US20010020363A1 - Exhaust gas heat exchange system for an internal combustion engine - Google Patents
Exhaust gas heat exchange system for an internal combustion engine Download PDFInfo
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- US20010020363A1 US20010020363A1 US09/777,326 US77732601A US2001020363A1 US 20010020363 A1 US20010020363 A1 US 20010020363A1 US 77732601 A US77732601 A US 77732601A US 2001020363 A1 US2001020363 A1 US 2001020363A1
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- exhaust
- exhaust gas
- inlet
- gas heat
- manifold
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 24
- 239000002826 coolant Substances 0.000 claims abstract description 9
- 238000007599 discharging Methods 0.000 claims abstract description 6
- 230000003134 recirculating effect Effects 0.000 claims abstract description 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 239000007789 gas Substances 0.000 abstract description 63
- 230000003197 catalytic effect Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 4
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 3
- 239000001301 oxygen Substances 0.000 description 3
- 229910052760 oxygen Inorganic materials 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 239000011324 bead Substances 0.000 description 2
- 238000010790 dilution Methods 0.000 description 2
- 239000012895 dilution Substances 0.000 description 2
- 239000011261 inert gas Substances 0.000 description 2
- 230000001737 promoting effect Effects 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910002091 carbon monoxide Inorganic materials 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 239000011236 particulate material Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
Images
Classifications
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- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
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- 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
- F02M26/23—Layout, e.g. schematics
- F02M26/25—Layout, e.g. schematics with coolers having bypasses
- F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
-
- 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
- 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
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
-
- 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
- F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
-
- 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
- F02M26/65—Constructional details of EGR valves
- F02M26/71—Multi-way valves
Definitions
- This invention relates to an exhaust gas heat exchanger system, and more specifically, to such a system intended for use with an internal combustion engine.
- Emission concerns associated with the operation of internal combustion engines have resulted in an increased emphasis on the use of exhaust gas heat exchange systems with such engines, particularly, but not always, in vehicular applications.
- EGR exhaust gas recirculation
- a portion of an engine's exhaust is returned to its combustion chambers via its intake system.
- EGR exhaust gas recirculation
- the result is that some of the oxygen that would ordinarily be inducted into the engine as part of its fresh combustion air charge is displaced with inert gases thus reducing the rate of NO x formation.
- EGR is also frequently designed to absorb heat from the combustion process, thus lowering its temperature and providing a further reduction in NO x . It has been shown that EGR is a very effective method in achieving NO x reduction.
- exhaust gas heat exchangers are employed.
- engine coolant is brought into heat exchange relation with the exhaust gas prior to its recirculation so as to lower its temperature.
- this provides a beneficial effect in terms of a reduced temperature of the gases entering the combustion chamber, leading to reduced combustion temperatures and the associated reduction of NO x , it causes the exhaust gases to become more dense due to their reduction in temperature so that for a given volumetric recirculation flow rate, a greater quantity of the exhaust gas is recirculated to the intake side of the engine, thereby promoting greater dilution of the intake air and promoting the associated reduction in NO x .
- the present invention is directed to overcoming one or more of the above problems.
- An exemplary embodiment of the invention achieves the foregoing objects in an exhaust gas heat exchange system for internal combustion engines which includes an intake manifold having an inlet for recirculating exhaust gas. Also included is an exhaust manifold having at least one inlet receiving exhaust gas from an engine as well as an outlet for discharging exhaust gas and spaced from the inlet(s).
- An exhaust gas heat exchanger includes a first flow path having an inlet connected to the exhaust manifold to receive exhaust gas therefrom, an outlet for discharging cooled exhaust gas and a second flow path in heat exchange relation with the first flow pass for receipt of a coolant whereby exhaust gas flowing in the first flow path may be cooled.
- An exhaust valve having a first inlet is connected to the first flow path outlet.
- a valve mechanism is included and has at least one movable component which is movable between positions (a) connecting the exhaust valve first inlet to the exhaust valve outlet and (b) connecting the exhaust valve second inlet to the exhaust valve outlet.
- an actuator is connected to the valve mechanism for moving the valve mechanism component(s) between the two aforementioned positions.
- the exhaust valve second inlet is connected to the exhaust manifold at a location downstream of the exhaust manifold inlet(s) and upstream of the exhaust manifold outlet.
- a preferred embodiment contemplates that the exhaust valve second inlet be connected to the exhaust manifold closely adjacent to the exhaust manifold outlet.
- first flow path inlet and the exhaust valve first and second inlets are approximately aligned with one another.
- the exhaust gas heat exchanger and the exhaust valve are mounted on the exhaust manifold.
- the exhaust manifold is elongated and the second inlet is connected to the exhaust manifold at a location that is spaced from the exhaust manifold outlet a distance equal to one-half or less of the length of the exhaust manifold. Even more preferably, the distance is one-third or less of the length of the exhaust manifold.
- a preferred embodiment of the invention contemplates that the exhaust manifold be elongated and the exhaust manifold outlet be adjacent to one end thereof.
- the exhaust gas heat exchanger first flow path inlet has a connection to the exhaust manifold at a location intermediate the ends thereof.
- connection is closely adjacent and end of the exhaust manifold opposite the one end.
- a preferred embodiment of the invention also contemplates that the exhaust gas heat exchanger and the exhaust manifold both be elongated and that the exhaust valve is mounted on one end of the exhaust gas heat exchanger to form an elongated assembly.
- the assembly is disposed generally parallel to the exhaust manifold.
- the exhaust valve first inlet, second inlet and outlet intersect at a common location and the valve component(s) includes a valve member located at the common location.
- the exhaust gas heat exchanger is elongated and has an axis of elongation, and the exhaust valve first and second inlets are approximately aligned on the axis of elongation.
- the exhaust valve outlet is disposed approximately transverse to the axis of elongation.
- FIG. 1 is a schematic of a turbocharged internal combustion engine employing exhaust gas recirculation and including an exhaust gas heat exchange system made according to the invention
- FIG. 2 is a partial schematic, partial mechanical depiction of part of one embodiment of the exhaust gas heat exchange system of the invention
- FIG. 3 is a view similar to FIG. 2 but showing an alternative embodiment
- FIG. 4 is an elevation illustrating the components of an embodiment of the invention shown in FIG. 2;
- FIG. 5 is a plan view of the same components
- FIG. 6 is an enlarged elevation of an exhaust gas heat exchanger that may be employed in practicing the invention.
- FIG. 7 is a sectional view of the exhaust gas heat exchanger taken approximately along the line 7 - 7 in FIG. 6;
- FIG. 8 is a side elevation of the exhaust gas heat exchanger taken from the bottom of FIG. 6.
- FIG. 1 an exemplary embodiment of an exhaust gas heat exchange system made according to the invention will be described generally.
- the description will involve the environment in which a typical diesel engine for a truck-like vehicle operates but it is to be understood that the invention is applicable to internal combustion engines other than diesel engines and may be employed with efficacy in stationary engine applications as well as in applications for engines other than trucks, as, for example, automobiles and construction, excavating, power generation, marine applications and others.
- a six cylinder diesel engine is generally designated 10 and includes an intake manifold 12 having outlet connections 14 to each of the cylinders of the engine 10 .
- the intake manifold 12 includes an inlet 16 for receiving recirculated exhaust gas from an exhaust gas recirculation line 18 as well as combustion air 20 . While a single inlet is illustrated, two separate inlets could be employed.
- Combustion air on the line 20 is received from a charge air cooler 22 which in turn receives combustion air from the compressor side 24 of a turbocharger, generally designated 26 .
- an exhaust manifold generally designated 28 which has a plurality of inlet connections 30 , one to each of the cylinders of the diesel engine 10 .
- the same is elongated and at one end 36 , includes a connection to the turbine side 38 of the turbocharger 26 to provide a driving force for the same whereby combustion air is compressed in the compressor side 24 and delivered to the charge air cooler 22 for ultimate delivery to the intake manifold 12 .
- a connecting line 42 extending to the exhaust gas heat exchanger 32 and a first flow path (not shown in FIG. 1) thereof.
- the opposite end of the first flow path discharges at a first inlet 44 to the exhaust valve 34 .
- a connecting line 46 connects to a second inlet 47 to the exhaust valve 34 .
- the exhaust valve 34 also includes an outlet 48 connected to the recirculation line 16 .
- the exhaust valve 34 may be configured to direct cooled exhaust entering the exhaust gas heat exchanger 32 on the line 42 to the recirculation line 18 or to direct uncooled exhaust entering the inlet 47 to the recirculation line 18 .
- FIG. 2 the valve 34 is illustrated in somewhat greater detail.
- the assembly of the heat exchanger 32 and the valve 34 results in an elongated assembly which is disposed approximately parallel to the exhaust manifold 28 .
- the arrangement is such that the first inlet 44 to the valve 34 as well as the second inlet 47 are aligned on approximately the longitudinal axis of the assembly of the heat exchanger 32 and the valve 34 .
- the inlet 50 to the first flow path within the exhaust gas heat exchanger 32 is also so aligned.
- the outlet 48 is at approximate right angles to the axis of elongation. Stated another way, the outlet 48 joins with the inlets 44 and 47 at a common point of intersection 54 . At that point, a movable valve component in the form of a rotatable valve member 56 is located and is movable between the solid and dotted line positions illustrated in FIG. 2. When in the solid line position, recirculation flow back to the inlet manifold 12 (FIG. 1) will be through the exhaust gas heat exchanger 32 meaning that the recirculated exhaust will be cooled. On the other hand, when the valve member 56 is moved to the dotted line position, flow will be from the second inlet 47 to the outlet 48 and the exhaust gas heat exchanger 32 will be bypassed entirely. Thus, hot exhaust gas that has not been cooled will be directed back to the intake manifold 12 .
- connection 42 linking the exhaust manifold 26 to the heat exchanger 32 includes a bellows such as schematically illustrated at 58 to provide for thermal expansion and contraction.
- the bellows is connected to an outlet 60 from the exhaust manifold 28 near the end 40 while the connection 46 is connected to the exhaust manifold 28 at a point 62 adjacent the end 36 .
- connection 62 is closely adjacent the end 36 whereat, by reason of its typical connection to a turbocharger 26 (FIG. 1), head pressure will be maximized. Thus pressure drop problems associated with ECR are minimized.
- FIG. 3 shows an alternative embodiment wherein the locations of the heat exchanger 32 and the valve 34 are interchanged. That is to say, the inlet 50 to the first flow path is connected to the connection 46 whereas the connection 42 is connected to the second inlet 47 . The outlet of the first flow path within the heat exchanger 32 is connected to the first inlet 44 . The orientation of the inlets 44 , 47 and outlet 48 is the same as in FIG. 2 except they have been reversed as illustrated.
- the valve member 56 is provided as before. Again, it is movable between solid and dotted line positions. In the case of the embodiment shown in FIG. 3, when the valve member 56 is in the solid line position, uncooled exhaust gas will be directed to the recirculation line 18 whereas when the valve member 56 is in the dotted line position as shown in FIG. 3, cooled exhaust will be provided for recirculation.
- the point of connection 62 of the connection 46 be reasonably adjacent to the end 36 of the manifold 28 .
- the manifold 28 is elongated and the point 62 is at a distance of one-half the length of the manifold 28 or less from the end 36 .
- the spacing is one-third of the length of the manifold 28 or less.
- the point 62 may be located most anywhere along the length of the manifold 28 .
- FIGS. 4 and 5 illustrate mechanical drawings of the assemblies shown in FIG. 2 (save for one less inlet connection 30 ) and it will be appreciated that the embodiment of FIG. 3 would be similarly configured except for the aforementioned reversing of the location of the heat exchanger 32 and the valve 34 .
- flanges 70 are located about the inlets 30 to the manifold 28 and are provided with bolt holes 72 whereby the manifold may be bolted to an engine.
- the bellows 58 may be provided with a flange 74 by which one end of the assembly of the heat exchanger 32 and 34 may be bolted to the manifold.
- An actuator such as a conventional pneumatic actuator or a servo-motor 76 is connected via a link 78 to an eccentric 80 which in turn is connected to the valve member 56 for moving the valve member 56 between the aforementioned positions.
- Mounting brackets 81 connect the assembly of the heat exchanger 32 and exhaust valve 34 to the manifold 28 .
- Coolant inlet and outlet ports 83 which typically receive engine coolant, are provided on the heat exchanger 32 .
- a flange 84 similar to the flanges 70 , is connected to the outlet port 48 and may be connected to the recirculation line 18 (FIG. 1) via the flange 84 .
- the exhaust gas heat exchanger 32 may take on many known forms known in the art, one preferred form is illustrated in FIGS. 6 - 8 , inclusive.
- the inlet to the first flow path includes a frusto-conical port 90 connected to one end of a core, generally designated 92 , made up of a series of stamped interior plates 94 flanked by end plates 96 .
- a housingless configuration for the core 92 of the heat exchanger results.
- the end plates 96 include relatively shallow depressions 98 in their centers surrounded by upstanding peripheral walls 100 which terminate in outwardly directed flanges 102 .
- Each interior plate 94 includes an enlarged, relatively deep interior depression 104 surrounded by an upstanding wall 106 which is peripheral and which terminates in outwardly directed flanges 108 .
- cylindrical bosses 112 are provided at two locations in each of the plates 94 (only one of which is shown in FIG. 7).
- the bosses 112 have central apertures 114 .
- the interior plates 94 are stacked in alternating fashion as illustrated in FIG. 7 with the bosses 112 aligned.
- the inlet and outlet ports 83 extend through the uppermost one of the end plates 96 and into fluid communication with the bosses 112 so as to allow for the entry and exit of coolant into the core 92 of the heat exchanger.
- Each of the interior plates 94 is also provided with a peripheral, exterior bead 116 at the base of the upstanding side walls 160 .
- the interior plates 94 are assembled in alternating fashion as illustrated in FIG. 7 with the beads 116 at adjacent plates being abutted to one another. The assembly is brazed and as a consequence, sealed coolant flow paths 120 are provided between adjacent pairs of the plates. Between abutted pairs of the plates 94 , exhaust gas passages 122 exist.
- Interior fins 124 are located in each of the exhaust gas flow paths 122 and preferably are quite smooth so as to avoid accumulation of particulate material that may be present in the exhaust stream.
- a header 130 (FIG. 6) is located at the end of core 92 opposite the inlet 90 and is connected to each of the flow paths 122 to receive exhaust gas therefrom.
- the header 130 may have the valve 34 mounted directly thereto.
- the same compactness of the assembly minimizes pressure drop and the advantageous location of the point 62 whereat the connector 46 connects from the manifold 28 assures that exhaust gas at its greatest head pressure will be available for recirculation.
- Appropriate sensors may be employed to control the actuator 76 and thus the position of the valve member 56 to selectively introduce the heat exchanger 32 into the flow system or remove it therefrom during warm-up, cold conditions, low and partial loads, etc.
- the arrangement of the two inlets and the outlet for the valve 34 provides an extremely simple valve construction and one that is not readily fouled by the exhaust gases flowing through it.
- the heat exchanger construction disclosed is essentially housingless and consequently, its cost and mass are both reduced from other sorts of heat exchangers conventionally employed in exhaust gas heat exchange systems.
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- Engineering & Computer Science (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Exhaust-Gas Circulating Devices (AREA)
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
- This invention relates to an exhaust gas heat exchanger system, and more specifically, to such a system intended for use with an internal combustion engine.
- Emission concerns associated with the operation of internal combustion engines, generally, but not always, diesel engines, have resulted in an increased emphasis on the use of exhaust gas heat exchange systems with such engines, particularly, but not always, in vehicular applications. These systems are employed as part of an exhaust gas recirculation (EGR) system by which a portion of an engine's exhaust is returned to its combustion chambers via its intake system. The result is that some of the oxygen that would ordinarily be inducted into the engine as part of its fresh combustion air charge is displaced with inert gases thus reducing the rate of NOx formation. EGR is also frequently designed to absorb heat from the combustion process, thus lowering its temperature and providing a further reduction in NOx. It has been shown that EGR is a very effective method in achieving NOx reduction.
- As generally alluded to previously, dilution of the combustion air with inert gases decreases the oxygen concentration of the mixture being combusted with the engine, thereby reducing the availability of oxygen for combination with nitrogen that would result in NOx. Temperature reduction in the combustion process, also leading to a reduction in NOx, is believed to be primarily due to the heat absorbing capacity of CO2 and H2O in the exhaust gas and the disassociation of CO2 which reduces combustion pressures and temperatures.
- In many applications employing EGR, exhaust gas heat exchangers are employed. In the usual case, engine coolant is brought into heat exchange relation with the exhaust gas prior to its recirculation so as to lower its temperature. Not only does this provide a beneficial effect in terms of a reduced temperature of the gases entering the combustion chamber, leading to reduced combustion temperatures and the associated reduction of NOx, it causes the exhaust gases to become more dense due to their reduction in temperature so that for a given volumetric recirculation flow rate, a greater quantity of the exhaust gas is recirculated to the intake side of the engine, thereby promoting greater dilution of the intake air and promoting the associated reduction in NOx.
- However, there are instances during the cycle of operation of an internal combustion engine wherein reduction of the temperature of the exhaust gas by an exhaust gas heat exchanger is undesirable. For example, where the exhaust system for the internal combustion engine is equipped with a catalytic converter to treat exhaust gases to reduce emissions, it is generally necessary that the catalytic converter operate at a high temperature to be effective. Of course, at start up, the catalytic converter will be at ambient temperature and ineffective. Thus, at start up, it is desired that uncooled exhaust gas be discharged into the catalytic converter to quickly bring it up to a temperature whereat it may be effective. Moreover, some sources have indicated a preference for bypassing the exhaust gas heat exchanger in conditions such as idle or no load conditions which often improves idle, no load and part load fuel economy while reducing hydrocarbon and carbon monoxide emissions.
- In some situations, it is difficult to achieve effective EGR because of the absence of a sufficient pressure differential between the exhaust gas recirculation line and the intake manifold. Thus, it is desirable that the exhaust gas heat exchange system minimize pressure drop so as to allow sufficient introduction of exhaust gases into the intake side of the engine to achieve the benefits of EGR.
- The present invention is directed to overcoming one or more of the above problems.
- It is the principal object of the invention to provide a new and improved exhaust gas heat exchanger for use with an internal combustion engine. Even more particularly, it is an object of the invention to provide such a system that is ideally suited for use with an internal combustion engine employed to propel a vehicle.
- An exemplary embodiment of the invention achieves the foregoing objects in an exhaust gas heat exchange system for internal combustion engines which includes an intake manifold having an inlet for recirculating exhaust gas. Also included is an exhaust manifold having at least one inlet receiving exhaust gas from an engine as well as an outlet for discharging exhaust gas and spaced from the inlet(s). An exhaust gas heat exchanger includes a first flow path having an inlet connected to the exhaust manifold to receive exhaust gas therefrom, an outlet for discharging cooled exhaust gas and a second flow path in heat exchange relation with the first flow pass for receipt of a coolant whereby exhaust gas flowing in the first flow path may be cooled. An exhaust valve having a first inlet is connected to the first flow path outlet. It also includes a second inlet connected to the exhaust manifold and an outlet connected to the intake manifold inlet. A valve mechanism is included and has at least one movable component which is movable between positions (a) connecting the exhaust valve first inlet to the exhaust valve outlet and (b) connecting the exhaust valve second inlet to the exhaust valve outlet. Finally, an actuator is connected to the valve mechanism for moving the valve mechanism component(s) between the two aforementioned positions.
- In one embodiment, the exhaust valve second inlet is connected to the exhaust manifold at a location downstream of the exhaust manifold inlet(s) and upstream of the exhaust manifold outlet.
- A preferred embodiment contemplates that the exhaust valve second inlet be connected to the exhaust manifold closely adjacent to the exhaust manifold outlet.
- In one embodiment, the first flow path inlet and the exhaust valve first and second inlets are approximately aligned with one another.
- Preferably, the exhaust gas heat exchanger and the exhaust valve are mounted on the exhaust manifold.
- In a highly preferred embodiment, the exhaust manifold is elongated and the second inlet is connected to the exhaust manifold at a location that is spaced from the exhaust manifold outlet a distance equal to one-half or less of the length of the exhaust manifold. Even more preferably, the distance is one-third or less of the length of the exhaust manifold.
- A preferred embodiment of the invention contemplates that the exhaust manifold be elongated and the exhaust manifold outlet be adjacent to one end thereof. The exhaust gas heat exchanger first flow path inlet has a connection to the exhaust manifold at a location intermediate the ends thereof.
- Preferably, the connection is closely adjacent and end of the exhaust manifold opposite the one end.
- A preferred embodiment of the invention also contemplates that the exhaust gas heat exchanger and the exhaust manifold both be elongated and that the exhaust valve is mounted on one end of the exhaust gas heat exchanger to form an elongated assembly. The assembly is disposed generally parallel to the exhaust manifold.
- In a highly preferred embodiment, the exhaust valve first inlet, second inlet and outlet intersect at a common location and the valve component(s) includes a valve member located at the common location.
- Even more preferably, the exhaust gas heat exchanger is elongated and has an axis of elongation, and the exhaust valve first and second inlets are approximately aligned on the axis of elongation. The exhaust valve outlet is disposed approximately transverse to the axis of elongation.
- Other objects and advantages will become apparent from the following specification taken in connection with the accompanying drawings.
- FIG. 1 is a schematic of a turbocharged internal combustion engine employing exhaust gas recirculation and including an exhaust gas heat exchange system made according to the invention;
- FIG. 2 is a partial schematic, partial mechanical depiction of part of one embodiment of the exhaust gas heat exchange system of the invention;
- FIG. 3 is a view similar to FIG. 2 but showing an alternative embodiment;
- FIG. 4 is an elevation illustrating the components of an embodiment of the invention shown in FIG. 2;
- FIG. 5 is a plan view of the same components;
- FIG. 6 is an enlarged elevation of an exhaust gas heat exchanger that may be employed in practicing the invention;
- FIG. 7 is a sectional view of the exhaust gas heat exchanger taken approximately along the line7-7 in FIG. 6; and
- FIG. 8 is a side elevation of the exhaust gas heat exchanger taken from the bottom of FIG. 6.
- Referring first to FIG. 1, an exemplary embodiment of an exhaust gas heat exchange system made according to the invention will be described generally. The description will involve the environment in which a typical diesel engine for a truck-like vehicle operates but it is to be understood that the invention is applicable to internal combustion engines other than diesel engines and may be employed with efficacy in stationary engine applications as well as in applications for engines other than trucks, as, for example, automobiles and construction, excavating, power generation, marine applications and others.
- A six cylinder diesel engine is generally designated10 and includes an
intake manifold 12 havingoutlet connections 14 to each of the cylinders of theengine 10. Theintake manifold 12 includes aninlet 16 for receiving recirculated exhaust gas from an exhaustgas recirculation line 18 as well ascombustion air 20. While a single inlet is illustrated, two separate inlets could be employed. Combustion air on theline 20 is received from acharge air cooler 22 which in turn receives combustion air from thecompressor side 24 of a turbocharger, generally designated 26. - Also included is an exhaust manifold, generally designated28 which has a plurality of
inlet connections 30, one to each of the cylinders of thediesel engine 10. An exhaust gas heat exchanger, generally designated 32, along with an exhaust valve, generally designated 34, are mounted on theheat exchanger 32, and specifically are together mounted on themanifold 28 in a manner to be seen. - Returning to the
exhaust manifold 28, the same is elongated and at oneend 36, includes a connection to theturbine side 38 of theturbocharger 26 to provide a driving force for the same whereby combustion air is compressed in thecompressor side 24 and delivered to thecharge air cooler 22 for ultimate delivery to theintake manifold 12. Near theopposite end 40 of theexhaust manifold 26 there is a connectingline 42 extending to the exhaustgas heat exchanger 32 and a first flow path (not shown in FIG. 1) thereof. The opposite end of the first flow path discharges at afirst inlet 44 to theexhaust valve 34. At the same time, a connectingline 46 connects to asecond inlet 47 to theexhaust valve 34. Theexhaust valve 34 also includes anoutlet 48 connected to therecirculation line 16. As will be seen, theexhaust valve 34 may be configured to direct cooled exhaust entering the exhaustgas heat exchanger 32 on theline 42 to therecirculation line 18 or to direct uncooled exhaust entering theinlet 47 to therecirculation line 18. - Turning now to FIG. 2, the
valve 34 is illustrated in somewhat greater detail. As can be seen, the assembly of theheat exchanger 32 and thevalve 34 results in an elongated assembly which is disposed approximately parallel to theexhaust manifold 28. The arrangement is such that thefirst inlet 44 to thevalve 34 as well as thesecond inlet 47 are aligned on approximately the longitudinal axis of the assembly of theheat exchanger 32 and thevalve 34. Also on the axis of elongation of that assembly is theinlet 50 to the first flow path within the exhaustgas heat exchanger 32. An outlet from that flow path, located in the vicinity of thefirst inlet 44 to thevalve 34 and given thereference numeral 52 is also so aligned. Theoutlet 48 is at approximate right angles to the axis of elongation. Stated another way, theoutlet 48 joins with theinlets intersection 54. At that point, a movable valve component in the form of arotatable valve member 56 is located and is movable between the solid and dotted line positions illustrated in FIG. 2. When in the solid line position, recirculation flow back to the inlet manifold 12 (FIG. 1) will be through the exhaustgas heat exchanger 32 meaning that the recirculated exhaust will be cooled. On the other hand, when thevalve member 56 is moved to the dotted line position, flow will be from thesecond inlet 47 to theoutlet 48 and the exhaustgas heat exchanger 32 will be bypassed entirely. Thus, hot exhaust gas that has not been cooled will be directed back to theintake manifold 12. - Desirably, the
connection 42 linking theexhaust manifold 26 to theheat exchanger 32 includes a bellows such as schematically illustrated at 58 to provide for thermal expansion and contraction. The bellows is connected to anoutlet 60 from theexhaust manifold 28 near theend 40 while theconnection 46 is connected to theexhaust manifold 28 at apoint 62 adjacent theend 36. - The embodiment illustrated in FIG. 2 is preferred because the
connection 62 is closely adjacent theend 36 whereat, by reason of its typical connection to a turbocharger 26 (FIG. 1), head pressure will be maximized. Thus pressure drop problems associated with ECR are minimized. - FIG. 3 shows an alternative embodiment wherein the locations of the
heat exchanger 32 and thevalve 34 are interchanged. That is to say, theinlet 50 to the first flow path is connected to theconnection 46 whereas theconnection 42 is connected to thesecond inlet 47. The outlet of the first flow path within theheat exchanger 32 is connected to thefirst inlet 44. The orientation of theinlets outlet 48 is the same as in FIG. 2 except they have been reversed as illustrated. At the point ofintersection 54 of the inlets and the outlet, thevalve member 56 is provided as before. Again, it is movable between solid and dotted line positions. In the case of the embodiment shown in FIG. 3, when thevalve member 56 is in the solid line position, uncooled exhaust gas will be directed to therecirculation line 18 whereas when thevalve member 56 is in the dotted line position as shown in FIG. 3, cooled exhaust will be provided for recirculation. - In both the embodiments shown in FIGS. 2 and 3, it is desirable that the point of
connection 62 of theconnection 46 be reasonably adjacent to theend 36 of the manifold 28. As illustrated, the manifold 28 is elongated and thepoint 62 is at a distance of one-half the length of the manifold 28 or less from theend 36. Preferably, the spacing is one-third of the length of the manifold 28 or less. However, in some cases thepoint 62 may be located most anywhere along the length of the manifold 28. - FIGS. 4 and 5 illustrate mechanical drawings of the assemblies shown in FIG. 2 (save for one less inlet connection30) and it will be appreciated that the embodiment of FIG. 3 would be similarly configured except for the aforementioned reversing of the location of the
heat exchanger 32 and thevalve 34. It will be observed thatflanges 70 are located about theinlets 30 to the manifold 28 and are provided withbolt holes 72 whereby the manifold may be bolted to an engine. Similarly, thebellows 58 may be provided with aflange 74 by which one end of the assembly of theheat exchanger motor 76 is connected via alink 78 to an eccentric 80 which in turn is connected to thevalve member 56 for moving thevalve member 56 between the aforementioned positions. Mountingbrackets 81 connect the assembly of theheat exchanger 32 andexhaust valve 34 to themanifold 28. Coolant inlet andoutlet ports 83 which typically receive engine coolant, are provided on theheat exchanger 32. Aflange 84, similar to theflanges 70, is connected to theoutlet port 48 and may be connected to the recirculation line 18 (FIG. 1) via theflange 84. - While the exhaust
gas heat exchanger 32 may take on many known forms known in the art, one preferred form is illustrated in FIGS. 6-8, inclusive. The inlet to the first flow path includes a frusto-conical port 90 connected to one end of a core, generally designated 92, made up of a series of stampedinterior plates 94 flanked byend plates 96. As a result, a housingless configuration for thecore 92 of the heat exchanger results. Theend plates 96 include relativelyshallow depressions 98 in their centers surrounded by upstandingperipheral walls 100 which terminate in outwardly directedflanges 102. Eachinterior plate 94 includes an enlarged, relatively deepinterior depression 104 surrounded by anupstanding wall 106 which is peripheral and which terminates in outwardly directedflanges 108. At two locations in each of the plates 94 (only one of which is shown in FIG. 7),cylindrical bosses 112 are provided. Thebosses 112 havecentral apertures 114. Theinterior plates 94 are stacked in alternating fashion as illustrated in FIG. 7 with thebosses 112 aligned. The inlet andoutlet ports 83 extend through the uppermost one of theend plates 96 and into fluid communication with thebosses 112 so as to allow for the entry and exit of coolant into thecore 92 of the heat exchanger. - Each of the
interior plates 94 is also provided with a peripheral,exterior bead 116 at the base of the upstanding side walls 160. Theinterior plates 94 are assembled in alternating fashion as illustrated in FIG. 7 with thebeads 116 at adjacent plates being abutted to one another. The assembly is brazed and as a consequence, sealedcoolant flow paths 120 are provided between adjacent pairs of the plates. Between abutted pairs of theplates 94,exhaust gas passages 122 exist.Interior fins 124 are located in each of the exhaustgas flow paths 122 and preferably are quite smooth so as to avoid accumulation of particulate material that may be present in the exhaust stream. That is to say, the first flow paths referred to previously are defined by theflow paths 122 for the exhaust while a second flow path for the coolant is defined by theflow paths 120. A header 130 (FIG. 6) is located at the end ofcore 92 opposite theinlet 90 and is connected to each of theflow paths 122 to receive exhaust gas therefrom. Theheader 130 may have thevalve 34 mounted directly thereto. From the foregoing, it will be appreciated that an exhaust gas heat exchange system made according to the invention is of compact construction and thus may be readily housed within, for example, the engine compartment of a vehicle. This compactness is significantly aided by the fact that the assembly of theheat exchanger 32 and thevalve 34 is disposed parallel to theexhaust header 28. The same compactness of the assembly minimizes pressure drop and the advantageous location of thepoint 62 whereat theconnector 46 connects from the manifold 28 assures that exhaust gas at its greatest head pressure will be available for recirculation. Appropriate sensors may be employed to control theactuator 76 and thus the position of thevalve member 56 to selectively introduce theheat exchanger 32 into the flow system or remove it therefrom during warm-up, cold conditions, low and partial loads, etc. The arrangement of the two inlets and the outlet for thevalve 34 provides an extremely simple valve construction and one that is not readily fouled by the exhaust gases flowing through it. The heat exchanger construction disclosed is essentially housingless and consequently, its cost and mass are both reduced from other sorts of heat exchangers conventionally employed in exhaust gas heat exchange systems.
Claims (12)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10011954A DE10011954A1 (en) | 2000-03-11 | 2000-03-11 | Exhaust gas heat exchanger in an exhaust gas recirculation arrangement |
DE10011954.9 | 2000-03-11 | ||
DE10011954 | 2000-03-11 |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010020363A1 true US20010020363A1 (en) | 2001-09-13 |
US6360532B2 US6360532B2 (en) | 2002-03-26 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/777,326 Expired - Fee Related US6360532B2 (en) | 2000-03-11 | 2001-02-06 | Exhaust gas heat exchange system for an internal combustion engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US6360532B2 (en) |
EP (1) | EP1132609B1 (en) |
AT (1) | ATE340924T1 (en) |
DE (2) | DE10011954A1 (en) |
ES (1) | ES2273753T3 (en) |
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US20090120418A1 (en) * | 2007-11-08 | 2009-05-14 | Bayerische Motoren Werke Aktiengesellschaft | Internal-Combustion Engine Having a Cooled Exhaust Gas Recirculation System as Well as an Exhaust Gas Manifold |
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-
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- 2001-02-14 ES ES01103422T patent/ES2273753T3/en not_active Expired - Lifetime
- 2001-02-14 AT AT01103422T patent/ATE340924T1/en not_active IP Right Cessation
- 2001-02-14 DE DE50111065T patent/DE50111065D1/en not_active Expired - Lifetime
- 2001-02-14 EP EP01103422A patent/EP1132609B1/en not_active Expired - Lifetime
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JP2021110235A (en) * | 2019-12-31 | 2021-08-02 | 株式会社クボタ | Exhaust manifold for industrial engine, and the industrial engine |
JP7260466B2 (en) | 2019-12-31 | 2023-04-18 | 株式会社クボタ | industrial engine exhaust manifold and industrial engine |
Also Published As
Publication number | Publication date |
---|---|
US6360532B2 (en) | 2002-03-26 |
DE10011954A1 (en) | 2001-09-13 |
DE50111065D1 (en) | 2006-11-09 |
EP1132609B1 (en) | 2006-09-27 |
EP1132609A2 (en) | 2001-09-12 |
EP1132609A3 (en) | 2002-03-20 |
ATE340924T1 (en) | 2006-10-15 |
ES2273753T3 (en) | 2007-05-16 |
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