EP2831529A1 - Abgaskühler - Google Patents
AbgaskühlerInfo
- Publication number
- EP2831529A1 EP2831529A1 EP13713839.2A EP13713839A EP2831529A1 EP 2831529 A1 EP2831529 A1 EP 2831529A1 EP 13713839 A EP13713839 A EP 13713839A EP 2831529 A1 EP2831529 A1 EP 2831529A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exhaust gas
- region
- inlet
- exhaust
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
- F02M26/32—Liquid-cooled heat exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/08—Assemblies of conduits having different features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
Definitions
- the present invention relates to an exhaust gas cooler for an exhaust system or for an exhaust gas recirculation system of an internal combustion engine.
- the invention also relates to an operating method for such an exhaust gas cooler.
- Exhaust coolers may be used in an exhaust system to extract heat energy from the exhaust gas to otherwise utilize it, for example to heat a refrigerant of a refrigeration cycle or evaporate a working fluid of a Rankine cycle or to heat an airflow for air conditioning of a passenger compartment at one vehicle application.
- an exhaust gas cooler is used to cool the recirculated exhaust gas. The cooling of the recirculated exhaust gas increases the mass flow and reduces the combustion temperatures in the combustion chambers of the internal combustion engine, which is advantageous in terms of pollutant emissions, in particular NOX emissions.
- an exhaust gas cooler comprises an exhaust gas path, which leads from an exhaust gas inlet to an exhaust gas outlet, as well as a coolant path coupled therewith for heat transfer, which leads from a coolant inlet to a coolant outlet.
- fouling In the case of heat exchangers, so-called “fouling” (English for contamination, fouling) occurs, which means the contamination of heat-transferring components by ingredients of the coolant used, for example, algae can form in the coolant path, which can lead to an increase in the coolant path.
- fouling on the exhaust gas side also means the accumulation of soot. Carbon black entrained in the exhaust gas can accumulate on the surfaces of the exhaust gas cooler in the exhaust gas path and thus also lead to a gradual clogging of the exhaust path.
- the present invention is concerned with the problem of providing for an exhaust gas cooler of the type mentioned in an improved embodiment, which is characterized in particular by the fact that the risk of clogging of the exhaust gas path is reduced by soot particles.
- the invention is based on the general idea of equipping the exhaust gas cooler on the exhaust gas side with at least three different cooling power ranges, which follow one another in the flow direction of the exhaust gas, ie are arranged in series.
- an inlet region comprises the exhaust gas inlet and is designed for an inlet cooling capacity. Downstream of the inlet area is an intermediate area which is designed for an intermediate cooling capacity. Downstream of the intermediate region, an outlet region is provided, which comprises the exhaust gas outlet and which is designed for an outlet cooling capacity.
- the exhaust gas cooler is now designed so that the intermediate cooling capacity is smaller than the inlet cooling capacity and smaller than the outlet cooling capacity.
- This construction according to the invention is based on the knowledge that at high exhaust gas temperatures, which occur in the inlet region of the exhaust path, the tendency for soot deposition is comparatively low. Accordingly, a comparatively high inlet cooling capacity can be realized in the inlet area. At medium exhaust gas temperatures, on the other hand, the tendency for soot build-up increases sharply. This can be counteracted by a reduced intermediate cooling capacity. At low exhaust gas temperatures, as in the exit area of the exhaust path Although relatively strong deposits can be observed, but they adhere less and therefore can be rinsed out in particular. Accordingly, a higher outlet cooling capacity can again be realized in the outlet area.
- the exhaust gas cooler presented here in particular within a common housing, has at least three differently structured regions, which follow one another in the exhaust gas path and which allow different heat transfer capacities due to their different structure.
- cooling capacity is meant a heat flow from the exhaust gas in the direction of the coolant per unit of time.
- the exhaust gas cooler has a single housing in which the entire exhaust gas path is accommodated and which has the exhaust gas inlet and the exhaust gas outlet.
- the three power ranges are within this common housing of the exhaust gas cooler, whereby a particularly compact design can be realized.
- the exhaust gas cooler has two or three housings, on which the exhaust gas path is distributed and which are connected in series via one or two connecting pipes.
- the exhaust inlet and the exhaust outlet are located on different housings.
- the inlet region and the exhaust gas inlet are located in an inlet-side first housing, while the outlet region and the exhaust gas outlet are located in an outlet-side second housing.
- the intermediate region can now be accommodated either in the inlet-side housing or in the outlet-side housing or else in a middle third housing.
- a single and thus common coolant path is provided, which preferably in succession, ie in series is guided by the at least three cooling power ranges.
- a flow guide for the single exhaust path and the single cooling path in the countercurrent flow path is also preferred.
- the dwell times of the exhaust gas and the coolant in the individual cooling power ranges can vary.
- the surfaces available for heat transfer can be varied, for example by the use of heat transfer structures and their design.
- the flow conditions such as the presence of turbulent or laminar flows and / or the thickness of the self-adjusting boundary layers, by appropriate measures, such as the use of turbulators and their configuration, vary.
- the exhaust gas cooler may be designed for a predetermined operating state of the exhaust gas cooler such that a hydrocarbon dew point lies in the region of a transition from the inlet region to the intermediate region, while the water dew point lies in the region of a transition from the intermediate region to the outlet region.
- the hydrocarbons are the molecules of the respective internal combustion engine for the combustion of fuel supplied, which have not been or not fully implemented in the respective combustion chamber. These are therefore mainly long-chain hydrocarbons based on diesel, bio-diesel, gasoline, bio-gasoline and other commonly liquid fuels.
- This special design of the exhaust gas cooler with respect to the three cooling power ranges is based on the finding that water vapor and unburned vaporous hydrocarbons are carried along with soot in the exhaust gas.
- the soot accumulation on the heat-transferring surfaces in the exhaust gas path is comparatively small. Accordingly, this temperature range assigned to the inlet area with the comparatively high inlet cooling capacity.
- the Rußstromrung is extremely critical, since the carbon black with the condensing hydrocarbons can combine to form a sticky mass, which is relatively difficult to remove.
- this temperature range is assigned to the intermediate area with the reduced intermediate cooling capacity.
- the condensing water can rinse out the soot which accumulates, so that an increased cooling capacity can again be achieved in this temperature range. Accordingly, this lower temperature range is associated with the exit area with the increased exit cooling capacity.
- the predetermined operating state can be defined for example by a predetermined exhaust gas volume flow and / or a predetermined exhaust gas temperature at the exhaust gas inlet and / or a predetermined coolant volume flow and / or a predetermined coolant temperature at the coolant inlet.
- the outlet region of the exhaust gas path can now be configured for discharging condensate. As explained above, it is mainly in the outlet area for the condensation of water.
- the proposed embodiment of the outlet region the resulting condensate can be selectively removed.
- the condensate may carry flushed out soot deposits.
- the inlet cooling capacity is greater than the outlet cooling capacity.
- the cooling capacity may be determined by the available in the exhaust path for heat transfer surface. This means that this heat exchanger surface is chosen to be significantly larger in the inlet region than in the intermediate region and that also the outlet region has a larger heat transfer surface than the intermediate region. The more surface available for heat transfer, the more surface is available for the addition of soot. Accordingly, if the heat transfer surface is significantly reduced in the intermediate region, significantly less surface area is available for the soot deposited in the exhaust gas, which leads to a reduction in soot accumulation in the intermediate region.
- the cooling capacity may be determined by the density of heat transfer means in the exhaust path.
- the density of the heat transfer means is the number of heat transfer means per unit volume in the exhaust path. The higher the density of the heat transfer medium, the greater the available heat transfer surface and the higher the cooling capacity. In terms of the exhaust gas cooler presented here, this means that the heat transfer medium density is greater in the inlet area than in the intermediate area and larger in the outlet area than in the intermediate area.
- such heat transfer means can be formed for example by ribs and / or by turbulators and / or by flow obstacles, so-called winglets, and / or by fins and the like, which are arranged in the exhaust path.
- the heat transfer medium density or the heat transfer surface by the rib density ie by the number of ribs be determined per unit volume in the exhaust path.
- the rib density in the intermediate area would be smaller than in the inlet area and smaller than in the outlet area.
- the cooling capacity can be determined by the permeable cross section of the exhaust path and / or by the flow resistance in the exhaust path.
- the flow resistance results firstly from the heat transfer medium density and secondly from the flow-through cross section.
- the flow resistance in the exhaust gas path is preferably smaller in the intermediate region than in the inlet region and smaller than in the outlet region. Additionally or alternatively, in the intermediate region, the flow-through cross section of the exhaust gas path is greater than in the inlet region and as in the outlet region.
- the coolant path may lead from a coolant inlet to a coolant outlet, wherein the coolant inlet is arranged at the outlet region and the coolant outlet at the inlet region, whereby the exhaust gas cooler flows through the exhaust gas and the coolant according to the countercurrent principle. It is also possible to arrange the coolant inlet at the inlet region and the coolant outlet at the outlet region, which then results in a flow through the exhaust gas cooler with exhaust gas and coolant according to the DC principle. In any case, the coolant path is passed through all three regions of the exhaust gas path, namely one after the other. the, that is in series. In this way, the structural integration of the three cooling power ranges is amplified into a single exhaust gas cooler.
- the exhaust gas cooler can be configured as a ribbed tube heat exchanger in which a plurality of coolant tubes extend through the exhaust path, which guide the coolant inside and carry ribs on the outside at least in the inlet region and in the outlet region.
- the different cooling capacities in the different regions of the exhaust gas path can be changed particularly easily by varying the rib size and / or number of ribs and / or rib density.
- the coolant path comprises an inlet chamber, a plurality of deflection chambers and an outlet chamber.
- at least four chambers are thus provided, which are formed in the coolant path or along the coolant path, in particular in a common housing of the exhaust gas cooler.
- the optionally provided common housing of the exhaust gas cooler on the side of the exhaust path encloses the three cooling power areas and on the side of the coolant path the above-mentioned at least four chambers.
- the coolant path then comprises exactly six chambers.
- the inlet chamber has a coolant inlet and is fluidly connected to the first deflection chamber via a first group of coolant tubes which are passed through the exhaust path.
- the first deflection chamber can now be fluidically connected to the second deflection chamber via a second group of coolant tubes which are passed through the exhaust path.
- the second deflection chamber may be connected via a third group of coolant tubes guided through the exhaust gas path to the third deflection chamber. be fluidly connected chamber.
- the third deflection chamber may be fluidically connected to the fourth deflection chamber via a fourth group of coolant tubes guided through the exhaust gas path.
- the fourth deflection chamber may be fluidically connected to the outlet chamber via a fifth group of coolant tubes which are passed through the exhaust path, which has a coolant outlet.
- the coolant flows through the six chambers of the coolant path in sequence, so that they form a series circuit.
- a correspondingly different number of groups of coolant pipes guided through the exhaust gas path is present.
- the coolant tube of the first group and the second group in the outlet region and the coolant tubes of the fourth group and the fifth group in the inlet region extend (countercurrent principle) or vice versa (the DC principle).
- the coolant pipes of the third group run in the intermediate area.
- the exhaust gas cooler is designed as a shell-and-tube heat exchanger, in which a plurality of exhaust pipes extend from the exhaust gas inlet to the exhaust gas outlet through the coolant path, which carry the exhaust gas inside and are exposed outside to the coolant.
- heat transfer means can now be arranged in the exhaust pipes in the entry region and in the exit region. These heat transfer means now define by their dimensioning and / or number and / or density, the cooling capacity of the respective region of the exhaust path.
- flow-guiding elements or flow obstacles can be provided in the exhaust-gas region.
- flow guide elements or flow obstructions can be realized particularly simply as so-called "winglets.” These are generally embossments and impressions that are produced on the facing longitudinal sides of the individual flat tubes by means of deformation. The geometry and / or number and / or density and / or distribution of these winglets, the heat transfer performance can be determined in the exhaust path.
- An inventive method for operating an exhaust gas cooler which is characterized in that it has at least three areas in the exhaust path, namely an inlet area, an intermediate area and an access area, characterized in that in the at least three areas different cooling capacities are realized, namely a Inlet cooling capacity, an intermediate cooling capacity and an outlet cooling capacity, wherein the intermediate cooling capacity is smaller than the inlet cooling capacity and smaller than the outlet cooling capacity.
- the exhaust gas is cooled in the exhaust gas cooler before the intermediate region at least up to a hydrocarbon dew point and that the exhaust gas is cooled in the exhaust gas cooler after the intermediate region at least up to a water dew point.
- the hydrocarbon dew point is reached in the region of a transition from the inlet region to the intermediate region, and / or that the water dew point is reached in the region of a transition from the intermediate region to the outlet region.
- FIG. 2 is a longitudinal section as in Fig. 1, but in another embodiment of the exhaust gas cooler,
- FIG. 3 simplified plan views of a flat tube of such an exhaust gas cooler in a further embodiment, in different areas a to c.
- an exhaust gas cooler 1 comprises a housing 2 with which it can be installed in an exhaust system 3 or in an exhaust gas recirculation system 4 of an internal combustion engine, not shown here.
- the exhaust gas cooler 1 contains in its housing 2 an exhaust gas path 5 through which, during operation of the exhaust gas cooler 1, an exhaust gas flow 6 is passed.
- the exhaust gas path 5 leads from an exhaust gas inlet 7 formed on the radiator housing 2 to an exhaust gas outlet 8 formed on the radiator housing 2.
- the exhaust gas radiator 1 in the radiator housing 2 has a coolant path 9, through which a coolant flow 10 is passed during operation of the exhaust gas radiator 1.
- the coolant path 9 leads from a coolant inlet 1 1 formed on the radiator housing 2 to a coolant outlet 12 formed on the radiator housing 2.
- the coolant path 9 is coupled to the exhaust path 5 in a suitable manner in a media-separated manner in a heat-transmitting manner.
- the coolant inlet 11 is located proximal to the exhaust gas outlet 8, while the coolant outlet 12 is arranged proximal to the exhaust gas inlet 7. Accordingly, in the embodiments shown here, a flow through the exhaust gas cooler 1 with respect to the exhaust gas flow 6 and the coolant flow 10 according to the countercurrent principle. It is clear that, in principle, a flow according to the DC principle can be realized.
- the exhaust path 5 has an inlet region 13 indicated by a brace, downstream of this an intermediate region 14 indicated by a brace and downstream thereof an outlet region 15 indicated by a brace.
- the inlet region 13 comprises the exhaust gas inlet 7.
- the outlet region 15 comprises the exhaust gas outlet 8
- the intermediate region 14 is arranged in the flow direction of the exhaust gas between the inlet region 13 and the outlet region 15. The intermediate region 14 is thus arranged distally to the exhaust gas inlet 7 and distally to the exhaust gas outlet 8.
- the inlet area 13 is designed for an inlet cooling capacity.
- the intermediate region 14 is designed for an intermediate cooling performance.
- the exit area 15 is designed for a discharge cooling capacity.
- the intermediate cooling capacity is smaller than the inlet cooling capacity and smaller than the outlet cooling capacity.
- the outlet cooling capacity is also smaller than the inlet cooling capacity. Accordingly, the cooling power in the inlet region 13 is greater than in the intermediate region 14 and greater than in the outlet region 15. In the outlet region 15, the cooling capacity is greater than the intermediate region 14. In the intermediate region 14, the cooling capacity is smaller than in the inlet region 14 and smaller than in the outlet region 15th
- the exhaust gas cooler 1 is expediently designed so that a dew point of hydrocarbons T H c lies in a region 16 indicated by a brace between a transition from the inlet region 13 to the intermediate region 14. Furthermore, the design of the exhaust gas cooler 1 for the predetermined operating state is expediently such that a dew point of water T H 2o lies in a region 17, indicated by a brace, of a transition from the intermediate region 14 to the outlet region 15.
- the outlet region 15 can also be designed such that it is suitable for removing condensate 18.
- a condensate drain line 19 is indicated for this purpose with a broken line.
- the condensate drain line 19 is fluidly connected to the exhaust path 5.
- the exhaust gas cooler 1 is designed as a ribbed tube heat exchanger 20, which is characterized in that a plurality of coolant tubes 21 extend through the exhaust gas path 5.
- the coolant tubes 21 carry the coolant inside and are equipped with ribs 22 on the outside at least in the inlet region 13 and in the outlet region 15. Is recognizable In FIG. 1, a rib density, that is to say a number of ribs 22 per coolant tube 21, is greater than in the outlet region 15. It is further provided here that the coolant tubes 21 do not carry any cooling ribs 22 in the intermediate region 14.
- the number of ribs 22 per coolant tube 21 determines the cooling capacity in the respective power range 13, 14, 15 of the exhaust path 5.
- the high rib density in the inlet region 13 results in a high inlet cooling capacity.
- the reduced rib density in the outlet region 15 accordingly leads to a reduced outlet cooling performance.
- the missing in the intermediate region 14 ribs 22 accordingly lead to a particularly low intermediate cooling capacity.
- the coolant path 9 in the radiator housing 2 comprises an inlet chamber 23, four deflection chambers 24, 25, 26, 27 and an outlet chamber 28.
- the deflection chambers 24, 25, 26, 27 are between the inlet chamber 23 and the Outlet chamber 28 is arranged.
- the inlet chamber 23 has the coolant inlet 11.
- a first group 29 of coolant tubes 21 connects the inlet chamber 23 with the first deflection chamber 24.
- a second group 30 of coolant tubes 21 connects the first deflection chamber 24 with the second deflection chamber 25.
- a third group 31 of coolant tubes 21 connects the second deflection chamber 25 with the third Deflection chamber 26.
- a fourth group 32 of coolant tubes 21 connects the third deflection chamber 26 with the fourth deflection chamber 27.
- a fifth group 33 of coolant tubes 21 connects the fourth deflection chamber 27 with the outlet chamber 28.
- the coolant tubes 21 of the first group 29 and the second group 30 are assigned to the outlet region 15.
- the coolant tubes 21 of the third group 31 are assigned to the intermediate region 14.
- the coolant tubes 21 of the fourth group 32 and the fifth group 33 are assigned to the inlet area 13. All coolant tubes 21 run parallel to one another here and connect the chambers 23 to 28 in series with each other.
- the exhaust gas cooler 1 is configured as a tube bundle heat exchanger 34, which is characterized by a plurality of exhaust pipes 35, which are led from the exhaust gas inlet 7 to the exhaust gas outlet 8 through the coolant path 9.
- the exhaust pipes 35 lead inside the exhaust stream 6 and are exposed to the outside coolant flow 10.
- the exhaust pipes 35 are round tubes with circular cross-sections.
- the exhaust pipes 35 may be configured as flat tubes having a substantially rectangular cross-section.
- heat transfer means 36 can be arranged in the exhaust pipes 35, which can be formed, for example, by a lamellar structure.
- a pipe cross section for such an exhaust pipe 35 is shown, wherein this pipe cross section in the outlet region 15 is designated by a, in the intermediate region 14 by b and in the inlet region 15 by c.
- a lamellar structure 36 is arranged only in the exhaust pipes 35 of the inlet region 13 and the outlet region 15, while in the intermediate region 4 the cross-sections of the exhaust pipes 35 are free of such heat transfer means 36.
- the lamellar structure 36 in the inlet region 13 according to the illustration c has a larger lamella number or lamellar density and a smaller wall thickness than the lamellar structure 36 in the outlet region 15 according to the illustration a.
- a larger inlet cooling capacity can be set in the inlet area 13 than in the outlet area 15.
- the outlet cooling capacity is also greater than in the intermediate area 14.
- FIGS. 3a-3c each show a plan view of an exhaust pipe 35 designed as a flat tube.
- These exhaust pipes 35 can be seen with indentations or Variants equipped flow guide elements 37 or Strömungshin- to form.
- the indentations are in front of the exhaust-carrying interior of the respective exhaust pipe 35.
- the forms protrude into the cooling path in path 9.
- adjacent exhaust pipes 35 can be supported against each other or distanced from each other via such distinct flow guide elements 37.
- FIG. 3a shows a top view of the exhaust pipe 35 in the outlet region 15. Shown are purely exemplary eight flow guide elements 37 within the outlet region 15.
- FIG. 3b shows the same exhaust pipe 35 within the intermediate region 14. It can be seen here only four flow guide elements 37 are provided. Accordingly, in the intermediate region 14, the heat transfer performance compared to the outlet region 15 is reduced.
- FIG. 3c now shows the same exhaust pipe 35 in the inlet region 13. It can be seen here that sixteen flow guide elements 37 are provided, whereby the cooling capacity in the inlet region 13 is significantly greater than in the intermediate region 14 and in the outlet region 15.
- the exhaust gas cooler 1 During operation of the exhaust gas cooler 1 or during operation of the internal combustion engine equipped therewith, hot exhaust gas flows through the exhaust gas inlet 7 into the inlet region 13.
- the inlet region 13 is dimensioned so that at the end of the inlet region 13, ie in the transition region 16 of the hydrocarbon dew point T H c is located. Since above the hydrocarbon dew point temperature T H c soot deposition is largely uncritical or hardly takes place, can Here, a particularly high cooling capacity can be realized, which is realized by the large heat transfer surface with the help of the high rib density in Fig. 1 or with the help of the high lamellar density in Fig. 2.
- the exhaust gas is cooled below the HC dew point T H c, so that condensation takes place in the intermediate region 14 of hydrocarbons.
- the cooling capacity is significantly reduced in the intermediate region 14. This is achieved in FIG. 1 by the absence of ribs 22 or by the use of a significantly reduced rib density and in FIG. 2 by the absence of a laminar structure 36 or by the use of a significantly reduced laminar density.
- the intermediate region 14 is designed so that at its end, ie in the transition region 17, the water dew point temperature T H 2o is reached. In the subsequent exit region 15, a condensation of water thus takes place, which ensures that sooting carbon black can be rinsed out immediately with the aid of the condensed water.
- a higher cooling capacity can be set, which is realized with the aid of a corresponding rib density in FIG. 1 or lamellar density in FIG. 2.
- the condensate which forms can be collected and removed, for example, via a condensate drain 19 according to FIG. 1.
- the exhaust gas cooler 1 presented here can be characterized in summary by having a cooling capacity adapted to the exhaust gas temperature which decreases along the exhaust gas path 5, such that in the intermediate region 14 in which a hydrocarbon condensation but no water condensation takes place , a significantly reduced cooling capacity is realized. In this way, in this intermediate region 14, in which the hydrocarbon condensation takes place, the accumulation of soot particles can be significantly reduced, which reduces the risk of clogging and clogging of the exhaust gas path 5 in the exhaust gas cooler 1. Although in the exit region 15 is a soot deposit in Purchase, but can be flushed out by the water condensation.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Geometry (AREA)
- Exhaust Gas After Treatment (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012205026 | 2012-03-28 | ||
DE102012208742A DE102012208742A1 (de) | 2012-03-28 | 2012-05-24 | Abgaskühler |
PCT/EP2013/056542 WO2013144214A1 (de) | 2012-03-28 | 2013-03-27 | Abgaskühler |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2831529A1 true EP2831529A1 (de) | 2015-02-04 |
EP2831529B1 EP2831529B1 (de) | 2017-05-10 |
Family
ID=49154801
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13713839.2A Not-in-force EP2831529B1 (de) | 2012-03-28 | 2013-03-27 | Abgaskühler |
Country Status (4)
Country | Link |
---|---|
US (1) | US20150047619A1 (de) |
EP (1) | EP2831529B1 (de) |
DE (1) | DE102012208742A1 (de) |
WO (1) | WO2013144214A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9938935B2 (en) | 2012-07-12 | 2018-04-10 | General Electric Company | Exhaust gas recirculation system and method |
US10508621B2 (en) | 2012-07-12 | 2019-12-17 | Ge Global Sourcing Llc | Exhaust gas recirculation system and method |
DE102013224038A1 (de) * | 2013-11-25 | 2015-05-28 | MAHLE Behr GmbH & Co. KG | Abgaswärmetauscher zur Abgaskühlung einer Brennkraftmaschine, vorzugsweise für ein Kraftfahrzeug |
EP2937660A1 (de) * | 2014-04-24 | 2015-10-28 | Siemens Aktiengesellschaft | Turbulator zum Einsatz in einem Kühlmittelkanal und Wärmeübertragungselement mit einem derartigen Turbulator |
DE112016001487T5 (de) * | 2015-04-01 | 2018-01-11 | General Electric Company | Abgasrückführungssystem und -verfahren |
DE102016002380B4 (de) * | 2016-03-01 | 2023-10-05 | Volkswagen Aktiengesellschaft | Kraftfahrzeug mit einem Abgaskondensator |
TWI835709B (zh) * | 2016-04-18 | 2024-03-21 | 俄勒岡州大學 | 層壓的微通道熱交換器 |
DE102016221566A1 (de) * | 2016-11-03 | 2018-05-03 | Bayerische Motoren Werke Aktiengesellschaft | Wasserabscheider zum Abscheiden von Wasser in einem Fahrzeug |
DE102017113964A1 (de) * | 2017-06-23 | 2018-12-27 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Vorrichtung zum Laden einer Mehrzahl von Elektrofahrzeugen |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002180915A (ja) * | 2000-12-08 | 2002-06-26 | Hino Motors Ltd | Egrクーラ |
JP2005220747A (ja) * | 2004-02-03 | 2005-08-18 | Usui Kokusai Sangyo Kaisha Ltd | Egrガス冷却機構 |
US7213639B2 (en) * | 2005-03-16 | 2007-05-08 | Detroit Diesel Coporation | Heat exchanger exhaust gas recirculation cooler |
DE102005029321A1 (de) * | 2005-06-24 | 2006-12-28 | Behr Gmbh & Co. Kg | Wärmeübertrager |
JP4756585B2 (ja) * | 2005-09-09 | 2011-08-24 | 臼井国際産業株式会社 | 熱交換器用伝熱管 |
DE102007062826A1 (de) * | 2007-01-17 | 2008-09-25 | Behr Gmbh & Co. Kg | Wärmetauscher für ein Kraftfahrzeug |
DE102008007073A1 (de) * | 2007-01-31 | 2008-08-07 | Behr Gmbh & Co. Kg | Wärmetauscher, Abgasrückführsystem und Verwendung eines Wärmetauschers |
DE102008014169A1 (de) * | 2007-04-26 | 2009-01-08 | Behr Gmbh & Co. Kg | Wärmetauscher, insbesondere zur Abgaskühlung, System mit einem Wärmetauscher zur Abgaskühlung, Verfahren zum Betreiben eines Wärmetauschers |
US7798134B2 (en) * | 2008-05-07 | 2010-09-21 | General Electric Company | System, kit, and method for locomotive exhaust gas recirculation cooling |
DE102010008175B4 (de) * | 2010-02-16 | 2014-12-04 | Thesys Gmbh | Wärmeübertrager |
DE102010048466A1 (de) * | 2010-10-14 | 2012-04-19 | Daimler Ag | Abgasrückführung mit Kondensat-Abführung |
DE102011087962A1 (de) * | 2011-02-08 | 2012-08-09 | Behr Gmbh & Co. Kg | Wärmeübertrager |
-
2012
- 2012-05-24 DE DE102012208742A patent/DE102012208742A1/de not_active Withdrawn
-
2013
- 2013-03-27 US US14/388,694 patent/US20150047619A1/en not_active Abandoned
- 2013-03-27 WO PCT/EP2013/056542 patent/WO2013144214A1/de active Application Filing
- 2013-03-27 EP EP13713839.2A patent/EP2831529B1/de not_active Not-in-force
Also Published As
Publication number | Publication date |
---|---|
WO2013144214A1 (de) | 2013-10-03 |
DE102012208742A1 (de) | 2013-10-02 |
EP2831529B1 (de) | 2017-05-10 |
US20150047619A1 (en) | 2015-02-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2831529B1 (de) | Abgaskühler | |
EP1985953B1 (de) | Wärmetauscher, insbesondere zur Abgaskühlung, Verfahren zum Betreiben eines solchen Wärmetauschers und System mit einem Abgaskühler | |
EP2852805B1 (de) | Abgaswärmeübertrager | |
WO2007104580A2 (de) | Wärmetauscher für ein kraftfahrzeug | |
WO2006100072A1 (de) | Abgaswärmeübertrager, insbesondere abgaskühler für eine abgasrückführung in kraftfahrzeugen | |
EP1604163A1 (de) | W rme bertrager, insbesondere abgaskühler für kraftfahrzeuge | |
DE102011103110A1 (de) | Abgassystem mit Kreislaufwärmerohr | |
EP2134941B1 (de) | Strömungskanal, wärmetauscher, abgasrückführsystem, ladeluft-zuführsystem, verwendung eines wärmetauschers | |
DE102006012219B4 (de) | Wärmeübertragungseinheit mit einem verschließbaren Fluidteileinlass | |
DE102012208354B4 (de) | Wärmetauscher | |
WO2009089885A1 (de) | Vorrichtung zum austausch von wärme und kraftfahrzeug | |
EP2825832A2 (de) | Wärmeübertrager | |
DE102008058210A1 (de) | Wärmetauscher und Verfahren für dessen Herstellung | |
DE102007015146A1 (de) | Aluminium System Kühler | |
EP3039372B1 (de) | Wärmeübertrager | |
EP2485002A2 (de) | Wärmeübertrager | |
EP2278138B1 (de) | Brennkraftmaschine und Verfahren zum Betreiben dieser | |
DE102006013868A1 (de) | Abgaswärmeübertrager, insbesondere Abgaskühler für eine Abgasrückführung in Kraftfahrzeugen | |
DE102015204983A1 (de) | Wärmetauscher, insbesondere für ein Kraftfahrzeug | |
EP2278149B1 (de) | Wärmetauscher und aufladesystem | |
EP3203173B1 (de) | Abgaswärmeübertrager | |
WO2012168042A1 (de) | Brennkraftmaschine mit zumindest einer katalysatoreinheit | |
EP4235074A1 (de) | Wärmetauscher | |
DE102011117089A1 (de) | Abgaswärmetauscher und Abgasrückführanordnung mit einem Abgaswärmetauscher | |
DE102008038498A1 (de) | Wärmetauscher für ein Kraftfahrzeug |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20140910 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
DAX | Request for extension of the european patent (deleted) | ||
17Q | First examination report despatched |
Effective date: 20160204 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F28D 21/00 20060101ALI20161202BHEP Ipc: F28F 1/40 20060101AFI20161202BHEP Ipc: F28F 13/06 20060101ALI20161202BHEP Ipc: F28F 13/12 20060101ALI20161202BHEP |
|
INTG | Intention to grant announced |
Effective date: 20161221 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 892812 Country of ref document: AT Kind code of ref document: T Effective date: 20170515 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502013007227 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170510 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170810 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170811 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170910 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170810 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502013007227 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20180213 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180530 Year of fee payment: 6 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20180327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20180331 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180331 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180331 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180331 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180331 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 892812 Country of ref document: AT Kind code of ref document: T Effective date: 20180327 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502013007227 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20191001 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 Ref country code: MK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170510 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20130327 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170510 |