US20150240705A1 - Two-Stage Turbocharger System For Internal Combustion Engines Featuring Cylinder Deactivation - Google Patents
Two-Stage Turbocharger System For Internal Combustion Engines Featuring Cylinder Deactivation Download PDFInfo
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- US20150240705A1 US20150240705A1 US14/192,469 US201414192469A US2015240705A1 US 20150240705 A1 US20150240705 A1 US 20150240705A1 US 201414192469 A US201414192469 A US 201414192469A US 2015240705 A1 US2015240705 A1 US 2015240705A1
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- cylinders
- exhaust passage
- turbocharger
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- exhaust
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
- F02B37/002—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel the exhaust supply to one of the exhaust drives can be interrupted
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
- F02D17/02—Cutting-out
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D23/00—Controlling engines characterised by their being supercharged
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- F02M25/0713—
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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
- F02M26/02—EGR systems specially adapted for supercharged engines
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present disclosure relates to a two-stage turbocharger system for internal combustion engines featuring cylinder deactivation.
- Cylinder deactivation is a technology that often is applied to naturally aspirated internal combustion engines to improve the engine's efficiencies under part-load conditions by switching off a selected number of cylinders so the remaining cylinders would operate with reduced pumping losses [see “Active Fuel Management Technology: Hardware Development on a 2007 GM 3.9L V-6 OHV SI Engine,” SAE Paper 2007-01-1292, 2007.]
- Cylinder deactivation can be applied to turbocharged engines as disclosed in U.S. Pat. Nos. 6,715,289 and 6,786,190.
- the operating ranges of the engine in the deactivated mode can be limited by the turbocharger compressor's flow and boost pressure capabilities [see “The 1.4-L TSI Gasoline Engine with Cylinder Deactivation,” MTZ, volume 73, March 2012.]
- turbocharger compressor it is possible to size a turbocharger compressor to favor the deactivated operation of the engine, primarily at lower engine speeds. This would require the use of a smaller compressor, by compromising the engine's performance at high engine speeds.
- the compressor can be at a size such that a single fixed geometry turbine is not capable of driving the compressor to meet performance requirements. As anticipated, a smaller turbine is desired to meet the low engine speed target while a larger turbine is desired to meet the high engine speed target.
- turbocharger When packaging and complexity are not of concerns, a two-stage turbocharger system can be adopted with greater flexibilities than what can be achieved with a single turbocharger. With the addition of another turbocharger, the so-called high-pressure turbocharger can be sized for the deactivated operation.
- the present disclosure provides an enhanced two-stage turbocharger system that is architected for engines featuring cylinder deactivation and its operating modes.
- An internal combustion engine includes an engine defining a plurality of cylinders including full-time active cylinders and cylinders capable of being deactivated.
- a turbocharger system having a high pressure turbocharger in communication with the exhaust passages from the full-time active cylinders and a low pressure turbocharger in communication with the exhaust passages from the cylinders capable of being deactivated.
- a control valve is provided in communication with the exhaust passages from the full-time active cylinders and being operable in an open position to allow exhaust gases from the full-time active cylinders to pass through the second turbocharger along with the exhaust gasses from the cylinders capable of being deactivated, and being operable in a closed position to direct exhaust gases from the full-time active cylinders to pass through the first turbocharger.
- FIG. 1 is a schematic view of an engine featuring cylinder deactivation and a two-stage turbocharger system according to the principles of the present disclosure
- FIG. 2 is a schematic view of the engine featuring cylinder deactivation and a two-stage turbocharger system as shown in FIG. 1 with cylinders deactivated for operation at low speed and under low load and the high pressure turbocharger being operated;
- FIG. 3 is a schematic view of the engine featuring cylinder deactivation and a two-stage turbocharger system as shown in FIG. 1 with all cylinders operable and the exhaust routed to a low pressure turbocharger;
- FIG. 4 is a schematic view of an engine featuring cylinder deactivation and a two-stage turbocharger system according to the principles of the present disclosure with the exhaust manifold being an integral part of the cylinder head.
- Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
- first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
- Spatially relative terms such as “inner,” “outer,” “beneath,” “below,” “lower,” “above,” “upper,” and the like, may be used herein for ease of description to describe one element or feature's relationship to another element(s) or feature(s) as illustrated in the figures. Spatially relative terms may be intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as “below” or “beneath” other elements or features would then be oriented “above” the other elements or features. Thus, the example term “below” can encompass both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
- An engine assembly 10 is illustrated in FIG. 1 and includes an engine structure 12 .
- the engine structure 12 may include an engine block 14 and a cylinder head 16 .
- the engine structure 12 may define first, second, third and fourth cylinders 18 , 20 , 22 , 24 .
- the description includes first, second, third and fourth cylinders 18 , 20 , 22 , 24 for simplicity and it is understood that the present teachings apply to any number of piston-cylinder arrangements and a variety of reciprocating engine configurations including, but not limited to, V-engines, in-line engines, and horizontally opposed engines, as well as both overhead cam and cam-in-block configurations.
- the engine structure supports a crankshaft and a plurality of pistons that are disposed in the respective cylinders 18 , 20 , 22 , 24 as is known in the art.
- the engine 10 features cylinder deactivation such that, by way of example, a controller 26 can deactivate one or more of the cylinders 18 , 20 , 22 , 24 .
- cylinders 20 and 22 can be deactivated by the controller 26 .
- the cylinder deactivation occurs as a function of load or torque demand by the vehicle as determined by variables such as manifold pressure. If the internal combustion engine is in a condition where it can deliver the desired torque with partial displacement to improve efficiency, the controller 26 will deactivate the mechanisms operating the valves for the selected cylinders and also shut off fuel and spark to the selected cylinders. The deactivated cylinders will then function as air springs.
- the engine structure 12 may define a plurality of intake ports 30 (only one is labeled) and a plurality of exhaust ports 32 (only one is labeled) in the cylinder head 16 associated with each of the cylinders 18 , 20 , 22 and 24 .
- Engine assembly 10 includes an intake manifold 34 having a plurality of runners 36 (only one is labeled) in communication with each of the intake ports 30 .
- a plurality of exhaust runners 40 , 42 , 44 , 46 are in communication with each of the exhaust ports 32 .
- the exhaust runners are bifurcated so that the exhaust runners 40 and 46 from the full-time active cylinders 18 , 24 are connected to each other at first exhaust passage 48 and the exhaust runners 42 and 44 , from the cylinders 20 , 22 that can be deactivated, are connected to each other at second exhaust passage 50 .
- appropriate deactivated cylinders can be chosen based on the same firing order considerations.
- appropriate exhaust manifold(s) can be constructed to achieve the same method of cylinder grouping.
- FIG. 4 illustrates an alternative engine assembly 10 ′ similar to the system of engine assembly 10 , with the exhaust manifold including exhaust runners 40 , 42 , 44 , and 46 as well as the first and second exhaust passages 48 , 50 integrated into the cylinder head 16 .
- a two-stage turbocharger system 52 includes a first turbocharger 54 and a second turbocharger 56 .
- the first turbocharger 54 receives exhaust gases from the first exhaust passage 48 and the second turbocharger 56 receives exhaust gasses from the second exhaust passage 50 .
- Each of the first and second turbochargers 54 , 56 include a turbine 58 that is connected to a shaft that drives a compressor 60 .
- the turbines 58 of the first and second turbochargers 54 , 56 are driven by the exhaust gasses from the first and second exhaust passages 48 , 50 .
- the exhaust gasses that pass through the turbines 58 are exhausted through the exhaust system 62 .
- the compressors 60 are in communication with an intake system 64 and provide compressed air to the intake manifold 34 .
- a control valve 66 is controlled by the controller 26 for selectively directing exhaust gases from the first exhaust passage 48 to the second exhaust passage so that all of the exhaust gasses are directed to the turbine 58 of the second turbocharger 56 .
- a wastegate 68 is controlled by the controller for allowing exhaust gasses from the turbine 58 of the first turbocharger 54 to bypass the second turbocharger 56 and go directly to the exhaust system 62 .
- a bypass valve 70 is controlled by the controller 26 for allowing compressed intake air from the compressor 60 of the second turbocharger 56 to bypass the first turbocharger for delivery to the intake manifold 34 .
- a purge valve 72 is in communication with the intake system 64 .
- the intake air from the turbochargers 54 , 56 passes through a heat exchanger 74 to cool the intake air prior to passing through a throttle valve 76 that is controlled by the controller 26 .
- the engine assembly 10 can be provided with a low-pressure exhaust gas recirculation (EGR) passage 78 that is controlled by an EGR control valve 80 to direct exhaust gases from the exhaust system to be mixed with the intake air from the intake system 64 .
- the EGR passage 78 can be provided with a heat exchanger 82 to cool the recirculated exhaust gases prior to introduction into the intake system 64 .
- FIG. 2 The operation of the engine 10 when the cylinders 20 and 22 are deactivated by the controller 26 is illustrated in FIG. 2 .
- the turbine control valve 66 , high-pressure compressor bypass 70 and purge valve 72 are closed while the wastegate 68 is preferably open to minimize the exhaust backpressure.
- the exhaust flow from the cylinders 18 and 24 can be fully utilized to power the turbine of the first (high pressure) turbocharger 54 , which in turn drives the compressor 60 of the first turbocharger to generate the desired boost.
- FIG. 3 illustrates the other engine operating mode when all the cylinders are active.
- the turbine control valve 66 is open to allow the exhaust flow from the cylinders 18 and 24 to merge with the exhaust flow from the cylinders 20 and 22 before entering the low-pressure turbine 58 of the second (low pressure) turbocharger 56 .
- the wastegate 68 can be modulated to allow the turbine 58 to drive the compressor 60 of the low pressure turbocharger to generate desired boost.
- the high-pressure compressor bypass 70 is open to allow the air flow from the compressor of the low pressure turbocharger 56 to reach the intake manifold 34 of the engine 10 .
- the engine 10 of the present disclosure is intended to achieve the desired functionalities with minimum complexities, i.e., by having a single turbine control valve 66 . It is conceivable that optional control valves can be added to fully isolate the two turbines.
- the EGR system 78 has been demonstrated to help alleviate combustion limitations under high-load conditions such as pre-ignition and knock for gasoline engines and NOx and smoke emissions for diesel engines. Since the engine in the deactivated mode would operate more frequently in higher specific load range in a vehicle relative to the full-engine mode, by having a dedicated high-pressure turbocharger allows the greatest flow and boost capabilities for EGR flows in addition to air.
- the controller 26 coordinates the operation of the turbochargers' bypass valves and engine deactivation along with any necessary sensors.
- the controller controls the throttle body 76 , which regulates the engine's load, by regulating the inlet flow rates.
- the controller also controls the EGR valve, if equipped.
- the turbocharger 54 can be sized to generate desired boost to extend the engine's operating range in the deactivated mode at higher available efficiencies, even with EGR, and thus enhancing the engine's efficiency characteristics.
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Abstract
Description
- The present disclosure relates to a two-stage turbocharger system for internal combustion engines featuring cylinder deactivation.
- This section provides background information related to the present disclosure which is not necessarily prior art.
- Present regulatory conditions in the automotive market have led to an increasing demand to improve fuel economy and reduce emissions in present vehicles. These regulatory conditions must be balanced with the demands of a consumer for high-performance and quick response for a vehicle. Cylinder deactivation is a technology that often is applied to naturally aspirated internal combustion engines to improve the engine's efficiencies under part-load conditions by switching off a selected number of cylinders so the remaining cylinders would operate with reduced pumping losses [see “Active Fuel Management Technology: Hardware Development on a 2007 GM 3.9L V-6 OHV SI Engine,” SAE Paper 2007-01-1292, 2007.]
- Cylinder deactivation can be applied to turbocharged engines as disclosed in U.S. Pat. Nos. 6,715,289 and 6,786,190. However, when an engine is equipped with a single turbocharger, the operating ranges of the engine in the deactivated mode can be limited by the turbocharger compressor's flow and boost pressure capabilities [see “The 1.4-L TSI Gasoline Engine with Cylinder Deactivation,” MTZ, volume 73, March 2012.]
- It is possible to size a turbocharger compressor to favor the deactivated operation of the engine, primarily at lower engine speeds. This would require the use of a smaller compressor, by compromising the engine's performance at high engine speeds. The compressor can be at a size such that a single fixed geometry turbine is not capable of driving the compressor to meet performance requirements. As anticipated, a smaller turbine is desired to meet the low engine speed target while a larger turbine is desired to meet the high engine speed target.
- When packaging and complexity are not of concerns, a two-stage turbocharger system can be adopted with greater flexibilities than what can be achieved with a single turbocharger. With the addition of another turbocharger, the so-called high-pressure turbocharger can be sized for the deactivated operation.
- The present disclosure provides an enhanced two-stage turbocharger system that is architected for engines featuring cylinder deactivation and its operating modes.
- This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.
- An internal combustion engine includes an engine defining a plurality of cylinders including full-time active cylinders and cylinders capable of being deactivated. A turbocharger system having a high pressure turbocharger in communication with the exhaust passages from the full-time active cylinders and a low pressure turbocharger in communication with the exhaust passages from the cylinders capable of being deactivated. A control valve is provided in communication with the exhaust passages from the full-time active cylinders and being operable in an open position to allow exhaust gases from the full-time active cylinders to pass through the second turbocharger along with the exhaust gasses from the cylinders capable of being deactivated, and being operable in a closed position to direct exhaust gases from the full-time active cylinders to pass through the first turbocharger.
- Further areas of applicability will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- The drawings described herein are for illustrative purposes only of selected embodiments and not all possible implementations, and are not intended to limit the scope of the present disclosure.
-
FIG. 1 is a schematic view of an engine featuring cylinder deactivation and a two-stage turbocharger system according to the principles of the present disclosure; -
FIG. 2 is a schematic view of the engine featuring cylinder deactivation and a two-stage turbocharger system as shown inFIG. 1 with cylinders deactivated for operation at low speed and under low load and the high pressure turbocharger being operated; -
FIG. 3 is a schematic view of the engine featuring cylinder deactivation and a two-stage turbocharger system as shown inFIG. 1 with all cylinders operable and the exhaust routed to a low pressure turbocharger; -
FIG. 4 is a schematic view of an engine featuring cylinder deactivation and a two-stage turbocharger system according to the principles of the present disclosure with the exhaust manifold being an integral part of the cylinder head. - Corresponding reference numerals indicate corresponding parts throughout the several views of the drawings.
- Example embodiments will now be described more fully with reference to the accompanying drawings.
- Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
- The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting. As used herein, the singular forms “a,” “an,” and “the” may be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms “comprises,” “comprising,” “including,” and “having,” are inclusive and therefore specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order discussed or illustrated, unless specifically identified as an order of performance. It is also to be understood that additional or alternative steps may be employed.
- When an element or layer is referred to as being “on,” “engaged to,” “connected to,” or “coupled to” another element or layer, it may be directly on, engaged, connected or coupled to the other element or layer, or intervening elements or layers may be present. In contrast, when an element is referred to as being “directly on,” “directly engaged to,” “directly connected to,” or “directly coupled to” another element or layer, there may be no intervening elements or layers present. Other words used to describe the relationship between elements should be interpreted in a like fashion (e.g., “between” versus “directly between,” “adjacent” versus “directly adjacent,” etc.). As used herein, the term “and/or” includes any and all combinations of one or more of the associated listed items.
- Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as “first,” “second,” and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
- Spatially relative terms, such as “inner,” “outer,” “beneath,” “below,” “lower,” “above,” “upper,” and the like, may be used herein for ease of description to describe one element or feature's relationship to another element(s) or feature(s) as illustrated in the figures. Spatially relative terms may be intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as “below” or “beneath” other elements or features would then be oriented “above” the other elements or features. Thus, the example term “below” can encompass both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
- An
engine assembly 10 is illustrated inFIG. 1 and includes anengine structure 12. Theengine structure 12 may include anengine block 14 and acylinder head 16. Theengine structure 12 may define first, second, third andfourth cylinders fourth cylinders respective cylinders - The
engine 10 features cylinder deactivation such that, by way of example, acontroller 26 can deactivate one or more of thecylinders cylinders controller 26. The cylinder deactivation occurs as a function of load or torque demand by the vehicle as determined by variables such as manifold pressure. If the internal combustion engine is in a condition where it can deliver the desired torque with partial displacement to improve efficiency, thecontroller 26 will deactivate the mechanisms operating the valves for the selected cylinders and also shut off fuel and spark to the selected cylinders. The deactivated cylinders will then function as air springs. - The
engine structure 12 may define a plurality of intake ports 30 (only one is labeled) and a plurality of exhaust ports 32 (only one is labeled) in thecylinder head 16 associated with each of thecylinders Engine assembly 10 includes anintake manifold 34 having a plurality of runners 36 (only one is labeled) in communication with each of theintake ports 30. A plurality ofexhaust runners exhaust ports 32. The exhaust runners are bifurcated so that theexhaust runners active cylinders first exhaust passage 48 and theexhaust runners cylinders second exhaust passage 50. For other engine architectures like inline-6, V6, V8, etc., appropriate deactivated cylinders can be chosen based on the same firing order considerations. For each of these engine configurations, appropriate exhaust manifold(s) can be constructed to achieve the same method of cylinder grouping.FIG. 4 illustrates analternative engine assembly 10′ similar to the system ofengine assembly 10, with the exhaust manifold includingexhaust runners second exhaust passages cylinder head 16. - A two-
stage turbocharger system 52 includes afirst turbocharger 54 and asecond turbocharger 56. Thefirst turbocharger 54 receives exhaust gases from thefirst exhaust passage 48 and thesecond turbocharger 56 receives exhaust gasses from thesecond exhaust passage 50. Each of the first andsecond turbochargers turbine 58 that is connected to a shaft that drives acompressor 60. Theturbines 58 of the first andsecond turbochargers second exhaust passages turbines 58 are exhausted through theexhaust system 62. Thecompressors 60 are in communication with anintake system 64 and provide compressed air to theintake manifold 34. Acontrol valve 66 is controlled by thecontroller 26 for selectively directing exhaust gases from thefirst exhaust passage 48 to the second exhaust passage so that all of the exhaust gasses are directed to theturbine 58 of thesecond turbocharger 56. Awastegate 68 is controlled by the controller for allowing exhaust gasses from theturbine 58 of thefirst turbocharger 54 to bypass thesecond turbocharger 56 and go directly to theexhaust system 62. Abypass valve 70 is controlled by thecontroller 26 for allowing compressed intake air from thecompressor 60 of thesecond turbocharger 56 to bypass the first turbocharger for delivery to theintake manifold 34. Apurge valve 72 is in communication with theintake system 64. The intake air from theturbochargers throttle valve 76 that is controlled by thecontroller 26. Theengine assembly 10 can be provided with a low-pressure exhaust gas recirculation (EGR)passage 78 that is controlled by anEGR control valve 80 to direct exhaust gases from the exhaust system to be mixed with the intake air from theintake system 64. TheEGR passage 78 can be provided with aheat exchanger 82 to cool the recirculated exhaust gases prior to introduction into theintake system 64. - The operation of the
engine 10 when thecylinders controller 26 is illustrated inFIG. 2 . In this mode of operation, theturbine control valve 66, high-pressure compressor bypass 70 andpurge valve 72 are closed while thewastegate 68 is preferably open to minimize the exhaust backpressure. The exhaust flow from thecylinders turbocharger 54, which in turn drives thecompressor 60 of the first turbocharger to generate the desired boost. -
FIG. 3 illustrates the other engine operating mode when all the cylinders are active. In this mode of operation, theturbine control valve 66 is open to allow the exhaust flow from thecylinders cylinders pressure turbine 58 of the second (low pressure)turbocharger 56. Similar to the conventional practice, thewastegate 68 can be modulated to allow theturbine 58 to drive thecompressor 60 of the low pressure turbocharger to generate desired boost. The high-pressure compressor bypass 70 is open to allow the air flow from the compressor of thelow pressure turbocharger 56 to reach theintake manifold 34 of theengine 10. - The
engine 10 of the present disclosure is intended to achieve the desired functionalities with minimum complexities, i.e., by having a singleturbine control valve 66. It is conceivable that optional control valves can be added to fully isolate the two turbines. - The
EGR system 78 has been demonstrated to help alleviate combustion limitations under high-load conditions such as pre-ignition and knock for gasoline engines and NOx and smoke emissions for diesel engines. Since the engine in the deactivated mode would operate more frequently in higher specific load range in a vehicle relative to the full-engine mode, by having a dedicated high-pressure turbocharger allows the greatest flow and boost capabilities for EGR flows in addition to air. - The
controller 26 coordinates the operation of the turbochargers' bypass valves and engine deactivation along with any necessary sensors. In addition, the controller controls thethrottle body 76, which regulates the engine's load, by regulating the inlet flow rates. The controller also controls the EGR valve, if equipped. - With the high-
pressure turbocharger 54 of a two-stage system dedicated for engine operation with a selected number of its cylinders deactivated, theturbocharger 54 can be sized to generate desired boost to extend the engine's operating range in the deactivated mode at higher available efficiencies, even with EGR, and thus enhancing the engine's efficiency characteristics. - The foregoing description of the embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment, but, where applicable, are interchangeable and can be used in a selected embodiment, even if not specifically shown or described. The same may also be varied in many ways. Such variations are not to be regarded as a departure from the disclosure, and all such modifications are intended to be included within the scope of the disclosure.
Claims (6)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US14/192,469 US9121338B1 (en) | 2014-02-27 | 2014-02-27 | Two-stage turbocharger system for internal combustion engines featuring cylinder deactivation |
DE102015102647.3A DE102015102647B4 (en) | 2014-02-27 | 2015-02-25 | Two-stage turbocharging system for an internal combustion engine with cylinder deactivation |
CN201510089396.6A CN104879207B (en) | 2014-02-27 | 2015-02-27 | Twin turbo-charger system for the internal combustion engine with cylinder deactivation feature |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US14/192,469 US9121338B1 (en) | 2014-02-27 | 2014-02-27 | Two-stage turbocharger system for internal combustion engines featuring cylinder deactivation |
Publications (2)
Publication Number | Publication Date |
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US20150240705A1 true US20150240705A1 (en) | 2015-08-27 |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160010594A1 (en) * | 2014-07-11 | 2016-01-14 | GM Global Technology Operations LLC | Engine with cylinder deactivation and multi-stage turbocharging system |
US20170306865A1 (en) * | 2016-04-26 | 2017-10-26 | Hyundai Motor Company | Engine system and control method of engine system |
US20180003070A1 (en) * | 2016-06-30 | 2018-01-04 | General Electric Company | Method and systems for an energy recovery and energy converting unit for an engine |
CN107587947A (en) * | 2016-07-06 | 2018-01-16 | 现代自动车株式会社 | Control the method and system of vehicle Charge device |
US20190386318A1 (en) * | 2015-12-29 | 2019-12-19 | Northeastern University | Non-Noble Metal Electrocatalysts for Oxygen Depolarized Cathodes and Their Application in Chlor-Alkali Electrolysis Cells |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101734250B1 (en) * | 2015-12-08 | 2017-05-24 | 현대자동차 주식회사 | Engine system |
DE102017200363B4 (en) * | 2016-02-04 | 2022-07-07 | Ford Global Technologies, Llc | Method for operating a parallel-charged internal combustion engine with switchable turbine and internal combustion engine for carrying out such a method |
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US10132252B2 (en) * | 2016-08-22 | 2018-11-20 | Hyundai Motor Company | Engine system |
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DE102019201018A1 (en) * | 2019-01-28 | 2020-08-27 | Volkswagen Aktiengesellschaft | "Procedure for operating a charging system" |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3629841A1 (en) * | 1986-09-02 | 1987-05-21 | Daimler Benz Ag | Multicylinder supercharged internal combustion engine |
US20060021347A1 (en) * | 2004-07-28 | 2006-02-02 | Ford Global Technologies, Llc | Series/parallel turbochargers and switchable high/low pressure egr for internal combustion engines |
US20070056282A1 (en) * | 2005-09-14 | 2007-03-15 | Iwaszkiewicz Titus J | Diesel engine charge air cooler bypass passage and method |
US20100024416A1 (en) * | 2008-07-31 | 2010-02-04 | Gladden John R | Exhaust system having parallel asymmetric turbochargers and EGR |
DE102008052167A1 (en) * | 2008-10-17 | 2010-04-22 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage exhaust gas turbocharger for internal-combustion engine, has closing element provided in manifold, so that exhaust gases from different cylinders are separated and guided to high pressure turbines |
EP2246543A1 (en) * | 2009-04-01 | 2010-11-03 | Ford Global Technologies, LLC | Cylinder head with two exhaust manifolds and method to operate an internal combustion engine with such a cylinder head |
US20120260650A1 (en) * | 2011-04-14 | 2012-10-18 | Caterpillar Inc. | Internal combustion engine with improved efficiency |
US20120285164A1 (en) * | 2011-05-12 | 2012-11-15 | Ford Global Technologies, Llc | Turbocharged engine with separate exhaust manifolds and method for operating such an engine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19511232A1 (en) * | 1995-03-27 | 1996-10-02 | Abb Management Ag | Method and device for supercharging an internal combustion engine |
US6715289B2 (en) | 2002-04-08 | 2004-04-06 | General Motors Corporation | Turbo-on-demand engine with cylinder deactivation |
US6786190B2 (en) | 2002-11-25 | 2004-09-07 | General Motors Corporation | Compact turbocharged cylinder deactivation engine |
DE102004035323A1 (en) * | 2004-07-21 | 2006-02-16 | Bayerische Motoren Werke Ag | Sequential loader control with cylinder deactivation |
DE102011090160B4 (en) * | 2011-12-30 | 2023-02-23 | Dr.Ing.H.C. F. Porsche Ag | Internal combustion engine with an arrangement for routing exhaust gas and charge air |
-
2014
- 2014-02-27 US US14/192,469 patent/US9121338B1/en active Active
-
2015
- 2015-02-25 DE DE102015102647.3A patent/DE102015102647B4/en active Active
- 2015-02-27 CN CN201510089396.6A patent/CN104879207B/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3629841A1 (en) * | 1986-09-02 | 1987-05-21 | Daimler Benz Ag | Multicylinder supercharged internal combustion engine |
US20060021347A1 (en) * | 2004-07-28 | 2006-02-02 | Ford Global Technologies, Llc | Series/parallel turbochargers and switchable high/low pressure egr for internal combustion engines |
US20070056282A1 (en) * | 2005-09-14 | 2007-03-15 | Iwaszkiewicz Titus J | Diesel engine charge air cooler bypass passage and method |
US20100024416A1 (en) * | 2008-07-31 | 2010-02-04 | Gladden John R | Exhaust system having parallel asymmetric turbochargers and EGR |
DE102008052167A1 (en) * | 2008-10-17 | 2010-04-22 | Bayerische Motoren Werke Aktiengesellschaft | Two-stage exhaust gas turbocharger for internal-combustion engine, has closing element provided in manifold, so that exhaust gases from different cylinders are separated and guided to high pressure turbines |
EP2246543A1 (en) * | 2009-04-01 | 2010-11-03 | Ford Global Technologies, LLC | Cylinder head with two exhaust manifolds and method to operate an internal combustion engine with such a cylinder head |
US20120260650A1 (en) * | 2011-04-14 | 2012-10-18 | Caterpillar Inc. | Internal combustion engine with improved efficiency |
US20120285164A1 (en) * | 2011-05-12 | 2012-11-15 | Ford Global Technologies, Llc | Turbocharged engine with separate exhaust manifolds and method for operating such an engine |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160010594A1 (en) * | 2014-07-11 | 2016-01-14 | GM Global Technology Operations LLC | Engine with cylinder deactivation and multi-stage turbocharging system |
US9945329B2 (en) * | 2014-07-11 | 2018-04-17 | GM Global Technology Operations LLC | Engine with cylinder deactivation and multi-stage turbocharging system |
US20190386318A1 (en) * | 2015-12-29 | 2019-12-19 | Northeastern University | Non-Noble Metal Electrocatalysts for Oxygen Depolarized Cathodes and Their Application in Chlor-Alkali Electrolysis Cells |
US20170306865A1 (en) * | 2016-04-26 | 2017-10-26 | Hyundai Motor Company | Engine system and control method of engine system |
US10190513B2 (en) * | 2016-04-26 | 2019-01-29 | Hyundai Motor Company | Control method of engine system |
US20180003070A1 (en) * | 2016-06-30 | 2018-01-04 | General Electric Company | Method and systems for an energy recovery and energy converting unit for an engine |
US10337347B2 (en) * | 2016-06-30 | 2019-07-02 | Ge Global Sourcing Llc | Method and systems for an energy recovery and energy converting unit for an engine |
US10900373B2 (en) | 2016-06-30 | 2021-01-26 | Transportation Holdings, LLC | Method and systems for an energy recovery and energy converting unit for an engine |
US11346238B2 (en) | 2016-06-30 | 2022-05-31 | Transportation Ip Holdings, Llc | Method and systems for an energy recovery and energy converting unit for an engine |
US11781443B2 (en) | 2016-06-30 | 2023-10-10 | Transportation Ip Holdings, Llc | Method and systems for an energy recovery and energy converting unit for an engine |
CN107587947A (en) * | 2016-07-06 | 2018-01-16 | 现代自动车株式会社 | Control the method and system of vehicle Charge device |
Also Published As
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DE102015102647B4 (en) | 2022-05-05 |
CN104879207A (en) | 2015-09-02 |
DE102015102647A1 (en) | 2015-08-27 |
CN104879207B (en) | 2018-11-06 |
US9121338B1 (en) | 2015-09-01 |
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