Patent Abstract:
Power drivers are commonly used in production to tighten fasteners such as nuts and bolts. The socket which engages the fastener is normally coupled to the drive shaft of the power driver by a square male end on the drive shaft and a complementary square female connector on the socket. These components are not produced to close tolerances and as a result there is substantial play permitting misalignment of the rotational axes of the drive shaft and the socket and some rotational freedom between the drive shaft and the socket. In accordance with the invention an anti-vibration adaptor is provided comprising a sleeve containing a cylinder of resilient material which surrounds a portion of the drive shaft and a portion of the socket, including the point of coupling, sufficiently closely to minimize misalignment of the rotational axes of the drive shaft and the socket and reduce rotational freedom.

Full Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application is a division of application Ser. No. 09/270,799, filed Mar. 17, 1999, now U.S. Pat. No. 6,123,157, a continuation-in-part of U.S. patent application Ser. No. 08/843,613 filed Apr. 10, 1997, now abandoned, which is a continuation-in-part of application Ser. No. 08/510,364 filed Aug. 2, 1995, now abandoned. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to anti-vibration adaptors. More specifically, the present invention relates to anti-vibration adaptors which, when employed in conjunction with standard powered fastener drivers and socket-type driven heads, increases the torque transmitted to a fastener and decreases vibration experienced by the fastener driver which is subsequently transmitted to the operator. 
     DESCRIPTION OF THE PRIOR ART 
     Power fastener drivers such as pneumatic or electric powered pulse and/or impact wrenches as well as anglehead and/or straight nut runners, 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, airline connections and a drive shaft which removably connects with any one of a plurality of driver heads and/or drive shaft extensions. 
     The driver heads comprise a plurality of various sized Imperial or SAE type sockets and screwdriver fittings, herein referred to as sockets, all of which are used to drive or “run down” a variety of fasteners including nuts and bolts. The variety of sockets available varies with the head style of the fastener. For example, while hexagonal type bolt heads are common, Allen-type and Torx-head bolts are are also used extensively in the automobile industry in a variety of sizes. Typically, the connection between the driver and the socket is accomplished via a male square drive connector on the drive shaft of the driver and a complementary female square drive connector on the socket which may be snapped together and retained by a spring pin disposed through the surface of the male square drive connector. However, other snap-on connector profiles are available which are equally effective. Generally these tools are designed to enable the operator to change sockets quickly depending on the size or head style of the fastener to be run-down, hence the popularity of these types of snap-on connections. However, due to the frequency of socket changes and the fact that the sockets are mass produced items, the majority of these types of drivers and sockets, including automotive industrial grade tooling, are not designed to close tolerances and have relatively large mating clearance. In most instances the resulting connection between the driver and the socket will suffer from two degrees of freedom, first the socket will be free to rotate a few degrees relative to the rotational position of drive shaft and second the rotational axis of the socket will be free deviate a few degrees from the rotational axis of the drive shaft. 
     In operation, deviation of the rotational axis of the socket from the rotational axis of the drive shaft will result in a circular motion of the end of the drive shaft and vibration of the driver. The relative freedom of rotation of the socket with respect to the drive shaft, particularly when the driver is an impact or pulsing driver, results in vibration of the driver and socket components relative to each other. Consequently, the tool operator is exposed to these vibrations which are transferred through the tool to the operator&#39;s hands and arms. In an environment such as the automotive industry where a typical assembly worker&#39;s primary function is to operate these drivers, these vibrations can cause serious physical injury. Further, the vibrations result in substantially elevated noise levels which can result in the operator suffering from permanent hearing loss if exposed for sufficient periods of time. 
     These vibrations have other detrimental effects. In particular, excessive vibration can cause premature breakdown of the internal bearings of the driver. Further, in many circumstances, such as the production of automobiles, fasteners are designed to be installed with a specific torque to which the drivers are preset. The vibrations result in losses in torque applied to the fastener which consequently results in fasteners not tightened to specification during production which results in poor statistical process control. 
     Overall 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 reduces vibration when employed with a standard driver and socket. 
     SUMMARY OF THE INVENTION 
     It is an object of the present invention to provide a novel anti-vibration which mitigates at least one of the above described disadvantages of the prior art. 
     According to one aspect of the invention there is provided an anti-vibration adaptor for use with a standard releasable connection between the drive shaft of a driver and a socket the adaptor comprising: a housing which extends at least partially over both said drive shaft and said socket; a damping means disposed within said housing surrounding, but not intervening between the parts said releasable connection and enclosing at least a portion of said drive shaft and said socket with negligible clearance such that any misalignment of the rotational axes of the drive shaft and said socket is minimized. 
     According to another aspect of the present invention there is provided an anti-vibration adaptor for use with a driver having a drive shaft and socket coupled to said drive shaft through a releasable connection the adaptor comprising: a hollow cylindrical housing for enclosing said releasable connection and extending at least partially over both said drive shaft and said socket; damping means disposed in said housing having a first bore disposed in one of its ends, coaxially aligned and in communication with a second bore disposed in its opposite end; said first bore having a diameter to permit it to releasably receive a cylindrical portion of said drive shaft with negligible clearance or limited interference and said second having a diameter to permit it to releasably receive a cylindrical portion said socket with negligible clearance or limited interference whereby misalignment of the axes of rotation of said drive shaft and said socket is minimized and rotation of said drive shaft with respect said socket is inhibited. 
     The present invention further includes an anti vibration adaptor for use in association with a driver having a drive shaft releasably secured by a coupling to an extension shaft comprising: a housing which extends over said coupling and over at least a portion of said drive shaft and said extension shaft, said housing enclosing damping means which surrounds, but does not intervene between, said portions of said drive shaft and said extension shaft, with negligible clearance or slight interference. 
     Preferably said damping means is formed from Ultra High Molecular Weight (UHMW) polyethylene. 
     In accordance with the present invention the housing is preferably in the form of a hollow cylinder formed from any one of steel, stainless steel, aluminum, copper, brass, cast iron, and titanium, fibreglass, carbon fibre composites and plastics. 
     The present invention includes anti-vibration adaptors which fit tightly over both that portion of the socket that contains the releasable connection and a portion of the drive shaft, but does not intervene between the drive shaft and the socket, thereby substantially eliminating axial misalignment of the rotational axis of the socket and the rotational axis of the drive shaft and additionally inhibiting rotational movement of the drive shaft with respect to the socket. 
     Advantages of the present invention include an anti-vibration adaptor which tightly fits over the conventional joint between a drive shaft on a fastener driver and a driver head thereby eliminating any run-out in the joint. 
     Advantages of the present invention include reduction of vibration due to misalignment of the rotational axes of the drive shaft and the socket and/or rotational movement of the drive shaft with respect to the socket. 
     Another advantage of the present invention is that reduction of misalignment of the rotational axis of the drive shaft and the rotational axis of the socket, reduces torque lost due to such misalignment significantly and errors of torque measurement caused by vibration from axial misalignment or from freedom of the drive shaft to rotate with respect to the socket are also reduced. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Presently preferred embodiments of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which: 
     FIG. 1 shows an exploded view of a pulse wrench, a socket and a section of an anti-vibration adaptor in accordance with an embodiment of the present invention. 
     FIG. 2 shows a sectional view of a socket mounted on one end of a conventional extension shaft and held in alignment by an anti-vibration adaptor. with the other end of the extension shaft connected to a drive shaft and held in alignment by a further anti-vibration adaptor. 
     FIG. 3 shows a perspective view of a right angle tool fitted with a tool mounted anti-vibration adaptor and an extension shaft in accordance with a second embodiment of the present invention. 
     FIG. 4 shows a sectional view of the tool mounted anti-vibration adaptor of FIG. 3 taken along section line  4 — 4 . 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     An anti-vibration adaptor in accordance with the present invention is shown in FIG.  1  and is indicated generally at  10 . Adaptor  10  generally comprises a housing  14 , a damping means, which in the present 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 . The size of both ends of the damping sleeve is preferably such as to produce a slight interference fit. The resulting fit may be termed a slip fit. Because of the resilience of the material of the damping sleeve the driver and socket may be assembled or disassembled by hand but the interference inhibits rotary motion between the adaptor, socket and the shaft. Pulse wrench  38  may be any conventional pneumatic or electric driver as, previously described, which typically accommodates ¼″, ⅜″or ½″ square or hexagonal drive type sockets  42 . However, adaptor  10  may be sized to accommodate smaller or larger type socket wrench systems with a variety of drive configurations. It will be noted that the adaptor does not replace the standard coupling between the drive and the socket but merely surrounds it. 
     Housing  14  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 . Preferably, damping sleeve  18  is formed from Ultra High Molecular Weight polyethylene (UHMW) such as that manufactured by the Cadillac Plastic &amp; Chemical Company of Troy, Mich., in the United States. UMHW is presently preferred as it provides a high degree of abrasion resistance and has a relatively low coefficient of friction which provides for a longer life cycle and good vibration damping properties. 
     First bore  54  has a diameter which is selected to provide minimal clearance or a slight interference around the cylindrical portion of square drive  34  and shaft  30  of pulse wrench  38  and is of a length which allows square drive  34  to pass into the second bore  58 . Second bore  58  is sized to removably receive the cylindrical portion of socket  42 , preferably with a slight interference , and to permit engagement of the socket with the square drive  34  in the conventional manner. The diameter of bores  54  and  58  is preferably such as to produce a slip fit, as earlier defined, between the adaptor and shaft  30  and the adaptor and the socket  42 . As shown in FIG. 1, 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 rotationally locate adaptor  10  relative to socket  42  is provided. 
     In the presently preferred embodiment the means to rotationally locate the adaptor relative to the socket 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 enter a bored hole  74 , dimple or retaining groove on socket  42 . It is contemplated that other means of locating 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. or any other means which inhibits rotation of the socket relative to the adaptor. 
     To employ the present invention, socket  42  is pressed through end  26  into bore  58  until it is firmly seated against seat  62 . Grub screw  70  is then screwed through threaded bored hole  74 , until socket  42  is secured in place. Adaptor  10 , disposed over socket  42  is then placed onto pulse wrench  38  by pressing 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 fit between shaft  30  and, first bore  54  provides negligible clearance or preferably a slight interference as does the fit between socket  42  and second bore  58 . Consequently the adaptor  10  surrounds the conventional square drive joint between socket  42  and shaft  30  and minimizes any rotational axis misalignment of these two elements and additionally inhibits rotational motion of the socket  42  relative to shaft  30 . 
     In operation the damping sleeve  18  serves several purposes. First, as it fits tightly around both shaft  30  and socket  42  axial misalignment is minimized. This reduces vibration of the driver and more torque is transferred to the socket  42 . Second, the tight fit inhibits relative rotational motion between the drive shaft  30  and socket  42  which is particularly important when the driver is an impact or pulse driver. Thirdly, the UHMW material used in sleeve  18  absorbs a portion of any vibration which is created thus reducing any vibration transmitted to the driver and experienced by the operator. 
     As shown in FIG. 2, when pulse wrench  38  is used in conjunction with a shaft extension  100 , additional vibration reduction can be achieved by using a second anti-vibration adaptor  104 . 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. In this embodiment, the 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 enter a bored hole  112 , dimple or retainer groove on the female end  108  of shaft 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 . In practice, 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 FIG.  2 . However it is contemplated that it is possible to size bore  58  with a small clearance or very slight interference and so create a releasable connection between female end  108  and second bore  58 . Provided that any clearance maintains a connection with minimum rotational axis misalignment the anti-vibration characteristics of adaptor  104  will not be unduly compromised. 
     First bore  54  is sized to receive shaft  30  removably and square drive  34  in a manner substantially identical to the connection of adaptor  10  and pulse wrench  38  of FIG.  1 . 
     Similarly adaptor  10  and socket  42  mounted therein installs to male end  110  of extension shaft  100  in a manner identical to the installation of the adaptor to pulse wrench  38 , as described with respect to FIG.  1 . 
     Performance testing of adaptors  10  and  104  was performed using a 12 mm socket, a 6″ extension shaft mounted onto a Uryu UX500 Pulse wrench having a ⅜″ square drive. The socket, extension shaft were all new and the pulse wrench was rebuilt to new conditions. Comparison measurements for torque and vibration were made with this configuration with and without adaptors  10  and  104 . The test was conducted in an automotive production environment, specifically a bumper installation application, in which five fastener run-downs were required per vehicle. Initial torque settings for each pulse wrench were made with a Uryu UET200 torque setting tool. Torque measurements were made prior to installation using a Tonichi torque wrench. Vibration measurements were made at the pulse wrench using a SKF CMVP20 Vibration Check Unit. 
     The results obtained were as follows. Initial measurements of the pulse wrench were conducted with the torque set at 200 kgf-cm indicated a 32.14% increase in static torque measured on the fastener and a 97.35% decrease in vibration at the tool when adaptors  10  and  104  were used compared to the control case without adaptors  10  and  104 . 
     After 50,000 fastener run-downs, to determine the effect of wear on the results, measurements conducted with the torque set at 250 kgf-cm indicated a 21% increase in static torque measured on the fastener and a 94.2% decrease in vibration at the tool when adaptors  10  and  104  were used compared to the control case without adaptors  10  and  104 . 
     These tests were again performed after 225,000 fastener run-downs, with measurements conducted with the torque set at 220 kgf-cm and a 12.5% increase in torque was measured on the fastener and a 95.9% decrease in vibration at the tool was measured when adaptors  10  and  104  were used as compared to the control case without adaptors  10  and  104 . 225,000 run-downs is representative of the full life of adaptors  10  and  104 . These results clearly indicate that significant increases in torque and decreases in vibration experienced by the operator can be achieved when adaptors  10  and  104  are employed. 
     A similar test was performed using the above-identified equipment but instead using a single adaptor mounted directly on the pulse wrench with no shaft extension in place. The results indicated a 92.35% reduction of vibration at the tool and an increase in fastener torque of 18.2%. 
     In some situations it has been found advantageous to employ an anti-vibration adaptor which physically mounts to the body of the tool. 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. However, tool  200  may be any suitable straight nutrunner, multi-head driver or similar tool as previously described. Adaptor  204 , as seen in section in FIG. 4, generally comprises a housing  208  having a pair of ends  212  and  216 , a bearing  220  and a damping means which, in the 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 with respect to FIG. 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. Other tool 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 skilled 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 square drive  234  in the 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  and  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 purpose 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 one end which cannot pass through bearing  220  and a smaller shoulder  261  at the other end which can be forced through bearing  220 . The spacing between shoulders  261  and  262  substantially corresponds to the longitudinal length of the inner diameter of bearing  220 . Damping sleeve  224  is press-fitted into bearing  220  so that shoulders  261  and  262  abut bearing  220  to maintain damping sleeve  224  in place. As with other previously described damping sleeves, 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. 
     In operation, female end  108  of extension shaft  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. 
     In addition to adaptor  204 , 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 increased the torque transmitted to shaft  100  in a manner similar to that described above in regard to adaptor  10 . 
     The present invention has been described with reference to a presently preferred embodiment. Other variations and embodiments of the present invention may be apparent to those of ordinary skill, in the art. It is emphasized ,however, that the adaptor is not a replacement for the conventional driver socket coupling but is employed as an auxiliary device which improves the operation of the coupling. Accordingly, the scope of protection sought for the present invention is only limited as set out in the attached claims.

Technology Classification (CPC): 8