US20120222419A1 - Turbocharger having balance valve, wastegate, and common actuator - Google Patents
Turbocharger having balance valve, wastegate, and common actuator Download PDFInfo
- Publication number
- US20120222419A1 US20120222419A1 US13/472,175 US201213472175A US2012222419A1 US 20120222419 A1 US20120222419 A1 US 20120222419A1 US 201213472175 A US201213472175 A US 201213472175A US 2012222419 A1 US2012222419 A1 US 2012222419A1
- Authority
- US
- United States
- Prior art keywords
- valve
- volute
- exhaust
- turbocharger
- turbine
- 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.)
- Abandoned
Links
Images
Classifications
-
- 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
- F02M26/45—Sensors specially adapted for EGR systems
- F02M26/46—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition
- F02M26/47—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition the characteristics being temperatures, pressures or flow rates
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
-
- 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
- F02B37/183—Arrangements of bypass valves or actuators therefor
-
- 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
-
- 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 is directed to a turbocharger and, more particularly, to a turbocharger having a balance valve, a wastegate, and an actuator common to both the balance valve and the wastegate valve.
- Combustion engines such as diesel engines, gasoline engines, and gaseous fuel-powered engines are supplied with a mixture of air and fuel for combustion within the engine that generates a mechanical power output.
- the engine is often equipped with a divided exhaust manifold in fluid communication with a turbocharged air induction system.
- the divided exhaust manifold increases engine power by helping to preserve exhaust pulse energy generated by the engine's combustion chambers. Preserving the exhaust pulse energy improves turbocharger operation, which results in a more efficient use of fuel.
- the turbocharged air induction system increases engine power by forcing more air into the combustion chambers than would otherwise be possible. This increased amount of air allows for enhanced fueling that further increases the power output generated by the engine.
- combustion engines exhaust a complex mixture of air pollutants as byproducts of the combustion process. And, due to increased attention on the environment, exhaust emission standards have become more stringent.
- the amount of pollutants emitted to the atmosphere from an engine can be regulated depending on the type of engine, size of engine, and/or class of engine.
- EGR exhaust gas recirculating
- EGR systems require a certain level of backpressure in the exhaust system to push a desired amount of exhaust back to the intake of the engine. And, the backpressure needed for adequate operation of the EGR system varies with engine load. Although effective, utilizing exhaust backpressure to drive EGR can adversely affect engine operation, thereby reducing fuel economy. Thus, a system is required to reduce exhaust back pressure while still providing the necessary EGR flow.
- U.S. Pat. No. 6,321,537 to Coleman et al. (“the '537 patent”) discloses a combustion engine utilizing an EGR system and a divided exhaust manifold together with a turbocharged air induction system.
- the '537 patent describes an internal combustion engine having a plurality of combustion cylinders and an intake manifold in common fluid communication with the combustion cylinders.
- a first exhaust manifold and a second exhaust manifold are separately coupled with the combustion cylinders.
- a first variable geometry turbine is associated with the first exhaust manifold, and a second variable geometry turbine is associated with the second exhaust manifold.
- the EGR system includes a 3-way valve assembly disposed in fluid communication between the first exhaust manifold, the second exhaust manifold, and the intake manifold.
- the valve assembly includes an inlet fluidly coupled with an inlet of the first variable geometry turbine, a first outlet fluidly coupled with an inlet of the second variable geometry turbine, and a second outlet fluidly coupled with the intake manifold.
- exhaust flows in parallel from the first exhaust manifold to the first variable geometry turbine and from the first exhaust manifold to the valve assembly.
- Spent exhaust from the first variable geometry turbine is mixed with exhaust from the second exhaust manifold and fed to the second variable geometry turbine.
- Spent exhaust from the second variable geometry turbine is discharged to the ambient environment.
- the valve assembly is selectively actuated to control a flow of exhaust from the two outlets. Exhaust flowing from the first outlet mixes with exhaust from the second exhaust manifold and flows into the second variable geometry turbine. Exhaust from the second outlet is cooled and then mixed with combustion air. The mixture of combustion air and exhaust is then transported to the inlet manifold.
- Controlling the amount of exhaust gas which is transported to the intake manifold provides effective exhaust gas recirculation within the combustion engine. Moreover, controlling the flow of exhaust to the second variable geometry turbine utilizes energy from the exhaust which is not transported to the intake manifold to drive the second variable geometry turbine.
- the system in the '537 patent may adequately control exhaust gas recirculation in a turbocharged engine, it may be less than optimal. That is, in some situations, the backpressure within the first exhaust manifold may be excessive. And, without any way to relieve this backpressure, damage to the first variable geometry turbocharger may be possible.
- the disclosed turbocharger is directed to overcoming one or more of the problems set forth above and/or other problems of the prior art.
- the disclosure is directed toward a turbocharger.
- the turbocharger may include a turbine housing with a first volute, a second volute, and a common outlet.
- the turbocharger may also include a turbine wheel disposed between the common outlet and the first and second volutes.
- the turbocharger may further include a first valve configured to selectively fluidly communicate the first volute with the second volute upstream of the turbine wheel, a second valve configured to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel, and a common actuator configured to move the first and second valves.
- the disclosure is directed toward a method of handling exhaust from an engine having a first plurality of combustion chambers and a second plurality of combustion chambers.
- the method may include receiving exhaust from the first plurality of combustion chambers, and receiving exhaust from the second plurality of combustion chambers.
- the method may also include moving a valve assembly in a first direction by a first amount to mix exhaust received from the first plurality of combustion chambers with exhaust received from the second plurality of combustion chambers, directing exhaust received from the first and second pluralities of combustion chambers through a turbine, and moving the valve assembly in the first direction by a second amount to allow exhaust received from the second plurality of combustion chambers to bypass the turbine.
- the disclosure is directed toward a power system.
- the power system may include an engine having a first plurality of combustion chambers and a second plurality of combustion chambers.
- the power system may also include a first exhaust manifold configured to receive exhaust from only the first plurality of combustion chambers, a second exhaust manifold configured to receive exhaust from only the second plurality of combustion chambers, and a turbocharger.
- the turbocharger may have a first volute in fluid communication with the first exhaust manifold, a second volute having a greater flow capacity than the first volute and being in fluid communication with the second exhaust manifold, a turbine wheel configured to receive exhaust from the first and second volutes, and a common outlet.
- the power system may further include a valve assembly configured to selectively fluidly communicate the first volute with the second volute at a location upstream of the turbine wheel, and to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel and a single actuator configured to move the valve assembly.
- FIG. 1 is a diagrammatic illustration of an exemplary disclosed power system
- FIG. 2 is a pictorial illustration of an exemplary disclosed turbocharger that may be used with the power system of FIG. 1 ;
- FIG. 3 is a pictorial illustration of a portion of the turbocharger shown in FIG. 2 ;
- FIG. 4 is a pictorial illustration of a portion of the turbocharger shown in FIG. 2 ;
- FIG. 5 is a pictorial illustration of another exemplary disclosed power system
- FIG. 6 is a pictorial illustration of an exemplary disclosed turbocharger that may be used with the power system of FIG. 5 ;
- FIG. 7 is a pictorial illustration of a portion of the turbocharger shown in FIG. 6 ;
- FIG. 8 is a pictorial illustration of a portion of the turbocharger shown in FIG. 6 .
- FIG. 1 illustrates a power system 10 having a power source 12 , an air induction system 14 , and an exhaust system 16 .
- power source 12 is depicted and described as a four-stroke diesel engine.
- power source 12 may be any other type of combustion engine such as, for example, a gasoline or a gaseous fuel-powered engine.
- Power source 12 may include an engine block 18 that at least partially defines a plurality of cylinders 20 .
- a piston (not shown) may be slidably disposed within each cylinder 20 to reciprocate between a top-dead-center position and a bottom-dead-center position, and a cylinder head (not shown) may be associated with each cylinder 20 .
- Cylinder 20 , the piston, and the cylinder head may form a combustion chamber 22 .
- power source 12 includes six such combustion chambers 22 .
- power source 12 may include a greater or lesser number of combustion chambers 22 and that combustion chambers 22 may be disposed in an “in-line” configuration, a “V” configuration, or in any other suitable configuration.
- Air induction system 14 may include components configured to introduce charged air into power source 12 .
- air induction system 14 may include an induction valve 24 , one or more compressors 26 , and an air cooler 28 .
- Induction valve 24 may be connected upstream of compressor 26 via a fluid passageway 30 and configured to regulate a flow of atmospheric air to power source 12 .
- Compressor 26 may embody a fixed geometry compressor configured to receive air from induction valve 24 and compress the air to a predetermined pressure level before it enters power source 12 .
- Compressor 26 may be connected to power source 12 via a fluid passageway 32 .
- Air cooler 28 may be disposed within fluid passageway 32 , between power source 12 and compressor 26 and embody, for example, an air-to-air heat exchanger, an air-to-liquid heat exchanger, or a combination of both to facilitate the transfer of thermal energy to or from the compressed air directed into power source 12 .
- Exhaust system 16 may include components configured to direct exhaust from power source 12 to the atmosphere.
- exhaust system 16 may include first and second exhaust manifolds 34 and 36 in fluid communication with combustion chambers 22 , an exhaust gas recirculation (EGR) circuit 38 fluidly communicating first exhaust manifold 34 with air induction system 14 , a turbine 40 associated with first and second exhaust manifolds 34 , 36 , and a control system 44 for regulating exhaust flows from exhaust system 16 to air induction system 14 .
- EGR exhaust gas recirculation
- exhaust system 16 may include components in addition to those listed above such as, for example, particulate removing devices, constituent absorbers or reducers, and attenuation devices, if desired.
- Exhaust produced during the combustion process within combustion chambers 22 may exit power source 12 via either first exhaust manifold 34 or second exhaust manifold 36 .
- First exhaust manifold 34 may fluidly connect a first plurality of combustion chambers 22 of power source 12 (e.g., the first three combustion chambers 22 from the right shown in FIG. 1 ) to turbine 40 .
- Second exhaust manifold 36 may fluidly connect a second plurality of combustion chambers 22 of power source 12 (e.g., the final three combustion chambers from the right shown in FIG. 1 ) to turbine 40 .
- EGR circuit 38 may include components that cooperate to redirect a portion of the exhaust produced by power source 12 from first exhaust manifold 34 to air induction system 14 .
- EGR circuit 38 may include an inlet port 52 , an EGR cooler 54 , a recirculation control valve 56 , and a discharge port 58 .
- Inlet port 52 may be fluidly connected to first exhaust manifold 34 upstream of turbine 40 and fluidly connected to EGR cooler 54 via a fluid passageway 60 .
- Discharge port 58 may receive exhaust from EGR cooler 54 via a fluid passageway 62 , and discharge the exhaust to air induction system 14 at a location downstream of air cooler 28 .
- Recirculation control valve 56 may be disposed within fluid passageway 62 , between EGR cooler 54 and discharge port 58 . It is contemplated that a check valve, for example a reed-type check valve 50 may be situated within fluid passageway 62 upstream or downstream of recirculation control valve 56 at a location where exhaust mixes with inlet air to provide for a unidirectional flow of exhaust through EGR circuit 38 (i.e., to inhibit bidirectional exhaust flows through EGR circuit 38 ), if desired.
- a check valve for example a reed-type check valve 50 may be situated within fluid passageway 62 upstream or downstream of recirculation control valve 56 at a location where exhaust mixes with inlet air to provide for a unidirectional flow of exhaust through EGR circuit 38 (i.e., to inhibit bidirectional exhaust flows through EGR circuit 38 ), if desired.
- Recirculation control valve 56 may be located to control the flow of exhaust recirculated through EGR circuit 38 .
- Recirculation control valve 56 may be any type of valve known in the art such as, for example, a butterfly valve, a diaphragm valve, a gate valve, a ball valve, a poppet valve, or a globe valve.
- recirculation control valve 56 may be solenoid-actuated, hydraulically-actuated, pneumatically-actuated or actuated in any other manner to selectively restrict or completely block the flow of exhaust through fluid passageways 60 and 62 .
- EGR cooler 54 may be configured to cool exhaust flowing through EGR circuit 38 and, subsequently, components within EGR circuit 38 (e.g., recirculation control valve 56 ).
- EGR cooler 54 may include a liquid-to-air heat exchanger, an air-to-air heat exchanger, or any other type of heat exchanger known in the art for cooling an exhaust flow.
- Turbine 40 may be a fixed geometry turbine configured to drive compressor 26 .
- turbine 40 may be directly and mechanically connected to compressor 26 by way of a shaft 64 to form a fixed geometry turbocharger 66 .
- turbine 40 may rotate and drive the connected compressor 26 to pressurize inlet air.
- Turbine 40 may include a divided housing having a first volute 76 with a first inlet 78 fluidly connected with first exhaust manifold 34 , and a second volute 80 with a second inlet 82 fluidly connected with second exhaust manifold 36 (i.e., turbocharger 66 may have dual volutes).
- a wall member 84 may divide first volute 76 from second volute 80 . It should be understood that at least a part of first volute 76 and/or first inlet 78 may have a smaller cross-sectional area and/or area/radius (A/R) ratio than second volute 80 and/or second inlet 82 . The smaller cross-sectional area or A/R ratio may help restrict the flow of exhaust through first exhaust manifold 34 , thereby creating backpressure sufficient to push at least a portion of the exhaust from first exhaust manifold 34 through EGR circuit 38 .
- a valve assembly 86 may be associated with turbine 40 to regulate a pressure of exhaust within EGR circuit 38 .
- Valve assembly 86 may include, among other things, a balance valve 88 , a wastegate valve 90 , and a common actuator 92 .
- Balance valve 88 may be configured to selectively allow exhaust from first volute 76 to pass to second volute 80 .
- Wastegate valve 90 may be configured to selectively allow exhaust from second volute 80 to bypass a turbine wheel 93 of turbine 40 .
- Common actuator 92 may be controlled to move both balance valve 88 and wastegate valve 90 between flow passing and flow blocking positions.
- Valve assembly 86 may be integral with turbine 40 and at least partially enclosed by a valve housing 94 that mounts to a turbine housing 96 of turbine 40 .
- Balance valve 88 may be configured to regulate a pressure of exhaust within first exhaust manifold 34 by selectively allowing exhaust to flow from first volute 76 to second volute 80 . It should be understood that the pressure within first exhaust manifold 34 may affect the amount of exhaust pushed through EGR circuit 38 . That is, when exhaust flows from first volute 76 to second volute 80 by way of balance valve 88 , a pressure within first exhaust manifold 34 may be reduced and, as a result of this reduction, an amount of exhaust forced from first exhaust manifold 34 through EGR circuit 38 may be reduced by a proportional amount.
- exhaust may selectively be allowed to flow from first volute 76 to second volute 80 by way of balance valve 88 , a pressure differential between first and second volutes 76 and 80 may be minimized, thereby minimizing an impact this pressure differential may have on turbocharger efficiency.
- balance valve 88 may be fixedly connected to common actuator 92 .
- balance valve 88 may include a valve member 98 having a pivot axis 100 .
- a pivot member 102 may be fixedly connected at a center thereof to valve member 98 , and at an end thereof to common actuator 92 .
- pivot member 102 and connected valve member 98 may both be caused to rotate together about pivot axis 100 .
- valve housing 94 may at least partially define a fluid chamber 106 divided into two compartments 106 a and 106 b by a wall member 108 .
- Compartment 106 a may fluidly communicate with first volute 76
- compartment 106 b may fluidly communicate with second volute 80 .
- a port 110 within wall member 108 may fluidly connect compartments 106 a and 106 b, and a sealing element 111 of valve member 98 may selectively pivot about pivot axis 100 to open or close port 110 and thereby selectively restrict a flow of exhaust from first volute 76 to second volute 80 by way of port 110 .
- wastegate valve 90 may be connected to balance valve 88 and to common actuator 92 by way of a link member 112 .
- a pivot member 114 may be connected at one end thereof to a valve member 115 of wastegate valve 90 , and include a protrusion 114 a at an opposing end thereof.
- Link member 112 may be fixedly connected to an end of pivot member 102 , opposite the connection of pivot member 102 to common actuator 92 , and include a channel 112 a configured to slidingly receive protrusion 114 a of pivot member 114 .
- link member 112 may also move linearly in a direction substantially opposite the movement of common actuator 92 .
- protrusion 114 a may be caused to slide within channel 112 a of link member 112 until an end of channel 112 a is engaged.
- pivot member 114 and connected valve member 115 may then be rotated about an axis 116 together with pivot member 102 and connected valve member 98 about pivot axis 100 by further movement of common actuator 92 in the same direction.
- balance valve 88 may again move first (i.e., before movement of wastegate valve 90 is initiated) until an opposing end of channel 112 a is engaged by protrusion 114 a.
- fluid chamber 106 may be separated from a common outlet 118 of turbine 40 by a wall member 120 .
- a port 122 within wall member 120 may connect fluid chamber 106 with common outlet 118 , and a sealing element 124 of valve member 115 may selectively pivot about axis 116 to open or close port 122 and thereby restrict a flow of exhaust from second volute 80 to outlet 118 (i.e., sealing element 124 may selectively allow or restrict exhaust within second volute 80 from bypassing turbine wheel 93 of turbine 40 ).
- common actuator 92 may be pneumatically operated to initiate movement of balance valve 88 and wastegate valve 90 .
- common actuator 92 may include a spring-biased piston member (not shown) disposed within a pressure chamber 92 a and fixedly connected to a piston rod 92 b. Pressurized air directed into pressure chamber 92 a may urge the spring-biased piston member from a first position away from pressure chamber 92 a toward a second position. Conversely, allowing the pressurized air to drain from pressure chamber 92 a may return the spring-biased piston member to the first position. As piston rod 92 b translates between the first and second positions, balance valve 88 may first move, followed by movement of wastegate valve 90 .
- common actuator 92 may alternatively be mechanically operated, hydraulically operated, electrically operated, or operated in any other suitable manner. It is also contemplated that piston rod 92 b may be moved to any position between the first and second positions to thereby provide more than two levels of actuation, if desired (i.e., common actuator 92 may be a proportional actuator, wherein a movement amount of piston rod 92 b is directly proportional to a pressure of the air directed into pressure chamber 92 a ).
- control system 44 may include components that function to regulate the flow rate and pressure of exhaust passing though first volute 76 , second volute 80 , and EGR circuit 38 by adjusting the position of recirculation control valve 56 , balance valve 88 , and/or wastegate valve 90 in response to sensory input.
- control system 44 may include a sensor 46 , and a controller 48 in communication with sensor 46 , recirculation control valve 56 , and common actuator 92 . Based on signals received from sensor 46 , controller 48 may adjust a position of recirculation control valve 56 and/or of common actuator 92 to vary the restrictions provided by recirculation control valve 56 , balance valve 88 , and/or wastegate valve 90 .
- sensor 46 may alternatively be located anywhere within EGR circuit 38 and embody, for example, a mass air flow sensor such as a hot wire anemometer or a venturi-type sensor configured to sense pressure and/or a flow rate of exhaust passing through EGR circuit 38 .
- Controller 48 may use signals produced by sensor 46 to determine and/or adjust a backpressure within first exhaust manifold 34 such that a desired amount of exhaust is recirculated back into power source 12 for subsequent combustion. This adjustment of pressure will be further explained in more detail below.
- Controller 48 may embody a single or multiple microprocessors, field programmable gate arrays (FPGAs), digital signal processors (DSPs), etc. that include a means for controlling an operation of power system 10 in response to signals received from sensor 46 .
- Numerous commercially available microprocessors can be configured to perform the functions of controller 48 . It should be appreciated that controller 48 could readily embody a microprocessor separate from that controlling other non-exhaust related power system functions, or that controller 48 could be integral with a general power system microprocessor and be capable of controlling numerous power system functions and modes of operation. If separate from a general power system microprocessor, controller 48 may communicate with the general power system microprocessor via data links or other methods.
- controller 48 Various other known circuits may be associated with controller 48 , including power supply circuitry, signal-conditioning circuitry, actuator driver circuitry (i.e., circuitry powering solenoids, motors, or piezo actuators), communication circuitry, and other appropriate circuitry.
- actuator driver circuitry i.e., circuitry powering solenoids, motors, or piezo actuators
- controller 48 may first receive data indicative of an operational condition of power source 12 or a desired exhaust flow rate and/or pressure. Such data may be received from another controller or computer (not shown). In an alternative embodiment, operational condition data may be received from sensors strategically located throughout power system 10 . Controller 48 may then utilize stored algorithms, equations, subroutines, look-up maps, and/or tables to analyze the operational condition data and determine a corresponding desired exhaust pressure and/or flow rate through EGR circuit 38 .
- Controller 48 may also receive signals from sensor 46 indicative of the flow rate or pressure of exhaust flowing through first exhaust manifold 34 . Upon receiving input signals from sensor 46 , controller 48 may perform a plurality of operations utilizing stored algorithms, equations, subroutines, look-up maps and/or tables to determine whether the flow rate or pressure of exhaust flowing through first exhaust manifold 34 is within a desired range for producing the desired exhaust flow rate through EGR circuit 38 . In an alternate embodiment, it is contemplated that controller 48 may receive signals from various sensors (not shown) located throughout exhaust system 16 and/or power system 10 instead of sensor 46 . Such sensors may sense parameters that may be used to calculate the flow rate or pressure of exhaust flowing through first exhaust manifold 34 , if desired.
- controller 48 may adjust operation of exhaust system 16 . That is, controller 48 may adjust operation of recirculation control valve 56 , of balance valve 88 , and/or of wastegate valve 90 to affect the pressure within first exhaust manifold 34 and the resulting flow rates of exhaust through EGR circuit 38 , first volute 76 , and second volute 80 . To increase the flow rate and pressure of exhaust passing through first volute 76 and EGR circuit 38 , and to simultaneously decrease the flow rates and pressures of exhaust passing through second volute 80 , balance valve 88 may be closed to a greater extent.
- balance valve 88 may be opened.
- Recirculation control valve 56 may be opened to increase an EGR flow rate and decrease exhaust flow through first volute 76 , and closed to decrease an EGR flow rate and increase exhaust flow through first volute 76 .
- controller 48 may primarily adjust operation of balance valve 88 to achieve a desired flow rate and/or pressure of exhaust through EGR circuit 38 . After balance valve 88 has been adjusted to a maximum or minimum position, controller 48 may then adjust operation of recirculation control valve 56 and/or wastegate valve 90 to provide further EGR modulation.
- FIG. 5 illustrates an alternative embodiment of power system 10 .
- the embodiment of FIG. 5 includes power system 10 having power source 12 , air induction system 14 , and exhaust system 16 .
- turbine 40 of exhaust system 16 may include a different valve assembly 86 . That is, valve assembly 86 of FIG. 5 may include a balance valve 126 and a wastegate valve 128 moved by common actuator 92 .
- Balance valve 126 may include two separate valve members, and wastegate valve 128 may have a different configuration than in the previous embodiments.
- the linkage connecting balance valve 126 and wastegate valve 128 to common actuator 92 may be different, as will be described in more detail below.
- Balance valve 126 and wastegate valve 128 may connect to and be moved by common actuator 92 in a manner similar to the embodiments of FIGS. 1-5 . That is, as illustrated in FIG. 6 , balance valve 126 may be fixedly connected to common actuator 92 by way of a pivot member 130 to rotate about a pivot axis 132 . Wastegate valve 128 may include a pivot member 134 having a channel 134 a. And, as common actuator 92 begins to move linearly, only pivot member 130 and connected balance valve 126 may move until a protrusion 130 a of pivot member 130 engages an end of channel 134 a. Once protrusion 130 a engages the end of channel 134 a, pivot member 134 and connected wastegate valve 128 may also be moved by the linear motion of common actuator 92 .
- balance valve 126 may include a first valve member 136 and a second valve member 138 rigidly connected to each other and disposed at least partially within a fluid chamber 140 .
- Fluid chamber 140 may be at least partially defined by turbine housing 96 (i.e., at least partially defined by a wall member 141 of turbine housing 96 ) and fluidly communicate with fluid chamber 106 of valve housing 94 . No walls may separate fluid chambers 140 or 106 into separate compartments in this embodiment.
- First valve member 136 may be associated with first volute 76
- second valve member 138 may be associated with second volute 80 .
- a first port 142 within wall member 141 may communicate fluid chamber 140 with first volute 76
- a second port 144 within wall member 141 may fluidly communicate fluid chamber 140 with second volute 80
- First and second valve members 136 , 138 may include first and second sealing surfaces (not shown), respectively, that are configured to selectively restrict fluid flow through first and second ports 142 , 144 . Both of first and second valve members 136 , 138 may be connected to a rod member 146 to rotate together about pivot axis 132 when an input from common actuator 92 is received.
- wastegate valve 128 may be substantially axially aligned with balance valve 126 and include a sleeve member 148 fixedly connected to pivot member 126 and configured to at least partially receive rod member 146 of balance valve 126 .
- a valve member 150 of wastegate valve 128 may be rigidly connected to rotate with sleeve member 148 and selectively restrict exhaust flow through a port 152 to common outlet 118 of turbine 40 .
- the disclosed exhaust system may be implemented into any power system application where charged air induction and exhaust gas recirculation are utilized.
- the disclosed exhaust system may be simple, have high durability, and offer control precision.
- the fixed geometry nature of turbocharger 66 may decrease the complexity and cost of the disclosed exhaust system, while recirculation control valve 56 , balance valves 88 or 126 , and wastegate valves 90 or 128 may help to maintain precision and controllability:
- the location of recirculation control valve 56 , sensor 46 , and check valve 50 downstream of EGR cooler 54 may result in cooler operating temperatures of those components and extended component lives.
- the use of check valve 50 may enhance turbocharger stability and efficiency.
- precise regulation of exhaust gas recirculation may be possible.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Analytical Chemistry (AREA)
- Supercharger (AREA)
Abstract
A turbocharger for a use with a combustion engine is provided. The turbocharger may have a turbine housing with a first volute, a second volute, and a common outlet. The turbocharger may also have a turbine wheel disposed between the common outlet and the first and second volutes. The turbocharger may further have a first valve configured to selectively fluidly communicate the first volute with the second volute upstream of the turbine wheel, a second valve configured to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel, and a common actuator configured to move the first and second valves.
Description
- The present disclosure is directed to a turbocharger and, more particularly, to a turbocharger having a balance valve, a wastegate, and an actuator common to both the balance valve and the wastegate valve.
- Combustion engines such as diesel engines, gasoline engines, and gaseous fuel-powered engines are supplied with a mixture of air and fuel for combustion within the engine that generates a mechanical power output. In order to maximize the power output generated by this combustion process, the engine is often equipped with a divided exhaust manifold in fluid communication with a turbocharged air induction system.
- The divided exhaust manifold increases engine power by helping to preserve exhaust pulse energy generated by the engine's combustion chambers. Preserving the exhaust pulse energy improves turbocharger operation, which results in a more efficient use of fuel. In addition, the turbocharged air induction system increases engine power by forcing more air into the combustion chambers than would otherwise be possible. This increased amount of air allows for enhanced fueling that further increases the power output generated by the engine.
- In addition to the goal of maximizing engine power output and efficiency, it is desirable to simultaneously minimize exhaust emissions. That is, combustion engines exhaust a complex mixture of air pollutants as byproducts of the combustion process. And, due to increased attention on the environment, exhaust emission standards have become more stringent. The amount of pollutants emitted to the atmosphere from an engine can be regulated depending on the type of engine, size of engine, and/or class of engine.
- One method that has been implemented by engine manufacturers to comply with the regulation of these exhaust emissions includes utilizing an exhaust gas recirculating (EGR) system. EGR systems operate by recirculating a portion of the exhaust produced by the engine back to the intake of the engine to mix with fresh combustion air. The resulting mixture has a lower combustion temperature and, subsequently, produces a reduced amount of regulated pollutants.
- EGR systems require a certain level of backpressure in the exhaust system to push a desired amount of exhaust back to the intake of the engine. And, the backpressure needed for adequate operation of the EGR system varies with engine load. Although effective, utilizing exhaust backpressure to drive EGR can adversely affect engine operation, thereby reducing fuel economy. Thus, a system is required to reduce exhaust back pressure while still providing the necessary EGR flow.
- U.S. Pat. No. 6,321,537 to Coleman et al. (“the '537 patent”) discloses a combustion engine utilizing an EGR system and a divided exhaust manifold together with a turbocharged air induction system. Specifically, the '537 patent describes an internal combustion engine having a plurality of combustion cylinders and an intake manifold in common fluid communication with the combustion cylinders. A first exhaust manifold and a second exhaust manifold are separately coupled with the combustion cylinders. A first variable geometry turbine is associated with the first exhaust manifold, and a second variable geometry turbine is associated with the second exhaust manifold. The EGR system includes a 3-way valve assembly disposed in fluid communication between the first exhaust manifold, the second exhaust manifold, and the intake manifold. The valve assembly includes an inlet fluidly coupled with an inlet of the first variable geometry turbine, a first outlet fluidly coupled with an inlet of the second variable geometry turbine, and a second outlet fluidly coupled with the intake manifold.
- During operation of the combustion engine described in the '537 patent, exhaust flows in parallel from the first exhaust manifold to the first variable geometry turbine and from the first exhaust manifold to the valve assembly. Spent exhaust from the first variable geometry turbine is mixed with exhaust from the second exhaust manifold and fed to the second variable geometry turbine. Spent exhaust from the second variable geometry turbine is discharged to the ambient environment. The valve assembly is selectively actuated to control a flow of exhaust from the two outlets. Exhaust flowing from the first outlet mixes with exhaust from the second exhaust manifold and flows into the second variable geometry turbine. Exhaust from the second outlet is cooled and then mixed with combustion air. The mixture of combustion air and exhaust is then transported to the inlet manifold. Controlling the amount of exhaust gas which is transported to the intake manifold provides effective exhaust gas recirculation within the combustion engine. Moreover, controlling the flow of exhaust to the second variable geometry turbine utilizes energy from the exhaust which is not transported to the intake manifold to drive the second variable geometry turbine.
- Although the system in the '537 patent may adequately control exhaust gas recirculation in a turbocharged engine, it may be less than optimal. That is, in some situations, the backpressure within the first exhaust manifold may be excessive. And, without any way to relieve this backpressure, damage to the first variable geometry turbocharger may be possible.
- The disclosed turbocharger is directed to overcoming one or more of the problems set forth above and/or other problems of the prior art.
- In one aspect, the disclosure is directed toward a turbocharger. The turbocharger may include a turbine housing with a first volute, a second volute, and a common outlet. The turbocharger may also include a turbine wheel disposed between the common outlet and the first and second volutes. The turbocharger may further include a first valve configured to selectively fluidly communicate the first volute with the second volute upstream of the turbine wheel, a second valve configured to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel, and a common actuator configured to move the first and second valves.
- In another aspect, the disclosure is directed toward a method of handling exhaust from an engine having a first plurality of combustion chambers and a second plurality of combustion chambers. The method may include receiving exhaust from the first plurality of combustion chambers, and receiving exhaust from the second plurality of combustion chambers. The method may also include moving a valve assembly in a first direction by a first amount to mix exhaust received from the first plurality of combustion chambers with exhaust received from the second plurality of combustion chambers, directing exhaust received from the first and second pluralities of combustion chambers through a turbine, and moving the valve assembly in the first direction by a second amount to allow exhaust received from the second plurality of combustion chambers to bypass the turbine.
- In yet another aspect, the disclosure is directed toward a power system. The power system may include an engine having a first plurality of combustion chambers and a second plurality of combustion chambers. The power system may also include a first exhaust manifold configured to receive exhaust from only the first plurality of combustion chambers, a second exhaust manifold configured to receive exhaust from only the second plurality of combustion chambers, and a turbocharger. The turbocharger may have a first volute in fluid communication with the first exhaust manifold, a second volute having a greater flow capacity than the first volute and being in fluid communication with the second exhaust manifold, a turbine wheel configured to receive exhaust from the first and second volutes, and a common outlet. The power system may further include a valve assembly configured to selectively fluidly communicate the first volute with the second volute at a location upstream of the turbine wheel, and to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel and a single actuator configured to move the valve assembly.
-
FIG. 1 is a diagrammatic illustration of an exemplary disclosed power system; -
FIG. 2 is a pictorial illustration of an exemplary disclosed turbocharger that may be used with the power system ofFIG. 1 ; -
FIG. 3 is a pictorial illustration of a portion of the turbocharger shown inFIG. 2 ; -
FIG. 4 is a pictorial illustration of a portion of the turbocharger shown inFIG. 2 ; -
FIG. 5 is a pictorial illustration of another exemplary disclosed power system; -
FIG. 6 is a pictorial illustration of an exemplary disclosed turbocharger that may be used with the power system ofFIG. 5 ; -
FIG. 7 is a pictorial illustration of a portion of the turbocharger shown inFIG. 6 ; and -
FIG. 8 is a pictorial illustration of a portion of the turbocharger shown inFIG. 6 . -
FIG. 1 illustrates apower system 10 having apower source 12, anair induction system 14, and anexhaust system 16. For the purposes of this disclosure,power source 12 is depicted and described as a four-stroke diesel engine. One skilled in the art will recognize, however, thatpower source 12 may be any other type of combustion engine such as, for example, a gasoline or a gaseous fuel-powered engine.Power source 12 may include anengine block 18 that at least partially defines a plurality ofcylinders 20. A piston (not shown) may be slidably disposed within eachcylinder 20 to reciprocate between a top-dead-center position and a bottom-dead-center position, and a cylinder head (not shown) may be associated with eachcylinder 20.Cylinder 20, the piston, and the cylinder head may form acombustion chamber 22. In the illustrated embodiment,power source 12 includes sixsuch combustion chambers 22. However, it is contemplated thatpower source 12 may include a greater or lesser number ofcombustion chambers 22 and thatcombustion chambers 22 may be disposed in an “in-line” configuration, a “V” configuration, or in any other suitable configuration. -
Air induction system 14 may include components configured to introduce charged air intopower source 12. For example,air induction system 14 may include aninduction valve 24, one ormore compressors 26, and anair cooler 28.Induction valve 24 may be connected upstream ofcompressor 26 via afluid passageway 30 and configured to regulate a flow of atmospheric air topower source 12.Compressor 26 may embody a fixed geometry compressor configured to receive air frominduction valve 24 and compress the air to a predetermined pressure level before it enterspower source 12.Compressor 26 may be connected topower source 12 via afluid passageway 32.Air cooler 28 may be disposed withinfluid passageway 32, betweenpower source 12 andcompressor 26 and embody, for example, an air-to-air heat exchanger, an air-to-liquid heat exchanger, or a combination of both to facilitate the transfer of thermal energy to or from the compressed air directed intopower source 12. -
Exhaust system 16 may include components configured to direct exhaust frompower source 12 to the atmosphere. Specifically,exhaust system 16 may include first andsecond exhaust manifolds combustion chambers 22, an exhaust gas recirculation (EGR)circuit 38 fluidly communicatingfirst exhaust manifold 34 withair induction system 14, aturbine 40 associated with first andsecond exhaust manifolds control system 44 for regulating exhaust flows fromexhaust system 16 toair induction system 14. It is contemplated thatexhaust system 16 may include components in addition to those listed above such as, for example, particulate removing devices, constituent absorbers or reducers, and attenuation devices, if desired. - Exhaust produced during the combustion process within
combustion chambers 22 may exitpower source 12 via eitherfirst exhaust manifold 34 orsecond exhaust manifold 36.First exhaust manifold 34 may fluidly connect a first plurality ofcombustion chambers 22 of power source 12 (e.g., the first threecombustion chambers 22 from the right shown inFIG. 1 ) toturbine 40.Second exhaust manifold 36 may fluidly connect a second plurality ofcombustion chambers 22 of power source 12 (e.g., the final three combustion chambers from the right shown inFIG. 1 ) toturbine 40. -
EGR circuit 38 may include components that cooperate to redirect a portion of the exhaust produced bypower source 12 fromfirst exhaust manifold 34 toair induction system 14. Specifically,EGR circuit 38 may include aninlet port 52, anEGR cooler 54, arecirculation control valve 56, and adischarge port 58.Inlet port 52 may be fluidly connected tofirst exhaust manifold 34 upstream ofturbine 40 and fluidly connected toEGR cooler 54 via afluid passageway 60.Discharge port 58 may receive exhaust fromEGR cooler 54 via afluid passageway 62, and discharge the exhaust toair induction system 14 at a location downstream ofair cooler 28.Recirculation control valve 56 may be disposed withinfluid passageway 62, betweenEGR cooler 54 anddischarge port 58. It is contemplated that a check valve, for example a reed-type check valve 50 may be situated withinfluid passageway 62 upstream or downstream ofrecirculation control valve 56 at a location where exhaust mixes with inlet air to provide for a unidirectional flow of exhaust through EGR circuit 38 (i.e., to inhibit bidirectional exhaust flows through EGR circuit 38), if desired. -
Recirculation control valve 56 may be located to control the flow of exhaust recirculated throughEGR circuit 38.Recirculation control valve 56 may be any type of valve known in the art such as, for example, a butterfly valve, a diaphragm valve, a gate valve, a ball valve, a poppet valve, or a globe valve. In addition,recirculation control valve 56 may be solenoid-actuated, hydraulically-actuated, pneumatically-actuated or actuated in any other manner to selectively restrict or completely block the flow of exhaust throughfluid passageways -
EGR cooler 54 may be configured to cool exhaust flowing throughEGR circuit 38 and, subsequently, components within EGR circuit 38 (e.g., recirculation control valve 56).EGR cooler 54 may include a liquid-to-air heat exchanger, an air-to-air heat exchanger, or any other type of heat exchanger known in the art for cooling an exhaust flow. -
Turbine 40 may be a fixed geometry turbine configured to drivecompressor 26. For example,turbine 40 may be directly and mechanically connected tocompressor 26 by way of ashaft 64 to form a fixedgeometry turbocharger 66. As the hot exhaust gases exitingpower source 12 move throughturbine 40 and expand against blades (not shown) therein,turbine 40 may rotate and drive the connectedcompressor 26 to pressurize inlet air. -
Turbine 40 may include a divided housing having afirst volute 76 with afirst inlet 78 fluidly connected withfirst exhaust manifold 34, and asecond volute 80 with asecond inlet 82 fluidly connected with second exhaust manifold 36 (i.e.,turbocharger 66 may have dual volutes). Awall member 84 may dividefirst volute 76 fromsecond volute 80. It should be understood that at least a part offirst volute 76 and/orfirst inlet 78 may have a smaller cross-sectional area and/or area/radius (A/R) ratio thansecond volute 80 and/orsecond inlet 82. The smaller cross-sectional area or A/R ratio may help restrict the flow of exhaust throughfirst exhaust manifold 34, thereby creating backpressure sufficient to push at least a portion of the exhaust fromfirst exhaust manifold 34 throughEGR circuit 38. - A
valve assembly 86 may be associated withturbine 40 to regulate a pressure of exhaust withinEGR circuit 38.Valve assembly 86 may include, among other things, abalance valve 88, awastegate valve 90, and acommon actuator 92.Balance valve 88 may be configured to selectively allow exhaust fromfirst volute 76 to pass tosecond volute 80.Wastegate valve 90 may be configured to selectively allow exhaust fromsecond volute 80 to bypass aturbine wheel 93 ofturbine 40.Common actuator 92 may be controlled to move bothbalance valve 88 andwastegate valve 90 between flow passing and flow blocking positions.Valve assembly 86 may be integral withturbine 40 and at least partially enclosed by avalve housing 94 that mounts to aturbine housing 96 ofturbine 40. -
Balance valve 88 may be configured to regulate a pressure of exhaust withinfirst exhaust manifold 34 by selectively allowing exhaust to flow fromfirst volute 76 tosecond volute 80. It should be understood that the pressure withinfirst exhaust manifold 34 may affect the amount of exhaust pushed throughEGR circuit 38. That is, when exhaust flows fromfirst volute 76 tosecond volute 80 by way ofbalance valve 88, a pressure withinfirst exhaust manifold 34 may be reduced and, as a result of this reduction, an amount of exhaust forced fromfirst exhaust manifold 34 throughEGR circuit 38 may be reduced by a proportional amount. It should also be noted that, because exhaust may selectively be allowed to flow fromfirst volute 76 tosecond volute 80 by way ofbalance valve 88, a pressure differential between first andsecond volutes - As shown in
FIG. 2 ,balance valve 88 may be fixedly connected tocommon actuator 92. Specifically,balance valve 88 may include avalve member 98 having apivot axis 100. Apivot member 102 may be fixedly connected at a center thereof tovalve member 98, and at an end thereof tocommon actuator 92. In this configuration, ascommon actuator 92 moves linearly in the direction of anarrow 104,pivot member 102 andconnected valve member 98 may both be caused to rotate together aboutpivot axis 100. - As illustrated in
FIGS. 3 and 4 ,valve housing 94 may at least partially define afluid chamber 106 divided into twocompartments wall member 108.Compartment 106 a may fluidly communicate withfirst volute 76, whilecompartment 106 b may fluidly communicate withsecond volute 80. Aport 110 withinwall member 108 may fluidly connectcompartments sealing element 111 ofvalve member 98 may selectively pivot aboutpivot axis 100 to open orclose port 110 and thereby selectively restrict a flow of exhaust fromfirst volute 76 tosecond volute 80 by way ofport 110. - Referring back to
FIG. 2 ,wastegate valve 90 may be connected to balancevalve 88 and tocommon actuator 92 by way of alink member 112. In particular, apivot member 114 may be connected at one end thereof to avalve member 115 ofwastegate valve 90, and include aprotrusion 114 a at an opposing end thereof.Link member 112 may be fixedly connected to an end ofpivot member 102, opposite the connection ofpivot member 102 tocommon actuator 92, and include achannel 112 a configured to slidingly receiveprotrusion 114 a ofpivot member 114. In this configuration, asbalance valve 88 andpivot member 102 are rotated aboutpivot axis 100 by linear movement ofcommon actuator 92,link member 112 may also move linearly in a direction substantially opposite the movement ofcommon actuator 92. And, aslink member 112 moves linearly,protrusion 114 a may be caused to slide withinchannel 112 a oflink member 112 until an end ofchannel 112 a is engaged. Once the end ofchannel 112 a is engaged byprotrusion 114 a,pivot member 114 andconnected valve member 115 may then be rotated about anaxis 116 together withpivot member 102 andconnected valve member 98 aboutpivot axis 100 by further movement ofcommon actuator 92 in the same direction. Whencommon actuator 92 moves in a reverse direction,balance valve 88 may again move first (i.e., before movement ofwastegate valve 90 is initiated) until an opposing end ofchannel 112 a is engaged byprotrusion 114 a. - Referring again to
FIGS. 3 and 4 ,fluid chamber 106 may be separated from acommon outlet 118 ofturbine 40 by awall member 120. Aport 122 withinwall member 120 may connectfluid chamber 106 withcommon outlet 118, and asealing element 124 ofvalve member 115 may selectively pivot aboutaxis 116 to open orclose port 122 and thereby restrict a flow of exhaust fromsecond volute 80 to outlet 118 (i.e., sealingelement 124 may selectively allow or restrict exhaust withinsecond volute 80 from bypassingturbine wheel 93 of turbine 40). - Referring again to
FIG. 2 ,common actuator 92 may be pneumatically operated to initiate movement ofbalance valve 88 andwastegate valve 90. Specifically,common actuator 92 may include a spring-biased piston member (not shown) disposed within apressure chamber 92 a and fixedly connected to apiston rod 92 b. Pressurized air directed intopressure chamber 92 a may urge the spring-biased piston member from a first position away frompressure chamber 92 a toward a second position. Conversely, allowing the pressurized air to drain frompressure chamber 92 a may return the spring-biased piston member to the first position. Aspiston rod 92 b translates between the first and second positions,balance valve 88 may first move, followed by movement ofwastegate valve 90. It is contemplated thatcommon actuator 92 may alternatively be mechanically operated, hydraulically operated, electrically operated, or operated in any other suitable manner. It is also contemplated thatpiston rod 92 b may be moved to any position between the first and second positions to thereby provide more than two levels of actuation, if desired (i.e.,common actuator 92 may be a proportional actuator, wherein a movement amount ofpiston rod 92 b is directly proportional to a pressure of the air directed intopressure chamber 92 a). - Referring back to
FIG. 1 ,control system 44 may include components that function to regulate the flow rate and pressure of exhaust passing thoughfirst volute 76,second volute 80, andEGR circuit 38 by adjusting the position ofrecirculation control valve 56,balance valve 88, and/orwastegate valve 90 in response to sensory input. Specifically,control system 44 may include asensor 46, and acontroller 48 in communication withsensor 46,recirculation control valve 56, andcommon actuator 92. Based on signals received fromsensor 46,controller 48 may adjust a position ofrecirculation control valve 56 and/or ofcommon actuator 92 to vary the restrictions provided byrecirculation control valve 56,balance valve 88, and/orwastegate valve 90. - Although shown as located downstream of
EGR cooler 54 and upstream ofrecirculation control valve 56,sensor 46 may alternatively be located anywhere withinEGR circuit 38 and embody, for example, a mass air flow sensor such as a hot wire anemometer or a venturi-type sensor configured to sense pressure and/or a flow rate of exhaust passing throughEGR circuit 38.Controller 48 may use signals produced bysensor 46 to determine and/or adjust a backpressure withinfirst exhaust manifold 34 such that a desired amount of exhaust is recirculated back intopower source 12 for subsequent combustion. This adjustment of pressure will be further explained in more detail below. -
Controller 48 may embody a single or multiple microprocessors, field programmable gate arrays (FPGAs), digital signal processors (DSPs), etc. that include a means for controlling an operation ofpower system 10 in response to signals received fromsensor 46. Numerous commercially available microprocessors can be configured to perform the functions ofcontroller 48. It should be appreciated thatcontroller 48 could readily embody a microprocessor separate from that controlling other non-exhaust related power system functions, or thatcontroller 48 could be integral with a general power system microprocessor and be capable of controlling numerous power system functions and modes of operation. If separate from a general power system microprocessor,controller 48 may communicate with the general power system microprocessor via data links or other methods. Various other known circuits may be associated withcontroller 48, including power supply circuitry, signal-conditioning circuitry, actuator driver circuitry (i.e., circuitry powering solenoids, motors, or piezo actuators), communication circuitry, and other appropriate circuitry. - Before regulating the flow of exhaust through
EGR circuit 38,controller 48 may first receive data indicative of an operational condition ofpower source 12 or a desired exhaust flow rate and/or pressure. Such data may be received from another controller or computer (not shown). In an alternative embodiment, operational condition data may be received from sensors strategically located throughoutpower system 10.Controller 48 may then utilize stored algorithms, equations, subroutines, look-up maps, and/or tables to analyze the operational condition data and determine a corresponding desired exhaust pressure and/or flow rate throughEGR circuit 38. -
Controller 48 may also receive signals fromsensor 46 indicative of the flow rate or pressure of exhaust flowing throughfirst exhaust manifold 34. Upon receiving input signals fromsensor 46,controller 48 may perform a plurality of operations utilizing stored algorithms, equations, subroutines, look-up maps and/or tables to determine whether the flow rate or pressure of exhaust flowing throughfirst exhaust manifold 34 is within a desired range for producing the desired exhaust flow rate throughEGR circuit 38. In an alternate embodiment, it is contemplated thatcontroller 48 may receive signals from various sensors (not shown) located throughoutexhaust system 16 and/orpower system 10 instead ofsensor 46. Such sensors may sense parameters that may be used to calculate the flow rate or pressure of exhaust flowing throughfirst exhaust manifold 34, if desired. - Based on the comparison of the actual EGR flow rate and/or pressure with the desired range of flow rates and/or pressures,
controller 48 may adjust operation ofexhaust system 16. That is,controller 48 may adjust operation ofrecirculation control valve 56, ofbalance valve 88, and/or ofwastegate valve 90 to affect the pressure withinfirst exhaust manifold 34 and the resulting flow rates of exhaust throughEGR circuit 38,first volute 76, andsecond volute 80. To increase the flow rate and pressure of exhaust passing throughfirst volute 76 andEGR circuit 38, and to simultaneously decrease the flow rates and pressures of exhaust passing throughsecond volute 80,balance valve 88 may be closed to a greater extent. To decrease the flow rate and pressure of exhaust passing throughfirst volute 76 andEGR circuit 38, and to simultaneously increase the flow rates and pressures of exhaust passing throughsecond volute 80,balance valve 88 may be opened.Recirculation control valve 56 may be opened to increase an EGR flow rate and decrease exhaust flow throughfirst volute 76, and closed to decrease an EGR flow rate and increase exhaust flow throughfirst volute 76. In one embodiment,controller 48 may primarily adjust operation ofbalance valve 88 to achieve a desired flow rate and/or pressure of exhaust throughEGR circuit 38. Afterbalance valve 88 has been adjusted to a maximum or minimum position,controller 48 may then adjust operation ofrecirculation control valve 56 and/orwastegate valve 90 to provide further EGR modulation. -
FIG. 5 illustrates an alternative embodiment ofpower system 10. Similar to the embodiment ofFIG. 1 , the embodiment ofFIG. 5 includespower system 10 havingpower source 12,air induction system 14, andexhaust system 16. However, in contrast to the embodiment ofFIG. 1 ,turbine 40 ofexhaust system 16 may include adifferent valve assembly 86. That is,valve assembly 86 ofFIG. 5 may include abalance valve 126 and awastegate valve 128 moved bycommon actuator 92.Balance valve 126 may include two separate valve members, andwastegate valve 128 may have a different configuration than in the previous embodiments. In addition, the linkage connectingbalance valve 126 andwastegate valve 128 tocommon actuator 92 may be different, as will be described in more detail below. -
Balance valve 126 andwastegate valve 128 may connect to and be moved bycommon actuator 92 in a manner similar to the embodiments ofFIGS. 1-5 . That is, as illustrated inFIG. 6 ,balance valve 126 may be fixedly connected tocommon actuator 92 by way of apivot member 130 to rotate about apivot axis 132.Wastegate valve 128 may include apivot member 134 having achannel 134 a. And, ascommon actuator 92 begins to move linearly,only pivot member 130 andconnected balance valve 126 may move until aprotrusion 130 a ofpivot member 130 engages an end ofchannel 134 a. Onceprotrusion 130 a engages the end ofchannel 134 a,pivot member 134 andconnected wastegate valve 128 may also be moved by the linear motion ofcommon actuator 92. - As shown in
FIGS. 7 and 8 ,balance valve 126 may include afirst valve member 136 and asecond valve member 138 rigidly connected to each other and disposed at least partially within afluid chamber 140.Fluid chamber 140 may be at least partially defined by turbine housing 96 (i.e., at least partially defined by awall member 141 of turbine housing 96) and fluidly communicate withfluid chamber 106 ofvalve housing 94. No walls may separatefluid chambers First valve member 136 may be associated withfirst volute 76, whilesecond valve member 138 may be associated withsecond volute 80. Afirst port 142 withinwall member 141 may communicatefluid chamber 140 withfirst volute 76, while asecond port 144 withinwall member 141 may fluidly communicatefluid chamber 140 withsecond volute 80. First andsecond valve members second ports second valve members rod member 146 to rotate together aboutpivot axis 132 when an input fromcommon actuator 92 is received. - In the embodiment of
FIGS. 5-8 ,wastegate valve 128 may be substantially axially aligned withbalance valve 126 and include asleeve member 148 fixedly connected to pivotmember 126 and configured to at least partially receiverod member 146 ofbalance valve 126. Avalve member 150 ofwastegate valve 128 may be rigidly connected to rotate withsleeve member 148 and selectively restrict exhaust flow through aport 152 tocommon outlet 118 ofturbine 40. - The disclosed exhaust system may be implemented into any power system application where charged air induction and exhaust gas recirculation are utilized. The disclosed exhaust system may be simple, have high durability, and offer control precision. Specifically, the fixed geometry nature of
turbocharger 66 may decrease the complexity and cost of the disclosed exhaust system, whilerecirculation control valve 56,balance valves wastegate valves recirculation control valve 56,sensor 46, andcheck valve 50 downstream ofEGR cooler 54 may result in cooler operating temperatures of those components and extended component lives. Further, the use ofcheck valve 50 may enhance turbocharger stability and efficiency. Finally, by utilizing direct flow sensing and feedback control, precise regulation of exhaust gas recirculation may be possible. - It will be apparent to those skilled in the art that various modifications and variations can be made to the disclosed turbocharger. Other embodiments will be apparent to those skilled in the art from consideration of the specification and practice of the disclosed turbocharger. It is intended that the specification and examples be considered as exemplary only, with a true scope being indicated by the following claims and their equivalents.
Claims (24)
1. A turbocharger, comprising:
a turbine housing having a first volute, a second volute, and a common outlet;
a turbine wheel disposed between the common outlet and the first and second volutes;
a first valve configured to selectively fluidly communicate the first volute with the second volute upstream of the turbine wheel;
a second valve configured to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel;
a common actuator configured to move the first and second valves; and
a first wall fluidly separating the first volute from the second volute, the first wall having a first port, the first valve being configured to selectively block the first port.
2. The turbocharger of claim 1 , wherein the first and second valves are configured to rotate, and the common actuator is configured to move linearly.
3. The turbocharger of claim 2 , wherein the common actuator is configured to move in a first direction by a first amount to rotate only the first valve, and the common actuator is configured to move in the first direction by a second amount to rotate both the first valve and the second valve.
4. The turbocharger of claim 1 , wherein the common actuator is pneumatically operated.
5. The turbocharger of claim 1 , further including a valve housing connected to the turbine housing to at least partially enclose the first and second valves, the valve housing including the first wall.
6. (canceled)
7. The turbocharger of claim 1 , wherein the common actuator is fixedly connected to only the first valve.
8. The turbocharger of claim 7 , further including:
a first pivot member fixedly connecting the common actuator to the first valve;
a second pivot member fixedly connected to only the second valve; and
a link member fixedly connected to the first pivot member and including a channel configured to slidingly receive the second pivot member.
9. (canceled)
10. The turbocharger of claim 1 , wherein the common actuator is configured to move to permit the first valve to fluidly communicate the first volute with the second volute before the second valve fluidly communicates the second volute with the common outlet.
11. The turbocharger of claim 1 , wherein the first valve includes a first pivot axis, and the second valve includes a second pivot axis offset from the first pivot axis.
12. (canceled)
13. (canceled)
14. The turbocharger of claim 1 , further including:
a second wall fluidly separating the second volute from the common outlet, the second wall having a second port,
wherein:
the second valve is configured to selectively block the second port.
15.-17. (canceled)
18. A method of handling exhaust from an engine having a first plurality of combustion chambers and a second plurality of combustion chambers, the method comprising:
receiving exhaust from the first plurality of combustion chambers;
receiving exhaust from the second plurality of combustion chambers;
directing exhaust received from the first and second pluralities of combustion chambers through a turbine, the turbine including a housing having a first volute and a second volute;
moving a common actuator in a first direction by a first amount to actuate a first valve of a valve assembly to open a first port, thereby mixing exhaust received from the first plurality of combustion chambers with exhaust received from the second plurality of combustion chambers, the first port being provided in a first wall fluidly separating the first volute from the second volute; and
moving the common actuator in the first direction by a second amount to actuate a second valve of the valve assembly to open a second port, thereby allowing exhaust received from the second plurality of combustion chambers to bypass the turbine, the second port being provided in a second wall fluidly separating the second volute from a common outlet of the turbine.
19. The method of claim 18 , further including converting linear motion from a common actuator to rotation of the valve assembly.
20. A power system, comprising:
an engine having a first plurality of combustion chambers and a second plurality of combustion chambers;
a first exhaust manifold configured to receive exhaust from only the first plurality of combustion chambers;
a second exhaust manifold configured to receive exhaust from only the second plurality of combustion chambers;
a turbocharger having:
a turbine housing, the turbine housing including a first volute in fluid communication with the first exhaust manifold, a second volute having a greater flow capacity than the first volute and being in fluid communication with the second exhaust manifold, and a common outlet, and
a turbine wheel configured to receive exhaust from the first and second volutes;
a valve assembly including:
a first valve configured to selectively fluidly communicate the first volute with the second volute at a location upstream of the turbine wheel, and
a second valve configured to selectively fluidly communicate the second volute with the common outlet to bypass the turbine wheel;
a single actuator configured to move the valve assembly; and
a valve housing connected to the turbine housing and at least partially enclosing the first and second valves, the valve housing including:
a first wall member separating a first compartment fluidly communicating with the first volute from a second compartment fluidly communicating with the second volute, and
a second wall member separating the second compartment from the common outlet, the first valve being provided in the first compartment between the first and second walls.
21. The power system of claim 20 , wherein the first valve includes a first pivot axis, and the second valve includes a second pivot axis offset from the first pivot axis.
22. The power system of claim 20 , wherein the first and second wall members are substantially parallel.
23. The power system of claim 20 , wherein the first valve is disposed between the first and second wall members.
24. The method of claim 18 , wherein, prior to moving the common actuator in the first direction, the first valve closes the first port and the second valve closes the second port.
25. The method of claim 18 , wherein the second amount of movement of the common actuator is greater than the first amount of movement of the common actuator.
26. The turbocharger of claim 14 , further including a valve housing connected to the turbine housing to at least partially enclose the first and second valves, the valve housing including the first wall and the second wall.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/472,175 US20120222419A1 (en) | 2008-07-31 | 2012-05-15 | Turbocharger having balance valve, wastegate, and common actuator |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/222,009 US8196403B2 (en) | 2008-07-31 | 2008-07-31 | Turbocharger having balance valve, wastegate, and common actuator |
US13/472,175 US20120222419A1 (en) | 2008-07-31 | 2012-05-15 | Turbocharger having balance valve, wastegate, and common actuator |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/222,009 Division US8196403B2 (en) | 2008-07-31 | 2008-07-31 | Turbocharger having balance valve, wastegate, and common actuator |
Publications (1)
Publication Number | Publication Date |
---|---|
US20120222419A1 true US20120222419A1 (en) | 2012-09-06 |
Family
ID=41606892
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/222,009 Expired - Fee Related US8196403B2 (en) | 2008-07-31 | 2008-07-31 | Turbocharger having balance valve, wastegate, and common actuator |
US13/472,175 Abandoned US20120222419A1 (en) | 2008-07-31 | 2012-05-15 | Turbocharger having balance valve, wastegate, and common actuator |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/222,009 Expired - Fee Related US8196403B2 (en) | 2008-07-31 | 2008-07-31 | Turbocharger having balance valve, wastegate, and common actuator |
Country Status (1)
Country | Link |
---|---|
US (2) | US8196403B2 (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110067680A1 (en) * | 2009-09-22 | 2011-03-24 | Gm Global Technology Operations, Inc. | Turbocharger and Air Induction System Incorporating the Same and Method of Making and Using the Same |
US20110088393A1 (en) * | 2009-10-16 | 2011-04-21 | Gm Global Technology Operations, Inc. | Turbocharger and Air Induction System Incorporating the Same and Method of Using the Same |
US20120255297A1 (en) * | 2009-10-20 | 2012-10-11 | Continental Automotive Gmbh | Turbine for an exhaust turbocharger, exhaust turbocharger, motor vehicle and method for operating an exhaust turbocharger |
US20130061831A1 (en) * | 2011-09-13 | 2013-03-14 | Caterpillar Inc. | Egr flow measurement |
US20140138562A1 (en) * | 2012-11-16 | 2014-05-22 | Ford Global Technologies, Llc | Vacuum-actuated wastegate |
US9297298B2 (en) | 2014-03-17 | 2016-03-29 | Ford Global Technologies, Llc | Dual wastegate actuation |
DE102015122351A1 (en) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Exhaust gas guide section for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
DE102015122355A1 (en) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Exhaust gas guide section for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
US20180142610A1 (en) * | 2015-04-21 | 2018-05-24 | IFP Energies Nouvelles | Improved device for controlling the amount of air fed into the intake of a supercharged internal combustion engine and method using such a device |
US10301952B2 (en) | 2014-05-19 | 2019-05-28 | Borgwarner Inc. | Dual volute turbocharger to optimize pulse energy separation for fuel economy and EGR utilization via asymmetric dual volutes |
US10655534B2 (en) | 2018-02-06 | 2020-05-19 | Garrett Transportation I Inc. | Rotary axial valve |
Families Citing this family (52)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8397745B2 (en) | 2007-02-12 | 2013-03-19 | Colt Irrigation, LLC | Fluid activated flow control apparatus |
US9341281B2 (en) | 2007-02-12 | 2016-05-17 | Colt Irrigation Llc | Fluid activated flow control apparatus |
JP4894877B2 (en) * | 2009-03-26 | 2012-03-14 | マツダ株式会社 | Turbocharged engine |
US8549854B2 (en) | 2010-05-18 | 2013-10-08 | Achates Power, Inc. | EGR constructions for opposed-piston engines |
DE102010031500A1 (en) * | 2010-07-19 | 2012-01-19 | Bayerische Motoren Werke Aktiengesellschaft | Device for actuating a flap |
EP2630353B1 (en) * | 2010-10-18 | 2015-11-25 | BorgWarner Inc. | Turbocharger egr module |
US9217396B2 (en) * | 2010-12-22 | 2015-12-22 | GM Global Technology Operations LLC | Boosting devices with integral features for recirculating exhaust gas |
DE102010064226A1 (en) * | 2010-12-28 | 2012-06-28 | Continental Automotive Gmbh | Exhaust gas turbocharger with a turbine housing with integrated wastegate actuator |
DE102011011451B4 (en) | 2011-02-17 | 2022-05-05 | Ihi Charging Systems International Gmbh | Actuating device for an exhaust gas turbocharger |
US8539768B2 (en) * | 2011-05-10 | 2013-09-24 | GM Global Technology Operations LLC | Exhaust bypass system for turbocharged engine with dedicated exhaust gas recirculation |
US20120285427A1 (en) * | 2011-05-10 | 2012-11-15 | GM Global Technology Operations LLC | Exhaust manifold assembly with integrated exhaust gas recirculation bypass |
US20130174548A1 (en) | 2011-05-16 | 2013-07-11 | Achates Power, Inc. | EGR for a Two-Stroke Cycle Engine without a Supercharger |
GB201202339D0 (en) * | 2012-02-10 | 2012-03-28 | Caterpillar Motoren Gmbh & Co | Exhaust gas cooler |
US9416724B2 (en) * | 2012-08-08 | 2016-08-16 | Ford Global Technologies, Llc | Multi-staged wastegate |
US9874139B2 (en) * | 2012-12-17 | 2018-01-23 | Honeywell International Inc. | Assembly with wastegate opening, wastegate seat and wall |
US9359939B2 (en) * | 2013-02-20 | 2016-06-07 | Ford Global Technologies, Llc | Supercharged internal combustion engine with two-channel turbine and method |
EP2770169B1 (en) * | 2013-02-20 | 2019-08-14 | Ford Global Technologies, LLC | Charged combustion engine with a double-flow turbine and method for operating such a combustion engine |
DE102013003031A1 (en) * | 2013-02-22 | 2014-08-28 | Daimler Ag | Exhaust tract for an internal combustion engine |
US10094339B2 (en) * | 2013-08-26 | 2018-10-09 | Westport Power Inc. | Direct exhaust gas recirculation system |
CN103711529B (en) * | 2013-12-23 | 2016-01-27 | 中国北车集团大连机车研究所有限公司 | Pressurized machine bleed regulator |
US9599286B2 (en) | 2014-01-23 | 2017-03-21 | Colt Irrigation, LLC | Fluid activated flow control apparatus |
US10088849B2 (en) | 2014-01-23 | 2018-10-02 | Colt Irrigation, LLC | Fluid activated flow control apparatus |
US10571937B1 (en) | 2014-01-23 | 2020-02-25 | Colt Irrigation, LLC | Valve control apparatus |
DE102014106517A1 (en) | 2014-05-09 | 2015-11-12 | Pierburg Gmbh | Exhaust gas turbocharger with a wastegate valve |
DE102014106515A1 (en) | 2014-05-09 | 2015-11-12 | Pierburg Gmbh | Exhaust gas turbocharger with a wastegate valve |
DE102014106513A1 (en) * | 2014-05-09 | 2015-11-12 | Pierburg Gmbh | Exhaust gas turbocharger with a wastegate valve |
GB2529133B (en) * | 2014-05-30 | 2020-08-05 | Cummins Inc | Engine systems and methods for operating an engine |
CN104675452A (en) * | 2015-02-25 | 2015-06-03 | 康跃科技股份有限公司 | Variable-section exhaust gas-bypassing turbine meeting EGR (Exhaust Gas Recirculation) requirement |
DE112015005553T5 (en) | 2014-12-12 | 2017-08-31 | Borgwarner, Inc. | Coaxial mono or double gate valve for controlling a twin-scroll turbocharger |
DE102014019091A1 (en) | 2014-12-18 | 2016-06-23 | Daimler Ag | Internal combustion engine for a motor vehicle |
DE102014019094A1 (en) | 2014-12-18 | 2016-06-23 | Daimler Ag | Internal combustion engine for a motor vehicle |
US9810143B2 (en) * | 2015-01-16 | 2017-11-07 | Ford Global Technologies, Llc | Exhaust control valve branch communication and wastegate |
DE102016200812A1 (en) * | 2016-01-21 | 2017-07-27 | Bayerische Motoren Werke Aktiengesellschaft | Turbocharger with slide for flood connection |
DE102016208159B4 (en) | 2016-05-12 | 2022-02-03 | Vitesco Technologies GmbH | Turbine for an exhaust gas turbocharger with a double-flow turbine housing and a valve for connecting the flows |
US10190486B2 (en) * | 2016-08-10 | 2019-01-29 | GM Global Technology Operations LLC | Turbocharger with twin waste-gate valves |
GB201617858D0 (en) * | 2016-10-21 | 2016-12-07 | Cummins Ltd | Method of design of a turbine |
US10677150B2 (en) | 2017-05-11 | 2020-06-09 | Garrett Transportation I Inc. | Rotatable valve for turbocharger system with plural volute members |
DE102017009452A1 (en) * | 2017-10-11 | 2019-04-11 | Daimler Ag | Internal combustion engine for a motor vehicle and motor vehicle with such an internal combustion engine |
US10273910B1 (en) * | 2018-01-17 | 2019-04-30 | Denso International America, Inc. | Exhaust gas distribution valve |
US11073076B2 (en) | 2018-03-30 | 2021-07-27 | Deere & Company | Exhaust manifold |
US10662904B2 (en) | 2018-03-30 | 2020-05-26 | Deere & Company | Exhaust manifold |
JP7103098B2 (en) * | 2018-09-13 | 2022-07-20 | トヨタ自動車株式会社 | Turbocharger |
US10677140B1 (en) * | 2019-04-04 | 2020-06-09 | Gm Global Technology Operations, Llc | Multi-port exhaust gas diverter valve for an internal combustion engine system |
DE112020004247T5 (en) * | 2019-10-10 | 2022-06-09 | Ihi Corporation | turbocharger |
RU2752116C1 (en) * | 2020-02-18 | 2021-07-22 | Федеральное государственное казённое военное образовательное учреждение высшего образования "Военная академия материально-технического обеспечения имени генерала армии А.В. Хрулева" Министерства обороны Российской Федерации | Device for express diagnostics of synchronous, parallel turbochargers of internal combustion engine |
GB2594042A (en) * | 2020-03-27 | 2021-10-20 | Cummins Ltd | Engine system |
US11193435B1 (en) * | 2020-05-15 | 2021-12-07 | Caterpillar Inc. | System and method of controlling a turbocharged engine |
CN112228167B (en) * | 2020-10-19 | 2023-03-17 | 潍柴动力股份有限公司 | Pneumatic actuating device, turbocharger and exhaust gas bypass valve control mechanism thereof |
RU2759782C1 (en) * | 2020-11-25 | 2021-11-17 | Федеральное государственное казенное военное образовательное учреждение высшего образования "ВОЕННАЯ АКАДЕМИЯ МАТЕРИАЛЬНО-ТЕХНИЧЕСКОГО ОБЕСПЕЧЕНИЯ имени генерала армии А.В. Хрулева" Министерства обороны Российской Федерации | Method for determining technical condition of diesel turbocharger |
RU209241U1 (en) * | 2021-08-06 | 2022-02-08 | Федеральное государственное казённое военное образовательное учреждение высшего образования "Военная академия материально-технического обеспечения имени генерала армии А.В. Хрулева" Министерства обороны Российской Федерации | DEVICE FOR EXPRESS DIAGNOSTICS OF PARALLEL TURBOCOMPRESSORS OF A DIESEL ENGINE |
WO2024017464A1 (en) * | 2022-07-19 | 2024-01-25 | Volvo Truck Corporation | Engine system |
EP4357595A1 (en) * | 2022-10-19 | 2024-04-24 | Volvo Truck Corporation | Engine system |
Family Cites Families (64)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3423926A (en) | 1966-08-31 | 1969-01-28 | Garrett Corp | Turbocharger control arrangement |
US3559397A (en) | 1969-03-21 | 1971-02-02 | Bernard J Navarro | Turbo supercharger control mechanism |
US4177006A (en) | 1977-09-29 | 1979-12-04 | The Garrett Corporation | Turbocharger control |
US4179892A (en) | 1977-12-27 | 1979-12-25 | Cummins Engine Company, Inc. | Internal combustion engine with exhaust gas recirculation |
US4474006A (en) | 1982-09-30 | 1984-10-02 | The Jacobs Mfg. Company | Method and apparatus for improved compression release engine retarding in a turbocharged internal combustion engine |
DE3346472C2 (en) | 1982-12-28 | 1991-09-12 | Nissan Motor Co., Ltd., Yokohama, Kanagawa | Radial turbine with variable power |
US4526004A (en) | 1983-10-25 | 1985-07-02 | Holset Engineering Company Limited | Exhaust brake valve |
JPS618421A (en) | 1984-06-22 | 1986-01-16 | Toyota Motor Corp | Exhaust bypass device of turbo charger |
DE3903563C1 (en) | 1988-07-19 | 1990-03-22 | Mtu Friedrichshafen Gmbh | |
US4893474A (en) * | 1988-07-25 | 1990-01-16 | Allied-Signal Inc. | Turbocharger with dual function actuator |
US5146754A (en) | 1991-02-08 | 1992-09-15 | Jacobs Brake Technology Corp. | Exhaust gas diverter for divided volute turbocharger of internal combustion engine |
DE4416572C1 (en) | 1994-05-11 | 1995-04-27 | Daimler Benz Ag | Turbocharged internal combustion engine |
SE506125C2 (en) | 1994-12-08 | 1997-11-10 | Scania Cv Ab | Arrangements for redirecting exhaust gases in supercharged engines with parallel turbines |
SE506130C2 (en) | 1994-12-08 | 1997-11-10 | Scania Cv Ab | Arrangements for redirecting exhaust gases in supercharged engines with serial turbines |
US5611203A (en) | 1994-12-12 | 1997-03-18 | Cummins Engine Company, Inc. | Ejector pump enhanced high pressure EGR system |
DE19618160C2 (en) | 1996-05-07 | 1999-10-21 | Daimler Chrysler Ag | Exhaust gas turbocharger for an internal combustion engine |
US7222614B2 (en) | 1996-07-17 | 2007-05-29 | Bryant Clyde C | Internal combustion engine and working cycle |
SE9700474L (en) | 1997-02-10 | 1997-12-22 | Scania Cv Ab | Supercharged internal combustion engine, preferably diesel type, equipped with an exhaust gas recirculation device |
US5740785A (en) | 1997-06-09 | 1998-04-21 | Southwest Research Institute | Two way-high pressure loop, exhaust gas recirculation valve |
DE19727141C1 (en) | 1997-06-26 | 1998-08-20 | Daimler Benz Ag | Turbocharger system for internal combustion engine |
US6079211A (en) * | 1997-08-14 | 2000-06-27 | Turbodyne Systems, Inc. | Two-stage supercharging systems for internal combustion engines |
SE510714C2 (en) * | 1997-10-09 | 1999-06-14 | Volvo Ab | Turbocharged internal combustion engine |
SE517844C2 (en) | 1997-12-03 | 2002-07-23 | Volvo Lastvagnar Ab | Combustion engine arrangement and procedure for reducing harmful emissions |
DE19835978C1 (en) | 1998-08-08 | 1999-11-25 | Daimler Chrysler Ag | Motor vehicle twin turbocharger internal combustion engine with exhaust gas recycling |
DE19836677C2 (en) | 1998-08-13 | 2001-04-19 | Daimler Chrysler Ag | Engine brake device for an internal combustion engine with an exhaust gas turbocharger |
DE19857234C2 (en) | 1998-12-11 | 2000-09-28 | Daimler Chrysler Ag | Exhaust gas recirculation device |
SE521798C2 (en) | 1999-03-09 | 2003-12-09 | Volvo Lastvagnar Ab | Combustion engine with exhaust gas recirculation |
US6715288B1 (en) | 1999-05-27 | 2004-04-06 | Borgwarner, Inc. | Controllable exhaust gas turbocharger with a double-fluted turbine housing |
CA2342404C (en) | 2000-03-27 | 2007-05-15 | Mack Trucks, Inc. | Turbocharged engine with exhaust gas recirculation |
US6324847B1 (en) | 2000-07-17 | 2001-12-04 | Caterpillar Inc. | Dual flow turbine housing for a turbocharger in a divided manifold exhaust system having E.G.R. flow |
US6460519B1 (en) | 2000-10-04 | 2002-10-08 | Caterpillar Inc | Twin turbine exhaust gas re-circulation system having fixed geometry turbines |
EP1203872A1 (en) * | 2000-11-01 | 2002-05-08 | BorgWarner Inc. | Turbocharger having by-pass valve operable to promote rapid catalytic converter light off. |
US6321537B1 (en) | 2000-11-03 | 2001-11-27 | Caterpillar Inc. | Exhaust gas recirculation system in an internal combustion engine |
US6412279B1 (en) | 2000-12-20 | 2002-07-02 | Caterpillar Inc. | Twin turbine exhaust gas re-circulation system having a second stage variable nozzle turbine |
US6484499B2 (en) | 2001-01-05 | 2002-11-26 | Caterpillar, Inc | Twin variable nozzle turbine exhaust gas recirculation system |
US6418721B1 (en) | 2001-01-05 | 2002-07-16 | Caterpillar Inc. | Two turbocharger exhaust gas re-circulation system having a first stage variable nozzle turbine |
DE10152804B4 (en) | 2001-10-25 | 2016-05-12 | Daimler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device |
DE10152803A1 (en) | 2001-10-25 | 2003-05-15 | Daimler Chrysler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device |
DE10202322A1 (en) | 2002-01-23 | 2003-07-31 | Daimler Chrysler Ag | Internal combustion engine with exhaust gas turbocharger has controller that controls turbine geometry if pressure in or upstream of turbine exceeds threshold to prevent turbine damage |
US6715289B2 (en) | 2002-04-08 | 2004-04-06 | General Motors Corporation | Turbo-on-demand engine with cylinder deactivation |
US7287378B2 (en) | 2002-10-21 | 2007-10-30 | International Engine Intellectual Property Company, Llc | Divided exhaust manifold system and method |
DE10303777A1 (en) | 2003-01-31 | 2004-08-12 | Daimlerchrysler Ag | Internal combustion engine with exhaust gas turbocharger has valve body with 2 separate different openings for communicating with exhaust gas line blow-out opening in first and second open positions |
SE525219C2 (en) | 2003-05-15 | 2004-12-28 | Volvo Lastvagnar Ab | Turbocharger system for an internal combustion engine where both compressor stages are of radial type with compressor wheels fitted with reverse swept blades |
JP4242212B2 (en) | 2003-06-23 | 2009-03-25 | 株式会社小松製作所 | Turbocharger |
US7013879B2 (en) | 2003-11-17 | 2006-03-21 | Honeywell International, Inc. | Dual and hybrid EGR systems for use with turbocharged engine |
US6871642B1 (en) | 2004-02-27 | 2005-03-29 | Daimlerchrysler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device and method of operating same |
US6877492B1 (en) | 2004-02-27 | 2005-04-12 | Daimlerchrysler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device and method of operating same |
JP4057549B2 (en) | 2004-03-31 | 2008-03-05 | 株式会社豊田自動織機 | Exhaust gas purification device in internal combustion engine |
US7165403B2 (en) | 2004-07-28 | 2007-01-23 | Ford Global Technologies, Llc | Series/parallel turbochargers and switchable high/low pressure EGR for internal combustion engines |
DE102004039927A1 (en) | 2004-08-18 | 2006-02-23 | Daimlerchrysler Ag | Internal combustion engine with an exhaust gas turbocharger and an exhaust gas recirculation device |
US7140357B2 (en) | 2004-09-21 | 2006-11-28 | International Engine Intellectual Property Company, Llc | Vortex mixing system for exhaust gas recirculation (EGR) |
SE0402409L (en) | 2004-10-06 | 2005-08-09 | Saab Automobile | Internal combustion engine with parallel turbocharger and method of control |
US20060174621A1 (en) | 2005-02-04 | 2006-08-10 | Kai Chen | Two-turbocharger engine and method |
JP2007040136A (en) | 2005-08-02 | 2007-02-15 | Denso Corp | Exhaust gas recirculation system of internal combustion engine with supercharger |
US7571608B2 (en) | 2005-11-28 | 2009-08-11 | General Electric Company | Turbocharged engine system and method of operation |
US7788923B2 (en) | 2006-02-02 | 2010-09-07 | International Engine Intellectual Property Company, Llc | Constant EGR rate engine and method |
US7490462B2 (en) | 2006-02-21 | 2009-02-17 | Caterpillar Inc. | Turbocharged exhaust gas recirculation system |
US20080000228A1 (en) | 2006-06-30 | 2008-01-03 | Caterpillar Inc. | System and method for exhaust recirculation |
JP2008019835A (en) * | 2006-07-14 | 2008-01-31 | Mazda Motor Corp | Engine with supercharger |
US7363761B1 (en) * | 2006-10-31 | 2008-04-29 | International Engine Intellectual Property Company, Llc | Exhaust gas throttle for divided turbine housing turbocharger |
US20090000296A1 (en) | 2007-06-29 | 2009-01-01 | David Andrew Pierpont | Turbocharger having divided housing with integral valve |
US8161747B2 (en) | 2008-07-31 | 2012-04-24 | Caterpillar Inc. | Exhaust system having series turbochargers and EGR |
US8176737B2 (en) | 2008-07-31 | 2012-05-15 | Caterpillar Inc. | Exhaust system having 3-way valve |
US8297053B2 (en) | 2008-07-31 | 2012-10-30 | Caterpillar Inc. | Exhaust system having parallel asymmetric turbochargers and EGR |
-
2008
- 2008-07-31 US US12/222,009 patent/US8196403B2/en not_active Expired - Fee Related
-
2012
- 2012-05-15 US US13/472,175 patent/US20120222419A1/en not_active Abandoned
Cited By (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110067680A1 (en) * | 2009-09-22 | 2011-03-24 | Gm Global Technology Operations, Inc. | Turbocharger and Air Induction System Incorporating the Same and Method of Making and Using the Same |
US9759228B2 (en) * | 2009-10-16 | 2017-09-12 | GM Global Technology Operations LLC | Turbocharger and air induction system incorporating the same and method of using the same |
US20110088393A1 (en) * | 2009-10-16 | 2011-04-21 | Gm Global Technology Operations, Inc. | Turbocharger and Air Induction System Incorporating the Same and Method of Using the Same |
US20120255297A1 (en) * | 2009-10-20 | 2012-10-11 | Continental Automotive Gmbh | Turbine for an exhaust turbocharger, exhaust turbocharger, motor vehicle and method for operating an exhaust turbocharger |
US8991174B2 (en) * | 2009-10-20 | 2015-03-31 | Continental Automotive Gmbh | Turbine for an exhaust turbocharger, exhaust turbocharger, motor vehicle and method for operating an exhaust turbocharger |
US20130061831A1 (en) * | 2011-09-13 | 2013-03-14 | Caterpillar Inc. | Egr flow measurement |
US9068502B2 (en) * | 2011-09-13 | 2015-06-30 | Caterpillar Inc. | EGR flow measurement |
US20140138562A1 (en) * | 2012-11-16 | 2014-05-22 | Ford Global Technologies, Llc | Vacuum-actuated wastegate |
US9175783B2 (en) * | 2012-11-16 | 2015-11-03 | Ford Global Technologies, Llc | Vacuum-actuated wastegate |
US9297298B2 (en) | 2014-03-17 | 2016-03-29 | Ford Global Technologies, Llc | Dual wastegate actuation |
US9670834B2 (en) | 2014-03-17 | 2017-06-06 | Ford Global Technologies, Llc | Dual wastegate actuation |
US10301952B2 (en) | 2014-05-19 | 2019-05-28 | Borgwarner Inc. | Dual volute turbocharger to optimize pulse energy separation for fuel economy and EGR utilization via asymmetric dual volutes |
US10458316B2 (en) * | 2015-04-21 | 2019-10-29 | IFP Energies Nouvelles | Device for controlling the amount of air fed into the intake of a supercharged internal combustion engine and method using such a device |
US20180142610A1 (en) * | 2015-04-21 | 2018-05-24 | IFP Energies Nouvelles | Improved device for controlling the amount of air fed into the intake of a supercharged internal combustion engine and method using such a device |
DE102015122355A1 (en) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Exhaust gas guide section for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
DE102015122351A1 (en) * | 2015-12-21 | 2017-06-22 | Ihi Charging Systems International Gmbh | Exhaust gas guide section for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
US10662869B2 (en) | 2015-12-21 | 2020-05-26 | Ihi Charging Systems International Gmbh | Exhaust gas guide for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
US10890084B2 (en) | 2015-12-21 | 2021-01-12 | Ihi Charging Systems International Gmbh | Exhaust gas guide section for an exhaust gas turbocharger and method for operating an exhaust gas turbocharger |
US10655534B2 (en) | 2018-02-06 | 2020-05-19 | Garrett Transportation I Inc. | Rotary axial valve |
US11015517B2 (en) | 2018-02-06 | 2021-05-25 | Garrett Transoportation I Inc | Rotary axial valve |
Also Published As
Publication number | Publication date |
---|---|
US8196403B2 (en) | 2012-06-12 |
US20100024414A1 (en) | 2010-02-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8196403B2 (en) | Turbocharger having balance valve, wastegate, and common actuator | |
US8176737B2 (en) | Exhaust system having 3-way valve | |
US8297053B2 (en) | Exhaust system having parallel asymmetric turbochargers and EGR | |
US8161747B2 (en) | Exhaust system having series turbochargers and EGR | |
US8499555B2 (en) | Charge-cooled valve | |
US8234864B2 (en) | Engine system having multi-stage turbocharging and exhaust gas recirculation | |
US8096124B2 (en) | Exhaust system having parallel asymmetric turbochargers and EGR | |
US7654086B2 (en) | Air induction system having bypass flow control | |
US9163586B2 (en) | Exhaust system having parallel EGR coolers | |
US20090000296A1 (en) | Turbocharger having divided housing with integral valve | |
US6378509B1 (en) | Exhaust gas recirculation system having multifunction valve | |
US8297054B2 (en) | Exhaust system having turbo-assisted high-pressure EGR | |
US6412279B1 (en) | Twin turbine exhaust gas re-circulation system having a second stage variable nozzle turbine | |
US6138650A (en) | Method of controlling fuel injectors for improved exhaust gas recirculation | |
US6418721B1 (en) | Two turbocharger exhaust gas re-circulation system having a first stage variable nozzle turbine | |
GB2352272A (en) | Forced exhaust gas recirculation (EGR) system for i.c. engines | |
MXPA01003078A (en) | Exhaust gas recirculation system for a turbocharged engine. | |
US9255552B2 (en) | Engine system having dedicated donor cylinders for EGR | |
US9732668B2 (en) | Discharge valve and associated device | |
US9664148B2 (en) | Engine system having increased pressure EGR system | |
US9518519B2 (en) | Transient control of exhaust gas recirculation systems through mixer control valves | |
US8938962B2 (en) | Exhaust system | |
WO2017100097A1 (en) | Air handling in a heavy-duty opposed-piston engine | |
US20020088231A1 (en) | Twin variable nozzle turbine exhaust gas recirculation system | |
US9726121B2 (en) | Engine system having reduced pressure EGR system |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |