Patent Document

BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The field of the present invention relates generally to flexible shaft couplings, more particularly to bellows style flexible shaft couplings, and most specifically to bellows style flexible shaft couplings further possessing an elastomeric covering. 
     2. Discussion of the Prior Art 
     Bellows style flexible shaft couplings are considered to be well known in the art. The annular convolutions of a relatively thin sheet of metal formed into a generally cylindrical shape provide torsional rigidity and longitudinal flexibility. Angular misalignments of up to half a degree are accommodated. U.S. Pat. No. 3,232,076 issued Feb. 1, 1966 to Sundt is an example. Torsional wind-up, i.e. backlash, is considered a problem with increased torsional load. 
     Rubber or elastomer sleeve shaft connectors are also known. U.S. Pat. No. 2,170,627 issued Aug. 22, 1939 to Berryman, U.S. Pat. No. 2,171,999 issued Sep. 5, 1939 to Weiland and U.S. Pat. No. 2,195,993 issued to Morrill are examples, respectively, of uniform cylindrical, medially enlarged, and medially concave configurations. Vulcanized rubber elements attached at either end to metal shaft bosses generally characterize these couplings. Rubber boots disposed loosely about, i.e. spaced apart from, metal shaft couplings are also well known. 
     U.S. Pat. No. 3,621,674 issued Nov. 23, 1971 to Ulics and Wheatley discloses a bellows style flexible shaft coupling encased in a molded rubber sleeve in combination with a Cardan style ball joint held in an elastomer socket for the purpose of reducing velocity fluctuations in the latter. U.S. Pat. No. 3,623,339 issued Nov. 30, 1971 to Muller discloses use of two concentrically disposed bellows having elastomer therebetween for the purpose of increasing torsional rigidity and decreasing torsional wind-up. U.S. Pat. No. 3,747,367 issued Jul. 24, 1973 to Muller discloses an improvement in this dual bellows style coupling wherein elastomer is injected between the two thereby alleviating the need for removal of an internal core necessary in molding of the elastomer intermediary layer. 
     STATEMENT OF NEED 
     Molding rubber about generally cylindrical bellows style flexible shaft couplings having annular convolutions has been shown to reduce torsional wind-up. Molding rubber about a metal bellows requires a complex pressurized molding however which is an expensive process. Injection of elastomer in between concentrically disposed bellows is simpler and hence less expensive than this type of molding but it still requires pressurization in addition to the use of two bellows instead of one. 
     In addition to torsional wind-up it is noted that the resonant frequency of a bellows type shaft coupling presents problems at relatively large rotational speeds, i.e. above 3,000 revolutions per minute (rpm), and metal fatigue results which, unchecked, rapidly leads to catastrophic failure, i.e breaking, in common language. Operation is hence effectively limited to the rotational velocity at which resonant frequency obtains. For relatively small shaft couplings, i.e. less than one inch diameter, operating at relatively high speeds this is considered, quite logically, to be a much greater problem than torsional wind-up. 
     A need is hence discerned for a means of reducing the stress experienced by bellows style flexible shaft couplings during resonant frequency, for extending the operational life and increasing the maximum operational velocity of bellows style flexible shaft couplings, without the expense associated with molding an elastomer about the metal bellows in a pressurized manufacturing operation. 
     SUMMARY OF THE INVENTION 
     Objects of the Invention 
     The encompassing object of the present invention is the enhancement of operational characteristics of a bellows style flexible shaft coupling possessing a single layer metal bellows of generally cylindrical shape without the expense of molding an elastomer about the same. 
     A principal object of the present invention is to prolong the operational life of a bellows style flexible shaft coupling possessing a single layer metal bellows of generally cylindrical shape without the expense of molding an elastomer about the same. 
     An ancillary object of the present invention is reducing the duration of resonant frequency experienced by a bellows style flexible shaft coupling possessing a single layer metal bellows of generally cylindrical shape without the expense of molding an elastomer about the same. 
     Another principal object of the present invention is to increase the maximum operational rotational velocity of a bellows style flexible shaft coupling possessing a single layer metal bellows of generally cylindrical shape without the expense of molding an elastomer about the same. 
     Another ancillary object of the present invention is increasing the rotational velocity resulting in resonant frequency being experienced by a bellows style flexible shaft coupling possessing a single layer metal bellows of generally cylindrical shape without the expense of molding an elastomer about the same. 
     Principles Relating to the Present Invention 
     In achievement of the above stated objects it is suggested that a substantially cylindrical rubber sleeve be disposed about the bellows of a single bellows style flexible shaft coupling without the use of pressurization. A rubber sleeve can be molded to the desired configuration separately from the metal bellows and fitted about the same under ambient conditions. Molding the rubber sleeve alone is much less complicated and hence less expensive than molding the same about the bellows. The rubber sleeve is not bonded to the metal bellows and torsional rigidity is hence unimproved but the rotational velocity at which resonant frequency is encountered is generally increased thereby increasing the maximum operational speed of the coupling. The duration of resonant frequency, moreover, is reduced by a factor of five which results in a commensurate increase in operational life at speeds exceeding the rotational velocity resulting in resonant frequency. 
     After fitting the rubber sleeve about the bellows appropriate application of heat melts the rubber and adheres the same to the metal bellows without the need for and expense of molding the sleeve about the bellows. The duration of resonant frequency is reduced by a factor often, resulting in a commensurate increase in operational life at speeds exceeding the rotational velocity resulting in resonant frequency, and torsional rigidity is increased thereby reducing torsional wind-up as well. The rubber sleeve can also be applied in a dip molding operation under ambient conditions. 
     The very considerable expense associated with a compound molding of elastomer about the metal bellows is avoided and both the operational life and maximum operational speed are increased largely owing to the unexpectedly large reduction in the duration of resonant frequency obtained by the dampening of vibration provided by a simple cylindrical rubber sleeve disposed about the metal bellows. 
     Other benefits and advantages of an embodiment in accordance with the principles relating to the present invention may be appreciated with a reading of the detailed discussion of the preferred embodiment following especially if conducted with reference to the drawings attached hereto and briefly described immediately below. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is an isometric view of a preferred embodiment in accordance with the principles relating to the present invention. 
     FIG. 2 is a cross sectional view of a preferred embodiment in accordance with the principles relating to the present invention depicting a cold fit. 
     FIG. 3 is a cross sectional view of a preferred embodiment in accordance with the principles relating to the present invention depicting a hot fit. 
     FIG. 4 is a graphic depiction of PRIOR ART performance characteristics relating to resonant frequency. 
     FIG. 5 is a graphic depiction of a preferred embodiment performance characteristics relating to resonant frequency. 
     FIG. 6 is a graphic depiction of the damping coefficient δ=log e (χ 1 /χ 2 ) as a function of time. 
     
       
         
               
             
               
               
               
             
           
               
                   
               
               
                 NOMENCLATURE 
               
               
                   
               
             
             
               
                   
               
             
          
           
               
                   
                 10 
                 coupling 
               
               
                   
                 11 
                 bellows 
               
               
                   
                 12 
                 boss(es) 
               
               
                   
                 13 
                 rubber sleeve 
               
               
                   
                 15 
                 shaft bore 
               
               
                   
                 16 
                 shaft bore diameter 
               
               
                   
                 17 
                 peripheral recess 
               
               
                   
                 19 
                 threading 
               
               
                   
                 20 
                 body (of boss) 
               
               
                   
                 21 
                 outward convolution 
               
               
                   
                 22 
                 inward convolution 
               
               
                   
                 23 
                 radial flange 
               
               
                   
                 25 
                 set screw 
               
               
                   
                 26 
                 boss diameter 
               
               
                   
                 27 
                 shoulder 
               
               
                   
                 29 
                 axial flange 
               
               
                   
                 31 
                 silicone rubber 
               
               
                   
                   
               
             
          
         
       
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     FIG. 1 depicts a shaft coupling  10  in accordance with the principles relating to the present invention possessing two opposed axially aligned terminal bosses  12  longitudinally connected by a bellows  11 , as seen in FIGS. 2 &amp; 3, shielded by a rubber sleeve  13  and possessing a shaft bore  15  at either end with which two perpendicular, radially disposed, set screws  25  communicate for securement of the end of a drive shaft, not shown, in the conventional manner. The coupling  10  is seen to possess a substantially cylindrical shape with the medially located rubber sleeve  13  presenting a radially enlarged cylindrical surface. The coupling  10  including the rubber sleeve  13  is substantially symmetric radially and longitudinally with respect to a medial plane normal to the central, rotational, axis. Radial symmetry is important to preserve rotational inertial balance during operation, particularly at relatively high speeds, i.e. above 3,000 rpm, but longitudinal symmetry is unnecessary. 
     Both shaft bores  15 , as clearly seen in FIGS. 2 &amp; 3, are radially symmetric but may vary in diameter  16  from each other, as in FIG. 3, or possess the same diameter  16  as shown in FIG.  2 . If the diameters  16  differ than longitudinal symmetry about a medial plane normal the central axis is lacking. This is wholly immaterial to operation. The diameter  16  of each shaft bore  15  is simply determined by the diameter of the shaft intended to be disposed therein and engaged by one or more set screws  25 . Use of two perpendicular set screws  25  for each shaft bore  15  is preferred for the same reason that this configuration is commonly used in less expensive shaft couplings: perpendicularly avoids opposition of forces and each set screw  25  can be tightened independently of the other. The set screws  25  must possess and engage threading  19  in adjustable connection to the body  20  of a boss  12  through which each set screw  25  necessarily extends in order to communicate with the shaft bore  15  and contact a shaft disposed therein. Other means for engaging a shaft end inserted into the shaft bore  15  can, moreover, be utilized. The boss  12  can be slotted and traversed by a threaded connector in a collar style engagement which does not mar the shaft and does not require that the body  20  of the boss  12  be made of metal. 
     Set screws  25  are simply considered the most economic means of engaging the shaft end disposed in a shaft bore  15  of a coupling  10  possessing a metal bellows  11  shielded by a rubber sleeve  13  in accordance with the principles relating to the present invention. The bellows  11  must be metal, preferably phosphorus bronze, and must be connected at either end to a boss  12  which is hence preferably metal as well. The attachment of each end of the metal bellows  12  to one of the two bosses  12  must resist slippage and preserve axial alignment. 
     It is preferred, as depicted in FIGS. 2 &amp; 3, that each opposed end of the metal bellows  11  comprise a short cylindrical sleeve, known herein as an axial flange  29 , fitting about an exterior peripheral recess  17 , or reduced diameter  26 , of the proximate end of the body  20  of the boss  12  and butted against a shoulder  27  on the outward end of the peripheral recess  17 . A peripheral groove about the proximate end of the boss  12  engaged by a peripheral detent in an axial flange  29  of equivalent diameter  26  to the body  20  of the boss  12  is also suggested as a substantially equivalent construction. In any case it is recommended that each end of the metal bellows  11  possess an axial flange  29  permanently bonded to one boss  12 . And it is suggested that this bonding be accomplished by soldering or brazing if the bosses  12  are of metal dissimilar to the metal bellows  11  or welding if similar. Phosphorus bronze is specifically recommended for the metal bellows  11 , brass for the bosses  12 , and soldering for bonding the two together. 
     The external peripheral recess  17  with resulting shoulder  27  on the end of each boss  12  also, as clearly depicted in FIGS. 2 &amp; 3, preferably captures the distal edge of a radial flange  23  on each end of the rubber sleeve  13 . This is not necessary but is considered a simple and elegant construction. It is desirable to prevent displacement of the rubber sleeve  13  but the resilience of elastomeric material readily permits sizing of the rubber sleeve  13  relative the external substantially cylindrical configuration of the metal bellows  11  to ensure compression of the former about the latter preventing accidental displacement. The convoluted configuration of the metal bellows  11  further enhances a friction fit which is not readily displaced and the fitting of the two radial flanges  23  on the ends of the rubber sleeve  13  into the external peripheral recess  17 , and against the shoulder  27  adjacent the same, is mainly considered useful in locating the rubber sleeve  13  in the desired location enclosing the exterior of the metal bellows  11  in compressed contact with the same. 
     This is beneficial regardless of whether a ‘hot’ or ‘cold’ fitting is made because in either case the rubber sleeve is molded as a separate piece and fit over the metal bellows  11  after the same has been secured to two opposed bosses  12 . In the case of a cold fitting, as depicted in FIG. 2, this completes the assembly of the coupling  10 . In the case of a hot fitting, as depicted in FIG. 3, the rubber sleeve  13  is still first cold fitted, substantially as shown in FIG. 2, and then melted with the application of heat thereby filling the exterior annular grooves between the outward convolutions  21  of the metal bellows  11  as seen in FIG.  3  and adhering the rubber sleeve  13  to the exterior of the metal bellows  11  while leaving the interior of the same free including the interior annular grooves between the inward convolutions  22 . The configuration depicted in FIG. 3 can also be achieved with a dip molding utilizing appropriate masking of the exterior of the bosses  12 . This approach, however, is not preferred for several reasons: it is messy; requires rotation during curing to obtain a satisfactorily radially uniform rubber sleeve  13 ; and the material is inferior to vulcanized rubber. 
     With specific regard to the material used in manufacture of the rubber sleeve  13  it is first emphasized that the term ‘rubber’ connotes an elastomer and that a wide range of elastomers are suitable but the structural integrity obtained with the cross bonding effected during vulcanization is considered highly desirable. The term ‘rubber’ is used as being more widely understood and substantially equivalent to elastomer. Synthetic rubber is recommended because it costs less than natural rubber. Either is suitable. Chloroprene, also known as Neoprene™, is specifically recommended. It is “chemically and structurally similar to natural rubber, and its mechanical properties are also similar.” ( Materials Handbook , George S. Brady &amp; Henry R. Clauser, McGraw-Hill, Inc., 13 th  edition, 1991, page 286) Chloroprene also has excellent chemical and oil resistance among other desirable properties and is less expensive than many other synthetic rubbers. 
     A coupling  10  in accordance with the principles relating to the present invention having a rubber sleeve  13  fitted about a metal bellows  11  possesses superior vibration characteristics in comparison with the equivalent, conventional, bellows style coupling without rubber shielding. Conventional bellows style couplings are characterized by a relatively low resonant frequency, as shown in FIG. 4, and may even have more than one natural resonant frequency. FIG. 4 depicts the performance of a conventional bellows style (PRIOR ART) coupling with a resonant frequency at 85 hertz (HZ) corresponding to a rotational velocity of 5,100 rpm. Resonance greatly increases the stresses upon the coupling and diminishes operational life. Fracture, typically at one of the connections of the metal bellows  11  to the bosses  12 , inevitably results from prolonged resonant operation. It is also noted that the decibel peak attained at resonance by a conventional bellows style coupling is quite sharp which is an indication of the severity of the vibration and consequent stress experienced. 
     FIG. 5 depicts the frequency characteristics of a coupling  10  in accordance with the principles relating to the present invention possessing a hot fitted rubber sleeve  13  as depicted in FIG. 3 which is otherwise identical to the conventional coupling for which frequency characteristics are depicted in FIG.  4 . Resonant frequency is seen in FIG. 5 to obtain at 300 HZ which corresponds to a rotational velocity, i.e. shaft speed, of 14,700 rmp, nearly three times the speed of the PRIOR ART. Practical, safe, maximum operational speed is hence increased by 286% in this representative example. And, even more importantly, the severity of the vibration and stress experienced during resonance is seen by the rounded peak connoting resonant frequency, at 26.3 dB, in FIG. 5 to be much less than that characterizing resonance, at 34.5 dB, in the PRIOR ART. 
     The underlying physical difference is the vibration dampening provided by the rubber sleeve  13  about the metal bellows  11  in a coupling  10  in accordance with the principles relating to the present invention. An exemplary damping coefficient δ=log e (χ 1 /χ 2 ) is depicted in FIG. 6 as a function of time. The larger the damping coefficient the more quickly resonance is eliminated and the greater the reduction of vibration generally. PRIOR ART damping coefficients range from 0.03 to 0.04 for three different size bellows style couplings with basic, i.e. boss  12 , external diameters  26  of ¾″, ⅞″, and 1″. Couplings  10  in accordance with the principles relating to the present invention possessing a cold fitted rubber sleeve  13  about the metal bellows  11  of the same sizes and of otherwise identical construction possess damping coefficients of 0.37, 0.25, &amp; 0.29, i.e. between six and ten times the PRIOR ART. 
     Perhaps the most useful measure of the vibration characteristics concerned is the length of (time required to stop resonance. The PRIOR ART coupling obtaining resonance at 85 HZ as depicted in FIG. 4 requires 2.5 seconds to stop resonating. The coupling  10  in accordance with the principles relating to the present invention with a hot fitted rubber sleeve  13  about the metal bellows  11  obtaining resonance at 245 HZ as depicted in FIG. 5 stops resonance in 0.07 seconds or in less than 3 percent of the time required of the PRIOR ART. The average value for a range of PRIOR  9  ART bellows style couplings between ¾″ and 1″ basic diameter is approximately 1.0 seconds. The average value for the same range of couplings  10  with a cold fitted rubber sleeve  13  about the metal bellows  11  is approximately 0.2 seconds and the average value for the same range of couplings  10  with a hot fitted rubber sleeve  13  about the metal bellows  11  is approximately 0.1 seconds. A coupling  10  in accordance with the principles relating to the present invention with a rubber sleeve  13  fitted about the metal bellows  11  stops resonating five to ten times more quickly than the equivalent PRIOR ART couplings. 
     It is not intended that couplings  10  in accordance with the principles relating to the present invention possessing a rubber sleeve  13  about the metal bellows  11  be operated at speeds which obtain resonance but rather that these data indicate the extension of operational life gained by the reduction in vibration experienced in normal operation provided by adherence to said principles. The data presented herein were obtained with careful testing of PRIOR ART bellows style couplings and couplings  10  in accordance with the principles relating to the present invention possessing a rubber sleeve  13  about the metal bellows  11  all manufactured by YUNIKA™ Corporation of Tokyo, Japan wherein each was secured to one end of a spindle driven at gradually increasing rotational velocity in accordance with commonly accepted industry practice. 
     It is noted that couplings  10  in accordance with the principles relating to the present invention possessing a rubber sleeve  13  about the metal bellows  11  accommodate up to 0.5 mm or 2.5 degrees of angular misalignment between drive and driven shafts coupled by the same depending on whether the rubber sleeve  13  is, respectively, hot or cold fitted as the melted rubber in the exterior annular grooves between the outward convolutions  21  essentially retards longitudinal flexure. 
     It is also noted that silicone rubber  31  which vulcanizes at room temperature may be applied to the interior of the metal bellows  11  of a coupling  10  having a hot fitted rubber sleeve  13  in obtainment of maximum vibration dampening characteristics. Silicon rubber  31  is more expensive than chloroprene rubber but the application of both at ambient pressure is still far more economic than pressurized complex molding of any elastomer about a metal bellows. 
     Lastly it is noted that couplings  10  made in accordance with the principles relating to the present invention are further characterized by negligible backlash, constant velocity ratio, relatively high torsional rigidity with minimal wind up, and are considered to be ideally suited for precise rotation transmission by stepper and servo motors especially.

Technology Category: f