Abstract:
In an elliptical rim neutral line of each axially perpendicular cross section in a tooth trace direction of a flexible externally toothed gear of a wave gear device, external teeth are applied with addendum modification along the external teeth tooth trace direction so that the bending stress generated at the root rim surface of the external teeth that is caused by flexing of the flexible externally toothed gear is averaged out, the maximum value thereof can be reduced, and the transferred torque of the wave gear device can be increased.

Description:
BACKGROUND OF THE INVENTION 
       [0001]    1. Field of the Invention 
         [0002]    The present invention relates to a wave gear device equipped with a tapered flexible externally toothed gear that can reduce the bending stress generated at the root-rim surface of the flexible externally toothed gear and increase transferred torque. 
         [0003]    2. Description of the Related Art 
         [0004]    Since its invention (Patent Document 1) by C. W. Musser until now, the wave gear device has had a variety of inventions and designs of the present device made by many researchers including the present inventor. There is a variety of inventions relating only to the tooth profile. For example, the present inventor proposes having the basic tooth profile to be an involute tooth profile in Patent Document 2, and proposes a tooth profile design method for defining the addendum tooth profile of a rigid internally toothed gear and a flexible externally toothed gear for performing wide-area contact using a method for approximating the meshing of the teeth of both gears with a rack in Patent Documents 3, 4. 
         [0005]    In general, a wave gear device has an annular rigid internally toothed gear, a flexible externally toothed gear coaxially arranged on the inside of the internally toothed gear, and a wave generator fitted to the inside of the externally toothed gear. The flexible externally toothed gear comprises a flexible cylindrical part, a disk-shaped diaphragm extending in the radial direction from the rear end of the cylindrical part, and external teeth formed on the external peripheral surface of the front end opening side of the cylindrical part. The front end opening side portion of the cylindrical part of the flexible externally toothed gear is made to elliptically flex by the wave generator, and the external teeth at the two end parts along a direction of the major axis of the elliptical curve mesh with the internal teeth of the rigid internally toothed gear. 
         [0006]    The external teeth of the flexible externally toothed gear that is elliptically flexed has increased flexing amount from the diaphragm side to the front end opening along the tooth trace direction. Each portion of the teeth of the flexible externally toothed gear repeats flexing in the radial direction in association with the rotation of the wave generator. The present inventor proposes a method for setting the tooth profile with consideration given to such flexing motions (coning) of the flexible externally toothed gear by the wave generator in Patent Document 5. 
         [0007]    In the wave gear device proposed in Patent Document 5, an arbitrary axially perpendicular cross-sectional position of the tooth trace direction of the flexible externally toothed gear is defined to be a primary cross section, and a tooth profile of the flexible externally toothed gear and the rigid internally toothed gear that is able to continually mesh at the primary cross section are formed. Assuming the flexing amount of the external teeth of the flexible externally toothed gear to be proportionate to the distance from the diaphragm from rear end of the diaphragm side to the front end opening, addendum modification is applied on the portions of the external teeth other than the primary cross section in accordance with the flexing amount, and interference of tooth profiles of both gears is avoided. 
         [0008]    In Patent Document 6, the present inventor proposes the use of a conical tooth profile for the external teeth of the flexible externally toothed gear to avoid interference of tooth profiles of both gears caused by the flexing of the flexible externally toothed gear at the locations other than the axially perpendicular cross section (primary cross section) defined at a predetermined position of the tooth trace direction of the flexible externally toothed gear of the wave gear device. 
         [0009]    [Patent Document 1] U.S. Pat. No. 2906143 
         [0010]    [Patent Document 2] JP-B 45-41171 
         [0011]    [Patent Document 3] JP-A 63-115943 
         [0012]    [Patent Document 4] JP-A 64-79448 
         [0013]    [Patent Document 5] WO 2010/070712 
         [0014]    [Patent Document 6] WO 2005/124189 
       SUMMARY OF THE INVENTION 
       [0015]    There is presently a strong market demand for an improvement in load torque performance in a wave gear device. Accomplishing this particularly requires an improvement in strength of the flexible externally toothed gear. 
         [0016]    To solve the above problem, the wave gear device of the present invention was devised to average out and reduce bending stress generated at the root-rim surface of the external teeth caused by the flexing of the flexible externally toothed gear. In doing so, addendum modification of teeth with consideration given to coning of the flexible externally toothed gear is applied. 
         [0017]    The wave gear device of the present invention has a rigid internally toothed gear, a cup-shaped or silk hat-shaped flexible externally toothed gear on the inside of the internally toothed gear, and a wave generator for flexing the flexible externally toothed gear into an elliptical shape to cause the flexible externally toothed gear to partially mesh with the rigid internally toothed gear. The position at which the two gears mesh moves in a circumferential direction when the wave generator rotates, and a relative rotation is generated between the two gears in correspondence with the difference in the number of teeth of the two gears. For each axially perpendicular cross section in the tooth trace direction of the flexible externally toothed gear that is flexed into an elliptical shape by the wave generator, flexing that is proportionate to its distance from the diaphragm is generated at a position on a major axis of the elliptical curved line of flexible externally toothed gear as it progresses from the rear end of the diaphragm side of the flexible externally toothed gear to the front end opening of the flexible externally toothed gear. In the elliptical rim neutral line of each axially perpendicular cross section in the tooth trace direction of the flexible externally toothed gear, the product tw of t and w is set so as to be constant in each axially perpendicular cross section of the tooth trace direction in the external teeth of the flexible externally toothed gear, where w=κmn (where m is the module of the teeth of both gears, n is ½ of the difference in the number of teeth between the rigid internally toothed gear and the flexible externally toothed gear, and κ is the flexing coefficient), and t is the rim thickness of the axially perpendicular cross section. The external teeth of the flexible externally toothed gear are subjected to addendum modification in the tooth trace direction thereof to satisfy this relation. The root shape in the tooth trace direction of the external teeth obtained in this manner is prescribed by a theoretical root curved line that satisfies the above relation. 
         [0018]    It is desirable, from a perspective of tooth profile processing, for the root shape in the tooth trace direction of the external teeth to be prescribed by a root straight line that is approximate to the theoretical root curved line of the external teeth that satisfies the relation in which the product of the root rim thickness t and the flexing amount w is constant. The approximate root straight line is a line tangent to the theoretical root curved line, the tangent line being drawn to a point on the theoretical root curved line that corresponds to a position in the tooth width center of the external teeth. 
         [0019]    In accordance with the present invention, in each axially perpendicular cross section in the tooth trace direction of the flexible externally toothed gear of the wave gear device, the bending stress generated at the root rim surface by the flexing of the elliptical rim neutral line in the major axis direction can be averaged and its maximum value can be reduced. Accordingly, a wave gear device that can transmit greater torque via the flexible externally toothed gear can be attained. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0020]      FIG. 1  is a schematic front view of a common wave gear device; 
           [0021]      FIG. 2  is an illustrative drawing for showing the flexing state of the flexible externally toothed gear, wherein (a) shows the state of the longitudinal cross section of the flexible externally toothed gear before deforming, (b) shows the state of the longitudinal cross section in a position that includes the major axis of the flexible externally toothed gear deformed in an elliptical shape, and (c) shows the state of the longitudinal cross section in a position that includes the minor axis of the flexible externally toothed gear deformed in an elliptical shape; and 
           [0022]      FIG. 3  is an illustrative drawing showing the shape of the teeth of the two gears of the wave gear device to which the present invention is applied. 
       
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0023]    (Configuration of the Wave Gear Device) 
         [0024]    The configuration of the wave gear device of the present invention and the flexing action (coning) of the flexible externally toothed gear will now be described with reference to  FIGS. 1 and 2 . The solid lines in  FIGS. 2(   a ) to ( c ) show a cup-shaped flexible externally toothed gear, and the dash lines show a silk hat-shaped flexible externally toothed gear. 
         [0025]    The wave gear device  1  has an annular rigid internally toothed gear  2 , a flexible externally toothed gear  3  arranged on the inside of the rigid internally toothed gear, and a wave generator  4  having an elliptical profile that is fitted inside of the flexible externally toothed gear. The rigid internally toothed gear  2  and the flexible externally toothed gear  3  are both spur gears of a module m. The difference in the number of teeth of the two gears is 2n (where n is a positive integer), and the rigid internally toothed gear  2  has more teeth. The flexible externally toothed gear  3  is flexed into an elliptical shape by the wave generator  4  having an elliptical profile and meshes with the rigid internally toothed gear  2  at the two end portions of the major axis L 1  direction of the ellipse. When the wave generator  4  rotates, the meshing position of the two gears  2 ,  3  moves in a circumferential direction, and a relative rotation in correspondence with the difference in the number of teeth of the two gears is generated between the two gears  2 ,  3 . The flexible externally toothed gear  3  comprises a flexible cylindrical part  31 , a disk-shaped diaphragm  32  extending in a radial direction continuous with the rear end  31   b  of the cylindrical part, a boss  33  that is continuous with the diaphragm  32 , and external teeth  34  formed on the external peripheral portion of the front end opening  31   a  of the cylindrical part  31 . 
         [0026]    The wave generator  4  having an elliptical profile is fitted inside of an external teeth-formed portion of the front end opening  31   a  side in the cylindrical part  31  of the flexible externally toothed gear  3 . The cylindrical part  31  that is elliptically flexed by the wave generator  4  has gradually increasing flexing amount to the outside or inside of the radial direction from the rear end  31   b  of the diaphragm side to the front end opening  31   a . As shown in  FIG. 2(   b ), the flexing amount to the outside gradually increases substantially proportionate to the distance from the rear end  31   b  to the front end opening  31   a  in a cross-sectional position that includes the major axis L 1  (see  FIG. 1)  of the elliptical curved line of the cylindrical part  31 ; as shown in  FIG. 2(   c ), the flexing amount to the inside gradually increases substantially proportionate to the distance from the front end opening  31   a  to the rear end  31   b  in a cross-sectional position that includes the minor axis L 2  (see  FIG. 1)  of the elliptical curved line. 
         [0027]    The external teeth  34  formed on the external peripheral portion of the front end opening  31   a  side of the cylindrical part  31  also varies in flexing amount at each axially perpendicular cross section in the tooth trace direction. The flexing amount gradually increases substantially proportionate to the distance from the rear end  31   b  in the tooth trace direction of the external teeth  34  from the rear end  34   b  of the diaphragm side to the front end  34   a  of the front end opening  31   a  side within a cross section that includes the major axis L 1  of the elliptical curved line. 
         [0028]    In an axially perpendicular cross section of any position in the tooth trace direction of the external teeth  34 , a circle that passes through the center of the thickness direction of the root rim of the external teeth  34  prior to being elliptically flexed is a rim neutral circle. In contrast, the curved line that passes through the center of the thickness direction of the root rim after being elliptically flexed is referred to as an elliptical rim neutral line. In the major axis position of elliptical rim neutral line, the flexing distance in the major axis direction relative to the rim neutral circle is 2 κmn, where κ is the flexing coefficient. 
         [0029]    Z F  is the number of teeth of the external teeth  34  of the flexible externally toothed gear  3 , Z C  is the number of teeth of the internal teeth  24  of the rigid internally toothed gear  2 , R (=Z F /(Z C −Z F )=Z F /2n) is the speed reduction ratio of the wave gear device  1 , and the value (mZ F /R=2 mn) obtained by dividing the pitch circle diameter mZ F  of the flexible externally toothed gear  3  by the speed reduction ratio R is the normal flexing distance w O  in the major axis direction. The wave gear device  1  is generally designed to flex at its normal flexing distance (=2 mn) at a position at the ball center of the wave bearing of the wave generator  4  in the tooth trace direction of the flexible externally toothed gear  3 . The flexing coefficient K represents a value obtained by dividing the flexing amount w by the normal flexing amount in each axially perpendicular cross section of the tooth trace direction of the flexible externally toothed gear  3 . In the external teeth  34 , therefore, the flexing coefficient at the position where the normal flexing amount is obtained is κ=1, the flexing coefficient at a cross section position of a flexing amount that is less than the normal flexing distance is κ&lt;1, and the flexing coefficient at a cross section position of a flexing amount w that is greater than the normal flexing distance is κ&gt;1. 
         [0030]    (Shape of External Teeth) 
         [0031]    In the present invention, an object is to reduce bending stress generated at the root rim surface of the flexible externally toothed gear  3 , and to ensure that bending stress is made uniform with focus on the variation in flexing amount in the tooth trace direction of the root rim surface. The amount of addendum modification to be applied on the external teeth  34  is set as described below in correspondence with each position in the tooth trace direction of the external teeth  34  of the flexible externally toothed gear  3 . That is, addendum modification is applied on the external teeth so the root curved line is prescribed by a curved line (theoretical curved line) where the root rim thickness t at each axially perpendicular cross section satisfies the expression 
         [0000]        t ×κmn=const
 
         [0000]    in correspondence with the flexing coefficient K at each axially perpendicular cross section for each axially perpendicular cross section in the tooth trace direction from the front end  34   a  of the external teeth  34  to the rear end  34   b  of the diaphragm side. This is based on a fact of material mechanics in which bending stress on the major axis is proportionate to the product of the rim thickness t and the flexing coefficient κ because the curvature changes in accordance with the flexing coefficient when a ring is deformed into an elliptical curved line. 
         [0032]    In a preferred embodiment of the present invention, the tangent line drawn at the tooth width center of the external teeth of a curved line (theoretical curved line), in which the root rim thickness t at each axially perpendicular cross section of the external teeth  34  satisfies t×κmn=const, is used as the root straight line for prescribing the root shape in the tooth trace direction of the external teeth  34 . 
         [0033]    To describe in greater detail with reference to  FIG. 3 , the external teeth  34  of the flexible externally toothed gear  3  are addendum-modified tooth profiles to which addendum modification has been applied so that the root rim thickness t for each axially perpendicular cross section satisfies t×κmn=const in accordance with the flexing coefficient κ at each axially perpendicular cross section for each axially perpendicular cross section in the tooth trace direction from the front end  34   a  to the rear end  34   b.    
         [0034]    The axial cross sectional shape of the root rim in the external teeth  34  of the flexible externally toothed gear  3  has its inside profile shape prescribed by the straight line L, and the root shape on the outside is prescribed by a root curved line A derived from the theoretical curved line that satisfies the expression t×κmn=const. The root curved line A is a curved line that is convex to the inside, and the root rim thickness t that is prescribed by the root curved line A and the straight line L on the inside is greatest at the rear end  34   b  of the diaphragm side, is smallest at the front end  34   a , and gradually decreases in correspondence with the distance from the diaphragm between the ends. 
         [0035]    In the root curved line A obtained in this manner, a tangent line drawn to the tooth width center of the external teeth  34  is then used as the root straight line of the external teeth  34 . In the example of the drawings, the tooth width center  34   c  corresponds with the ball center of the wave bearing  4   a  of the wave generator  4 . The root shape of the transpositioned (addendum-modified) tooth profile that is prescribed by the root curved line A derived from the theoretical curved line is corrected to become the root straight line B. The transpositioned tooth profile after correction that is obtained in this manner is tapered, and this is used as the tooth profile of the external teeth  34 . 
         [0036]    In the present invention, an object is to average the bending stress using the fact that, based on a formula from material mechanics, the bending stress on the major axis that is generated by the elliptical deformation of the thin, annular external teeth of the flexible externally toothed gear is proportionate to the product of its thickness and its flexing distance from its elliptical deformation, as described above. The bending stress generated in the external teeth is therefore reduced, and an increase in strength of the flexible externally toothed gear is thereby accomplished.