CA2311075A1 - High-speed overrunning, instantaneous, accessory decoupler - Google Patents
High-speed overrunning, instantaneous, accessory decoupler Download PDFInfo
- Publication number
- CA2311075A1 CA2311075A1 CA 2311075 CA2311075A CA2311075A1 CA 2311075 A1 CA2311075 A1 CA 2311075A1 CA 2311075 CA2311075 CA 2311075 CA 2311075 A CA2311075 A CA 2311075A CA 2311075 A1 CA2311075 A1 CA 2311075A1
- Authority
- CA
- Canada
- Prior art keywords
- cylindrical member
- annular member
- bearings
- central
- pulley
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
- F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
Abstract
The present invention is a pulley having a high speed clutch mechanism located in the hub of the circular pulley which mechanically couples a drive belt to an accessory spindle. The circular pulley has a central hub opening and a peripheral edge configured to engage the drive belt. The hub opening has a central axis, an internal diameter, and an inside surface. An annular member is coaxially and rigidly mounted to the inside surface of the pulley hub opening, the annular member having a central opening with an inside diameter, a central axis and an inside surface. Coaxially mounted within the central opening of the annular member is a cylindrical member having a first and second opposite end portions and a central portion between the end portions. The central portion of the cylindrical member has an outside surface, an outside diameter and a plurality of grooves equally spaced along the circumference of the outside surface.
Each groove is defined by a first sloping wall and a second sloping wall, the sloping walls being configured to retain a roller bearing between them. The outside diameter of the central portion of the cylindrical member is slightly less than the inside diameter of the annular member. The cylindrical member is mechanically coupled to the accessory spindle. A first bearing is mounted to the first end portion of the cylindrical member and a second bearing is mounted to the second end portion of the cylindrical member. Both of the bearings are dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings. Furthermore, the bearings are also dimensioned so that the cylindrical member does not touch the annular member. Finally, the first and second sloping walls and the roller bearings are all dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, while preventing the annular member from rotating in the first direction relative to the cylindrical member.
Each groove is defined by a first sloping wall and a second sloping wall, the sloping walls being configured to retain a roller bearing between them. The outside diameter of the central portion of the cylindrical member is slightly less than the inside diameter of the annular member. The cylindrical member is mechanically coupled to the accessory spindle. A first bearing is mounted to the first end portion of the cylindrical member and a second bearing is mounted to the second end portion of the cylindrical member. Both of the bearings are dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings. Furthermore, the bearings are also dimensioned so that the cylindrical member does not touch the annular member. Finally, the first and second sloping walls and the roller bearings are all dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, while preventing the annular member from rotating in the first direction relative to the cylindrical member.
Description
CANADA
Title: High-speed Overrunning, Instantaneous, Accessory Decoupler Inventor: Pavel Babetin !II
FIELD OF THE INVENTION:
The invention relates generally to multipurpose, minimal friction one-way overrunning clutches for use with serpentine belt driven components under high tension often found in engines in automotive applications.
BACKGROUND OF THE INVENTION:
Internal combustion engines incorporate belt systems and pulleys for attachment to either an engine crankshaft extension or to the drive spindle of an accessory. As such, the accessories are subject to the low speed oscillations of the engine caused by the inherent pulsations of the crankshaft spindle. The pistons of the engine, being forced down, cause the crankshaft velocity to fluctuate above and below a base level. In turn, the tension of the belt driven by the crankshaft spindle extension also fluctuates. Accessories are also subject to the sudden decelerations of the internal combustion engine of an automobile. These sudden decelerations often occur during the up shifts of the transmission where the engine speed is decreased.
When a sudden decrease in engine speed occurs, accessories, such as the alternator and other driven components, resist slowing down due to their rotational inertia.
Occasionally, this can cause a loud "squeal" from the belt-pulley interface. This slippage causes stress on the belt and is also very annoying to drivers. In an attempt to remedy the problem, designers of these systems increased the tension of the belts at the cost of increased belt wear.
This countermeasure also affected the accessories in that their output was forced to be proportional to that of the engine. Therefore, as the engine speed is decreased, so to is the output of the accessories. Thus the presence of an oscillatory component or a drive pulley that is inconstant in its rotational velocity is detrimental to accessories and exposes conventional belt systems to an increased stress.
There is an exigency for a device which can minimize the mooring of oscillations to accessories. There is a need for an arrangement which can eliminate "belt squeal" and reduce the loss of power provided by an accessory that is driven by an inconstant source.
SUMMARY OF THE INVENTION:
The present invention overcomes the drawbacks of the prior art by providing a pulley having a high speed clutch mechanism located in the hub of the circular pulley which is mechanically coupled to the accessory spindle. The circular pulley has a peripheral edge configured to engage the drive belt and a central hub opening. The hub opening has a central axis, an internal diameter, and an inside surface. An annular member is coaxially and rigidly mounted to the inside surface of the pulley hub opening, the annular member having a central opening with an inside diameter, a central axis and an inside surface.
Coaxially mounted within the central opening of the annular member is a cylindrical member having a first and second opposite end portions and a central portion between the end portions. The central portion of the cylindrical member has an outside surface, an outside diameter and a plurality of grooves equally spaced along the circumference of the outside surface. Each groove is defined by a first sloping wall and a second sloping wall, the sloping walls being configured to retain a roller bearing between them. The outside diameter of the central portion of the cylindrical member is slightly less than the inside diameter of the annular member. The cylindrical member is mechanically coupled to the accessory spindle. A first bearing is mounted to the first end portion of the cylindrical member and a second bearing is mounted to the second end portion of the cylindrical member. Both of the bearings are dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings.
Furthermore, the bearings are also dimensioned so that the cylindrical member does not touch the annular member. Finally, the first and second sloping walls and the roller bearings are all dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, while preventing the annular member from rotating in the first direction relative to the cylindrical member.
Other objects and advantages of the invention will be evident from the following detailed description when read in conjunction with the accompanying drawings which illustrate the invention.
BRIEF DESCRIPTION OF THE DRAWINGS:
FIGURE 1. is a schematic view of the present invention coupled to a motor.
FIGURE 2. is an exploded view of the present invention.
FIGURE 3. is a long sectional view of the invention.
1 S FIGURE 4. is a cross sectional view of the invention in its free wheeling position.
FIGURE 4A is a cross sectional view of the clutch mechanism of the invention in its free wheeling position.
FIGURE 5. is a cross sectional view of the invention in its locking position.
FIGURE SA is a cross sectional view of the clutch mechanism of the invention in its locking position.
Title: High-speed Overrunning, Instantaneous, Accessory Decoupler Inventor: Pavel Babetin !II
FIELD OF THE INVENTION:
The invention relates generally to multipurpose, minimal friction one-way overrunning clutches for use with serpentine belt driven components under high tension often found in engines in automotive applications.
BACKGROUND OF THE INVENTION:
Internal combustion engines incorporate belt systems and pulleys for attachment to either an engine crankshaft extension or to the drive spindle of an accessory. As such, the accessories are subject to the low speed oscillations of the engine caused by the inherent pulsations of the crankshaft spindle. The pistons of the engine, being forced down, cause the crankshaft velocity to fluctuate above and below a base level. In turn, the tension of the belt driven by the crankshaft spindle extension also fluctuates. Accessories are also subject to the sudden decelerations of the internal combustion engine of an automobile. These sudden decelerations often occur during the up shifts of the transmission where the engine speed is decreased.
When a sudden decrease in engine speed occurs, accessories, such as the alternator and other driven components, resist slowing down due to their rotational inertia.
Occasionally, this can cause a loud "squeal" from the belt-pulley interface. This slippage causes stress on the belt and is also very annoying to drivers. In an attempt to remedy the problem, designers of these systems increased the tension of the belts at the cost of increased belt wear.
This countermeasure also affected the accessories in that their output was forced to be proportional to that of the engine. Therefore, as the engine speed is decreased, so to is the output of the accessories. Thus the presence of an oscillatory component or a drive pulley that is inconstant in its rotational velocity is detrimental to accessories and exposes conventional belt systems to an increased stress.
There is an exigency for a device which can minimize the mooring of oscillations to accessories. There is a need for an arrangement which can eliminate "belt squeal" and reduce the loss of power provided by an accessory that is driven by an inconstant source.
SUMMARY OF THE INVENTION:
The present invention overcomes the drawbacks of the prior art by providing a pulley having a high speed clutch mechanism located in the hub of the circular pulley which is mechanically coupled to the accessory spindle. The circular pulley has a peripheral edge configured to engage the drive belt and a central hub opening. The hub opening has a central axis, an internal diameter, and an inside surface. An annular member is coaxially and rigidly mounted to the inside surface of the pulley hub opening, the annular member having a central opening with an inside diameter, a central axis and an inside surface.
Coaxially mounted within the central opening of the annular member is a cylindrical member having a first and second opposite end portions and a central portion between the end portions. The central portion of the cylindrical member has an outside surface, an outside diameter and a plurality of grooves equally spaced along the circumference of the outside surface. Each groove is defined by a first sloping wall and a second sloping wall, the sloping walls being configured to retain a roller bearing between them. The outside diameter of the central portion of the cylindrical member is slightly less than the inside diameter of the annular member. The cylindrical member is mechanically coupled to the accessory spindle. A first bearing is mounted to the first end portion of the cylindrical member and a second bearing is mounted to the second end portion of the cylindrical member. Both of the bearings are dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings.
Furthermore, the bearings are also dimensioned so that the cylindrical member does not touch the annular member. Finally, the first and second sloping walls and the roller bearings are all dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, while preventing the annular member from rotating in the first direction relative to the cylindrical member.
Other objects and advantages of the invention will be evident from the following detailed description when read in conjunction with the accompanying drawings which illustrate the invention.
BRIEF DESCRIPTION OF THE DRAWINGS:
FIGURE 1. is a schematic view of the present invention coupled to a motor.
FIGURE 2. is an exploded view of the present invention.
FIGURE 3. is a long sectional view of the invention.
1 S FIGURE 4. is a cross sectional view of the invention in its free wheeling position.
FIGURE 4A is a cross sectional view of the clutch mechanism of the invention in its free wheeling position.
FIGURE 5. is a cross sectional view of the invention in its locking position.
FIGURE SA is a cross sectional view of the clutch mechanism of the invention in its locking position.
DETAILED DESCRIPTION OF THE INVENTION:
The invention is a high rpm overrunning instantaneous accessory decoupler which is particularly useful for automobile internal combustion engines. As seen in figure 1, a typical automobile engine, shown generally as item 10, has a rotating fly wheel 12 which supplies power to various accessories such as alternator 20 via a serpentine belt 14. As fly wheel 12 rotates serpentine belt 14 drives pulley 16 which in turn makes spindle 22 of alternator 20 turn. In prior art engines, a tensioner is provided between alternator 20 and fly wheel 12 in order to maintain the proper tension in belt 14. The present invention overcomes the drawbacks of the prior art by providing a high speed overrunning instantaneous decoupler in the form of hub 18 on pulley 16.
Hence, the present invention may be applied to existing engine systems merely by replacing the pulley hub.
Referring now to figure 2, the high speed overrunning instantaneous accessory decoupler consists of clutch assembly 15 mounted at the hub of pulley 28. Clutch assembly 11 has a cylindrical member 34 having elongated hub 36 and central ridge 38.
Cylindrical member 34 has a plurality of grooves 42 equal distantly disposed along central ridge 38. Each groove 42 is dimensioned to retain roller 44. Cylindrical member 34 is dimensioned to fit within opening 55 of annular member 54. Cylindrical member 34 has an elongated hub 36 having portions 46 and 50 located on either side of central ridge 38. Rollers 44 are secured within grooves 42 by sealed bearings 56 and 58 which are mounted to portions 46 and 50, respectively, of hub 36. Clutch assembly 11 is mounted within opening 32 of pulley 28. Angular member 54 has clasp 52 which permits the angular member to be rigidly mounted to pulley 28.
Refernng now to figure 3, clutch assembly 11 is mounted in pulley 28 such that the clutch assembly acts as a hub for the pulley. Central ridge 38 of cylindrical member 34, rollers 44 and annular member 54 form a decoupling mechanism, shown generally as item 15.
Decoupling mechanism 15 is sealed between sealed bearings 56 and 58. By placing decoupling mechanism 15 between sealed bearings 56 and 58, the bearings act to seal decoupling mechanism 15 thereby rendering the entire clutch assembly 11 maintenance free. If only one sealing bearing were used, then dirt and debris would eventually interfere with roller bearings 44. Given the close tolerances required for high speed applications, it is important that decoupling mechanism 15 be as free from contamination as possible. For high speed applications, it is also important that clutch assembly 11 generate as little vibration as possible. By placing decoupling mechanism 15 between the bearings, the amount of vibration clutch assembly 11 will generate is reduced.
Also, since central ridge 38 and hub portions 46 and 50 are all part of cylindrical member 34, then the vibration of the entire assembly is further reduced.
Referring now to figures 4 and 4a, central ridge 38 of member 34 has a plurality of grooves 42 which extend parallel to central axis 40. Grooves 42 are defined by first wall 60 and second wall 62 which are formed in central ridge 38. The height of wall 62 is defined as the distance between top surface 39 of central ridge 38 and trough 61 which is the deepest portion of grooves 42. The height of wall 62 must be slightly greater than the diameter of roller 44. Central ridge 38 is mounted within opening 55 of angular member 54. The internal diameter of opening 55 is slightly greater than the maximum outside diameter of central ridge 38 such that top surface 39 of the central ridge never contacts inside surface 57 of annular member 54.
When annular member 54 begins to rotate faster than cylindrical member 34, roller bearings 44 are trapped between sloping walls 60 and inside surface 57, which in turn forces member 34 to rotate along with annular member 54. However, should annular member 54 slow down its rotation relative to cylindrical member 34, then roller bearings 44 make physical contact with sloping walls 62 as shown in figures 5 and SA. Since wall 62 is at an angle from ray 64, wall 62 exerts a centripetal force onto roller bearing 44 which forces roller bearing 44 towards central axis 40 and away from annular member 54. Since the height of wall 62 is slightly greater than the diameter of roller bearings 44, the roller bearings do not then make contact with inner surface 57 of annular member 54 and cylindrical member 34 may rotate freely relative to annular member 54 in a clockwise direction. It has been discovered that the angle at which wall 62 is positioned relative to ray 64 is critical for the proper operation of the decoupling device under high rmps. If the angle between wall 62 and ray 64 is too low, then wall 62 will not be able to exert sufficient centripetal force on roller bearing 44 to move it away from annular member 54. As a result, bearing 44 will contact annular member 54 and cause the clutch mechanism to over heat. However, if wall 62 at angled too far away from ray 64, then roller bearing 44 will not engage inner surface 57 of annular member 54 very quickly when the annular member rotates clockwise relative to cylindrical member 34.
It has been discovered that if wall 62 is angled approximately 30 degrees from ray 64 then roller bearings 44 will disengage from surface 57 almost instantaneously when cylindrical member 34 begins to rotate quicker than angular member 54. In experimental trials, it was discovered that an angle of 20 degrees was insufficient since the roller bearings made constant contact with the annular member, causing the clutch mechanism to over heat and fail prematurely.
The diameter of bearings 56 and 58 are selected so that surface 39 of central ridge 38 never contacts inner surface 57 and annular member 54. When annular member 54 is rotating slower than cylindrical member 34, the bearings permit the cylindrical member to rotate freely with very little friction.
The present invention can be used with most any drive system, including V-belt, poly V-belt, timing belts, chains and gears. An added advantage of the design is that, because accessories can freewheel and slippage is no longer a concern, less surface area is required on the pulley-belt interface than the conventional 180°, and a tensioner is no longer required. Because of the reduced friction at the interface, pulleys can be made of less expensive and lighter materials such as aluminum and plastic. However, the greatest advantage of this specific design is the very minimal amount of friction.
Since the proposed clutch is implemented at the hub of the accessories drive pulley, it has no effect on what type of drive system is employed. Most any type of belt, chain or gear system is permissible as neither has an adverse affects. The clutches applications are plentiful as its instantaneous engagement renders it effective from 0 rpm to very high revolutions, exceeding 20,000 rpm. The clutch produces no heat or vibration. The design also has high torque and shock capabilities.
The system which the design actuates is one that is both very versatile in the lubrication systems it is able to work in and is very efficient in providing very minimal friction. Although the clutch assembly can reside in an oil bath, providing a very stress reduced environment, it is just as effective when only bearing grease is utilized. Because the bearings are sealed there is no opportunity for leakage and maintenance is not required. These characteristics ensure a long, trouble free life.
The invention is a high rpm overrunning instantaneous accessory decoupler which is particularly useful for automobile internal combustion engines. As seen in figure 1, a typical automobile engine, shown generally as item 10, has a rotating fly wheel 12 which supplies power to various accessories such as alternator 20 via a serpentine belt 14. As fly wheel 12 rotates serpentine belt 14 drives pulley 16 which in turn makes spindle 22 of alternator 20 turn. In prior art engines, a tensioner is provided between alternator 20 and fly wheel 12 in order to maintain the proper tension in belt 14. The present invention overcomes the drawbacks of the prior art by providing a high speed overrunning instantaneous decoupler in the form of hub 18 on pulley 16.
Hence, the present invention may be applied to existing engine systems merely by replacing the pulley hub.
Referring now to figure 2, the high speed overrunning instantaneous accessory decoupler consists of clutch assembly 15 mounted at the hub of pulley 28. Clutch assembly 11 has a cylindrical member 34 having elongated hub 36 and central ridge 38.
Cylindrical member 34 has a plurality of grooves 42 equal distantly disposed along central ridge 38. Each groove 42 is dimensioned to retain roller 44. Cylindrical member 34 is dimensioned to fit within opening 55 of annular member 54. Cylindrical member 34 has an elongated hub 36 having portions 46 and 50 located on either side of central ridge 38. Rollers 44 are secured within grooves 42 by sealed bearings 56 and 58 which are mounted to portions 46 and 50, respectively, of hub 36. Clutch assembly 11 is mounted within opening 32 of pulley 28. Angular member 54 has clasp 52 which permits the angular member to be rigidly mounted to pulley 28.
Refernng now to figure 3, clutch assembly 11 is mounted in pulley 28 such that the clutch assembly acts as a hub for the pulley. Central ridge 38 of cylindrical member 34, rollers 44 and annular member 54 form a decoupling mechanism, shown generally as item 15.
Decoupling mechanism 15 is sealed between sealed bearings 56 and 58. By placing decoupling mechanism 15 between sealed bearings 56 and 58, the bearings act to seal decoupling mechanism 15 thereby rendering the entire clutch assembly 11 maintenance free. If only one sealing bearing were used, then dirt and debris would eventually interfere with roller bearings 44. Given the close tolerances required for high speed applications, it is important that decoupling mechanism 15 be as free from contamination as possible. For high speed applications, it is also important that clutch assembly 11 generate as little vibration as possible. By placing decoupling mechanism 15 between the bearings, the amount of vibration clutch assembly 11 will generate is reduced.
Also, since central ridge 38 and hub portions 46 and 50 are all part of cylindrical member 34, then the vibration of the entire assembly is further reduced.
Referring now to figures 4 and 4a, central ridge 38 of member 34 has a plurality of grooves 42 which extend parallel to central axis 40. Grooves 42 are defined by first wall 60 and second wall 62 which are formed in central ridge 38. The height of wall 62 is defined as the distance between top surface 39 of central ridge 38 and trough 61 which is the deepest portion of grooves 42. The height of wall 62 must be slightly greater than the diameter of roller 44. Central ridge 38 is mounted within opening 55 of angular member 54. The internal diameter of opening 55 is slightly greater than the maximum outside diameter of central ridge 38 such that top surface 39 of the central ridge never contacts inside surface 57 of annular member 54.
When annular member 54 begins to rotate faster than cylindrical member 34, roller bearings 44 are trapped between sloping walls 60 and inside surface 57, which in turn forces member 34 to rotate along with annular member 54. However, should annular member 54 slow down its rotation relative to cylindrical member 34, then roller bearings 44 make physical contact with sloping walls 62 as shown in figures 5 and SA. Since wall 62 is at an angle from ray 64, wall 62 exerts a centripetal force onto roller bearing 44 which forces roller bearing 44 towards central axis 40 and away from annular member 54. Since the height of wall 62 is slightly greater than the diameter of roller bearings 44, the roller bearings do not then make contact with inner surface 57 of annular member 54 and cylindrical member 34 may rotate freely relative to annular member 54 in a clockwise direction. It has been discovered that the angle at which wall 62 is positioned relative to ray 64 is critical for the proper operation of the decoupling device under high rmps. If the angle between wall 62 and ray 64 is too low, then wall 62 will not be able to exert sufficient centripetal force on roller bearing 44 to move it away from annular member 54. As a result, bearing 44 will contact annular member 54 and cause the clutch mechanism to over heat. However, if wall 62 at angled too far away from ray 64, then roller bearing 44 will not engage inner surface 57 of annular member 54 very quickly when the annular member rotates clockwise relative to cylindrical member 34.
It has been discovered that if wall 62 is angled approximately 30 degrees from ray 64 then roller bearings 44 will disengage from surface 57 almost instantaneously when cylindrical member 34 begins to rotate quicker than angular member 54. In experimental trials, it was discovered that an angle of 20 degrees was insufficient since the roller bearings made constant contact with the annular member, causing the clutch mechanism to over heat and fail prematurely.
The diameter of bearings 56 and 58 are selected so that surface 39 of central ridge 38 never contacts inner surface 57 and annular member 54. When annular member 54 is rotating slower than cylindrical member 34, the bearings permit the cylindrical member to rotate freely with very little friction.
The present invention can be used with most any drive system, including V-belt, poly V-belt, timing belts, chains and gears. An added advantage of the design is that, because accessories can freewheel and slippage is no longer a concern, less surface area is required on the pulley-belt interface than the conventional 180°, and a tensioner is no longer required. Because of the reduced friction at the interface, pulleys can be made of less expensive and lighter materials such as aluminum and plastic. However, the greatest advantage of this specific design is the very minimal amount of friction.
Since the proposed clutch is implemented at the hub of the accessories drive pulley, it has no effect on what type of drive system is employed. Most any type of belt, chain or gear system is permissible as neither has an adverse affects. The clutches applications are plentiful as its instantaneous engagement renders it effective from 0 rpm to very high revolutions, exceeding 20,000 rpm. The clutch produces no heat or vibration. The design also has high torque and shock capabilities.
The system which the design actuates is one that is both very versatile in the lubrication systems it is able to work in and is very efficient in providing very minimal friction. Although the clutch assembly can reside in an oil bath, providing a very stress reduced environment, it is just as effective when only bearing grease is utilized. Because the bearings are sealed there is no opportunity for leakage and maintenance is not required. These characteristics ensure a long, trouble free life.
Claims (5)
1. A high speed pulley for mechanically coupling an accessory spindle to a drive belt comprising;
~ a circular member having a peripheral edge configured to engage the drive belt and a central hub opening, said hub opening having a central axis, an internal diameter, and an inside surface, ~ an annular member coaxially and rigidly mounted to the inside surface of the pulley hub opening, the annular member having a central opening with an inside diameter, a central axis and an inside surface, ~ a cylindrical member coaxially mounted within the central opening of the annular member, the cylindrical member having a first and second opposite end portions and a central portion between the end portions, the central portion having an outside surface, an outside diameter and a plurality of grooves equally spaced along the circumference of the outside surface, each groove defined by a first sloping wall and a second sloping wall, the first and second sloping walls configured to retain a roller bearing there between, the outside diameter of the central portion being slightly less than the inside diameter of the annular member, the cylindrical member being mechanically coupled to the accessory spindle, ~ a first bearing mounted to the first end portion of the cylindrical member and a second bearing mounted to the second end portion of the cylindrical member, the bearings dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings, the bearings further dimensioned such that the annular member does not touch the annular member, ~ the first and second sloping walls and the roller bearings dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, the first and second sloping walls and the roller bearings being further dimensioned and configured to prevent the annular member from rotating relative to the cylindrical member in the first direction.
~ a circular member having a peripheral edge configured to engage the drive belt and a central hub opening, said hub opening having a central axis, an internal diameter, and an inside surface, ~ an annular member coaxially and rigidly mounted to the inside surface of the pulley hub opening, the annular member having a central opening with an inside diameter, a central axis and an inside surface, ~ a cylindrical member coaxially mounted within the central opening of the annular member, the cylindrical member having a first and second opposite end portions and a central portion between the end portions, the central portion having an outside surface, an outside diameter and a plurality of grooves equally spaced along the circumference of the outside surface, each groove defined by a first sloping wall and a second sloping wall, the first and second sloping walls configured to retain a roller bearing there between, the outside diameter of the central portion being slightly less than the inside diameter of the annular member, the cylindrical member being mechanically coupled to the accessory spindle, ~ a first bearing mounted to the first end portion of the cylindrical member and a second bearing mounted to the second end portion of the cylindrical member, the bearings dimensioned and configured to position the cylindrical member at the center of the pulley hub with the annular member being positioned between the bearings, the bearings further dimensioned such that the annular member does not touch the annular member, ~ the first and second sloping walls and the roller bearings dimensioned and configured to permit the cylindrical member to rotate freely in a first direction relative to the annular member, the first and second sloping walls and the roller bearings being further dimensioned and configured to prevent the annular member from rotating relative to the cylindrical member in the first direction.
2. A high speed pulley as defined in claim 1 wherein the roller bearing has a diameter and wherein the first and second sloping walls are positioned at a first and second angle relative to a ray extending perpendicular from the central axis and extending through the outside surface of the cylindrical member, the first and second angles and the diameter of the roller bearings all being selected such that the roller bearings do not touch the annular member when the cylindrical member rotates in the first direction, the diameter of the roller bearings and the first and second angles being further selected such that the roller bearings roll along the second wall to a position wherein the roller bearings are jammed between the second wall and the annular member when the annular member begins to rotate in the first direction relative to the cylindrical member.
3. A high speed pulley as defined in claim 2 wherein the first angle is greater than 20 degrees.
4. A high speed pulley as defined in claim 3 wherein the first angle is 30 degrees.
5. A high speed pulley as defined in claim 1 wherein the first and second bearings are sealed bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2311075 CA2311075A1 (en) | 2000-06-08 | 2000-06-08 | High-speed overrunning, instantaneous, accessory decoupler |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2311075 CA2311075A1 (en) | 2000-06-08 | 2000-06-08 | High-speed overrunning, instantaneous, accessory decoupler |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2311075A1 true CA2311075A1 (en) | 2001-12-08 |
Family
ID=4166429
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2311075 Abandoned CA2311075A1 (en) | 2000-06-08 | 2000-06-08 | High-speed overrunning, instantaneous, accessory decoupler |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2311075A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111164319A (en) * | 2017-08-28 | 2020-05-15 | 盖茨公司 | Isolation decoupler |
-
2000
- 2000-06-08 CA CA 2311075 patent/CA2311075A1/en not_active Abandoned
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111164319A (en) * | 2017-08-28 | 2020-05-15 | 盖茨公司 | Isolation decoupler |
| CN111164319B (en) * | 2017-08-28 | 2022-05-03 | 盖茨公司 | Isolation decoupler |
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