WO1996021113A1 - Adaptateur anti-vibrations - Google Patents

Adaptateur anti-vibrations Download PDF

Info

Publication number
WO1996021113A1
WO1996021113A1 PCT/CA1995/000732 CA9500732W WO9621113A1 WO 1996021113 A1 WO1996021113 A1 WO 1996021113A1 CA 9500732 W CA9500732 W CA 9500732W WO 9621113 A1 WO9621113 A1 WO 9621113A1
Authority
WO
WIPO (PCT)
Prior art keywords
fastener
vibration
housing
resilient damping
driving
Prior art date
Application number
PCT/CA1995/000732
Other languages
English (en)
Inventor
George Edward Barnes
Original Assignee
1134564 Ontario 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
Priority claimed from CA 2134949 external-priority patent/CA2134949A1/fr
Priority claimed from CA 2135947 external-priority patent/CA2135947A1/fr
Application filed by 1134564 Ontario Inc. filed Critical 1134564 Ontario Inc.
Priority to AU42958/96A priority Critical patent/AU4295896A/en
Publication of WO1996021113A1 publication Critical patent/WO1996021113A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F3/00—Associations of tools for different working operations with one portable power-drive means; Adapters therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass

Definitions

  • the present invention relates to anti-vibration adaptors. More specifically, the present invention relates to anti-vibration adaptors which, when employed in conjunction with powered fastener drivers and socket-type driven heads, increase torque transmitted to a fastener and decreases vibration experienced by the fastener driver which is subsequently transmitted to an operator.
  • Power fastener drivers such as pneumatic or electric powered pulse and/or impact wrenches as well as anglehead and/or straight nutrunners, referred to herein simply as drivers, are well known in industrial environments. In particular, in the automotive industry, these types of drivers are used extensively in the assembly of automobiles. Typically, such drivers comprise a pistol or club-style main body, a trigger, air line connections and a drive shaft which removably connects with a plurality of driver heads and/or extension shafts.
  • the driver heads comprise a plurality of various sized Imperial or SAE type sockets and screwdriver fittings, herein referred to simply as sockets, all of which are used to drive, or "run-down" a variety of fasteners including nuts and bolts.
  • the variety of the sockets available also varies with the head style of the fastener.
  • hexagonal type bolt heads are common, Allen-type bolts and Torx*-head bolts are also used extensively in the automotive industry in a variety of sizes.
  • the connection between the driver and the socket is accomplished via a female square drive connector on the socket and a complementary male square drive connector on the driver which may be snapped together by means of a spring pin disposed through the surface on the male square drive connector.
  • the run-out in the connections, the speed of rotation and the pulsing or impacting action of the wrench results in vibration of the driver and socket components relative to each other. Consequently, the tool operator is exposed to this vibration which is transferred through the tool to the operator's hands and arms. In an environment such as the automotive industry where a typical assembly worker's primary function is to operate these drivers, this vibration can cause serious physical injury. Further, the vibration results in substantially elevated noise levels which can result in the operator suffering permanent hearing loss if exposed for sufficient periods of time.
  • Vibration resulting from this run-out has other detrimental effects.
  • excessive vibration can cause premature break down of the internal bearings in the wrenches which reduces driver life.
  • fasteners are designed to be installed with a specified torque to which the drivers are preset.
  • the above-described vibration results in losses in torque which consequently result in fasteners which are not tightened to specification during production and/or which results in poor statistical process control.
  • the above-identified disadvantages of typical socket-driver connections result in torque losses, quality control and operator health problems which increase manufacturing costs and/or reduce final product quality. Therefore, there is a long standing need in industry for an apparatus which improves the above-identified socket-driver connections to substantially reduce run-out.
  • an anti-vibration adaptor for use with a connection between a driving means and a driven member, comprising: a resilient damping means to encompass said connection between the driving means and the driven member, the resilient damping means receiving each of the driving means and the driven member with negligible clearance to reduce run-out which would otherwise occur in the connection; and, a housing within which the resilient damping means is substantially disposed.
  • a fastener driving tool comprising: a fastener driver including a driving means; a fastener driving head connected to said driving means; a housing; a resilient damping means disposed in said housing and having a first bore disposed in one end and a second bore disposed at an opposing end, said first and second bores being coaxially aligned and in communication, said first bore receiving an end of said driving means distal said fastener driver with negligible clearance and said second bore receiving said fastener driving head with negligible clearance such that said connection therebetween is disposed within said resilient damping means to reduce run-out which would otherwise occur in said connection.
  • the resilient damping means the present invention comprises a sleeve having a first bore which receives at least a portion of the driving means and a coaxially aligned second bore which receives at least a portion of the driven member.
  • the driving means used in the present invention is a fastener driver.
  • the housing of the present invention comprises a bearing, the bearing acting between part of the fastener driver and the resilient damping means such that the resilient damping means is rotatable with respect to the fastener driver.
  • the driven means used with the present invention comprises a female receptacle to receive one of a fastener driving head and an extension shaft.
  • Figure 1 shows an exploded assembly of a pulse wrench, a socket and a section of an anti-vibration adaptor in accordance with an embodiment of the present invention
  • Figure 2 shows a section view of the anti-vibration adaptor of Figure 1 mounted to the socket and connected to one end of a conventional extension shaft, the extension shaft having a second anti-vibration adaptor mounted to an opposing end thereof;
  • Figure 3 shows a perspective view of a right angle tool fitted with the anti-vibration adaptor of Figure 1 and a tool mounted anti-vibration adaptor in accordance with a second embodiment of the present invention.
  • Figure 4 shows a section view of the tool mounted anti-vibration adaptor of Figure 3 taken along line 4-4.
  • Adaptor 10 generally comprises a housing 14, a resilient damping means, which in the presently preferred embodiment comprises a damping sleeve 18 having a pair of ends 22 and 26. End 22 is sized to engage a shaft 30 and square drive 34 of a conventional driver such as pulse wrench 38 while end 26 is sized to engage a conventional socket 42.
  • Pulse wrench 38 may be any conventional pneumatic or electric driver, as previously described, which typically accommodates - " ,
  • adaptor 10 may be sized to accommodate smaller or larger type socket wrench systems with a variety of drive configurations.
  • Housing 14 is generally cylindrical, annular in cross-section and preferably is formed from stainless steel or aluminum having generally smooth inner and outer diameters 46 and 50 respectively. However, it is contemplated that housing 14 may be formed from any suitable material such as steel, brass, copper, titanium, cast iron, composites such as fibreglass or carbon fibre and plastics.
  • Damping sleeve 18, is provided with an outer diameter which is sized for interference press fit engagement with inner diameter 46 of housing 14 and is of a length which is substantially equal to the length of housing 14. Damping sleeve 18 is provided with a centrally located, longitudinal first bore 54, located adjacent end 22 and in communication with a longitudinal second bore 58 adjacent end 26, coaxially aligned with first bore 54.
  • damping sleeve 18 is formed from Ultra High Molecular Weight polyethylene (UHMW) such as that manufactured by the Cadillac Plastic & Chemical Company, (CADCOJ* of Troy Michigan, in the United States.
  • UHMW Ultra High Molecular Weight polyethylene
  • CADCOJ* Cadillac Plastic & Chemical Company
  • First bore 54 has a diameter which is selected to provide minimal clearance around square drive 34 and shaft 30 of pulse wrench 38 and is of a length which allows square drive 34 to pass into second bore 58.
  • Second bore 58 is sized to removably receive socket 42 and to permit engagement of the socket with square drive 34 in a conventional manner.
  • the diameter of second bore 58 is such that a seat 62 is formed at the junction of first bore 54 and second bore 58 which serves to locate socket 42 when positioned therein.
  • a means to fix adaptor 10 relative to socket 42 is provided.
  • the means to fix is at least one threaded bore 66 which passes radially through housing 14 and damping sleeve 18 to second bore 58 and is longitudinally positioned to permit a grub screw 70 or other suitable fastener, threaded therein, to engage a bored hole 74, dimple or retaining groove on socket 42. It is contemplated that other means of fixing adaptor 10 relative to socket 42 may also be employed, such as high strength glue, a key groove cut into socket 42 with a complementary key ridge in bore 58 etc.
  • socket 42 is placed through end 26 into second bore 58 until it is seated firmly against seat 62. Grub screw 70 is then screwed through threaded bore 66 to engage bored hole 74, thereby securing socket 42 in place.
  • Adaptor 10, disposed over socket 42, is then placed onto pulse wrench 38 by inserting square drive 34 and shaft 30 into end 22 and first bore 54. Square drive 34 passes through first bore 54 and engages a complementary female connector 78 on the rear face of socket 42 in a conventional manner.
  • a spring retainer 35 disposed through the surface of square drive 34, retains socket 42 also in a conventional manner. When fully assembled, the clearance between shaft 30 and first bore 54 is negligible as is the clearance between socket 42 and second bore 58. Consequently, adaptor 10 surrounds the conventional square drive joint between socket 42 and square drive 34.
  • damping sleeve 18 serves two purposes. First, as bore 54 is sized with negligible clearance to square drive 34 and shaft 30 and bore 58 is sized with negligible clearance to socket 42, run-out at the removable connection is reduced. The reduction in run-out results in less vibration being produced by the connection and more torque being transferred to socket 42.
  • the UHMW material used in damping sleeve 18 absorbs a portion of the vibration which is created, thus damping the vibration that is experienced by the driver and which gets transmitted to the tool operator.
  • Shaft extension 100 is of the conventional type and is provided with a square drive connector female end 108 and a square drive connector male end 110.
  • Adaptor 104 is substantially similar to adaptor 10, like elements being indicated with primed numerals.
  • second bore 58' is sized to accommodate female end 108 and threaded bore 66' is positioned along housing 14' such that grub screw 70' will engage with a bored hole 112, dimple or retainer groove on female end 108 of sliaft extension 100.
  • Second bore 58' is sized to create an interference fit when placed over female end 108 with negligible clearance thereby establishing a fixed connection between adaptor 104 and shaft extension 100.
  • engagement of adaptor 104 and shaft extension 100 is .accomplished by lightly press fitting the components together. This is achieved by pressing second bore 58' of adaptor 104 over female end 108 until in a fully seated position as indicated in Figure 2.
  • second bore 58' with a small clearance to create a releasable connection between female end 108 and second bore 58'. Provided that this clearance maintains a connection which is substantially free from any run-out, the anti- vibration characteristics of adapter 104 should not be unduly compromised.
  • First bore 54' is preferably sized to removably receive shaft 30 and square drive 34 in a manner substantially identical to the connection of adaptor 10 and pulse wrench 38 of Figure 1.
  • adaptor 10 and socket 42 mounted therein installs to male end 110 of extension shaft 100 in an manner identical to the installation of the adaptor to pulse wrench 38, as described with respect to Figure 1.
  • FIG. 3 shows such a situation in which an anti-vibration adaptor, generally indicated at 204 is directly mounted to a tool 200 which for example purposes, is illustrated as a right angle tool.
  • tool 200 may be any suitable straight nutrunner, multi-head driver or similar tool as previously described.
  • Adaptor 204 as seen in section in Figure 4, generally comprises a housing 208 having a pair of ends 212 and 216, a bearing 220 and a damping means, which in the presently preferred embodiment comprises a damping sleeve 224.
  • Housing 208 is generally cylindrical and annular in cross-section and preferably formed from stainless steel or aluminum although other materials such as the above-described materials with respect to Figure 1 may be employed. Housing 208 adjacent end 216 is provided with a first bore 228 which is sized to removably engage a body portion 232 of tool 200, centered about a square drive 234. Housing 208 is secured to tool 200 using suitable fixing means, such as three grub screws 236 circumferentially spaced 120° apart. For other tools fixing means may be a threaded portion on housing 208 which engages a complementary threaded portion on tool 200 or any other suitable method of fixing adaptor 204 to tool 200 as would occur to those of skill in the art.
  • a longitudinally oriented second bore 240 is located in a mid portion of housing 208 and is coaxially aligned and in communication with first bore 228. Second bore 240 is sized to freely accommodate shaft extension 100 which mounts to a square drive 234 in a conventional manner.
  • a longitudinal third bore 244 is coaxially aligned and in communication with second bore 240, adjacent end 212.
  • Third bore 244 is sized to accommodate bearing 220 which abuts a seat 248 formed at the union of second and third bores 240, 244 respectively.
  • a groove 252 is provided in the wall of third bore 244 adjacent bearing 220 which receives a snap ring 254 for the purposes of retaining bearing 220 in position.
  • Damping sleeve 224 is an annular member which is provided with an outer diameter sized for an interference press-fit engagement with the inner diameter of bearing 220.
  • the outer diameter of damping sleeve 224 includes a shoulder 262 at each longitudinal end. The spacing between shoulders 262 substantially corresponding to the longitudinal length of the inner diameter of bearing 220. Damping sleeve 224 is press-fit into bearing 220 such that shoulders 262 abut bearing 220 to maintain damping sleeve 224 in place.
  • damping sleeve 224 is preferably formed from UHMW such as that manufactured by CADCO* which offers a relatively high degree of abrasion resistance and a relatively low coefficient of friction. Damping sleeve 224 has an inner diameter 258 which is sized to fit around shaft extension 100 with negligible clearance.
  • female end 108 of shaft extension 100 is fitted to square drive 234 of tool 200 and is retained by a conventional spring pin 235.
  • Male end 110 of shaft extension 100 is pressed through inner diameter 258 of damping sleeve 224 until first bore 232 slides over and is seated on tool housing 228. Once seated, grub screws 236 are tightened onto tool 200 to secure adaptor 204 in place.
  • tool 200 may also preferably employ adaptor 10 at socket 42. In either case, adaptor 204 reduces the vibration experienced by the tool operator and increases the torque transmitted to shaft 100 in a manner similar to that described above in regard to adaptor 10.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)

Abstract

Adaptateur anti-vibrations comportant un manchon amortisseur de vibrations et résistant à l'usure monté par-dessus le raccord amovible traditionnel entre une clé à douille et une clé d'entraînement. Cet adaptateur assure une réduction sensible du desserrement qui caractérise les raccords à douille traditionnels où l'accouplement est relativement peu serré et où des vibrations trop importantes et des pertes de couple sont susceptibles de se produire. Par conséquent, ledit adaptateur assure une augmentation sensible du couple imprimé à un organe de fixation, et une réduction sensible des vibrations subies par l'opérateur, ce qui améliore la qualité des organes mis en place tout en réduisant le risque de blessure de l'opérateur.
PCT/CA1995/000732 1994-12-29 1995-12-29 Adaptateur anti-vibrations WO1996021113A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU42958/96A AU4295896A (en) 1994-12-29 1995-12-29 Anti-vibration adaptor

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CA 2134949 CA2134949A1 (fr) 1994-12-29 1994-12-29 Adaptateurs de securite
CA2,134,949 1994-12-29
CA2,135,947 1995-03-16
CA 2135947 CA2135947A1 (fr) 1995-03-16 1995-03-16 Dispositif de securite
US51036495A 1995-08-02 1995-08-02
US08/510,364 1995-08-02

Publications (1)

Publication Number Publication Date
WO1996021113A1 true WO1996021113A1 (fr) 1996-07-11

Family

ID=27169887

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA1995/000732 WO1996021113A1 (fr) 1994-12-29 1995-12-29 Adaptateur anti-vibrations

Country Status (2)

Country Link
AU (1) AU4295896A (fr)
WO (1) WO1996021113A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005107982A1 (fr) * 2004-05-07 2005-11-17 Mircona Ab Porte-outil dote d'un moyen d'amortissement des vibrations et procede de fabrication correspondant
US8020474B2 (en) 2004-02-03 2011-09-20 Microna Ab Vibration-damped tool holder
CN103537728A (zh) * 2013-10-10 2014-01-29 陕西航天导航设备有限公司 一种在铝基复合材料上加工小孔的方法
DE102008040047B4 (de) * 2007-07-10 2019-09-19 Private Brand Tools (Australia) Pty Ltd Zahnradpumpe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2464381A (en) * 1947-06-12 1949-03-15 Williams J H & Co Coupling
US2704681A (en) * 1952-08-28 1955-03-22 R fischer
US3312260A (en) * 1965-04-02 1967-04-04 Arden B Macneill Socket type adapter for torquetransmitting tools
US3463048A (en) * 1967-08-17 1969-08-26 Lovejoy Tool Co Inc Vibration damping device for milling cutters
GB2081613A (en) * 1980-07-31 1982-02-24 Illinois Tool Works Attachment of drill bits and drivers to power tools
US5050446A (en) * 1987-01-28 1991-09-24 Sanshin Kogyo Kabushiki Kaisha Vibration and torsional damping coupling for a power transmission

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2464381A (en) * 1947-06-12 1949-03-15 Williams J H & Co Coupling
US2704681A (en) * 1952-08-28 1955-03-22 R fischer
US3312260A (en) * 1965-04-02 1967-04-04 Arden B Macneill Socket type adapter for torquetransmitting tools
US3463048A (en) * 1967-08-17 1969-08-26 Lovejoy Tool Co Inc Vibration damping device for milling cutters
GB2081613A (en) * 1980-07-31 1982-02-24 Illinois Tool Works Attachment of drill bits and drivers to power tools
US5050446A (en) * 1987-01-28 1991-09-24 Sanshin Kogyo Kabushiki Kaisha Vibration and torsional damping coupling for a power transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8020474B2 (en) 2004-02-03 2011-09-20 Microna Ab Vibration-damped tool holder
WO2005107982A1 (fr) * 2004-05-07 2005-11-17 Mircona Ab Porte-outil dote d'un moyen d'amortissement des vibrations et procede de fabrication correspondant
US8240961B2 (en) 2004-05-07 2012-08-14 Mircona Ab Tool holder with vibration damping means and a method for manufacturing the same
DE102008040047B4 (de) * 2007-07-10 2019-09-19 Private Brand Tools (Australia) Pty Ltd Zahnradpumpe
CN103537728A (zh) * 2013-10-10 2014-01-29 陕西航天导航设备有限公司 一种在铝基复合材料上加工小孔的方法

Also Published As

Publication number Publication date
AU4295896A (en) 1996-07-24

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