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WO1996000856A1 - Couplage a arbre flexible - Google Patents

Couplage a arbre flexible Download PDF

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Publication number
WO1996000856A1
WO1996000856A1 PCT/CA1995/000335 CA9500335W WO9600856A1 WO 1996000856 A1 WO1996000856 A1 WO 1996000856A1 CA 9500335 W CA9500335 W CA 9500335W WO 9600856 A1 WO9600856 A1 WO 9600856A1
Authority
WO
WIPO (PCT)
Prior art keywords
decoupler
axial length
hub
radius
shaft
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.)
Ceased
Application number
PCT/CA1995/000335
Other languages
English (en)
Inventor
Jacek S. Komorowski
Zbigniew F. Lipowski
Pierre A. Mevissen
Henry W. Thomey
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
730143 ONTARIO Inc
730144 ONTARIO Inc
Tesma International Inc
Original Assignee
730143 ONTARIO Inc
730144 ONTARIO Inc
Tesma 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 730143 ONTARIO Inc, 730144 ONTARIO Inc, Tesma International Inc filed Critical 730143 ONTARIO Inc
Priority to EP95942627A priority Critical patent/EP0828953A1/fr
Priority to JP8502666A priority patent/JPH10502157A/ja
Publication of WO1996000856A1 publication Critical patent/WO1996000856A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/04—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for electric generators
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/76—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part

Definitions

  • This invention relates to a shaft decoupling device for use in a belt drive having relatively high angular vibrations and where installation space is at a premium.
  • this invention relates to a torsionally soft coupling which acts both as an angular decoupling spring and universal joint, used singularly or in pairs with or without an associated propeller shaft, by which an accessory can be remotely mounted from the belt plane and simultaneously decoupled.
  • Background of Invention In modern automobile engines, belt drives are used to drive various accessories. The elastic belt must transmit sharply varying torque impulses from the drive pulley to a driven pulley which drives an accessory having a high rotational inertia.
  • the sharply varying torque causes the driven inertia to accelerate then decelerate which induces angular vibration of the driven inertia.
  • this forced vibration coincides with the angular resonant frequency of the driver/belt/driven inertia system, the angular vibration is greatly amplified.
  • the amplified angular vibration causes very large and continuous oscillation in the tensions in each of the belt spans resulting in associated noise and vibration.
  • decouplers are commonly used in industry to increase the overall elasticity of the belt driven system by adding a low angular rate decoupler in series with the system.
  • the decoupler may be inserted between the crankshaft hub and the drive pulley or between the driven pulley and the accessory that it drives.
  • the decoupler cushions the drive from the sharp momentary accelerations of the crankshaft.
  • the reduction of the system angular rate is such that the new natural frequency is much lower than the frequency of any rotating load being forced upon it such as the engine firing frequency or the air-conditioning pumping frequency. This avoids resonant amplification during all operating speeds of forces and tensions within the system that might cause disagreeable noise or vibration.
  • a shaft decoupler device which comprises an inner hub, an outer hub and a rubber core bonded between the inner hub and the outer hub.
  • the axial length of the rubber core at its inner radius is greater than the axial length of the rubber core at its outer radius.
  • the outer radius to inner has a ratio of about 3:1.
  • the inner hub and outer hub are connectable between a pulley and a driven accessory.
  • the shaft decoupler joint acts as an angular decoupling spring and as a universal joint.
  • a shaft decoupler joint having a first radius R t and a first axial length Lj and a second radius R 2 and a second axial length L, have a relationship as follows:
  • a decoupler having a tensioner for providing a tensioning force to a belt in driving engagement with the pulley.
  • a decoupler joint wherein the rubber core is molded to an inner hub and an outer hub.
  • a decoupler joint wherein both ends a relatively long shaft transmits rotational forces and is journal mounted.
  • decoupler joint having a relatively short shaft wherein the decoupler joint is mounted between a driving pulley and a driven device.
  • Figure 1 is a plan view of a shaft decoupling device for remotely mounting an automobile accessory of the present invention
  • Figure 2 is a partial sectional view of decoupling device of Figure 1;
  • Figure 3 is a partial sectional view of a second embodiment of a decoupling device of the present invention;
  • Figure 4 is a graph illustrating tension fluctuation of an engine system without a decoupler of the present invention;
  • Figure 5 is a graph illustrating tension fluctuation of an engine system incorporating the decoupler of the present invention
  • Figure 6 is a third embodiment of a short shaft decoupler of the present invention
  • Figure 7 is a fourth embodiment of a short shaft decoupler of the present invention
  • Figure 8 is a fifth embodiment of a short shaft decoupler of the present invention
  • Figure 9 is a sixth embodiment of a short shaft decoupler of the present invention.
  • the shaft decoupler joint 10 of the present invention is illustrated.
  • the shaft decoupler joint 10 is intermediate to a remotely mounted driven device 12, such as an alternator, and a pulley 14.
  • Driven device 12 is in driving engagement with the pulley 14.
  • Shaft decoupler joint 10 and pulley 14 and are mounted on first and second ends of a shaft 16, respectively.
  • the second or pulley end of shaft 16 has a rotatable or journal mount.
  • Shaft 16 engages an inner race of ball bearing assembly 18, while an outer race is mounted within base assembly 20.
  • Base assembly 20 is mounted on a fixed location such as the engine block.
  • Base assembly 20 provides radial support but permits some "tilting" of the inner race relative to the outer race to accommodate misalignment of the pulley and shaft.
  • a tensioner 22 is pivotally mounted about the base assembly 20.
  • a spring assembly 24 is mounted between the pivoting arm 26 of tensioner 22 and the base assembly 20.
  • a cylindrical cap 28 extends about the spring 24.
  • Tensioner 22 is designed according to principles well known in the art.
  • the driven device 12 has a rotating shaft 30 on which a connecting bracket is attached for rotating with shaft 30.
  • the shaft decoupler joint 10 is illustrated in greater detail.
  • the shaft decoupler joint 10 is mounted at the first end of shaft 16 and comprises an inner hub 34 having a length L, and a radius R. and an outer hub 36 having a length L, and a radius R 2 . Bonded between inner hub 34 and outer hub 36 is a flexible rubber core 38.
  • inner hub 34 is integral with shaft 16.
  • the pulley 14, shaft 16 and tensioner 22 are mounted on brackets (base assembly 20) allowing the decoupler joint 10 to be adjustable and flexible in the axial direction of the shaft 16.
  • the rubber core 38 is flexible and acts as a universal joint permitting misalignment of the shaft 30 of the driven device 12 and the shaft 16.
  • the shaft driven accessory may also have a pulley mounted on it (at the shaft end or back end) by which to transfer power to a second accessory remotely located. If this is done, then the drive shaft is also serving as a jack-shaft and additional ratios may be realized that are not practical on a single belt. In practice, the maximum practical ratio in automotive accessory drives is about 3 to 1. By jack- shafting, this ratio might be as high as 9 to 1 for light loads requiring high rotational speeds.
  • Flange 40 extends outwardly from outer hub 36. Flange 40 is integral with the outer hub 36. Flange 40 is connected to connecting bracket 32 for transmitting rotation from shaft 16 from driven device 12. Any suitable method may be used to connect the outer hub 36 to the driven device 12. In Figure 1, a series of bolts 42 and rivets 44 circumferentially spaced about flange 40 is used to connect the outer hub 36 to connecting bracket 32.
  • the outer hub is positioned midway along the axial length Lj whereupon molding, the rubber core 38 will have arcuate faces 46.
  • the sizing and selection of the rubber core 38 is made according to the following relations:
  • L - is length of rubber, parallel to axis [in]
  • the ratio between the radius of the outer hub to the radius of the inner hub, R 2 : Raise must be sufficiently large to reduce the resonant frequency of the system below the operating frequency and to minimize fatigue failure.
  • the ratio R 2 : Rj must exceed 2:1, and is preferably about
  • the end of tubing 16 having the decoupler joint 10 has a molded nylon pilot bushing 48 which is inserted in the end of tubing 16.
  • the pilot bushing has a central cavity for receiving a pilot bearing 50.
  • a pilot nut 52 engages driver device shaft 30 for supporting the pilot bushing 48.
  • the pilot bearing 50 provides support for the end of shaft 16 as the shaft rotates, but does not allow the transmission of rotational forces from the shaft 16 to the driven device shaft
  • the pilot bearing 50 is required to provide additional rotational stability to the shaft as it rotates.
  • the pilot bearing is contour to allow a certain small degree of misalignment between the rotation of shaft 16 and the rotation of driven device shaft 30.
  • pulley 14 is mounted for rotation.
  • Shaft 16 has a screw stud 54 press fitted into the end of the tube 16.
  • Screw stud 54 has a central passageway for receiving bolt 56, which has the hex head internally of the tubing 16 and a threaded end. Lock nut 58 is threadingly engaged with the bolt 56 for securing pulley 14 onto bearing assembly 18.
  • Figure 4 illustrates an engine system wherein the decoupler is locked with the engine idling at 750 RPM with maximum accessory load.
  • the strain of the arm of the tensioner for tensioning the accessory belt is dramatic.
  • Figure 5 illustrates the arm strain of the same engine operating at the same speed and load. The arm strain is dramatically reduced to acceptable levels.
  • the inner hub 34 of the decoupler joint 10 is integral with the shaft 30 of the driven device 12.
  • Outer hub 36 is integral with a cylindrical collar 60 which is connected to a rim of pulley 14 by bolts 62.
  • Pulley 14 has an axially extending bearing surface 72.
  • the end of shaft 30 has a threaded bore 64 for receiving bolt 66.
  • Bolt 66 retains a bearing collar 68.
  • Bearing cap 70 extends over bearing collar 68 presenting a bearing surface about which pulley 14 can rotate.
  • Bearing cap 70 is made of a suitable bearing material such as NYLON modified with high molecular weight polyethylene (HDPET).
  • HDPET high molecular weight polyethylene
  • shaft 16 extends axially of the mounting base assembly 20.
  • the decoupler joint 10 is mounted at the first end with inner hub 34 connected to the shaft 16.
  • Pulley 14 has an integral disc 74 which is integral with outer hub 36.
  • Pulley 14 is rotatably mounted on bearing assembly 18.
  • the inner race of bearing assembly 18 is mounted on base assembly 20 which is firmly mounted on the engine block.
  • Shaft 16 is in driving engagement with shaft 30 of the driven device 12.
  • a spline, key and keyway arrangement or threaded engagement may used.
  • the driving force is transmitted from pulley 14 to disc 74, through rubber core 38 to shaft 30.
  • shaft 16 is assembled to pulley 14 and can be sold as a unit.
  • Shaft 16 is rotatably mounted on the inner race of bearing assembly 18 while the outer race is mounted within the base assembly 20 which mounted on the engine block.
  • Inner hub 34 is sized to accommodate shaft 30 of the driven device 12 and the connection of bracket 32 and shaft 30.
  • Connecting bracket 32 is bolted to outer hub 36.
  • Base assembly 20 has suitable openings to permit bolting of outer hub 36 to connecting bracket 32.
  • Base assembly 20 may also be extended as illustrated in broken lines to be capable of mounting the driven device 12. In this manner, the driven device 12 could be assembled with the decoupler for quicker installation on an assembly line.
  • the driven device 12 with decoupler could be properly assembled and aligned away from the assembly line and thus allowing single piece installation.
  • the driving force is transmitted from pulley 14 to shaft 16, through rubber core 38 to connecting bracket 32 to shaft 30.
  • bearing assembly 18 is mounted on a mounting bracket 76 which has an axle 78.
  • Axle 78 has an axially extending passageway 80 to allow access for a hex key to operably engage hex extension 82 which retains the shaft decoupler to the driven device.
  • Mounting bracket 76 is mounted on the engine block.
  • Pulley 14 is mounted on the outer race of the bearing assembly 18. Pulley 14 has an integral disc 74 which is integral with outer hub 36. Inner hub 34 is in driving engagement with shaft 30 of driven device 12.
  • outer hub 36 has a flange 84 for complementarily fitting with the integral disc 74 for connection thereto. A spline or key and keyway arrangement may used.
  • the driving force is transmitted from pulley 14 to disc 74, through rubber core 38 to shaft 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Pulleys (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

Un dispositif de couplage flexible (10) comprend un moyeu interne (34), un moyeu externe (36) et un noyau en caoutchouc (38) tenu entre le moyeu interne (34) et le moyeu externe (36). La longueur axiale (L1) du noyau en caoutchouc (38) à son rayon interne (R1) est supérieure à la longueur axiale (L2) du noyau en caoutchouc (38) à son rayon externe (R2). Le rapport du rayon externe sur le rayon interne est de préférence de 3:1. Les moyeux interne et externe peuvent être reliés entre une poulie (14) et un accessoire entraîné (12). Le couplage d'arbre flexible (10) agit comme amortisseur angulaire et comme joint articulé.
PCT/CA1995/000335 1994-06-28 1995-06-06 Couplage a arbre flexible Ceased WO1996000856A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP95942627A EP0828953A1 (fr) 1994-06-28 1995-06-06 Accouplement d'arbres flexible
JP8502666A JPH10502157A (ja) 1994-06-28 1995-06-06 フレキシブルシャフトカプリング

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9412928.5 1994-06-28
GB9412928A GB9412928D0 (en) 1994-06-28 1994-06-28 Shaft decoupling device

Publications (1)

Publication Number Publication Date
WO1996000856A1 true WO1996000856A1 (fr) 1996-01-11

Family

ID=10757431

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA1995/000335 Ceased WO1996000856A1 (fr) 1994-06-28 1995-06-06 Couplage a arbre flexible

Country Status (5)

Country Link
EP (1) EP0828953A1 (fr)
JP (1) JPH10502157A (fr)
CA (1) CA2192217A1 (fr)
GB (1) GB9412928D0 (fr)
WO (1) WO1996000856A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0889261A1 (fr) * 1997-07-01 1999-01-07 Martin Family Trust Dispositif rotatif orientable relié flexiblement à l'arbre d'entraínement
US7416073B1 (en) 2007-02-09 2008-08-26 Geo. M. Martin Company Diverting flat belt support system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6117468B2 (ja) * 2011-12-06 2017-04-19 東洋ゴム工業株式会社 分割型ゴム継手

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE416872A (fr) *
GB875413A (en) * 1958-12-30 1961-08-16 Gelenkwellenbau Gmbh Improvements in or relating to couplings
GB907740A (en) * 1959-09-10 1962-10-10 Auto Union Gmbh Improvements in dynamo assemblies
FR2083817A5 (fr) * 1970-03-11 1971-12-17 Lohmann & Stolterfoht Ag
US3952546A (en) * 1974-08-23 1976-04-27 Kawasaki Jukogyo Kabushiki Kaisha Elastic coupling
WO1991010075A1 (fr) * 1989-12-26 1991-07-11 Dyneer Corporation Embrayage centrifuge pourvu d'un amortisseur de vibrations
DE4035583A1 (de) * 1990-11-08 1992-05-14 Audi Ag Anordnung eines generators am maschinengehaeuse einer brennkraftmaschine
US5219273A (en) * 1992-05-29 1993-06-15 General Motors Corporation Torsional damper for air conditioning compressor
EP0553471A2 (fr) * 1992-01-25 1993-08-04 Robert Bosch Gmbh Transmission à courroie pour machines électriques

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE416872A (fr) *
GB875413A (en) * 1958-12-30 1961-08-16 Gelenkwellenbau Gmbh Improvements in or relating to couplings
GB907740A (en) * 1959-09-10 1962-10-10 Auto Union Gmbh Improvements in dynamo assemblies
FR2083817A5 (fr) * 1970-03-11 1971-12-17 Lohmann & Stolterfoht Ag
US3952546A (en) * 1974-08-23 1976-04-27 Kawasaki Jukogyo Kabushiki Kaisha Elastic coupling
WO1991010075A1 (fr) * 1989-12-26 1991-07-11 Dyneer Corporation Embrayage centrifuge pourvu d'un amortisseur de vibrations
DE4035583A1 (de) * 1990-11-08 1992-05-14 Audi Ag Anordnung eines generators am maschinengehaeuse einer brennkraftmaschine
EP0553471A2 (fr) * 1992-01-25 1993-08-04 Robert Bosch Gmbh Transmission à courroie pour machines électriques
US5219273A (en) * 1992-05-29 1993-06-15 General Motors Corporation Torsional damper for air conditioning compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0889261A1 (fr) * 1997-07-01 1999-01-07 Martin Family Trust Dispositif rotatif orientable relié flexiblement à l'arbre d'entraínement
US6000531A (en) * 1997-07-01 1999-12-14 Martin Family Trust Steerable rotary device
US7416073B1 (en) 2007-02-09 2008-08-26 Geo. M. Martin Company Diverting flat belt support system

Also Published As

Publication number Publication date
CA2192217A1 (fr) 1996-01-11
EP0828953A1 (fr) 1998-03-18
JPH10502157A (ja) 1998-02-24
GB9412928D0 (en) 1994-08-17

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