WO2014205217A1 - Sealed actuator with internal clutching - Google Patents

Sealed actuator with internal clutching Download PDF

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Publication number
WO2014205217A1
WO2014205217A1 PCT/US2014/043185 US2014043185W WO2014205217A1 WO 2014205217 A1 WO2014205217 A1 WO 2014205217A1 US 2014043185 W US2014043185 W US 2014043185W WO 2014205217 A1 WO2014205217 A1 WO 2014205217A1
Authority
WO
WIPO (PCT)
Prior art keywords
detent ring
output shaft
output
internal clutching
sealed actuator
Prior art date
Application number
PCT/US2014/043185
Other languages
French (fr)
Inventor
Martin R. Matthews
Anthony J. Povinelli
Original Assignee
Magna International Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Magna International Inc. filed Critical Magna International Inc.
Priority to CA2940832A priority Critical patent/CA2940832C/en
Priority to EP14738703.9A priority patent/EP3011202B1/en
Priority to JP2016521576A priority patent/JP6496718B2/en
Priority to US14/899,729 priority patent/US10274027B2/en
Publication of WO2014205217A1 publication Critical patent/WO2014205217A1/en
Priority to US15/318,117 priority patent/US10124839B2/en
Priority to US16/158,556 priority patent/US11034395B2/en
Priority to US16/352,319 priority patent/US10738843B2/en
Priority to US16/924,137 priority patent/US11499595B2/en

Links

Classifications

    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D43/2024—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • 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
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/08—Air inlets for cooling; Shutters or blinds therefor
    • B60K11/085—Air inlets for cooling; Shutters or blinds therefor with adjustable shutters or blinds
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/22—Auxiliary parts of casings not covered by groups H02K5/06-H02K5/20, e.g. shaped to form connection boxes or terminal boxes
    • H02K5/225—Terminal boxes or connection arrangements
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/11—Structural association with clutches, brakes, gears, pulleys or mechanical starters with dynamo-electric clutches
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
    • H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion comprising worm and worm-wheel
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/26—Cover or bell housings; Details or arrangements thereof
    • 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
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/88—Optimized components or subsystems, e.g. lighting, actively controlled glasses

Definitions

  • the present invention relates to a clutch system for use in an actuator assembly for a vehicle.
  • Clutched actuator assemblies to fold a vehicle mirror are known. These mechanisms are known to have many disadvantages and are also not robust enough for particular applications.
  • the actuator is a hinged actuator with a base that must be fixed and an upper half that provides the movement of 80 degrees only. This base and upper half also move apart during clutching.
  • Known actuators are not waterproof, do not meet cycle requirements, and do not meet requirements for other more robust assembly needs such as are necessary in vehicle aerodynamic structures.
  • Conventional actuators do not have the combination of the desired attributes of a high cycle life, safety overload clutch, being waterproof, and holding torque capacity.
  • an actuator assembly that provides an actuator which is protected from environmental elements in vehicle underbody environments, has improved cycle durability, can drive in both directions, holds its position when stopped, has pass through drive, and has a clutch system to protect the actuator under higher predetermined loads.
  • the present invention is directed to a sealed actuator with internal clutching assembly.
  • a clutch system comprising an output shaft, output detent ring, moving detent ring, and a wave spring lock, which is fit inside a sealed two-part housing.
  • the moving detent ring is able to move axially to the output shaft and the output detent ring is able to rotate on the output shaft.
  • Intermeshing ramped teeth of these rings are held together by the wave spring lock and allow the output shaft to rotate and transmit torque to a motor through a main gear operably coupled to an output gear held by the output shaft to the outside of the two-part housing.
  • the actuator is operable to drive in both directions, but when stopped will hold its position without back driving when subjected to a load many times greater than its dynamic range.
  • the actuator will also protect itself from damage from predetermined loads, very high predetermined loads, due to the clutch system that will disengage the drive system allowing it to rotate.
  • the output and moving detent rings ramped teeth create an axial force that overcomes the load from the wave spring, which allows the moving detent ring to disengage and the output shaft to rotate freely to help prevent damage to the actuator.
  • FIG. 1 is a perspective view of a clutch system for an actuator assembly, in accordance with the present invention
  • Fig. 2 is a perspective view of an actuator with internal clutching assembly with a housing and motor arrangement removed for clarity, in accordance with the present invention
  • Fig. 3 is a perspective view of the sealed actuator with internal clutching assembly with a housing removed for clarity, in accordance with the present invention
  • Fig. 4 is an exploded view of the actuator with internal clutching assembly, in accordance with the present invention.
  • Fig. 5 is a partially broken away perspective view of a vehicle engine compartment having an active grille attached, as an example of an environment of use of an actuator with internal clutching assembly, in accordance with the present invention.
  • Fig. 6 is a partially broken away sectional plan view of an active grille system, as an example of an application of use with the actuator with internal clutching assembly, in accordance with the present invention.
  • a sealed actuator with internal clutching assembly in accordance with the present invention which provides desirable higher cycle durability and capability combined with a water tight arrangement for use, by way of example, in underbody environments exposed to the elements.
  • the sealed actuator with internal clutching assembly further provides a safety override clutch system which allows the actuator to rotate under predetermined conditions, e.g., predetermined nign loads, to help protect a motor and other components of the actuator with internal clutching assembly, as will be explained in greater detail below.
  • predetermined conditions e.g., predetermined nign loads
  • the actuator with internal clutching assembly will move features out of the way to help prevent damage thereto.
  • a sealed actuator with internal clutching assembly is shown generally at 10, comprising a clutch system, generally shown at 12, and housing portion, generally shown at 14.
  • the clutch system 12 comprises an output shaft 16 which is received within and holds an output detent ring 18 and a moving detent ring 20.
  • the output detent ring 18 is free to rotate on the output shaft 16 about a portion of the output shaft 16 that is not splined.
  • the moving detent ring 20 is able to move axially to the output shaft 16 but is locked radially by a plurality of interlocking splines 22,24 on both components.
  • the output shaft 16 has interlocking splines 22 that are arranged parallel to the longitudinal axis and operably spaced about an outer surface located on a lower half of the output shaft 16.
  • the moving detent ring 20 has outer interlocking splines 24 forming complementary channels to slidably interlock with the interlocking splines 22 for controlled axial movement of the moving detent ring 20.
  • the interlocking splines 22 of the output shaft 16 terminate at an integrally formed projecting ring 26 having an abutting surface 28, lying transverse to the axis, against which the output detent ring 18 engages.
  • the output detent ring 18 abuts against this surface 28 on the output shaft 16 and does not move axially.
  • An output gear 30 is in mesh with the output detent ring 18 for transmitting torque.
  • the output gear 30 has spaced circumferential segments 32 that are generally square teeth like shaped held in place within opposing recesses 34 of the output detent ring 18 for transmitting the torque.
  • the output and moving detent rings 18,20 have first and second intermeshing ramped teeth, generally shown at 36,38, respectively, that are held together in mesh by the biasing force of a wave spring 40.
  • the wave spring 40 is received on the outer output shaft 16 and provides a biasing force against the moving detent ring 20 in the direction of the output detent ring 18.
  • first and second locking rings 42,44 located toward respective ends the output shaft 16 of the clutch assembly 12.
  • a motor 46 selectively provides torque suitable for particular applications.
  • Suitable electontronics 48 e.g., a shut off printed circuit board (PCB)
  • PCB printed circuit board
  • connector contacts 50 correlate with vehicle communication networks and/or at least one sensor for commanding the motor 46 based upon predetermined conditions.
  • energizing of the motor correlating with vehicle speed.
  • the motor 46 has a worm gear, shown generally at 52, which causes a main gear, shown generally at 54, to rotate.
  • the main gear 54 has a gear and a helix angle portion 58.
  • the worm gear 52 has a shaft, e.g., a threaded shaft, which engages the teeth of the gear 56, which causes the gear 56 of the main gear 54 to rotate as the worm gear 52 rotates. Rotation of the gear 56 causes the helix angle portion 58 of the main gear 54 to also rotate.
  • the helix angle portion 58 rotatably engages the output gear 30.
  • the gear ratio range of the gear 56 to helix angle portion 58 is operably suitable for transmiting torque from the motor/worm gear 46/52 to the output gear 30.
  • the first and second intermeshing ramped teeth 36,38 of the output and moving detent rings 18,20 when held together by the biasing force of the wave spring 40 lock and allow the output shaft 16 to rotate and transmit the torque of the motor 4b through the main gear 54 and output gear 30 to the outside of the housing portion 14.
  • the output shaft 30 is coupled to a component and/or coupled to a drive shaft for selectively rotating, folding or otherwise moving at least one component located outside of the housing portion 14 between at least a first position and a second position.
  • the wave spring 40 allows for a more compact structure while meeting biasing and predetermined load requirements.
  • the housing portion 14 comprises a first half 60 and a second half 62.
  • the first half 60 has a first clutch assembly cavity 64 and a first motor cavity 66.
  • the second half 62 has a second clutch assembly cavity 68, a main gear cavity 70, and a second motor cavity.
  • the clutch system 12 fits fully inside the first and second halves 60,62 of the housing (within the first and second clutch assembly cavities 64,68), as well as the motor 46 and electronics 48/50 (within the first motor cavity 66 and second motor cavity), and main gear 54 (within the main gear cavity 70).
  • the first and second halves 60,62 of the housing portion 14 are joined together, and connected with fasteners, and first and second seals added 72,74 onto the output shaft 16 to form a weathertight housing.
  • the first and second intermeshing ramped teeth 36,38 of the output and moving detent rings 18,20 that when held together by the biasing force of the wave spring 40, lock together and allow the output shaft 16 to rotate.
  • This allows torque trasmission from the motor 46/worm gear 52 through the main gear 54 and output gear 30 to the outside of the housing portion 14 via the output shaft 16.
  • the first and second intermeshing ramped teeth 36,38 create an axile force that overcomes the load from the wave spring 40. This allows the moving detent ring 20 to disengage and allow the output shaft 16 to rotate freely, thereby preventing damage to the sealed actuator internal clutching assembly 10.
  • a sealed actuator with internal clutching assembly 10 which can drive in both directions, but when stopped will hold its position without back driving when subjected to a predetermined load, e.g. , a load many times greater than its dynamic range.
  • the actuator 10 also protects itself from damage from predetermined loads, e.g., very high loads, by means of the clutch that will disengage the drive system allowing it to rotate (e.g. , allowing the output shaft 16 to rotate freely).
  • the sealed actuator with internal clutching assembly 10 is in a waterproof housing and can rotate in both directions for as many revolutions as needed. The clutch is fully self contained in the housing.
  • the actuator has an output passthrough drive structure, e.g., output shaft 16 arrangment, allowing it to drive a shaft or part from either side or both sides.
  • the actuator can be mounted to a fixed part with the only external moving part is the drive.
  • the clutch system 12 of the sealed actuator with internal clutching assembly 10 also does not change shape or height when it clutches, which is yet another significant advantage.
  • the sealed actuator with internal clutching assembly 10 of the present invention can be, by way of non-limiting example, used with various applications including, but not limited to, vehicle rear spoilers, air diffusers that move, active grill shutter systems, and underbody environments with moving components.
  • the sealed actuator with internal clutching assembly 10 can be used in applications with a rear spoiler such that under regular aerodynamics the rear spoiler stays in position, but under a predetermined load such as contact from pushing on the spoiler, the rear spoiler will be moved out of the way without damage, e.g. , to the actuator.
  • FIG. 5 is a partially broken away perspective view of a vehicle engine compartment 100 is shown with an active grille 102 connected.
  • the active grille 102 has two or more vanes 104 that are moveable between an open position and a closed position in order to regulate airflow to the vehicle engine compartment 100.
  • the two or more vanes 104 as shown in Fig. 5 include a total of six vanes as part of the active grille 102. However, any number of vanes can be implemented including a single vane depending on the needs of a particular application.
  • the active grille 102 has a frame 106 and center bar 108 that serve to both define a passage for airflow and provide a mountable surface to which the two or more vanes 104 can rotate between the closed position and open position.
  • An electrically driven actuator is connectable to the active grille 102 and configured to provide power that drives the vanes 104 between the open position and closed position.
  • Figure 6 shows a partially broken away exploded perspective view of the active grille 102 of Figure 5.
  • the two or more vanes 104 have at least one driven vane 106 that is connected to an actuator 1 12 (e.g., sealed actuator with internal clutching assembly shown in Figs. 1 -4).
  • the actuator 1 12 provides power to drive and move the at least one driven vane 106 between the closed position and open position.
  • a fail safe module 1 10 is also connected to the at least one driven vane 106 that is connected between the at least one driven vane 106 and the actuator 1 12.
  • the fail safe module 1 10 functions to disconnect the at least one driven vane 106 and all of the other two or more vanes 104 from the actuator 1 12 in the event of power failure or other disruption of the actuator 1 12 in order to move the two or more vanes 104. It is desirable that the two or more vanes 104 are not in the closed position so that airflow through the active grille 102 to the vehicle engine compartment 100 will not be disrupted. When it is not desired to have airflow disrupted to the vehicle engine compartment 100, such as when the engine is already at optimal heating conditions, preventing airflow to the vehicle engine compartment 100 can result in engine overheating.
  • the description of the invention is merely exemplary in nature and, thus, variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Transportation (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Motor Or Generator Frames (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

A sealed actuator with internal clutching assembly including an output shaft, output detent ring, moving detent ring, and a wave spring, which is fit inside a sealed housing. The moving detent ring is able to move axially to the output shaft and the output detent ring is able to rotate on the output shaft. Intermeshing ramped teeth of these rings are held together by a wave spring and allow the output shaft to rotate and transmit torque of a motor through a main gear operably coupled to an output gear mounted on the output shaft to the outside of the housing. During predetermined high loads, the output and moving detent rings ramped teeth create an axial force that overcomes the load from the wave spring, which allows moving detent ring to disengage and output shaft to rotate freely to help prevent damage to the actuator.

Description

SEALED ACTUATOR WITH INTERNAL CLUTCHING
CROSS-REFERENCE TO RELATED APPLICATIONS
This application is a PCT International Application and claims benefit of United
States Provisional Patent Application No. 61/836,936, filed June 19, 2013.
FIELD OF THE INVENTION
The present invention relates to a clutch system for use in an actuator assembly for a vehicle.
BACKGROUND OF THE INVENTION
Clutched actuator assemblies to fold a vehicle mirror are known. These mechanisms are known to have many disadvantages and are also not robust enough for particular applications. Generally, the actuator is a hinged actuator with a base that must be fixed and an upper half that provides the movement of 80 degrees only. This base and upper half also move apart during clutching. Known actuators are not waterproof, do not meet cycle requirements, and do not meet requirements for other more robust assembly needs such as are necessary in vehicle aerodynamic structures. Conventional actuators do not have the combination of the desired attributes of a high cycle life, safety overload clutch, being waterproof, and holding torque capacity.
Therefore, it is desired to provide an actuator assembly that provides an actuator which is protected from environmental elements in vehicle underbody environments, has improved cycle durability, can drive in both directions, holds its position when stopped, has pass through drive, and has a clutch system to protect the actuator under higher predetermined loads. SUMMARY OF THE INVENTION
The present invention is directed to a sealed actuator with internal clutching assembly. There is provided a clutch system comprising an output shaft, output detent ring, moving detent ring, and a wave spring lock, which is fit inside a sealed two-part housing. The moving detent ring is able to move axially to the output shaft and the output detent ring is able to rotate on the output shaft. Intermeshing ramped teeth of these rings are held together by the wave spring lock and allow the output shaft to rotate and transmit torque to a motor through a main gear operably coupled to an output gear held by the output shaft to the outside of the two-part housing.
The actuator is operable to drive in both directions, but when stopped will hold its position without back driving when subjected to a load many times greater than its dynamic range. The actuator will also protect itself from damage from predetermined loads, very high predetermined loads, due to the clutch system that will disengage the drive system allowing it to rotate. During a predetermined high load condition, the output and moving detent rings ramped teeth create an axial force that overcomes the load from the wave spring, which allows the moving detent ring to disengage and the output shaft to rotate freely to help prevent damage to the actuator.
Further areas of applicability of the present invention will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention will become more fully understood from the detailed description and the accompanying drawings, wherein: Fig. 1 is a perspective view of a clutch system for an actuator assembly, in accordance with the present invention;
Fig. 2 is a perspective view of an actuator with internal clutching assembly with a housing and motor arrangement removed for clarity, in accordance with the present invention;
Fig. 3 is a perspective view of the sealed actuator with internal clutching assembly with a housing removed for clarity, in accordance with the present invention;
Fig. 4 is an exploded view of the actuator with internal clutching assembly, in accordance with the present invention;
Fig. 5 is a partially broken away perspective view of a vehicle engine compartment having an active grille attached, as an example of an environment of use of an actuator with internal clutching assembly, in accordance with the present invention; and
Fig. 6 is a partially broken away sectional plan view of an active grille system, as an example of an application of use with the actuator with internal clutching assembly, in accordance with the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses.
There is provided a sealed actuator with internal clutching assembly in accordance with the present invention which provides desirable higher cycle durability and capability combined with a water tight arrangement for use, by way of example, in underbody environments exposed to the elements. The sealed actuator with internal clutching assembly further provides a safety override clutch system which allows the actuator to rotate under predetermined conditions, e.g., predetermined nign loads, to help protect a motor and other components of the actuator with internal clutching assembly, as will be explained in greater detail below. When subjected to abnormal loads or a predetermined amount of force or other predetermined conditions, the actuator with internal clutching assembly will move features out of the way to help prevent damage thereto.
Referring generally to Figures 1 -4, a sealed actuator with internal clutching assembly is shown generally at 10, comprising a clutch system, generally shown at 12, and housing portion, generally shown at 14. The clutch system 12 comprises an output shaft 16 which is received within and holds an output detent ring 18 and a moving detent ring 20.
The output detent ring 18 is free to rotate on the output shaft 16 about a portion of the output shaft 16 that is not splined. The moving detent ring 20 is able to move axially to the output shaft 16 but is locked radially by a plurality of interlocking splines 22,24 on both components. The output shaft 16 has interlocking splines 22 that are arranged parallel to the longitudinal axis and operably spaced about an outer surface located on a lower half of the output shaft 16. The moving detent ring 20 has outer interlocking splines 24 forming complementary channels to slidably interlock with the interlocking splines 22 for controlled axial movement of the moving detent ring 20. The interlocking splines 22 of the output shaft 16 terminate at an integrally formed projecting ring 26 having an abutting surface 28, lying transverse to the axis, against which the output detent ring 18 engages. The output detent ring 18 abuts against this surface 28 on the output shaft 16 and does not move axially.
An output gear 30 is in mesh with the output detent ring 18 for transmitting torque. The output gear 30 has spaced circumferential segments 32 that are generally square teeth like shaped held in place within opposing recesses 34 of the output detent ring 18 for transmitting the torque.
The output and moving detent rings 18,20 have first and second intermeshing ramped teeth, generally shown at 36,38, respectively, that are held together in mesh by the biasing force of a wave spring 40. The wave spring 40 is received on the outer output shaft 16 and provides a biasing force against the moving detent ring 20 in the direction of the output detent ring 18.
The components of the clutch system 10 (e.g., output shaft 16, output gear 30, output detent ring 18, moving detent ring 20, and wave spring 40) are held together by first and second locking rings 42,44 located toward respective ends the output shaft 16 of the clutch assembly 12.
A motor 46 selectively provides torque suitable for particular applications. Suitable electontronics 48 (e.g., a shut off printed circuit board (PCB)) with connector contacts 50 correlate with vehicle communication networks and/or at least one sensor for commanding the motor 46 based upon predetermined conditions. By way of non- limiting example, energizing of the motor correlating with vehicle speed.
The motor 46 has a worm gear, shown generally at 52, which causes a main gear, shown generally at 54, to rotate. The main gear 54 has a gear and a helix angle portion 58. The worm gear 52 has a shaft, e.g., a threaded shaft, which engages the teeth of the gear 56, which causes the gear 56 of the main gear 54 to rotate as the worm gear 52 rotates. Rotation of the gear 56 causes the helix angle portion 58 of the main gear 54 to also rotate. The helix angle portion 58 rotatably engages the output gear 30. The gear ratio range of the gear 56 to helix angle portion 58 is operably suitable for transmiting torque from the motor/worm gear 46/52 to the output gear 30. The first and second intermeshing ramped teeth 36,38 of the output and moving detent rings 18,20 when held together by the biasing force of the wave spring 40 lock and allow the output shaft 16 to rotate and transmit the torque of the motor 4b through the main gear 54 and output gear 30 to the outside of the housing portion 14. By way of non-limiting example, the output shaft 30 is coupled to a component and/or coupled to a drive shaft for selectively rotating, folding or otherwise moving at least one component located outside of the housing portion 14 between at least a first position and a second position. The wave spring 40 allows for a more compact structure while meeting biasing and predetermined load requirements.
The housing portion 14 comprises a first half 60 and a second half 62. The first half 60 has a first clutch assembly cavity 64 and a first motor cavity 66. The second half 62 has a second clutch assembly cavity 68, a main gear cavity 70, and a second motor cavity. The clutch system 12 fits fully inside the first and second halves 60,62 of the housing (within the first and second clutch assembly cavities 64,68), as well as the motor 46 and electronics 48/50 (within the first motor cavity 66 and second motor cavity), and main gear 54 (within the main gear cavity 70). The first and second halves 60,62 of the housing portion 14 are joined together, and connected with fasteners, and first and second seals added 72,74 onto the output shaft 16 to form a weathertight housing.
In operation, the first and second intermeshing ramped teeth 36,38 of the output and moving detent rings 18,20, that when held together by the biasing force of the wave spring 40, lock together and allow the output shaft 16 to rotate. This allows torque trasmission from the motor 46/worm gear 52 through the main gear 54 and output gear 30 to the outside of the housing portion 14 via the output shaft 16. During a predetermined level of high load, the first and second intermeshing ramped teeth 36,38 create an axile force that overcomes the load from the wave spring 40. This allows the moving detent ring 20 to disengage and allow the output shaft 16 to rotate freely, thereby preventing damage to the sealed actuator internal clutching assembly 10. Thus, there is provided a sealed actuator with internal clutching assembly 10 which can drive in both directions, but when stopped will hold its position without back driving when subjected to a predetermined load, e.g. , a load many times greater than its dynamic range. The actuator 10 also protects itself from damage from predetermined loads, e.g., very high loads, by means of the clutch that will disengage the drive system allowing it to rotate (e.g. , allowing the output shaft 16 to rotate freely). The sealed actuator with internal clutching assembly 10 is in a waterproof housing and can rotate in both directions for as many revolutions as needed. The clutch is fully self contained in the housing. The actuator has an output passthrough drive structure, e.g., output shaft 16 arrangment, allowing it to drive a shaft or part from either side or both sides. The actuator can be mounted to a fixed part with the only external moving part is the drive. The clutch system 12 of the sealed actuator with internal clutching assembly 10 also does not change shape or height when it clutches, which is yet another significant advantage.
The sealed actuator with internal clutching assembly 10 of the present invention can be, by way of non-limiting example, used with various applications including, but not limited to, vehicle rear spoilers, air diffusers that move, active grill shutter systems, and underbody environments with moving components. For example, the sealed actuator with internal clutching assembly 10 can be used in applications with a rear spoiler such that under regular aerodynamics the rear spoiler stays in position, but under a predetermined load such as contact from pushing on the spoiler, the rear spoiler will be moved out of the way without damage, e.g. , to the actuator.
Referring now to Figure 5, there is illustrated an example of application with an active grill-type system. Figure 5 is a partially broken away perspective view of a vehicle engine compartment 100 is shown with an active grille 102 connected. The active grille 102 has two or more vanes 104 that are moveable between an open position and a closed position in order to regulate airflow to the vehicle engine compartment 100. The two or more vanes 104 as shown in Fig. 5 include a total of six vanes as part of the active grille 102. However, any number of vanes can be implemented including a single vane depending on the needs of a particular application. The active grille 102 has a frame 106 and center bar 108 that serve to both define a passage for airflow and provide a mountable surface to which the two or more vanes 104 can rotate between the closed position and open position. An electrically driven actuator is connectable to the active grille 102 and configured to provide power that drives the vanes 104 between the open position and closed position.
Figure 6 shows a partially broken away exploded perspective view of the active grille 102 of Figure 5. The two or more vanes 104 have at least one driven vane 106 that is connected to an actuator 1 12 (e.g., sealed actuator with internal clutching assembly shown in Figs. 1 -4). During normal operation of the active grille 102, the actuator 1 12 provides power to drive and move the at least one driven vane 106 between the closed position and open position. Optionally, also connected to the at least one driven vane 106 is a fail safe module 1 10 that is connected between the at least one driven vane 106 and the actuator 1 12. The fail safe module 1 10 functions to disconnect the at least one driven vane 106 and all of the other two or more vanes 104 from the actuator 1 12 in the event of power failure or other disruption of the actuator 1 12 in order to move the two or more vanes 104. It is desirable that the two or more vanes 104 are not in the closed position so that airflow through the active grille 102 to the vehicle engine compartment 100 will not be disrupted. When it is not desired to have airflow disrupted to the vehicle engine compartment 100, such as when the engine is already at optimal heating conditions, preventing airflow to the vehicle engine compartment 100 can result in engine overheating. The description of the invention is merely exemplary in nature and, thus, variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.

Claims

CLAIMS What is claimed is:
1. A sealed actuator with internal clutching for attachment to a vehicle component, comprising:
an output shaft with an output gear and an output detent ring rotatably mounted thereon;
a moving detent ring slidably mounted on said output shaft and intermeshable with said output detent ring;
a wave spring mounted on said output shaft providing a biasing force against said moving detent ring;
a housing portion that is fixed and sealed within which said output shaft is mounted;
a main gear having selective torsional force transferring gear contact with said output gear;
a motor having a worm gear providing selective torsional force transferring gear contact with said main gear;
wherein when said moving detent ring and said output detent ring are intermeshed by the force of said wave spring, said output shaft is rotatable to transmit torque from said motor through said main gear and said output gear to the outside of said housing portion; and wherein when during predetermined conditions said moving detent ring and said output detent ring create an axile force that overcomes the load from said wave spring, said output shaft is allowed to rotate freely for preventing damage to said sealed actuator with internal clutching.
2. The sealed actuator with internal clutching of claim 1 , wherein said output detent ring is mounted to selectively rotate on said output shaft.
3. The sealed actuator with internal clutching of claim 1 , wherein said moving detent ring is mounted to selectively move axially on said output shaft.
4. The sealed actuator with internal clutching of claim 1 , wherein said moving detent ring is locked radially with respect to said output shaft.
5. The sealed actuator with internal clutching of claim 1 , wherein said output shaft further comprises interlocking splines and said moving detent ring further comprises outer interlocking splines, wherein said moving detent ring is locked radially on said output shaft by said outer interlocking splines and respective interlocking splines.
6. The sealed actuator with internal clutching of claim 1 , wherein said output detent ring further comprises first intermeshing ramped teeth and said moving detent ring further comprises second intermeshing ramped teeth, wherein said first and second intermeshing ramped teeth are selectively held intermeshed by biasing force of said wave spring.
7. The sealed actuator with internal clutching of claim 6, wherein during said predetermined conditions said first and second intermeshing ramped teeth create said axile force that overcomes the load from said wave spring, which allows said moving detent ring to disengage and allow said output shaft to rotate freely.
8. The sealed actuator with internal clutching of claim 7, wherein said moving detent ring is disengaged from axially disposed interlocking splines formed on said output shaft.
9. The sealed actuator with internal clutching of claim 6, wherein said predetermined condition is a predetermined high load.
10. The sealed actuator with internal clutching of claim 1 , wherein said actuator does not change height when it clutches.
1 1 . The sealed actuator with internal clutching of claim 1 , wherein said actuator does not change shape or height when it clutches.
12. The sealed actuator with internal clutching of claim 1 , wherein said output gear has circumferential segments in mesh with recesses in said output detent ring.
13. The sealed actuator with internal clutching of claim 1 , further comprising a first locking ring and a second locking ring located toward respective ends of said output shaft to hold together said output shaft, output gear, output detent ring, moving detent ring, and wave spring on said output shaft.
14. The sealed actuator with internal clutching of claim 1 , wherein said motor further comprises a printed circuit board (PCB), said PCB correlating with vehicle communication networks and/or at least one sensor for commanding energizing of said motor based upon predetermined conditions.
15. The sealed actuator with internal clutching of claim 1 , wherein said housing portion has a first half and a second half that are joined and held together by fasteners to form a waterproof housing.
16. The sealed actuator with internal clutching of claim 15, further comprising a first seal and a second seal that are rings mounted toward the ends of said output shaft to form a weather tight seal between said output shaft and a respective opening in said first half and second half.
17. The sealed actuator with internal clutching of claim 16, wherein said motor and electronics and connector contacts of said motor are located within a cavity formed by a first motor cavity located in said second half and a second motor cavity in said second half, and said main gear is located within a cavity formed by a main gear cavity located in said first half and a second main gear cavity in said second half.
18. The sealed actuator with internal clutching of claim 17, wherein said moving detent ring, wave spring, output detent ring, output gear, output shaft, and a first and second retaining ring are located in a first clutch assembly cavity and second clutch assembly cavity in said first and second half, respectively.
19. The sealed actuator with internal clutching of claim 1 , wherein said output shaft is rotatable in both directions.
20. The sealed actuator with internal clutching of claim 1 , wherein said sealed actuator with internal clutching provides an output pass through drive arrangement allowing said sealed actuator with internal clutching to drive a shaft or an external moving part from either end or both ends.
21 . The sealed actuator with internal clutching of claim 1 , wherein said sealed actuator with internal clutching is used for driving an active grill system.
22. A sealed actuator with internal clutching for attachment to a vehicle component, comprising:
an output shaft with a lower portion having a plurality of interlocking splines;
an output detent ring rotatably mounted on a portion of said output shaft having no interlocking splines;
an output gear rotatably mounted on said portion of said output shaft having no interlocking splines, where said output gear is in mesh with said output detent ring;
a moving detent ring slidably mounted on said lower portion of said output shaft, where said moving detent ring is intermeshable with said output detent ring;
a wave spring mounted on said output shaft providing a biasing force against said moving detent ring;
a housing portion that is fixed and sealed within which said output shaft is mounted;
a main gear having selective torsional force transferring gear contact with said output gear;
a motor having a worm gear providing selective torsional force transferring gear contact with said main gear;
wherein when said moving detent ring and said output detent ring are intermeshed by the force of said wave spring, said output shaft is rotatable to transmit torque from said motor through said main gear and said output gear to the outside of said housing portion; and wherein when a predetermined high load amount is applied said moving detent ring and said output detent ring create an axile force that overcomes the load from said wave spring such that said output shaft is allowed to rotate freely for preventing damage to said sealed actuator with internal clutching.
23. The sealed actuator with internal clutching of claim 22, wherein said output detent ring is mounted to selectively rotate on said output shaft.
24. The sealed actuator with internal clutching of claim 22, wherein said moving detent ring further comprises outer interlocking splines, wherein said moving detent ring is locked radially on said output shaft by said outer interlocking splines and respective interlocking splines.
25. The sealed actuator with internal clutching of claim 22, wherein said output detent ring further comprises first intermeshing ramped teeth and said moving detent ring further comprises second intermeshing ramped teeth, wherein said first and second intermeshing ramped teeth are selectively held intermeshed by biasing force of said wave spring.
26. The sealed actuator with internal clutching of claim 25, wherein during said predetermined high load said first and second intermeshing ramped teeth create said axile force that overcomes the load from said wave spring, which allows said moving detent ring to disengage and allow said output shaft to rotate freely.
27. The sealed actuator with internal clutching of claim 26, wherein said moving detent ring is disengaged from axially disposed interlocking splines formed on said output shaft.
28. The sealed actuator with internal clutching of claim 1 , wherein said motor further comprises a printed circuit board (PCB), said PCB correlating with vehicle communication networks and/or at least one sensor for commanding energizing of said motor based upon predetermined conditions.
29. The sealed actuator with internal clutching of claim 22, further comprising a first seal and a second seal that are rings mounted toward the ends of said output shaft to form a weather tight seal between said output shaft and a respective opening in a first half and second half of said housing portion, said first seal and a second seal when joined together forming a waterproof housing.
30. A sealed actuator with internal clutching for attachment to a vehicle component, comprising:
an output shaft with a lower portion having a plurality of interlocking splines;
an output detent ring rotatably mounted on a portion of said output shaft having no interlocking splines such that said output detent ring is free to rotate on on said output shaft;
an output gear rotatably mounted on said portion of said output shaft having no interlocking splines, where said output gear is in mesh with said output detent ring;
a moving detent ring slidably mounted on said lower portion of said output shaft, where said moving detent ring is intermeshable with said output detent ring;
outer interlocking splines formed on said moving detent ring interlockable with said interlocking splines formed on said output shaft to prevent radial movement of said moving detent ring;
a wave spring mounted on said output shaft providing a biasing force against said moving detent ring;
first intermeshing ramped teeth and second intermeshing teeth formed on said output detent ring and moving detent ring, respectively, wherein said first and second intermeshing ramped teeth are selectively held intermeshed by the force of said wave spring;
a housing portion forming a weather tight seal;
a main gear having selective torsional force transferring gear contact with said output gear;
a motor having a worm gear providing selective torsional force transferring gear contact with said main gear;
wherein when said moving detent ring and said output detent ring are intermeshed by the force of said wave spring, said output shaft is rotatable to transmit torque from said motor through said main gear and said output gear to the outside of said housing portion; and
wherein during predetermined high load amount said first and second intermeshing ramped teeth create an axile force that overcomes the load from said wave spring, which allows said moving detent ring to disengage and allow said output shaft to rotate freely for preventing damage to said sealed actuator with internal clutching.
PCT/US2014/043185 2013-06-19 2014-06-19 Sealed actuator with internal clutching WO2014205217A1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
CA2940832A CA2940832C (en) 2013-06-19 2014-06-19 Sealed actuator with internal clutching
EP14738703.9A EP3011202B1 (en) 2013-06-19 2014-06-19 Sealed actuator with internal clutching
JP2016521576A JP6496718B2 (en) 2013-06-19 2014-06-19 Sealed actuator with internal clutch
US14/899,729 US10274027B2 (en) 2013-06-19 2014-06-19 Sealed actuator with internal clutching
US15/318,117 US10124839B2 (en) 2013-06-19 2015-06-10 Active front deflector
US16/158,556 US11034395B2 (en) 2013-06-19 2018-10-12 Active front deflector
US16/352,319 US10738843B2 (en) 2013-06-19 2019-03-13 Sealed actuator with internal clutching
US16/924,137 US11499595B2 (en) 2013-06-19 2020-07-08 Sealed actuator with internal clutching

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361836936P 2013-06-19 2013-06-19
US61/836,936 2013-06-19

Related Child Applications (4)

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US14/899,729 A-371-Of-International US10274027B2 (en) 2013-06-19 2014-06-19 Sealed actuator with internal clutching
PCT/US2015/035084 Continuation WO2015191697A2 (en) 2013-06-19 2015-06-10 Active front deflector
US15/318,117 Continuation US10124839B2 (en) 2013-06-19 2015-06-10 Active front deflector
US16/352,319 Continuation US10738843B2 (en) 2013-06-19 2019-03-13 Sealed actuator with internal clutching

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WO2014205217A1 true WO2014205217A1 (en) 2014-12-24

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EP (1) EP3011202B1 (en)
JP (1) JP6496718B2 (en)
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US20200386282A1 (en) 2020-12-10
CA2940832C (en) 2022-06-21
CA2940832A1 (en) 2014-12-24
EP3011202A1 (en) 2016-04-27
US20190211892A1 (en) 2019-07-11
US10274027B2 (en) 2019-04-30
JP6496718B2 (en) 2019-04-03
US20160230820A1 (en) 2016-08-11
EP3011202B1 (en) 2022-01-12
US10738843B2 (en) 2020-08-11
US11499595B2 (en) 2022-11-15
JP2016528861A (en) 2016-09-15

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