US20180355949A1 - Planetary damper architecture with centrifugal pendulum absorber - Google Patents
Planetary damper architecture with centrifugal pendulum absorber Download PDFInfo
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- US20180355949A1 US20180355949A1 US15/618,533 US201715618533A US2018355949A1 US 20180355949 A1 US20180355949 A1 US 20180355949A1 US 201715618533 A US201715618533 A US 201715618533A US 2018355949 A1 US2018355949 A1 US 2018355949A1
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- connection
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/13157—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses with a kinematic mechanism or gear system, e.g. planetary
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
- F16F15/1478—Masses connected to driveline by a kinematic mechanism or gear system with a planetary gear system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0268—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a gearing
Definitions
- the disclosure generally relates to a powertrain for a vehicle.
- Vehicle powertrains may include a vibration absorption assembly for reducing an amplitude of torsional vibration.
- the vibration absorption assembly may include, for example, damper springs that absorb the torsional vibration and release the torsional vibration at a later time.
- the vibration adsorption assembly may include some other device, such as a centrifugal pendulum absorber.
- the centrifugal pendulum absorber includes a drive plate and a mass that swings back and forth. The torsional vibration cancelling effect provided by the centrifugal pendulum absorber is dependent upon how much torque the mass generates against the drive plate as the mass swings.
- a powertrain includes an engine having a crankshaft, and a transmission having an input.
- a vibration absorption assembly includes a mechanical connection system.
- the mechanical connection system provides a first connection node, a second connection node, and a third connection node.
- the crankshaft of the engine is coupled to a first one of the first connection node, the second connection node, and the third connection node.
- the input of the transmission is connected to a second one of the first connection node, the second connection node, and the third connection node.
- a centrifugal pendulum absorber is connected to one of the first connection node, the second connection node, and the third connection node.
- one of the first connection node, the second connection node and the third connection node is a mechanically advantaged node.
- the centrifugal pendulum absorber is connected to the mechanically advantaged node.
- the powertrain includes a torque converter having a pump and a turbine.
- the pump is connected to the crankshaft for continuous rotation with the crankshaft.
- the turbine is connected to the third one of the first connection node, the second connection node, and the third connection node, which is connected to the centrifugal pendulum absorber. Furthermore, the turbine is connected to the mechanically advantaged node, just as the centrifugal pendulum absorber is.
- the first connection node, the second connection node, and the third connection node are each different nodes of the mechanical connection system.
- the centrifugal pendulum absorber is not connected to the first one of the first connection node, the second connection node, and the third connection node to which the output of the torque converter clutch is connected.
- the centrifugal pendulum absorber is not connected to the second one of the first connection node, the second connection node and the third connection node to which the input of the transmission is connected.
- the powertrain includes a spring that interconnects two of the first connection node, the second connection node, and the third connection node.
- the powertrain includes a torque converter clutch having an input and an output.
- the input of the torque converter clutch is connected to the crankshaft.
- the output of the torque converter clutch is connected to the first one of the connection nodes.
- the torque converter clutch interconnects the crankshaft and the first one of the connection nodes.
- the torque converter clutch is selectively controlled between an engaged state connecting the crankshaft and the mechanical connection system in direct torque communication, and a disengaged state disconnecting direct torque communication between the crankshaft and the mechanical connection system.
- the mechanical connection system includes a planetary gear set having a ring gear, a sun gear, and a planet carrier supporting a planet gear.
- a planetary gear set having a ring gear, a sun gear, and a planet carrier supporting a planet gear.
- Each of the ring gear, the sun gear, and the planet carrier define a respective one of the first connection node, the second connection node, and the third connection node.
- the centrifugal pendulum absorber is connected to the mechanically advantaged node of the mechanical connection system.
- the mechanically advantaged node amplifies the torsional vibration cancelling effect provided by the centrifugal pendulum absorber. Therefore, a mass of the centrifugal pendulum absorber may be reduced, while maintaining the same torsional vibration cancelling effect, because the torsional vibration cancelling effect from the reduced mass is amplified by the mechanically advantaged node of the mechanical connection system.
- FIG. 1 is a schematic diagram of a first embodiment of the powertrain.
- FIG. 2 is a schematic diagram of a second embodiment of the powertrain.
- FIG. 3 is a schematic diagram of a third embodiment of the powertrain.
- FIG. 4 is a schematic diagram of a fourth embodiment of the powertrain.
- FIG. 5 is a schematic diagram of a fifth embodiment of the powertrain.
- FIG. 6 is a schematic diagram of a sixth embodiment of the powertrain.
- FIG. 7 is a schematic diagram of a seventh embodiment of the powertrain.
- FIG. 8 is a schematic diagram of an eighth embodiment of the powertrain.
- FIG. 9 is a schematic diagram of a ninth embodiment of the powertrain.
- FIG. 10 is a schematic diagram of a tenth embodiment of the powertrain.
- FIG. 11 is a schematic diagram of an eleventh embodiment of the powertrain.
- FIG. 12 is a schematic diagram of a twelfth embodiment of the powertrain.
- FIG. 13 is a schematic lever diagram of a mechanical connection system of a powertrain.
- FIGS. 1-12 an exemplary embodiment of a powertrain is generally shown at 20 A- 20 L.
- Different connection combinations of the powertrain 20 A- 20 L are shown in FIGS. 1-12 , and are specifically referred to in each figure by the reference numerals 20 A- 20 L respectively.
- FIGS. 1-12 represent different possible connection combinations of the exemplary embodiment of the powertrain 20 A- 20 L. It should be appreciated that other embodiments of the powertrain are possible within the scope of the disclosure, and that other embodiments of the powertrain will each include their own respective possible component combinations and/or configurations.
- the description of the powertrain 20 A- 20 L is applicable to all embodiments, unless otherwise noted. Referring to FIGS.
- the exemplary embodiment of the powertrain 20 A- 20 L includes an engine 22 , a transmission 24 , a torque converter 26 , a torque converter clutch 28 , and a vibration absorption assembly 30 . It should be appreciated that other embodiments of the powertrain not shown or described herein may include other components and/or have the components arranged in different configurations.
- the engine 22 includes a crankshaft 32 , and is operable to generate torque and rotate the crankshaft 32 about a central axis.
- the engine 22 may include any device that is capable of generating torque and rotating the crankshaft 32 .
- the engine 22 may include, but is not limited to, an internal combustion engine 22 such as a gasoline engine 22 , a diesel engine 22 , etc. It should be appreciated that the engine 22 is not limited to an internal combustion engine 22 , and may include some other device not specifically described or mentioned herein. The specific type, construction, and operation of the engine 22 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein.
- the transmission 24 may include any type, style, and/or configuration suitable for a movable platform.
- the transmission 24 may include, but is not limited to, an automatic transmission, a manual transmission, a dual clutch transmission, a continuously variable transmission, etc.
- the transmission 24 includes an input 34 , an output 36 , and a gear set (not shown) interconnecting the input 34 and the output 36 .
- the input 34 is configured to receive torque from the engine 22 .
- the output 36 is configured to supply torque to a final drive system (not shown).
- the gear set provides different gear ratios through which the torque from the engine 22 may be transferred to change the torque and rotational speed of the output 36 of the transmission 24 relative to the input 34 of the transmission 24 .
- the specific, type, construction, and operation of the transmission 24 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein.
- the torque converter 26 includes a pump 38 and a turbine 40 that cooperate together to form a fluid coupling.
- the pump 38 is connected to the crankshaft 32 for continuous rotation with the crankshaft 32 .
- the turbine 40 is coupled to the input 34 of the transmission 24 .
- the turbine 40 is indirectly coupled to the input 34 via the vibration absorption assembly 30 .
- a fluid circulating through the torque converter 26 transfers torque between the pump 38 and the turbine 40 , thereby connecting the crankshaft 32 and the input 34 of the transmission 24 in torque communication.
- the specific, type, construction, and operation of the torque converter 26 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein.
- the exemplary embodiment of the powertrain 20 A- 20 L includes the torque converter clutch 28 interconnecting the crankshaft 32 and the vibration absorption assembly 30 .
- the powertrain may include other components not shown or described herein interconnecting the crankshaft 32 and the vibration absorption assembly 30 .
- some embodiments of the powertrain may include the crankshaft 32 being directly connected to the vibration absorption assembly 30 .
- the torque converter clutch 28 may be referred to as a torque converter lock-up clutch.
- the torque converter clutch 28 includes an input 42 and an output 44 .
- the input 42 of the torque converter clutch 28 is connected to the crankshaft 32 .
- the output 44 of the torque converter clutch 28 is connected to the input 34 of the transmission 24 , via the vibration absorption assembly 30 .
- the torque converter clutch 28 is selectively controlled between an engaged state and a disengaged state.
- the torque converter clutch 28 connects the crankshaft 32 and the input 34 of the transmission 24 , through the vibration absorption assembly 30 , in direct torque communication.
- the torque converter clutch 28 disconnects direct torque communication between the crankshaft 32 and the vibration absorption assembly 30 .
- torque only passes to the input 34 of the transmission 24 through the torque converter 26 .
- torque may pass to the input 34 of the transmission 24 through either the torque converter 26 and/or the torque converter clutch 28 .
- the vibration absorption assembly 30 includes a mechanical connection system 46 .
- the mechanical connection system 46 provides a first connection node 48 , a second connection node 50 , and a third connection node 52 .
- Each of the connection nodes provides a connection to a component of the powertrain 20 A- 20 L.
- the mechanical connection system 46 may include any mechanical system that provides the three connection nodes, and is able to provide at least one of the connection nodes with a mechanical advantage.
- the term mechanical advantage is defined as force amplification achieved by a mechanical device.
- the mechanical connection system 46 is embodied as a planetary gear set. As such, the planetary gear set provides a mechanical advantage to at least one of the connection nodes.
- the mechanical connection system 46 may be embodied as some other mechanical system, such as but not limited to a bar linkage system.
- the planetary gear set includes a ring gear 54 , a sun gear 56 , and a planet carrier 58 supporting at least one planet gear (not shown).
- Each of the ring gear 54 , the sun gear 56 , and the planet carrier 58 define a respective one of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the planetary gear set includes the planet gears rotating about and in meshing engagement with the sun gear 56 , with the ring gear 54 disposed about and in meshing engagement with the planet gears.
- a different component may be connected to each node respectively, i.e., each of the ring gear 54 , the sun gear 56 , and the planet carrier 58 .
- suitable planetary gear sets including the ring gear 54 , the sun gear 56 , and the planet carrier 58 supporting the planet gears, are well known in the art, and are therefore not described in greater detail herein.
- the each component of the planetary gear set i.e., the ring gear 54 , the sun gear 56 , and the planet carrier 58 , provides a respective one of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the mechanical connection system 46 provides one of the three connection nodes 48 , 50 , 52 with a mechanical advantage. Accordingly, one of the first connection node 48 , the second connection node 50 and the third connection node 52 is defined as a mechanically advantaged node.
- the term “mechanically advantaged node” is defined as any one of the first connection node 48 , the second connection node 50 or the third connection node 52 that has a mechanical advantage over any other one of the first connection node 48 , the second connection node 50 , or the third connection node 52 . It should be appreciated that two of the connection nodes 48 , 50 , 52 may have a mechanical advantage over the other connection node 48 , 50 , 52 , and that the mechanically advantaged node may be defined as either one of the two connection nodes 48 , 50 , 52 that have a mechanical advantage over the other connection node 48 , 50 , 52 . For example, as shown in the exemplary lever diagram of FIG.
- FIG. 13 further shows the angular velocity of the planet carrier 58 as the output arrow 74 , and the angular velocity of the ring gear 54 as the output arrow 76 . It should be appreciated that the respective nodes may differ from the exemplary embodiment shown in FIG. 13 .
- the crankshaft 32 is connected to one of the connection nodes 48 , 50 , 52 .
- the crankshaft 32 may be directly connected to one of the connection nodes, or may be indirectly connected to one of the connection nodes through one or more different components.
- the exemplary embodiment of the powertrain 20 A- 20 L shows the torque converter clutch 28 interconnecting the crankshaft 32 and one of the connection nodes 48 , 50 , 52 .
- the crankshaft 32 is connected to a first one of the first connection node 48 , the second connection node 50 , and the third connection node 52 . Referring to FIGS.
- the output 44 of the torque converter clutch 28 interconnects the crankshaft 32 and the first one of the connection nodes 48 , 50 , 52 .
- the output 44 of the torque converter clutch 28 is connected to the first one of the first connection node 48 , the second connection node 50 , or the third connection node 52 .
- the first one of the first connection node 48 , the second connection node 50 , and the third connection node 52 may include any one of the ring gear 54 , the sun gear 56 , or the planet carrier 58 .
- the input 34 of the transmission 24 is connected to a second one of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the second one of the first connection node 48 , the second connection node 50 , and the third connection node 52 may include any one of the ring gear 54 , the sun gear 56 , or the planet carrier 58 .
- a centrifugal pendulum absorber 60 is connected to a third one of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the third one of the first connection node 48 , the second connection node 50 , and the third connection node 52 may include any one of the ring gear 54 , the sun gear 56 , or the planet carrier 58 .
- the centrifugal pendulum absorber 60 is connected to the mechanically advantaged node. Additionally, in the exemplary embodiment of the powertrain 20 A- 20 L shown and described herein, the turbine 40 of the torque converter 26 is connected to the third one of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the third one of the connection nodes is the node that the centrifugal pendulum absorber 60 is connected to, the third one of the connection nodes is also the mechanically advantaged node. As such, the turbine 40 of the torque converter 26 is also connected to the mechanically advantaged node.
- the first connection node 48 , the second connection node 50 , and the third connection node 52 are each different nodes of the mechanical connection system 46 .
- the centrifugal pendulum absorber 60 is not connected to the first one of the first connection node 48 , the second connection node 50 , or the third connection node 52 to which the crankshaft 32 is connected. Additionally, the centrifugal pendulum absorber 60 is not connected to the second one of the first connection node 48 , the second connection node 50 and the third connection node 52 to which the input 34 of the transmission 24 is connected.
- the centrifugal pendulum absorber 60 is a type of tuned mass 64 absorber that reduces the amplitude of torsional vibration in the crankshaft 32 .
- the centrifugal pendulum absorber 60 includes a drive plate 62 and a mass 64 suspended from the drive plate 62 .
- the mass 64 has a center of gravity that moves along a prescribed path.
- the mass 64 swings back and forth like a pendulum, which counteracts the torsional vibrations.
- the centrifugal pendulum absorber 60 may be tuned to a given harmonic order of rotation, rather than to a set frequency, and is therefore effective over a continuous range of rotational speeds.
- the specific, construction, components, and operation of the centrifugal pendulum absorber 60 are well known in the art, and are therefore not described in detail herein.
- the centrifugal pendulum absorber 60 is connected to the mechanically advantaged node of the mechanical connection system 46 .
- the torque provided by the centrifugal pendulum absorber 60 is amplified by the mechanical advantage.
- the centrifugal pendulum absorber 60 may include a smaller mass 64 , while providing the same torsional vibration cancelling effect.
- the vibration absorption system may further includes at least one spring 66 .
- the vibration absorption system includes a plurality of springs 66 .
- the springs 66 interconnect two of the first connection node 48 , the second connection node 50 , and the third connection node 52 .
- the springs 66 may connect any two of the connection nodes.
- the springs 66 dampen the torsional vibration from the crankshaft 32 , as is well known in the art. The specific construction and operation of the springs 66 are not pertinent to the teachings of this disclosure and are therefore not described in detail herein.
- crankshaft 32 is connected to the first one of the connection nodes
- the input 34 of the transmission 24 is connected to the second one of the connection nodes
- the centrifugal pendulum absorber 60 is connected to the third one of the connection nodes.
- the turbine 40 of the torque converter 26 is also attached to the third one of the connection nodes
- the spring 66 is attached to two of the connection nodes.
- a first embodiment of the powertrain is generally shown at 20 A.
- the powertrain 20 A shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the sun gear 56 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the sun gear 56 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the planet carrier 58 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- a second embodiment of the powertrain is generally shown at 20 B.
- the powertrain 20 B shows the output 44 from the torque converter clutch 28 connected to the sun gear 56 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the sun gear 56 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the planet carrier 58 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- a third embodiment of the powertrain is generally shown at 20 C.
- the powertrain 20 C shows the output 44 from the torque converter clutch 28 connected to the sun gear 56 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the sun gear 56 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the sun gear 56 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- a fourth embodiment of the powertrain is generally shown at 20 D.
- the powertrain 20 D shows the output 44 from the torque converter clutch 28 connected to the ring gear 54 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the ring gear 54 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the planet carrier 58 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
- a fifth embodiment of the powertrain is generally shown at 20 E.
- the powertrain 20 E shows the output 44 from the torque converter clutch 28 connected to the ring gear 54 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the ring gear 54 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the sun gear 56 and the planet carrier 58 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
- a sixth embodiment of the powertrain is generally shown at 20 F.
- the powertrain 20 F shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the ring gear 54 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the ring gear 54 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the sun gear 56 and the planet carrier 58 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
- a seventh embodiment of the powertrain is generally shown at 20 G.
- the powertrain 20 G shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the sun gear 56 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the sun gear 56 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the sun gear 56 and the planet carrier 58 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- an eighth embodiment of the powertrain is generally shown at 20 H.
- the powertrain 20 H shows the output 44 from the torque converter clutch 28 connected to the sun gear 56 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the sun gear 56 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the sun gear 56 and the planet carrier 58 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- a ninth embodiment of the powertrain is generally shown at 20 I.
- the powertrain 20 I shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the sun gear 56 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the ring gear 54 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the sun gear 56 may be defined as the second one of the connection nodes
- the ring gear 54 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the sun gear 56 and the ring gear 54 .
- the ring gear 54 provides the mechanically advantaged node
- the planet carrier 58 and the sun gear 56 provide the non-mechanically advantaged nodes.
- a tenth embodiment of the powertrain is generally shown at 20 J.
- the powertrain 20 J shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the ring gear 54 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the ring gear 54 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the planet carrier 58 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
- an eleventh embodiment of the powertrain is generally shown at 20 K.
- the powertrain 20 K shows the output 44 from the torque converter clutch 28 connected to the planet carrier 58 , the input 34 of the transmission 24 connected to the ring gear 54 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the planet carrier 58 may be defined as the first one of the connection nodes
- the ring gear 54 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the sun gear 56 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
- an twelfth embodiment of the powertrain is generally shown at 20 L.
- the powertrain 20 L shows the output 44 from the torque converter clutch 28 connected to the ring gear 54 , the input 34 of the transmission 24 connected to the planet carrier 58 , the turbine 40 and the centrifugal pendulum absorber 60 connected to the sun gear 56 .
- the ring gear 54 may be defined as the first one of the connection nodes
- the planet carrier 58 may be defined as the second one of the connection nodes
- the sun gear 56 may be defined as the third one of the connection nodes.
- the spring 66 interconnects the ring gear 54 and the sun gear 56 .
- the sun gear 56 provides the mechanically advantaged node
- the planet carrier 58 and the ring gear 54 provide the non-mechanically advantaged nodes.
Abstract
Description
- The disclosure generally relates to a powertrain for a vehicle.
- Vehicle powertrains may include a vibration absorption assembly for reducing an amplitude of torsional vibration. The vibration absorption assembly may include, for example, damper springs that absorb the torsional vibration and release the torsional vibration at a later time. In addition to the damper springs, or as an alternative to the damper springs, the vibration adsorption assembly may include some other device, such as a centrifugal pendulum absorber. The centrifugal pendulum absorber includes a drive plate and a mass that swings back and forth. The torsional vibration cancelling effect provided by the centrifugal pendulum absorber is dependent upon how much torque the mass generates against the drive plate as the mass swings.
- A powertrain is provided. The powertrain includes an engine having a crankshaft, and a transmission having an input. A vibration absorption assembly includes a mechanical connection system. The mechanical connection system provides a first connection node, a second connection node, and a third connection node. The crankshaft of the engine is coupled to a first one of the first connection node, the second connection node, and the third connection node. The input of the transmission is connected to a second one of the first connection node, the second connection node, and the third connection node. A centrifugal pendulum absorber is connected to one of the first connection node, the second connection node, and the third connection node.
- In one aspect of the powertrain described herein, one of the first connection node, the second connection node and the third connection node is a mechanically advantaged node. The centrifugal pendulum absorber is connected to the mechanically advantaged node.
- In another aspect, the powertrain includes a torque converter having a pump and a turbine. The pump is connected to the crankshaft for continuous rotation with the crankshaft. The turbine is connected to the third one of the first connection node, the second connection node, and the third connection node, which is connected to the centrifugal pendulum absorber. Furthermore, the turbine is connected to the mechanically advantaged node, just as the centrifugal pendulum absorber is.
- In another aspect of the powertrain, the first connection node, the second connection node, and the third connection node are each different nodes of the mechanical connection system. The centrifugal pendulum absorber is not connected to the first one of the first connection node, the second connection node, and the third connection node to which the output of the torque converter clutch is connected. Similarly, the centrifugal pendulum absorber is not connected to the second one of the first connection node, the second connection node and the third connection node to which the input of the transmission is connected.
- In another aspect of the powertrain, the powertrain includes a spring that interconnects two of the first connection node, the second connection node, and the third connection node.
- In one embodiment, the powertrain includes a torque converter clutch having an input and an output. The input of the torque converter clutch is connected to the crankshaft. The output of the torque converter clutch is connected to the first one of the connection nodes. The torque converter clutch interconnects the crankshaft and the first one of the connection nodes. The torque converter clutch is selectively controlled between an engaged state connecting the crankshaft and the mechanical connection system in direct torque communication, and a disengaged state disconnecting direct torque communication between the crankshaft and the mechanical connection system.
- In one embodiment of the powertrain, the mechanical connection system includes a planetary gear set having a ring gear, a sun gear, and a planet carrier supporting a planet gear. Each of the ring gear, the sun gear, and the planet carrier define a respective one of the first connection node, the second connection node, and the third connection node.
- Accordingly, the centrifugal pendulum absorber is connected to the mechanically advantaged node of the mechanical connection system. As such, the mechanically advantaged node amplifies the torsional vibration cancelling effect provided by the centrifugal pendulum absorber. Therefore, a mass of the centrifugal pendulum absorber may be reduced, while maintaining the same torsional vibration cancelling effect, because the torsional vibration cancelling effect from the reduced mass is amplified by the mechanically advantaged node of the mechanical connection system.
- The above features and advantages and other features and advantages of the present teachings are readily apparent from the following detailed description of the best modes for carrying out the teachings when taken in connection with the accompanying drawings.
-
FIG. 1 is a schematic diagram of a first embodiment of the powertrain. -
FIG. 2 is a schematic diagram of a second embodiment of the powertrain. -
FIG. 3 is a schematic diagram of a third embodiment of the powertrain. -
FIG. 4 is a schematic diagram of a fourth embodiment of the powertrain. -
FIG. 5 is a schematic diagram of a fifth embodiment of the powertrain. -
FIG. 6 is a schematic diagram of a sixth embodiment of the powertrain. -
FIG. 7 is a schematic diagram of a seventh embodiment of the powertrain. -
FIG. 8 is a schematic diagram of an eighth embodiment of the powertrain. -
FIG. 9 is a schematic diagram of a ninth embodiment of the powertrain. -
FIG. 10 is a schematic diagram of a tenth embodiment of the powertrain. -
FIG. 11 is a schematic diagram of an eleventh embodiment of the powertrain. -
FIG. 12 is a schematic diagram of a twelfth embodiment of the powertrain. -
FIG. 13 is a schematic lever diagram of a mechanical connection system of a powertrain. - Those having ordinary skill in the art will recognize that terms such as “above,” “below,” “upward,” “downward,” “top,” “bottom,” etc., are used descriptively for the figures, and do not represent limitations on the scope of the disclosure, as defined by the appended claims. Furthermore, the teachings may be described herein in terms of functional and/or logical block components and/or various processing steps. It should be realized that such block components may be comprised of any number of hardware, software, and/or firmware components configured to perform the specified functions.
- Referring to the FIGS., wherein like numerals indicate like parts throughout the several views, an exemplary embodiment of a powertrain is generally shown at 20A-20L. Different connection combinations of the
powertrain 20A-20L are shown inFIGS. 1-12 , and are specifically referred to in each figure by thereference numerals 20A-20L respectively.FIGS. 1-12 represent different possible connection combinations of the exemplary embodiment of thepowertrain 20A-20L, It should be appreciated that other embodiments of the powertrain are possible within the scope of the disclosure, and that other embodiments of the powertrain will each include their own respective possible component combinations and/or configurations. The description of thepowertrain 20A-20L is applicable to all embodiments, unless otherwise noted. Referring toFIGS. 1-12 , the exemplary embodiment of thepowertrain 20A-20L includes anengine 22, atransmission 24, atorque converter 26, atorque converter clutch 28, and avibration absorption assembly 30. It should be appreciated that other embodiments of the powertrain not shown or described herein may include other components and/or have the components arranged in different configurations. - The
engine 22 includes acrankshaft 32, and is operable to generate torque and rotate thecrankshaft 32 about a central axis. Theengine 22 may include any device that is capable of generating torque and rotating thecrankshaft 32. For example, theengine 22 may include, but is not limited to, aninternal combustion engine 22 such as agasoline engine 22, adiesel engine 22, etc. It should be appreciated that theengine 22 is not limited to aninternal combustion engine 22, and may include some other device not specifically described or mentioned herein. The specific type, construction, and operation of theengine 22 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein. - The
transmission 24 may include any type, style, and/or configuration suitable for a movable platform. For example, thetransmission 24 may include, but is not limited to, an automatic transmission, a manual transmission, a dual clutch transmission, a continuously variable transmission, etc. Thetransmission 24 includes aninput 34, anoutput 36, and a gear set (not shown) interconnecting theinput 34 and theoutput 36. Theinput 34 is configured to receive torque from theengine 22. Theoutput 36 is configured to supply torque to a final drive system (not shown). The gear set provides different gear ratios through which the torque from theengine 22 may be transferred to change the torque and rotational speed of theoutput 36 of thetransmission 24 relative to theinput 34 of thetransmission 24. The specific, type, construction, and operation of thetransmission 24 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein. - The
torque converter 26 includes apump 38 and aturbine 40 that cooperate together to form a fluid coupling. Thepump 38 is connected to thecrankshaft 32 for continuous rotation with thecrankshaft 32. Theturbine 40 is coupled to theinput 34 of thetransmission 24. As described herein, theturbine 40 is indirectly coupled to theinput 34 via thevibration absorption assembly 30. As is understood by those skilled in the art, a fluid circulating through thetorque converter 26 transfers torque between thepump 38 and theturbine 40, thereby connecting thecrankshaft 32 and theinput 34 of thetransmission 24 in torque communication. The specific, type, construction, and operation of thetorque converter 26 are not pertinent to the teachings of this disclosure, and are therefore not described in detail herein. - The exemplary embodiment of the
powertrain 20A-20L includes thetorque converter clutch 28 interconnecting thecrankshaft 32 and thevibration absorption assembly 30. However, it should be appreciated that other embodiments of the powertrain may include other components not shown or described herein interconnecting thecrankshaft 32 and thevibration absorption assembly 30. Furthermore, some embodiments of the powertrain may include thecrankshaft 32 being directly connected to thevibration absorption assembly 30. Thetorque converter clutch 28 may be referred to as a torque converter lock-up clutch. Thetorque converter clutch 28 includes aninput 42 and anoutput 44. Theinput 42 of thetorque converter clutch 28 is connected to thecrankshaft 32. Theoutput 44 of thetorque converter clutch 28 is connected to theinput 34 of thetransmission 24, via thevibration absorption assembly 30. As is understood by those skilled in the art, thetorque converter clutch 28 is selectively controlled between an engaged state and a disengaged state. When disposed in the engaged sate, thetorque converter clutch 28 connects thecrankshaft 32 and theinput 34 of thetransmission 24, through thevibration absorption assembly 30, in direct torque communication. When disposed in the disengaged state, thetorque converter clutch 28 disconnects direct torque communication between thecrankshaft 32 and thevibration absorption assembly 30. When thetorque converter clutch 28 is disposed in the disengaged sate, torque only passes to theinput 34 of thetransmission 24 through thetorque converter 26. However, when thetorque converter clutch 28 is disposed in the engaged state, torque may pass to theinput 34 of thetransmission 24 through either thetorque converter 26 and/or thetorque converter clutch 28. - The
vibration absorption assembly 30 includes amechanical connection system 46. Themechanical connection system 46 provides afirst connection node 48, asecond connection node 50, and athird connection node 52. Each of the connection nodes provides a connection to a component of thepowertrain 20A-20L. Themechanical connection system 46 may include any mechanical system that provides the three connection nodes, and is able to provide at least one of the connection nodes with a mechanical advantage. As used herein, the term mechanical advantage is defined as force amplification achieved by a mechanical device. In the exemplary embodiment described herein and shown in the Figures, themechanical connection system 46 is embodied as a planetary gear set. As such, the planetary gear set provides a mechanical advantage to at least one of the connection nodes. However, it should be appreciated that themechanical connection system 46 may be embodied as some other mechanical system, such as but not limited to a bar linkage system. - As noted above, the embodiment of the
mechanical connection system 46 shown in the Figures and described herein is embodied as a planetary gear set. The planetary gear set includes aring gear 54, asun gear 56, and aplanet carrier 58 supporting at least one planet gear (not shown). Each of thering gear 54, thesun gear 56, and theplanet carrier 58 define a respective one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. In general, the planetary gear set includes the planet gears rotating about and in meshing engagement with thesun gear 56, with thering gear 54 disposed about and in meshing engagement with the planet gears. A different component may be connected to each node respectively, i.e., each of thering gear 54, thesun gear 56, and theplanet carrier 58. The components and the operation of suitable planetary gear sets, including thering gear 54, thesun gear 56, and theplanet carrier 58 supporting the planet gears, are well known in the art, and are therefore not described in greater detail herein. - As noted above, the each component of the planetary gear set, i.e., the
ring gear 54, thesun gear 56, and theplanet carrier 58, provides a respective one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. Furthermore, as described above, themechanical connection system 46 provides one of the threeconnection nodes first connection node 48, thesecond connection node 50 and thethird connection node 52 is defined as a mechanically advantaged node. As used herein, the term “mechanically advantaged node” is defined as any one of thefirst connection node 48, thesecond connection node 50 or thethird connection node 52 that has a mechanical advantage over any other one of thefirst connection node 48, thesecond connection node 50, or thethird connection node 52. It should be appreciated that two of theconnection nodes other connection node connection nodes other connection node FIG. 13 , aninput torque 70 is applied to theplanet carrier 58. Thesun gear 56 provides an output torque 72, and thering gear 54 provides anoutput torque 73. Since the output torque 72 and theoutput torque 73 are smaller than theinput torque 70, both thesun gear 56 and thering gear 54 have a mechanical advantage over theplanet carrier 58. As such, either one of thesun gear 56 or thering gear 54 may be defined as the mechanically advantaged node, because either one has a mechanical advantage of theplanet carrier 58.FIG. 13 further shows the angular velocity of theplanet carrier 58 as theoutput arrow 74, and the angular velocity of thering gear 54 as theoutput arrow 76. It should be appreciated that the respective nodes may differ from the exemplary embodiment shown inFIG. 13 . - The
crankshaft 32 is connected to one of theconnection nodes crankshaft 32 may be directly connected to one of the connection nodes, or may be indirectly connected to one of the connection nodes through one or more different components. For example, the exemplary embodiment of thepowertrain 20A-20L shows thetorque converter clutch 28 interconnecting thecrankshaft 32 and one of theconnection nodes crankshaft 32 is connected to a first one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. Referring toFIGS. 1-12 , in the exemplary embodiment of thepowertrain 20A-20L, theoutput 44 of thetorque converter clutch 28 interconnects thecrankshaft 32 and the first one of theconnection nodes output 44 of thetorque converter clutch 28 is connected to the first one of thefirst connection node 48, thesecond connection node 50, or thethird connection node 52. The first one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52 may include any one of thering gear 54, thesun gear 56, or theplanet carrier 58. Theinput 34 of thetransmission 24 is connected to a second one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. The second one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52 may include any one of thering gear 54, thesun gear 56, or theplanet carrier 58. - A
centrifugal pendulum absorber 60 is connected to a third one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. The third one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52 may include any one of thering gear 54, thesun gear 56, or theplanet carrier 58. Thecentrifugal pendulum absorber 60 is connected to the mechanically advantaged node. Additionally, in the exemplary embodiment of thepowertrain 20A-20L shown and described herein, theturbine 40 of thetorque converter 26 is connected to the third one of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. Since the third one of the connection nodes is the node that thecentrifugal pendulum absorber 60 is connected to, the third one of the connection nodes is also the mechanically advantaged node. As such, theturbine 40 of thetorque converter 26 is also connected to the mechanically advantaged node. - The
first connection node 48, thesecond connection node 50, and thethird connection node 52 are each different nodes of themechanical connection system 46. As such, thecentrifugal pendulum absorber 60 is not connected to the first one of thefirst connection node 48, thesecond connection node 50, or thethird connection node 52 to which thecrankshaft 32 is connected. Additionally, thecentrifugal pendulum absorber 60 is not connected to the second one of thefirst connection node 48, thesecond connection node 50 and thethird connection node 52 to which theinput 34 of thetransmission 24 is connected. - As is understood by those skilled in the art, the
centrifugal pendulum absorber 60 is a type of tunedmass 64 absorber that reduces the amplitude of torsional vibration in thecrankshaft 32. Generally described, thecentrifugal pendulum absorber 60 includes adrive plate 62 and amass 64 suspended from thedrive plate 62. Themass 64 has a center of gravity that moves along a prescribed path. When thedrive plate 62 is subjected to fluctuating torque, i.e., torsional vibrations, themass 64 swings back and forth like a pendulum, which counteracts the torsional vibrations. Thecentrifugal pendulum absorber 60 may be tuned to a given harmonic order of rotation, rather than to a set frequency, and is therefore effective over a continuous range of rotational speeds. The specific, construction, components, and operation of thecentrifugal pendulum absorber 60 are well known in the art, and are therefore not described in detail herein. - As noted above, the
centrifugal pendulum absorber 60 is connected to the mechanically advantaged node of themechanical connection system 46. By connecting thecentrifugal pendulum absorber 60 to the mechanically advantaged node, the torque provided by thecentrifugal pendulum absorber 60 is amplified by the mechanical advantage. Because the torque from thecentrifugal pendulum absorber 60 is amplified, thecentrifugal pendulum absorber 60 may include asmaller mass 64, while providing the same torsional vibration cancelling effect. - The vibration absorption system may further includes at least one
spring 66. In one exemplary embodiment, the vibration absorption system includes a plurality ofsprings 66. Thesprings 66 interconnect two of thefirst connection node 48, thesecond connection node 50, and thethird connection node 52. Thesprings 66 may connect any two of the connection nodes. Thesprings 66 dampen the torsional vibration from thecrankshaft 32, as is well known in the art. The specific construction and operation of thesprings 66 are not pertinent to the teachings of this disclosure and are therefore not described in detail herein. - As described above,
crankshaft 32 is connected to the first one of the connection nodes, theinput 34 of thetransmission 24 is connected to the second one of the connection nodes, and thecentrifugal pendulum absorber 60 is connected to the third one of the connection nodes. Additionally, theturbine 40 of thetorque converter 26 is also attached to the third one of the connection nodes, and thespring 66 is attached to two of the connection nodes. There exist many possible connection combinations for the exemplary embodiment of thepowertrain 20A-20L, with each connection combination for the exemplary embodiment of thepowertrain 20A-20L generally shown in one of the respectiveFIGS. 1-12 . It should be appreciated that other embodiments of the powertrain will have other possible combinations, and that the exemplary combinations shown and described herein are not exhaustive, and are merely provided as examples. - Referring to
FIG. 1 , a first embodiment of the powertrain is generally shown at 20A. Thepowertrain 20A shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thesun gear 56, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thesun gear 56 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and theplanet carrier 58. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 2 , a second embodiment of the powertrain is generally shown at 20B. Thepowertrain 20B shows theoutput 44 from thetorque converter clutch 28 connected to thesun gear 56, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, thesun gear 56 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and theplanet carrier 58. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 3 , a third embodiment of the powertrain is generally shown at 20C. Thepowertrain 20C shows theoutput 44 from thetorque converter clutch 28 connected to thesun gear 56, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, thesun gear 56 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and thesun gear 56. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 4 , a fourth embodiment of the powertrain is generally shown at 20D. The powertrain 20D shows theoutput 44 from thetorque converter clutch 28 connected to thering gear 54, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, thering gear 54 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and theplanet carrier 58. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - Referring to
FIG. 5 , a fifth embodiment of the powertrain is generally shown at 20E. Thepowertrain 20E shows theoutput 44 from thetorque converter clutch 28 connected to thering gear 54, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, thering gear 54 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thesun gear 56 and theplanet carrier 58. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - Referring to
FIG. 6 , a sixth embodiment of the powertrain is generally shown at 20F. Thepowertrain 20F shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thering gear 54, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thering gear 54 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thesun gear 56 and theplanet carrier 58. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - Referring to
FIG. 7 , a seventh embodiment of the powertrain is generally shown at 20G. Thepowertrain 20G shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thesun gear 56, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thesun gear 56 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thesun gear 56 and theplanet carrier 58. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 8 , an eighth embodiment of the powertrain is generally shown at 20H. Thepowertrain 20H shows theoutput 44 from thetorque converter clutch 28 connected to thesun gear 56, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, thesun gear 56 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thesun gear 56 and theplanet carrier 58. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 9 , a ninth embodiment of the powertrain is generally shown at 20I. The powertrain 20I shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thesun gear 56, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thering gear 54. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thesun gear 56 may be defined as the second one of the connection nodes, and thering gear 54 may be defined as the third one of the connection nodes. Thespring 66 interconnects thesun gear 56 and thering gear 54. Thering gear 54 provides the mechanically advantaged node, whereas theplanet carrier 58 and thesun gear 56 provide the non-mechanically advantaged nodes. - Referring to
FIG. 10 , a tenth embodiment of the powertrain is generally shown at 20J. Thepowertrain 20J shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thering gear 54, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thering gear 54 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and theplanet carrier 58. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - Referring to
FIG. 11 , an eleventh embodiment of the powertrain is generally shown at 20K. Thepowertrain 20K shows theoutput 44 from thetorque converter clutch 28 connected to theplanet carrier 58, theinput 34 of thetransmission 24 connected to thering gear 54, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, theplanet carrier 58 may be defined as the first one of the connection nodes, thering gear 54 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and thesun gear 56. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - Referring to
FIG. 12 , an twelfth embodiment of the powertrain is generally shown at 20L. Thepowertrain 20L shows theoutput 44 from thetorque converter clutch 28 connected to thering gear 54, theinput 34 of thetransmission 24 connected to theplanet carrier 58, theturbine 40 and thecentrifugal pendulum absorber 60 connected to thesun gear 56. Accordingly, in this embodiment, thering gear 54 may be defined as the first one of the connection nodes, theplanet carrier 58 may be defined as the second one of the connection nodes, and thesun gear 56 may be defined as the third one of the connection nodes. Thespring 66 interconnects thering gear 54 and thesun gear 56. Thesun gear 56 provides the mechanically advantaged node, whereas theplanet carrier 58 and thering gear 54 provide the non-mechanically advantaged nodes. - The detailed description and the drawings or figures are supportive and descriptive of the disclosure, but the scope of the disclosure is defined solely by the claims. While some of the best modes and other embodiments for carrying out the claimed teachings have been described in detail, various alternative designs and embodiments exist for practicing the disclosure defined in the appended claims.
Claims (16)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US15/618,533 US10151373B1 (en) | 2017-06-09 | 2017-06-09 | Planetary damper architecture with centrifugal pendulum absorber |
CN201810557985.6A CN109027123B (en) | 2017-06-09 | 2018-06-01 | Planetary damper structure with centrifugal pendulum type shock absorber |
DE102018113549.1A DE102018113549B4 (en) | 2017-06-09 | 2018-06-06 | DRIVE TRAIN WITH PLANETARY DAMPING ARCHITECTURE WITH CENTRIFUGAL SWING DAMPER |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US15/618,533 US10151373B1 (en) | 2017-06-09 | 2017-06-09 | Planetary damper architecture with centrifugal pendulum absorber |
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US10151373B1 US10151373B1 (en) | 2018-12-11 |
US20180355949A1 true US20180355949A1 (en) | 2018-12-13 |
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US15/618,533 Expired - Fee Related US10151373B1 (en) | 2017-06-09 | 2017-06-09 | Planetary damper architecture with centrifugal pendulum absorber |
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US (1) | US10151373B1 (en) |
CN (1) | CN109027123B (en) |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN111750035A (en) * | 2020-07-08 | 2020-10-09 | 山东交通学院 | Marine diesel vibration damper |
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US10955025B2 (en) * | 2018-05-31 | 2021-03-23 | GM Global Technology Operations LLC | Vehicle powertrain variable vibration absorber assembly |
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US8939860B2 (en) * | 2010-05-25 | 2015-01-27 | Zf Friedrichshafen Ag | Hydrodynamic coupling device, in particular a torque converter |
DE102012207862A1 (en) * | 2012-05-11 | 2013-11-14 | Zf Friedrichshafen Ag | Torsional vibration damping arrangement, in particular for the drive train of a vehicle |
DE102012212593A1 (en) * | 2012-07-18 | 2014-01-23 | Zf Friedrichshafen Ag | Torsional vibration damping arrangement for the drive train of a vehicle |
DE102013201619A1 (en) * | 2013-01-31 | 2014-07-31 | Zf Friedrichshafen Ag | Torsional vibration damping arrangement for the drive train of a vehicle |
DE102013214352A1 (en) * | 2013-07-23 | 2015-01-29 | Zf Friedrichshafen Ag | Torsional vibration damping arrangement for the drive train of a motor vehicle |
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2017
- 2017-06-09 US US15/618,533 patent/US10151373B1/en not_active Expired - Fee Related
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2018
- 2018-06-01 CN CN201810557985.6A patent/CN109027123B/en not_active Expired - Fee Related
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN111750035A (en) * | 2020-07-08 | 2020-10-09 | 山东交通学院 | Marine diesel vibration damper |
Also Published As
Publication number | Publication date |
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CN109027123B (en) | 2020-05-22 |
DE102018113549A1 (en) | 2018-12-13 |
US10151373B1 (en) | 2018-12-11 |
CN109027123A (en) | 2018-12-18 |
DE102018113549B4 (en) | 2022-02-10 |
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