously, and thus, for example, for economic reasons, Or it may often be advantageous to temporarily shut down the exhaust gas reactor, for example for maintenance work.

  Therefore, the exhaust gas can be supplied to bypass the exhaust gas reactor in the exhaust gas distribution pipe and be guided further to the supercharging assembly or turbocharger, that is, the exhaust gas no longer flows into the exhaust gas reactor. The bypass pipe can be advantageously arranged and mounted. For this purpose, a further bypass pipe can be provided, for example, between the exhaust gas collecting pipe and the exhaust gas distribution pipe.

  The bypass pipe itself can be provided so that it can be shut off by, for example, a bypass valve. Here, the bypass pipe itself is not essential, but can be advantageously configured as a bypass valve depending on the embodiment. That is, the bypass valve functions as a bypass pipe. This can be particularly advantageous, for example, when the exhaust gas distribution pipe is arranged very close to the exhaust gas collecting pipe, for example in parallel therewith.

  Here again, of course, the exhaust gas collecting pipe is shut off by the exhaust gas collecting pipe valve so that the exhaust gas is no longer supplied from the exhaust gas collecting pipe to the exhaust gas / reactor in the operating state where exhaust gas purification or treatment of the exhaust gas is not necessary as described above. can do. For this purpose, the exhaust gas distribution pipe can no longer be shut off by the exhaust gas distribution valve so that the exhaust gas cannot be supplied from the exhaust gas / reactor to the exhaust gas distribution pipe.

  In a further embodiment of the present invention, the exhaust gas collecting pipe comprises a first exhaust gas collecting chamber and a second exhaust gas collecting chamber in fluid communication with the first exhaust gas collecting chamber from the first assembly of the cylinder liner. So that the exhaust gas from the second assembly of the cylinder liner can only be supplied directly to the second exhaust gas collecting chamber, where the first exhaust gas collecting chamber can be supplied directly to the first exhaust gas collecting chamber. Particularly preferably, a compensation section for compensating for mechanical and / or thermal stress and / or elongation is provided between the exhaust gas collecting chamber and the second exhaust gas collecting chamber.

  This not only can better compensate for other types of thermal expansion or mechanical stress, such as vibrations, for example, but it can also optimize the distribution of the exhaust gas flow in the exhaust gas collecting pipe. The mutual influence of the exhaust gas flows from the various cylinder liners connected simultaneously to the exhaust gas collecting pipe can be at least sufficiently prevented or minimized.

  Exactly the same, the exhaust gas distribution pipe has a first exhaust gas distribution chamber and a second exhaust gas distribution chamber whose flow is connected to the first exhaust gas distribution chamber, and passes through the first bypass valve from the first bypass pipe or the exhaust gas collecting pipe. The exhausted gas can be directly supplied only to the first exhaust gas distribution chamber, and the exhaust gas that has passed through the second bypass pipe or the second bypass valve from the exhaust gas collecting pipe can be directly supplied only to the second exhaust gas collecting chamber. In addition, a flow is connected to the exhaust gas collecting pipe.

  In a particularly advantageous variant of the previously described embodiment of the invention, the exhaust gas from the first exhaust gas collecting chamber of the exhaust gas collecting pipe is only passed through the first bypass pipe or the first bypass valve into the first exhaust gas distribution chamber. The exhaust gas from the second exhaust gas collecting chamber of the exhaust gas collecting pipe is directly supplied, and is directly supplied only to the second exhaust gas collecting chamber through the second bypass pipe or the second bypass valve.

  Here, in each corresponding embodiment, there is preferably a compensation connection between the first exhaust gas distribution chamber and the second exhaust gas distribution chamber for compensating for mechanical and / or thermal stresses and / or expansions. Can be provided. This not only can better compensate for other types of thermal elongation or mechanical stress, such as vibrations, but can also optimize the distribution of exhaust gas flow in the exhaust gas distribution pipes. The mutual influences of the exhaust gas flows from the various exhaust gas collecting pipes and bypass pipes that are simultaneously connected to the distribution pipes can be at least sufficiently prevented or minimized.

  Here in the same way, the mixing channel, in particular the mixing line, can also be provided with a first mixing chamber and a second mixing chamber, mechanically and / or between the first mixing chamber and the second mixing chamber. Obviously, it is possible to attach a compensation tube for compensation of thermal stress and / or expansion.

  Of course, 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 collecting valve and / or the exhaust gas distribution valve, can also be controlled or adjusted, in particular electrically or hydraulically or It is self-evident that it can be controlled or adjusted pneumatically, particularly advantageously by means of a computer-controlled device, depending on the settable operating parameters of the reciprocating internal combustion engine.

  For this purpose, for example, as is known per se, sensors, in particular exhaust gas sensors, temperature sensors, pressure sensors or bypass valves, in particular first and / or second bypass valves and / or exhaust gas collecting valve And / or another sensor adapted for control or adjustment of the exhaust gas distribution valve can also be fitted appropriately.

  In order to further optimize the flow of the exhaust gas, the exhaust gas collecting pipe, in particular the first exhaust gas collecting chamber and / or the second exhaust gas collecting chamber, introduces the flow guide device, in particular the flow guide plate, into the exhaust gas collecting pipe. In particular, the exhaust gas can be distributed over different parts of the exhaust gas distribution pipe, in special cases on the first exhaust gas distribution chamber and the second exhaust gas distribution chamber of the exhaust gas distribution pipe.

  Exactly the same and for the same purpose, the exhaust gas distribution pipes, in particular the first exhaust gas distribution chamber and / or the second exhaust gas distribution chamber, are of course also used for the induction and distribution of the exhaust gas in the induction device, in particular the exhaust gas distribution pipe, in particular the excess Guidance plates can be provided for the distribution of the exhaust gas on the different exhaust gas turbochargers of the charging unit, in particular on the first and second supercharging assemblies of the supercharging unit, of course during the induction Also an orifice plate, in particular an orifice plate that can be controlled or adjusted, can be provided so that the gas flow can be controlled or adjusted by the orifice plate.

  For fixing, exhaust gas collecting pipes and / or mixing channels, in particular mixing pipes and / or exhaust gas distribution pipes, are particularly preferred, but do not have to be supported and / or guided by a common guide element, here The element is advantageously a guide plate, a guide box or another suitable induction or fixation device for fixing and induction of the exhaust gas collecting pipe and the exhaust gas distribution pipe.

  Here, the guide element is in fact very advantageously formed and the exhaust gas collecting pipe and / or the mixing flow path, in particular the mixing pipe and / or the exhaust gas distribution pipe, are arranged in the guide element. Even mechanical and / or thermally limited stresses and / or expansions or vibrations of the exhaust gas distribution pipes or other mechanical components can be at least partially compensated.

  Guide elements, in particular guide plates and / or guide boxes, can compensate for mechanical and / or thermally limited stresses and / or expansions and / or vibrations of exhaust gas collecting pipes and exhaust gas distribution pipes and / or It is particularly advantageous that it can be advantageously arranged to move within the slide shoe for adjustment.

  The invention further relates to a mixing channel, in particular to a mixing channel for a reciprocating internal combustion engine according to the invention described in the present application, wherein the mixing channel of the present invention is, in a special embodiment, an exhaust gas. It is a combination of mixing channels that can comprise a collecting pipe and / or an exhaust gas distribution pipe and / or an exhaust gas reactor.

  The invention is described in more detail below by means of the drawings. Shown schematically.

1 is a schematic diagram of an exhaust gas turbocharger system known from the background art of a two-cycle large diesel engine. It is a known large diesel engine with an SCR reactor for exhaust gas treatment. 1 is a perspective view of a first embodiment of a two-cycle large diesel engine according to the present invention with a mixing line under an exhaust gas collecting pipe. FIG. Fig. 3b is a side view of the embodiment according to Fig. 3a. Fig. 3b is a third view of the embodiment according to Fig. 3a. FIG. 3 is a schematic view of a second embodiment of a two-cycle large diesel engine according to the present invention with a guide box developed as a connection flow path with a connection valve. FIG. 5 shows a second embodiment according to FIG. 1 is an example of a two-cycle large diesel engine according to the present invention with a mixing line under the collecting pipe. An exhaust gas collecting pipe or an exhaust gas distribution pipe and a compensation part or a compensation connection part. 1 is a first example of an exhaust gas collecting pipe having an exhaust gas diversion device and an orifice plate. Fig. 7a is another embodiment according to Fig. 7a. Fig. 7a is a third embodiment according to Fig. 7a. 1 is a first embodiment of an exhaust gas distribution pipe with an exhaust gas induction device and an orifice plate. Fig. 8a is another embodiment according to Fig. 8a. FIG. 9c is a third embodiment according to FIG. 8a. FIG. 10 shows a guide element with a slide shoe, an exhaust gas collecting pipe and a mixing pipe flow path.

  1 and 2 relate to an example according to the background art and have already been explained in detail at the beginning, and need not be discussed again here.

  The reciprocating internal combustion engine according to the present invention, which is generally indicated below by reference numeral 1, is designed to be used extensively, for example in shipbuilding, especially designed as a two-cycle large diesel engine with uniflow scavenging.

  3a, 3b, and 3c, a first embodiment of the two-cycle heavy-duty diesel engine according to the invention of FIG. 3a is shown in perspective view with a mixing line under the exhaust gas collecting pipe, according to the invention. An important part of the present invention of a reciprocating internal combustion engine is shown in a special embodiment of a uniflow scavenging two-cycle large diesel engine with multiple cylinder liners for use on a ship, for example a container ship. . Here, FIG. 3b is merely a side view, while FIG. 3c is a front view of the engine according to FIG. 3a, which is shown to make the interaction of important components more understandable.

  The reciprocating internal combustion engine 1 according to the invention according to FIG. 3a or 3b and 3c comprises a plurality of cylinder liners GZ1, GZ2 with one combustion chamber 2 and one exhaust valve 3 in a manner known per se. This is a uniflow scavenging two-cycle large diesel engine equipped with a cylinder assembly GZ, and the combustion chambers 2 of the cylinder assemblies GZ of the cylinder liners GZ1 and GZ2 are connected to each other by a common exhaust gas collecting pipe 4. Thus, during operation, the exhaust gas 5 from each combustion chamber 2 of the cylinder assembly GZ of the cylinder liners GZ1 and GZ2 can be supplied to the exhaust gas collecting pipe 4 via the exhaust gas valves 3 arranged respectively. It has become. In order to treat or purify, that is, mainly to remove dangerous nitrogen oxides in the exhaust gas 5, the exhaust gas 5 in the exhaust gas collecting pipe 4 is exhausted via a mixing channel 12 developed as a mixing conduit in the purification mode. -It can be fed into the reactor 6.

  In addition, the supercharging unit 7 uses the first supercharging assembly 71 and the second supercharging assembly 72 to compress the air 80 sucked from the surroundings by one turbocharger of each of the supercharging assembly 71 and the supercharging assembly 72. The supercharging assemblies 71 and 72 can supply the exhaust gas 5 from the exhaust gas reactor 6 in the purification mode, but are compressed by the first supercharging assembly 71 and the second supercharging assembly 72. The air 80 is supplied to the cylinder liner Z or the cylinder liners GZ1 and GZ2 of the cylinder assembly GZ as scavenging air through a scavenging opening that is not shown in FIGS. 3a to 3c. It can be supplied.

  In the example of FIGS. 3a to 3c, here, by way of example, a mixing line 121, an exhaust gas reactor 6 and a supercharging assembly 7, 71, 72, for the sake of operational efficiency, here by a plurality of cylinder liners Z The two required arrangements are shown schematically.

  According to the invention, the mixing flow path 12 extends at least partly on the one hand in the region adjacent to the first supercharging assembly 71 and on the other hand mainly in parallel with the collecting pipe part 401 of the exhaust gas collecting pipe 4. The exhaust gas 5 can be supplied to the exhaust gas / reactor 6 via the passage 12.

  Here, the mixing passage 12 is mainly at least partly between the exhaust gas collecting pipe 4 on the one hand and the crankshaft 11 of the reciprocating internal combustion engine 1 on the other hand with respect to the vertical direction VR of the reciprocating internal combustion engine 1. It extends parallel to the tube 4. In the mixing channel 12, the exhaust gas 5 can be supplied to the exhaust gas / reactor 6 via the mixing channel 12. The mixing channel 12 is connected between the exhaust gas collecting pipe 4 and the exhaust gas / reactor 6. It arrange | positions so that it may become a form of this and is attached in an exhaust gas apparatus.

  In the following according to FIGS. 4 and 5, a schematic second embodiment of a two-cycle heavy-duty diesel engine 1 according to the invention will be discussed by means of a guide box 142 developed as a connection channel 130 with a connection valve V130.

  4 and 5 show each one guide / developed as a connecting flow path 130, each having one connecting valve V 130 between the exhaust gas collecting pipe 4 and the mixing flow path 12 developed as the mixing pipe 121. Box 142 is shown. In this practically particularly preferred embodiment, the mixing line 121 is arranged directly in the guide box 142 under the exhaust gas collecting pipe 4, and the connection valve V130 simultaneously forms a connection flow path 130 in the guide box 142, which As a result, the additional connection flow overflows in principle, so that space is particularly reduced. Here, in the bypass mode, the exhaust gas collecting pipe 4 can be shut off by the exhaust gas collecting pipe valve 40 so that the exhaust gas 5 can no longer be supplied from the exhaust gas collecting pipe 4 to the exhaust gas reactor 6.

  In addition, the exhaust gas distribution pipe 10 can be shut off by the exhaust gas distribution valve 100 so that the exhaust gas 5 of the exhaust gas distribution pipe 10 can no longer be supplied directly from the exhaust gas collecting pipes 4, 401. That is, when the exhaust gas reactor 6 is not required in a specific operating state of the reciprocating internal combustion engine 1 or is deactivated for another reason, the exhaust gas reactor 6 and the mixing channel 12 are disconnected from the exhaust gas system. Here, it is carried out by closing the exhaust gas collecting pipe valve 40 and simultaneously opening the exhaust gas distributing valve 10, and the exhaust gas 5 passes through the guide box 142 and the exhaust gas distribution pipe 10 from the exhaust gas collecting pipe 4. Thus, it becomes possible to supply directly to the turbochargers of the supercharging assemblies 7, 71, 72 not shown in FIG.

  In the case of the special embodiment of FIG. 6, the mixing flow path 12 is integrated with the exhaust gas collecting pipe 4 under the collecting pipe section 401 in the form of a mixing pipe 121. Here, the exhaust gas 5 is supplied directly to the mixing channel 12 via the supply valve DV, or the supercharging assembly 7 is closed by closing the supply valve DV and opening the exhaust gas collecting pipe valve 40 during the bypass mode. , 71, 72 can be supplied directly via the exhaust gas distribution pipe 10 when equipped.

  FIG. 7 schematically shows the exhaust gas collecting pipe 4 or the exhaust gas distribution pipe 10 with the compensation part 400 or the compensation connection part 500, where the mixing channel can be extended in parallel with the exhaust gas collection pipe 4 and / or the exhaust gas distribution pipe 10, for example. 12 and 121 are not explicitly shown for the sake of clarity.

  Here, the exhaust gas distribution pipe 10 is mainly shown in FIG. 7 so that the exhaust gas 5 can be supplied from the exhaust gas / reactor 6 via the exhaust gas distribution pipe 10 of the first supercharging assembly 71 and the second supercharging assembly 72. Not shown, parallel to the crankshaft 11 at a much lower position of the internal combustion engine 1, on the one hand in the adjacent region of the first supercharging assembly 71 and the second supercharging assembly 72, on the other hand of the reciprocating internal combustion engine 1 The exhaust gas collecting pipe 4 and the crankshaft 11 are disposed below the exhaust gas collecting pipe 4 with respect to the vertical direction VR. In a special embodiment, the exhaust gas distribution pipe 10 has a first supercharging assembly 71, one between the second supercharging assembly 72, the other between the exhaust gas collecting pipe 4 and the cylinder liner Z, in the vertical direction VR. Arranged adjacent to one of GZ1 and GZ2.

  In the case of this particularly preferred embodiment, according to FIG. 7, the exhaust gas collecting pipe 4 and the exhaust gas distribution pipe 10, which clearly show each one compensation part 400 or compensation connection 500 for compensation of mechanical or thermal stresses or other disturbances. Is attached. Here, the exhaust gas 5 from the first assembly EZ1 of the cylinder liner Z can be directly supplied only to the first exhaust gas collecting chamber 41, and the exhaust gas 5 from the second assembly EZ2 of the cylinder liner Z is supplied to the second exhaust gas collecting chamber. The exhaust gas collecting pipe 4 includes a first exhaust gas collecting chamber 41 and a second exhaust gas collecting chamber 42 in which a flow is connected to the first exhaust gas collecting chamber 41 so that only the gas can be supplied directly to 42.

  As already mentioned herein, there is a mechanical and / or thermal stress and / or expansion and / or vibration or other mechanical or heat between the first exhaust gas collecting chamber 41 and the second exhaust gas collecting chamber 42. A compensator 400 is attached for compensating for mechanical disturbances.

  In addition, the exhaust gas distribution pipe 10 includes a first exhaust gas distribution chamber 101 and a second exhaust gas distribution chamber 102 whose flow is connected to the first exhaust gas distribution chamber 101, and passes through the first bypass valve 1311 from the exhaust gas collecting pipe 4. The exhaust gas 5 can be supplied directly only to the first exhaust gas distribution chamber 101, and the exhaust gas 5 that has passed through the second bypass valve 1312 from the exhaust gas collection pipe 4 can be supplied directly only to the second exhaust gas collection chamber 102. In addition, a flow is connected to the exhaust gas collecting pipe 4. Here, the exhaust gas 5 that has passed through the first bypass valve 1311 from the first exhaust gas collecting chamber 41 of the exhaust gas collecting pipe 4 can be directly supplied only to the first exhaust gas distribution chamber 101, and the second exhaust gas collecting chamber of the exhaust gas collecting pipe 4. The exhaust gas 5 from 42 through the second bypass valve 1312 can be directly supplied only to the second exhaust gas collecting chamber 102. Similar to the exhaust gas collecting pipe 4, a compensation connection 500 is provided between the first exhaust gas distribution chamber 101 and the second exhaust gas distribution chamber 102 with mechanical and / or thermal stress and / or expansion and / or vibration and / or others. It is attached to compensate for mechanical or thermal faults.

  The bypass valve 131, here in particular the first bypass valve 1311 and / or the second bypass valve 1312 and / or the exhaust gas collecting valve 40 which is not specified and / or the exhaust gas distribution valve 100 which is also not specified, is particularly preferably controlled here. Or can be adjusted, and in particular can be controlled or adjusted electrically, hydraulically or pneumatically. For this purpose, sensors, in particular exhaust gas sensors, temperature sensors or pressure sensors, or bypass valves 131, in particular the first bypass valve 1311 and / or the second bypass valve 1312 and / or the exhaust gas collecting pipe valve 40 and / or the exhaust gas distribution valve 100. Other sensors adapted for the control or adjustment of the can also be fitted appropriately.

  FIG. 8a further schematically shows a particularly preferred first embodiment of the exhaust gas collecting pipe 4 with the flow guides 15, 151 for the exhaust gas 5, where an orifice plate B which can be controlled or adjusted is mounted. Therefore, the gas flow can be controlled or adjusted by the orifice plate B. FIG. 8b shows another embodiment according to FIG. 8a, while FIG. 8c shows a third embodiment according to FIG. 8a.

  As can be seen from FIGS. 8 a to 8 c, the exhaust gas collecting pipe 4, particularly the first exhaust gas collecting chamber 41 and / or the second exhaust gas collecting chamber 42, introduces the flow guide devices 15, 151, particularly the flow guide plate 151 into the exhaust gas collect pipe 4. For the introduction and distribution of the exhaust gas 5 in the exhaust gas 5, especially on the first exhaust gas distribution chamber 101 and the second exhaust gas distribution chamber 102 of the exhaust gas distribution pipe 10, especially in different parts of the exhaust gas distribution pipe 10. Is distributed. If the skilled person simply decides by his expertise whether any of the embodiments according to FIGS. 8a to 8c, or in some cases, simple and non-inventive developments of these embodiments can actually be used. I know what to do and how to apply it in a specific actual case.

  FIG. 9 shows a first embodiment of the exhaust gas distribution pipe 10 with the flow guide devices 16 and 161 for the exhaust gas 5, where an orifice plate B that can be controlled or adjusted is attached. The gas flow can be controlled or adjusted by the orifice plate B.

  FIG. 9b shows another embodiment according to FIG. 9a, while FIG. 9c shows a third embodiment according to FIG. 9a. Here, the exhaust gas distribution pipe 10, in particular the first exhaust gas distribution chamber 101 and / or the second exhaust gas distribution chamber 102, guides and distributes the induction device 16, 161, in particular the guide plate 161, in the exhaust gas distribution pipe 10. In particular, the exhaust gas 5 is distributed on different exhaust gas turbochargers of the supercharging unit 7, that is, on the first supercharging assembly 71 and the second supercharging assembly 72 of the supercharging unit 7. How can one of ordinary skill in the art simply determine, by his expertise, which of the embodiments according to FIGS. 9a to 9c, or whether simple and non-inventive developments of these embodiments are actually usable, I also know how to apply it in specific actual cases.

  FIG. 10 is of particular importance in practice for the guide elements 14, 141, in which it is advantageous in the end that in addition to the guide box, additionally the exhaust gas collecting pipe 4 and the exhaust gas distribution pipe 10 can be fixed together on the engine. A special embodiment is shown by way of example, in which the exhaust gas collecting pipe 4 and the exhaust gas distribution pipe 10 are supported and / or guided by a common guide element 14, 141. By means of the additional guide elements 14, 141, the exhaust gas collecting pipe 4 with the exhaust gas distribution pipe 10 is better fixed to the engine, for example, thermal expansion is even better compensated, and the vibration characteristics affected by the vibration are Significantly improved.

  The guide elements 14, 141 according to FIG. 10 are here formed in the form of guide plates 141, which may also cause thermal expansion of the exhaust gas collecting pipe and / or the exhaust gas collecting pipe 10, as well as other mechanical stresses such as mechanical Disturbances such as vibrations are also particularly well suited for receiving or compensating for mechanical vibrations that can occur very severely, for example in the operating state of a reciprocating internal combustion engine. Here, it is possible to compensate for thermal expansion or vibration in the longitudinal direction of the exhaust gas collecting pipe 4 or the exhaust gas collecting pipe 10, and it is also possible to compensate for a vertical one. This is possible, inter alia, by the construction of the guide plate as a relatively thin plate and by a special shape that can be adapted to the individual case. What is special here is that the guide elements 14, 141 in FIG. 10, in particular the guide plate 141 and / or the guide box 142, are mechanically and / or thermally limited in the exhaust gas collecting pipe 4 and the exhaust gas distribution pipe 10. To be able to move within the slide shoe 1400 for compensation and / or adjustment of stress and / or expansion and / or vibration.

  The person skilled in the art realizes that the present invention is not limited to the embodiments discussed explicitly, and that corresponding developments are likewise protected by the present invention. In particular, the invention relates to all suitable combinations of the specific embodiments discussed, which are self-evident.

Claims (36)

  A reciprocating internal combustion engine comprising a cylinder assembly (GZ) of a plurality of cylinder liners (GZ1, GZ2) with each one combustion chamber (2) and an exhaust gas valve (3) arranged in each, especially a uniflow scavenging system The two-cycle large diesel engine, wherein when operating, the exhaust gas (5) is disposed from each combustion chamber (2) of the cylinder assembly (GZ) of the cylinder liner (GZ1, GZ2). It can be supplied to the exhaust gas collecting pipe (4) via a valve (3). In the purification mode, the exhaust gas (5) from the exhaust gas collecting pipe (4) is treated for treatment in an exhaust gas reactor (6). Each of the combustion chambers (2) is provided in the cylinder liner (GZ1, GZ2) of the cylinder liner (GZ1, GZ2) with a common exhaust gas collecting pipe (4). The turbocharger (GZ) is connected to the flow, and further includes a supercharging unit (7, 71, 72) capable of supplying the exhaust gas (5) from the exhaust gas reactor (6) in the purification mode. The first supercharging assembly (71) is mounted for compression of air (80) so that the air (80) compressed by the first supercharging assembly (71) is one or more cylinders. Supply to the liner (Z) and / or one or more of the cylinder liners (GZ1, GZ2) of the cylinder assembly (GZ) as scavenging via a scavenging opening, one each arranged A reciprocating internal combustion engine, in particular a uniflow scavenging two-cycle large diesel engine, wherein the mixing flow path (12) is on the one hand the first supercharging assembly ( 1) at least partially mainly so that the exhaust gas (5) can be supplied to the exhaust gas reactor (6) in the region adjacent to 1) and on the other hand via the mixing channel (12). A reciprocating internal combustion engine, particularly a uniflow scavenging two-cycle large diesel engine, characterized by extending in parallel with the collecting pipe portion (401) of the exhaust gas collecting pipe (4).   The mixing passage (12) is between the exhaust gas collecting pipe (4) on the one hand and the crankshaft (11) of the reciprocating internal combustion engine on the other hand, with respect to the vertical direction (VR) of the reciprocating internal combustion engine. The reciprocating internal combustion engine according to claim 1, wherein the reciprocating internal combustion engine extends at least partially mainly in parallel with the exhaust gas collecting pipe (4).   The reciprocating internal combustion engine according to claim 1 or 2, wherein the mixing passage (12) is developed as a mixing pipe (121).   The exhaust gas collecting pipe (4) is supported by a guide element (14, 142) in the form of a guide box (142) and is fixed to the reciprocating internal combustion engine. In the purification mode, the guide box (142 ), The guide box (142) is formed as a connection channel (130) so that the exhaust gas (5) can be supplied to the mixing channel (12). The reciprocating internal combustion engine according to any one of claims 1 to 3, wherein the flow is connected to 12).   When the guide box (142) or the connection flow path (130) includes a connection valve (V130), the exhaust gas flow from the exhaust gas collecting pipe (4) can flow in the mixing flow path (12) in the bypass mode. The reciprocating internal combustion engine according to claim 4, wherein   The exhaust gas collecting pipe (12) is at least partially, preferably completely within the exhaust gas collecting pipe (4), preferably parallel to the collecting pipe part (401) as a mixing pipe (121). The reciprocating device according to any one of claims 1 to 5, wherein the reciprocating device is integrated in parallel in (4) and / or the exhaust gas collecting pipe (4) itself is formed as a mixing channel (12). Internal combustion engine.   In addition to the first supercharging assembly (71), at least one second supercharging assembly (72) is mounted for the compression of air (80), and during the purification mode the exhaust gas (5) is By being able to supply from the exhaust gas reactor (6), the first supercharging assembly (71) and the second supercharging assembly (72) allow one or more cylinders of the cylinder assembly (GZ) Supplying compressed air (80) as scavenging via a scavenging opening, each arranged one by one in the liner (Z) and / or one or more of the cylinder liners (GZ1, GZ2) The reciprocating internal combustion engine according to any one of claims 1 to 6, wherein   The exhaust gas (5) can be supplied from the exhaust gas reactor (6) to the first supercharging assembly (71) and the second supercharging assembly (72) via the exhaust gas distribution pipe (10). Thus, the exhaust gas distribution pipe (10) is at least partly parallel to the crankshaft (11) of the reciprocating internal combustion engine, while the first supercharging assembly (71) and the second supercharging assembly ( 72) and on the other hand, with respect to the vertical direction (VR) of the reciprocating internal combustion engine, the exhaust gas collecting pipe (4), preferably the mixing flow path (12) and the crankshaft (11). The reciprocating internal combustion engine according to any one of claims 1 to 7, which extends between   The exhaust gas distribution pipe (10) is in the vertical direction (VR), the first supercharging assembly (71), one of the second supercharging assembly (72) and the other of the exhaust gas collecting pipe (4). 9. A reciprocating internal combustion engine according to claim 8, preferably disposed between and adjacent to one of said cylinder liners (Z, GZ1, GZ2).   The exhaust gas distribution pipe (10) is disposed at a height of the first supercharging assembly (71) and the second supercharging assembly (72) with respect to the vertical direction (VR), and the first supercharging The assembly (71) and the second supercharging assembly (72) are arranged between the exhaust gas distribution pipe (10) and one cylinder liner (Z, GZ1, GZ2) adjacent to the exhaust gas distribution pipe (10). A reciprocating internal combustion engine according to claim 9.   Reciprocating type according to any one of the preceding claims, wherein the mixing channel (12) and the exhaust gas reactor (6) at least partly, preferably completely form an integral unit. Internal combustion engine.   The reciprocating internal combustion engine according to any one of claims 8 to 11, wherein the exhaust gas reactor (6) and the exhaust gas distribution pipe (10) form a common integrated assembly.   The exhaust gas collecting pipe (4), the mixing channel (12), the exhaust gas reactor (6), and the exhaust gas distribution pipe (10) are attached in the form of a common integrated assembly, and are mainly used for the internal combustion engine. Parallel to the crankshaft (11), on the one hand in the region adjacent to the first supercharging assembly (71) and the second supercharging assembly (72) and on the other hand cylinder liners (GZ1, GZ2, Z) The reciprocating internal combustion engine according to any one of claims 1 to 12, which extends adjacent to one of the two.   Bypassing the exhaust gas reactor (6) of the supercharging unit (7, 71, 72), in particular the first supercharging assembly (71) and / or the second supercharging assembly (72), in particular the supercharging The bypass pipe (13) is arranged and attached so that the exhaust gas (5) can be supplied via the exhaust gas distribution pipe (10) of the supply unit (7, 71, 72). Item 14. The reciprocating internal combustion engine according to any one of Items 1 to 13.   The reciprocating internal combustion engine according to claim 14, wherein the bypass pipe (13) is attached between the exhaust gas collecting pipe (4) and the exhaust gas distribution pipe (10).   The reciprocating internal combustion engine according to claim 14 or 15, wherein the bypass pipe (13) can be shut off by a bypass valve (131).   The reciprocating internal combustion engine according to claim 16, wherein the bypass pipe (13) is developed as a bypass valve (131).   The exhaust gas collecting pipe (4), in particular the collecting pipe part (401), is arranged to collect exhaust gas so that the exhaust gas (5) can no longer be supplied from the exhaust gas collecting pipe (4) to the exhaust gas reactor (6). The reciprocating internal combustion engine according to any one of claims 1 to 17, wherein the reciprocating internal combustion engine can be shut off by a pipe valve (40).   The exhaust gas distribution pipe (10) may be shut off by the exhaust gas distribution valve (100) so that the exhaust gas (5) can no longer be supplied from the exhaust gas reactor (6) to the exhaust gas distribution pipe (10). The reciprocating internal combustion engine according to any one of claims 1 to 18, which is capable.   The exhaust gas (5) from the first assembly (EZ1) of the cylinder liner (Z) can be supplied directly only to the first exhaust gas collecting chamber (41), and the second assembly of the cylinder liner (Z) ( The exhaust gas collecting pipe (4) is connected to the first exhaust gas collecting chamber (41) so that the exhaust gas (5) from EZ2) can be directly supplied only to the second exhaust gas collecting chamber (42). The reciprocating internal combustion engine according to any one of claims 1 to 19, further comprising the second exhaust gas collecting chamber (42) connected in flow with the first exhaust gas collecting chamber (41).   A compensation unit (400) for compensating for mechanical and / or thermal stress and / or expansion is attached between the first exhaust gas collecting chamber (41) and the second exhaust gas collecting chamber (42). The reciprocating internal combustion engine according to claim 20.   The exhaust gas distribution pipe (10) includes a first exhaust gas distribution chamber (101) and a second exhaust gas distribution chamber (102) whose flow is connected to the first exhaust gas distribution chamber (101). The exhaust gas (5) from the pipe (4) via the first bypass valve (1311) can be directly supplied only to the first exhaust gas distribution chamber (101), and the second bypass valve (1312) is supplied from the exhaust gas collecting pipe. The flow is connected to the exhaust gas collecting pipe (4) so that the exhaust gas (5) that has passed through) can be supplied directly only to the second exhaust gas collecting chamber (102). The reciprocating internal combustion engine according to any one of the above.   The exhaust gas (5) from the first exhaust gas collecting chamber (41) of the exhaust gas collecting pipe via the first bypass valve (1311) can be directly supplied only to the first exhaust gas distribution chamber (101), The exhaust gas (5) from the second exhaust gas collecting chamber (42) of the exhaust gas collecting pipe via the second bypass valve (1312) can be directly supplied only to the second exhaust gas collecting chamber (102). 23. A reciprocating internal combustion engine according to 22.   Between the first exhaust gas distribution chamber (101) and the second exhaust gas distribution chamber (102), a compensation connection (500) for mechanical and / or thermal stress and / or expansion compensation is mounted. 24. A reciprocating internal combustion engine according to claim 22 or 23.   The mixing channel (12), in particular, the mixing pipe (121) includes a first mixing chamber (1201) and a second mixing chamber (1202), and the first mixing chamber (1201) and the second mixing chamber. Reciprocating system according to any one of claims 1 to 24, wherein a compensation tube (600) for mechanical and / or thermal stress and / or expansion compensation is mounted during (1202). Internal combustion engine.   The connection valve (V130) and / or the bypass valve (131), in particular the first bypass valve (1311) and / or the second bypass valve (1312) and / or the exhaust gas collecting pipe valve (40) and / or 26. Reciprocating internal combustion engine according to any one of claims 5 to 25, wherein the exhaust gas distribution valve (100) is controllable or adjustable, in particular electrically or hydraulically or pneumatically controllable or adjustable. organ.   Sensors, in particular exhaust gas sensors, temperature sensors or pressure sensors, are connected to the connection valve (V130) and / or the bypass valve (131), in particular the first bypass valve (1311) and / or the second bypass valve (1312) and / or 27. A reciprocating internal combustion engine according to claim 26, adapted or adapted for control or adjustment of the exhaust gas collecting pipe valve (40) and / or the exhaust gas distribution valve (100).   The exhaust gas collecting pipe (4), in particular, the first exhaust gas collecting chamber (41) and / or the second exhaust gas collecting chamber (42) serves as a flow guide device (15, 151), particularly a flow guide plate (151) as the exhaust gas. Provided for the flow and distribution of the exhaust gas (5) in the collecting pipe (4), in particular the exhaust gas (5) for different parts of the exhaust gas distribution pipe (10), in special cases the exhaust gas distribution The reciprocating internal combustion engine according to any one of claims 1 to 27, wherein the reciprocating internal combustion engine is provided for distribution on the first exhaust gas distribution chamber (101) and the second exhaust gas distribution chamber (102) of piping. .   The exhaust gas distribution pipe (10), in particular the first exhaust gas distribution chamber (101) and / or the second exhaust gas distribution chamber (102) is the induction device (16, 161), in particular the induction plate (161) is the exhaust gas distribution pipe. (10) for the induction and distribution of the exhaust gas (5), in particular the exhaust gas (5) on a different exhaust gas turbocharger of the supercharging unit (7), in particular the supercharging unit ( Reciprocating internal combustion engine according to any one of claims 8 to 28, provided for distribution on the first supercharging assembly (71) and the second supercharging assembly (72) of 7). organ.   30. A reciprocating internal combustion engine according to claim 28 or 29, wherein a gas flow can be controlled or regulated by means of the orifice plate (B) by being able to attach a controllable or adjustable orifice plate (B).   The exhaust gas collecting pipe (4) and / or the mixing flow path (12), in particular the mixing pipe line (121) and / or the exhaust gas distribution pipe (10) are supported by a common guide element (14, 141) and The reciprocating internal combustion engine according to any one of claims 1 to 30, wherein the reciprocating internal combustion engine is induced.   32. A reciprocating internal combustion engine according to claim 31, wherein the guide element (14, 141) is a guide plate (141) or a guide box (142).   The guide element (14, 141) is so formed and the exhaust gas collecting pipe (4) and / or the mixing flow path (12), in particular the mixing pipe line (121) and / or the exhaust gas distribution pipe ( 10) is arranged in it so that mechanical and / or thermally limited stresses and / or expansions of the exhaust gas collecting pipe (4) and the exhaust gas distribution pipe (10) are at least partly. The reciprocating internal combustion engine according to claim 31 or 32, wherein the reciprocating internal combustion engine is compressible.   The guide elements (14, 141), in particular the guide plate (141) and / or the guide box (142) are mechanical and / or mechanical for the exhaust gas collecting pipe (4) and the exhaust gas distribution pipe (10). 34. Any one of claims 31 to 33, arranged to move within the slide shoe (1400) for compensation and / or adjustment of thermally limited stress and / or expansion and / or vibration. The reciprocating internal combustion engine according to item.   A mixing channel, in particular a mixing channel, for a reciprocating internal combustion engine (1) according to any one of the preceding claims.   36. Mixing according to claim 35, wherein the mixing pipe flow path is a combination of mixing flow paths comprising an exhaust gas collecting pipe (4) and / or the exhaust gas distribution pipe (10) and / or an exhaust gas reactor (6). Flow path.