Abstract:
The clutch hub includes a sheet-metal hub member which has an axial member projected from the center of its plate surface, and also includes an annular armature which is fixed to an outer peripheral portion of the axial member. First mounting the axial member of the clutch hub downward on a support member and thereby elastically supporting the end surface of the armature by the support member; holding the axial member of the clutch hub using a chuck; locating a fixing member just under a portion of a maximum runout portion of an inner hub; contacting a cylindrical end surface of a pressing member with an upper surface of the inner hub using pressure; and plastically deforming the inner hub by a pressing force of the pressing member using the locating portion of the fixing member as a fulcrum, which thereby corrects an inclination of the axial member.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application is based on and claims the benefit of priority from earlier Japanese Patent Application No. 2012-154515 filed Jul. 10, 2012, the description of which is incorporated herein by reference. 
     BACKGROUND 
     1. Technical Field of the Invention 
     The present invention relates to a deformation processing apparatus for correcting runout caused in the surface of an armature in a clutch hub which is used for a power transmission device. 
     2. Related Art 
     For example, an electromagnetic clutch is used in connecting a compressor of an air conditioner installed in an automobile to an engine that serves as a drive source. An electromagnetic clutch is configured such that an armature of a clutch hub faces a rotor rotated and driven by an engine, and that an inner hub is connected to a compressor-side drive shaft. The armature is attracted to the rotor by an electromagnetic force, while torque is transmitted to the compressor via the inner hub that integrally rotates with the armature. 
       FIG. 1  is a schematic diagram illustrating a clutch hub. As shown in  FIG. 1 , a spline shaft of a compressor is ensured to engage with a spline hole  102  which is positioned at the center of a hub member  101 . An armature  103  has an annular shape and is riveted to an outer periphery of the hub member  101 . In this case, if the accuracy of dimension and the accuracy of assemblage are insufficient, the axis of the hub member  101  will be inclined when the armature  103  is assembled to a rotor. In other words, runout will be caused in an armature surface  104  when the hub member  101  turns around on the axis of the hub member. 
     That is to say, in order to effectively transmit torque, the armature surface  104  is required to be perpendicular to the spline shaft (i.e. normal line D with respect to an inner end face C of the spline hole  102 ). Accordingly, as shown in  FIGS. 2A and 2B , when runout is caused in the armature surface  104  of the clutch hub (in other words, when the axis of the hub member  101  is inclined), a process of grinding the end surface of the armature  103  and removing the runout has conventionally been performed to suppress the runout so as to be lower than a standard value. 
     As conventional art, JP-A-H06-291475 discloses a method of performing high-spin deformation processing, instead of performing cutting or grinding, in the course of manufacturing a chassis used for a precision apparatus, so that accuracy of dimension is obtained in a processed sheet-metal product or in a molded product. Specifically, in this method, a mounting seat is provided to a sheet-metal chassis so as to be projected therefrom, followed by pressing a pressing member, which makes a conical runout motion, against the projected surface, thereby reducing the surface level to a predetermined level. 
       FIGS. 2A and 2B  shows a deformation processing method for correcting surface runout of a clutch hub, which is based on conventional grinding, and a relationship between amount of runout and processing time. As shown in  FIGS. 2A and 2B , in correcting surface runout using grinding, the amount of grinding increases as the amount of runout is increased. Therefore, a lot of time is spent for the processing, drastically reducing the productivity. On the other hand, while the technique disclosed in JP-A-H06-291475 is effective in entirely reducing the level of a projected portion, it is not suitable for correcting runout in the armature surface of a clutch hub. 
     It is thus desired to provide an apparatus for correcting surface runout, which is able to accurately and quickly correct runout caused in the armature surface of a clutch hub to enhance productivity. 
     SUMMARY 
     As an exemplary embodiment, the present application provides a deformation processing apparatus for correcting surface runout  73 . The apparatus is used for correcting runout caused in an end surface of an annular armature of a clutch hub. Such a clutch hub includes a sheet-metal hub member that has an axial member projected from the center of its plate surface, and also includes the annular armature which is fixed to the hub member so as to be located in an outer peripheral portion of the hub member near the axial member. 
     The apparatus includes a support member, a press mechanism and a fixing member. The support member is used for placing thereon the clutch hub, with the axial member, as an object to be corrected, being oriented downward, and for elastically supporting the end surface of the armature. The press mechanism has a cylindrical pressing member which is positioned above the hub member. The press mechanism allows a driving means to descend the pressing member to press the hub member. The fixing member is positioned below the hub member and includes a locating portion which is opposed to a predetermined position of the plate surface, according to the runout caused in the end surface of the armature. 
     When a pressing force is applied to the pressing member by the pressing mechanism, the pressing member plastically deforms the plate surface of the hub member by using the locating portion as a fulcrum, and thereby an inclination of the axial member with respect to the end surface of the armature can be corrected. (First aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     When runout is corrected using the deformation processing apparatus for correcting surface runout  73  of the present configuration, an amount of runout in the end surface of the clutch hub is measured in advance. Further, the position of the runout is permitted to coincide with the locating portion of the fixing member and then the end surface of the armature is placed on the support member. In this case, the axial member of the hub member is inclined with respect to the axis of the pressing member. Then, when the press mechanism is driven to descend the pressing member and press the hub member of the clutch hub, the entire clutch hub which is elastically supported by the support member is depressed. In this process, a predetermined position of the plate surface of the hub member is pressed against the locating portion of the fixing member. Then, the cylindrical pressing member depresses the outer periphery of the hub member to thereby deform the plate surface, with the locating portion being used as a fulcrum, and corrects the inclination of the axial member. 
     Accordingly, when an amount of depression of the pressing member is set according to an amount of runout in the end surface of the armature, the end surface of the armature is permitted to be perpendicular to the axial member, thereby correcting surface runout. Accordingly, in the event the amount of runout is comparatively large, it is no longer necessary to spend a lot of time for the correction of the runout, as would have been necessary in the grinding based on the conventional art. As a result, productivity is greatly enhanced. 
     The deformation processing apparatus for correcting surface runout  73  may preferably include a chuck. The chuck is brought into contact with the side faces of the axial member of the hub member to limit displacement in the rotation direction of the clutch hub. (Second aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     According to the apparatus for correcting surface runout having the present configuration, the axial member of the clutch hub is held by the chuck. Accordingly, when the pressing member is pushed down, displacement in the rotation direction of the clutch hub is suppressed. Thus, the contact position, at which the locating portion contacts the plate surface of the hub member, is prevented from being deviated. As a result, surface runout is corrected with good accuracy. 
     In the deformation processing apparatus for correcting surface runout  73 , the support member is configured by a retainer plate and elastic support legs. The retainer plate is brought into contact with the end surface of the armature. Each of the elastic legs includes in its upper portion a spring member that urges the retainer plate upward. (Third aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     According to the deformation processing apparatus for correcting surface runout  73  having the present configuration, the support member may specifically have a configuration in which the retainer plate, on which the end surface of the armature is placed, is urged upward by the spring members provided to the elastic support legs. Thus, with the descending of the pressing member, the end surface of the armature can be uniformly and elastically supported. 
     Further, in the deformation processing apparatus for correcting surface runout  73 , the amount of depression of the pressing member given by the press mechanism may be the sum of an amount of plastic deformation which depends on the amount of runout in the end surface of the armature measured in advance and an amount of elastic deformation of the hub member. (Fourth aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     According to the deformation processing apparatus for correcting surface runout  73  having the present configuration, the press mechanism sets an amount of depression of the pressing member, taking account of an amount of rebound attributed to the elastic deformation of the hub member. When the amount of elastic deformation is added to the amount of plastic deformation, which depends on the amount of runout in the end surface of the armature, an amount of correction of surface runout corresponding to the amount of plastic deformation is obtained after depression of the hub member. 
     Further, the locating portion of the fixing member may preferably be arranged on a line connecting between a maximum-runout position in the end surface of the armature measured in advance and the axial member. (Fifth aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     According to the deformation processing apparatus for correcting surface runout  73  having the present configuration, the position of the clutch hub is determined so that the maximum-runout position in the end surface of the armature coincides with the position of the fixing member of the clutch hub. Accordingly, when the plate surface is partially deformed, with the locating portion being used as a fulcrum, the axial member is relatively displaced in a direction in which the amount of runout is large, thereby efficiently correcting runout. 
     Further, the locating portion of the fixing member may preferably be formed on an arc-shaped surface which is coaxial with the hub member. (Sixth aspect of the deformation processing apparatus for correcting surface runout of the present invention) 
     According to the deformation processing apparatus for correcting surface runout  73  having the present configuration, the locating portion of the fixing member has an arc-shaped surface which is coaxial with the hub member. Thus, when the outer periphery of the plate surface of the hub member is depressed by the coaxially-positioned cylindrical pressing member, the hub member is prevented from being locally imposed with an excessive load. As a result, the load applied to the plate surface, which is in contact with the locating portion, is reduced to thereby enable effective correction of runout. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       In the accompanying drawings: 
         FIG. 1  is a schematic configuration diagram illustrating surface runout of a clutch hub; and 
         FIG. 2A  shows a schematic diagram illustrating a method of deformation processing for correcting surface runout of a clutch hub, and  FIG. 2B  shows a diagram illustrating a relationship between amount of runout and processing time, respectively according to conventional grinding. 
         FIG. 3  is a partial cross-sectional view illustrating a schematic configuration of a deformation processing apparatus for correcting surface runout  73 , according to a first embodiment of the present invention; 
         FIG. 4  is a general configuration diagram illustrating a deformation processing system for correcting surface runout, including the deformation processing apparatus for correcting surface runout  73 ; 
         FIG. 5  is a general cross-sectional view illustrating an example of a specific configuration of a clutch hub; 
         FIG. 6A  shows a front view, and  FIG. 6B  shows a right-side partial cross-sectional view, illustrating an electromagnetic clutch including the clutch hub; 
         FIG. 7  is a diagram illustrating processing steps in a method of correcting runout, performed by the system for correcting runout; 
         FIG. 8  is a schematic cross-sectional view illustrating a state where the clutch hub is mounted to a runout measurement section; 
         FIG. 9A  shows a schematic cross-sectional view illustrating the runout measurement section for the method of correcting runout; 
         FIG. 9B  shows a diagram illustrating an example of a result of measurements of runout; 
         FIG. 10  shows schematic diagrams illustrating a method of determining position performed in the runout measurement section; 
         FIG. 11  is a partial cross-sectional view illustrating an example of a specific configuration of the deformation processing apparatus for correcting surface runout; 
         FIG. 12A  shows a general plan view and  FIG. 12B  shows a side view, illustrating an example of a specific configuration of the deformation processing apparatus for correcting surface runout; 
         FIG. 13  is a general perspective view illustrating a fixing member; 
         FIG. 14  is a diagram illustrating the shape of a chuck member of a chuck; 
         FIG. 15  shows schematic cross-sectional views illustrating a step of setting the clutch hub in the deformation processing apparatus for correcting surface runout and descending the pressing member, wherein  FIG. 15A  shows a state where the clutch hub is placed on support member, and  FIG. 15B  shows state where the clutch hub is brought into contact with locating portion by pressing member; 
         FIG. 16  shows schematic cross-sectional views illustrating a step of correcting runout performed by the deformation processing apparatus for correcting surface runout, wherein  FIG. 16A  shows a state before pressing the clutch hub,  FIG. 16B  shows a state after pressing the clutch hub; 
         FIG. 17  shows diagrams illustrating a method of determining an amount of depression of the pressing member in a step of deformation processing for correcting surface runout, wherein  FIG. 17A  shows a relationship between amount of runout and amount of depression of a pressing member and  FIG. 17B  shows a relationship between amount of deformation of the clutch hub and amount of depression of a pressing member; 
     
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     With reference to the accompanying drawings, hereinafter is described a first embodiment of the present invention.  FIG. 3  shows a basic structure of a deformation processing apparatus for correcting surface runout  73  of the present invention. The basic structure configures a part of a deformation processing system  50  for correcting surface runout shown in  FIG. 4 . In  FIG. 3 , the deformation processing apparatus for correcting surface runout  73  has a clutch hub  1  as an object of correcting surface runout. The apparatus includes a support member  2  and a chuck  6  for supporting the clutch hub  1 . The apparatus also includes a fixing member  3  that faces a lower surface of a hub member  10  of the clutch hub  1 . The apparatus further includes a cylindrical pressing member  4  that faces an upper surface of the hub member  10  of the clutch hub  1 . The apparatus further includes a servo press mechanism  5  as a press mechanism that drives the pressing member  4  for the correction of surface runout. The support member  2  elastically supports an armature  14  of the clutch hub  1 , while the chuck  6  holds an axial member  16  of the clutch hub  1 . 
       FIG. 4  is a schematic diagram of the processing system  50  that includes the deformation processing apparatus for correcting surface runout  73 . In the correction processing system  50 , the clutch  1  that is an object to be corrected is taken in from a charge conveyor  71 , for the measurement of runout in a runout measurement section  72 . After that, the clutch hub  1  is positioned so as to be oriented to a predetermined direction and transferred to a runout correction section  73  that corresponds to the deformation processing apparatus for correcting surface runout  73 . Hereinafter in the correction processing system  50 , the deformation processing apparatus for correcting surface runout  73  referred to as “runout correction section  73 ”. Only one runout correction section  73  may be provided, or, as shown in  FIG. 4 , two or more runout correction sections  73  may be provided for alternate use to thereby enhance work efficiency. After that, the clutch hub  1  is taken out to the subsequent step from a discharge conveyor  75  via a runout check section  74 . If the runout check section  74  determines that a processed product does not satisfy a standard value, the product is ejected, as a defective product, to a defective product discharge section  76 . Also, a processed product is periodically ejected to a quality check product discharge section  77  to check quality of products. A delivery member  78 , which is a robot arm, is used for conveying products between these sections. 
       FIG. 5  is a specific structure diagram (center cross-sectional view) of the clutch hub  1 .  FIG. 6A  shows a front view of an electromagnetic clutch  8  that includes the clutch hub  1 .  FIG. 6B  shows a right-side partial cross-sectional view of the electromagnetic clutch  8 . In the right-side cross-sectional view, an upper half from the center shows a cross-sectional structure of the electromagnetic clutch  8 . 
     The electromagnetic clutch  8  has the clutch hub  1  that transmits power to the compressor such as of an air conditioner of an automobile. The electromagnetic clutch  8  is integrally connected to a rotary shaft of the compressor via a bolt. 
     The clutch hub  1  includes the hub member  10  which is formed by connecting an outer hub  12  to an outer periphery of a sheet-metal inner hub  11  via an elastic member  13 , such as rubber. Further, the annular armature  14  is fixed, via rivets  15 , to a bottom surface of the outer hub  12  that forms an outer peripheral surface of the hub member  10 . 
     The armature  14  is arranged, via a gap, opposed to a friction surface of a rotor  81  that configures the electromagnetic clutch  8 . The armature  14  is attracted to the rotor  81  by an electromagnetic force of an electromagnetic coil  83  which is accommodated in a stator  82 . 
     The axial member  16  of the inner hub  11  is provided being projected from the center of the plate surface near the armature  14 . The axial member  16  is provided in the inside thereof with a spline hole  17  through which the axial member  16  is spline-connected to the rotary shaft of the compressor. Thus, the axial member  16  transmits the torque of the rotor  81 , which is rotated by the torque of an engine of the automobile, to the rotary shaft. The rotor  81  is rotatably fixed with a compressor housing via a bearing  84 . 
     The clutch hub  1  has a structure in which the armature  14 , as a separate member, is fixed, via rivets, to the hub member  10  composed of the inner hub  11  and the outer hub  12 , which are obtained by sheet-metal processing. Therefore, the structure raises a problem of surface runout. The surface runout is caused in the end surface of the armature  14  (hereinafter referred to as “armature surface  141 ”) that faces the friction surface of the rotor  81 . For this reason, the surface runout of the armature  14  with respect to the axis of the inner hub  11  is required to be measured and corrected after the assemblage of the armature  14 . A flow of correcting the runout is shown in  FIG. 5 . 
     In the deformation processing system  50  for correcting surface runout shown in  FIG. 4 , the clutch hub  1  that has been taken in from the charge conveyor  71  is transferred to the runout measurement section  72  by the delivery member  78 . Thus, runout is measured, at step S 1  of  FIG. 7 , in the runout measurement section  72 .  FIG. 8  shows an example of a specific configuration of the runout measurement section  72 . The runout measurement section  72  includes a reference pin  85  which is threadably inserted from below into the spline hole  17  of the clutch hub  1 . The runout measurement section  72  also includes a work presser  86  that presses the inner hub  11  from above. The reference pin  85  is made rotatable about its axis by a work rotating motor  87 . The work presser  86  is arranged, sandwiching the inner hub  11  between itself and the reference pin  85 , so as to be coaxial with the reference pin  85  and be vertically movable. Opposed to the lower end surface of the armature  14  (armature surface  141 ), a runout measuring sensor  88  and a rivet hole detecting sensor  89  that detects the position of a rivet hole  151  are arranged. For example, the runout measuring sensor  88  and the rivet hole detecting sensor  89  are laser sensors. The work rotating motor  87  is a servo motor. 
     The inner hub  11  of the clutch hub  1  has a center portion which is held between the work presser  86  and the reference pin  85 . The reference pin  85  is rotated by the work rotating motor  87  to allow the runout measuring sensor  88  to measure a distance to the armature surface  141 . In this case, if no runout is caused in the armature surface  141 , the measured distances are uniform. However, as shown in  FIG. 9A , if the armature surface  141  has an inclination with respect to a plane perpendicular to the axial member  16  of the hub member  10 , runout will be detected with respect to the rotation angle. The rotation angle is managed by an encoder of the work rotating motor  87 . The encoder acquires the detection results of the runout measuring sensor  88  to calculate an amount of runout and determine a rotation angle having a maximum value (see  FIG. 9B ). In this case, since the shape around each rivet hole  151  may be deformed, the positions of the rivet holes  151 , which are detected by the rivet hole detecting sensor  89 , are removed from the calculation of runout. The range of removal may be arbitrarily determined. For example, measured values may be stored such as in a sequencer to prepare data relative to angles. Thus, depending on the degree of deformation of the rivet hole  151 , the range of removal may be increased with respect to the edge of the rivet hole  151 . In this way, the accuracy of measuring runout can be enhanced. 
     At step S 2  of  FIG. 7 , the runout measurement section  72  determines a position so that the value of the encoder (rotation angle), which corresponds to the maximum value of the detected runout, coincides with the angle of the fixing member  3  in the subsequent runout correction section  73 . In other words, as shown in  FIG. 10  on the left, in determining a position, a maximum-runout portion B indicated by the black circle is ensured to be constantly located at a predetermined rotation angle position with respect to the center of the inner hub  11 . Then, the clutch hub  1  is stopped at such a position. Instead of the maximum-runout portion B, a minimum-runout portion may be ensured to be located at a predetermined position. Then, at step S 3  of  FIG. 7 , keeping the predetermined rotation angle position, the delivery member  78  transfers the clutch hub  1  to the runout correction section  73 . In this case, as shown in  FIG. 10  on the right, the maximum-runout portion B, the inner hub  11  and the fixing member  3  of the runout correction section  3  are ensured to be aligned on a line. Thus, the position is optimized for the fixing member  3  to correct runout of the armature surface  141 . When the minimum-runout portion is ensured to be located at a predetermined position, the fixing member  3  is brought to a position opposite to the one shown in  FIG. 10 . 
       FIG. 11  and  FIG. 12  show an example of a specific configuration of the deformation processing apparatus for correcting surface runout  73 . In  FIG. 11 , the support member  2  that elastically supports the clutch hub  1  is fixed onto a base  21 . Above the clutch hub  1 , the pressing member  4 , which is supported by a movable member  41  of the servo press mechanism  5 , is coaxially positioned. The movable member  41  is movable in vertical and horizontal directions by a servo motor  51  that serves as a driving means. The movable member  41  determines a position, with respect to the clutch hub  1 , of the pressing member  4  mounted to an end thereof, while being able to apply a pressing force to the clutch hub  1  with a predetermined load. A load cell  52  is arranged above the pressing member  4  to enable detection of load. The fact that the pressing member  4  has been brought into contact with the inner hub  11  and then has depressed the inner hub  11  to bring it into contact with the fixing member  3 , can be confirmed by detecting the change in the load of the load cell  52 . Thus, an amount of depression of the pressing member  4  is correctly controllable as shown in  FIG. 17A  and  FIG. 17B  that will be referred to later. 
     In  FIG. 12A  and  FIG. 12B , the support member  2  is configured by fixing a retainer plate  22  to a plurality of elastic support legs  23  which are set up on the base  21 . The clutch hub  1  is placed on an opening edge portion of an opening  25  which is provided at the center of the retainer plate  22 . It is so configured that the axial member  16  of the clutch hub  1  is projected downward through the opening  25  and that a pair of chuck members  61  of the chuck  6  are located lateral to the axial member  16 . 
     The retainer plate  22  has a substantially rectangular shape. In the present embodiment, three elastic support legs  23  are mounted to the retainer plate  22 , two on the right end and one on the left end as viewed in the figure, to support the retainer plate  22  at three points. An air cylinder  62  is fixed to the lower surface of the retainer plate  22 , being positioned between the two elastic support legs  23  on the right end, to open/close the chuck members  61 . Each of the elastic support legs  23  incorporates a spring member  24  in its upper end portion to urge the retainer plate  22  upward. When the pressing member  4  is pushed down, the upper end portion of each elastic support leg  23  can be displaced downward by an amount corresponding to the contraction margin of the spring. Thus, the upper end portion of each elastic support leg  23  is ensured to allow the retainer plate  22  to descend, while elastically supporting the clutch hub  1 . The opening  25  has a substantially rectangular shape, with its right half, as viewed in the figure, facing the chuck members  61  and the left half facing the fixing member  3 . The fixing member  3 , which is fixed onto the base  21 , has an upper end portion provided with a locating portion  31  that contacts and supports the inner hub  11  of the clutch hub  1 . 
       FIG. 13  is a diagram illustrating a specific configuration of the fixing member  3 . A bolt hole  32  for fixation is formed at both ends of the fixing member  3  in the longitudinal direction. The center portion of the fixing member  3  is projected upward and has an inclined upper end surface in which the locating portion  31  having an arc shape is formed. As shown in  FIG. 12A  and  FIG. 12B , the arc-shaped locating portion  31  is formed in an upper end portion near the chuck members  61  so as to have a predetermined width and be coaxial with the axial member  16  of the clutch hub  1 . The upper end surface of the fixing member  3  is inclined from the arc-shaped locating portion  31  toward the opening edge portion of the opening  25  to form an inclined surface that smoothly inclines downward and outward from the arc. The fixing member  3  has a side face near the chuck members  61 , in which an arc-shaped recess that continues from the locating portion  31  is formed to avoid interference with the clutch hub  1 . 
     In this way, by forming the locating portion  31  into an arc-shaped surface, the load imposed at the time of correcting runout is prevented from being concentrated on a specified portion. The locating portion  31  is not necessarily required to have an arc or flat surface. Alternative to this, the entire upper surface of the fixing member  3  may be formed into a gently projected shape. 
       FIG. 14  is a diagram illustrating a specific configuration of the pair of chuck members  61 . The chuck members  61  have respective ends provided with claws  63  which are ensured to hold the axial member  16  of the clutch hub  1  from both sides. The pair of claws  63  have respective inner surfaces  64  that are opposed to each other via the axial member  16 . The inner surfaces  64  are each formed into a gentle concave surface that has a curvature radius larger than the outer diameter of the axial member  16 . In correcting runout, the claws  64  hold the axial member  16  to limit the rotation of the clutch hub  1 . The chuck members  61  only have to prevent the clutch hub  1  from being rotated by the pressing force of the pressing member  4  and thus to prevent the correcting position from being displaced. For this reason, the chuck members  61  are permitted to have a comparatively small holding force. Thus, in a state of being supported between the pair of claws  63 , the axial member  16  of the clutch hub  1  can be displaced in the vertical or horizontal direction with the depression and deformation of the inner hub  11 . 
     Referring now to the schematic diagrams of  FIGS. 15A and 15B  and  FIGS. 16A and 16B  hereinafter is described step S 4  in  FIG. 7 , a method of correcting runout of the armature surface, performed by the runout correction section  73 .  FIG. 15A  on the left shows a state where the clutch hub  1  is placed on the support member  2  of the runout correction section  73 . In this state, the pressing member  4  is located above the inner hub  11  of the clutch hub  1  so as to be coaxial with the center of the armature surface  141  and the chuck members  61 . The clutch hub  1  is placed so that the armature surface  141  is in contact with and supported by the retainer plate  22  and that the axial member  16  projected downward through the opening  25  is held by the pair of chuck members  61 . Specifically, as described above, the clutch hub  1  is placed so that a portion of the armature surface  141 , the portion having a maximum amount of runout, faces the fixing member  3 . Further, in this state, the locating portion  31  of the fixing member  3  is not in contact with the inner hub  11 , and thus the lower surface of the inner hub  11  facing the opening  25  is spaced apart from the fixing member  3 . 
     From this state, when the servo press mechanism  5  is driven to descend the pressing member  4 , an end surface of the cylindrical pressing member  4  (lower end surface in the figure) firstly comes into contact with the upper surface of the inner hub  11  of the clutch hub  1 . Then, as shown in  FIG. 15B  on the right, the lower surface of the inner hub  11  comes into contact with the locating portion  31  of the fixing member  3 . The contact portion between the locating portion  31  and the inner hub  11  in this case is indicated by the dash-dot-dot line in the surface of the locating portion  31  shown in  FIG. 13 . The contact position (position during the descending of the servo press) can be detected by detecting the change in the load of the load cell  52  shown in  FIG. 11 . As shown in  FIG. 16A  and  FIG. 16B , the pressing member  4  is further descended to bring the inner hub  11  into partial contact with the locating portion  31  of the fixing member  3 . With this contact being kept, the pressing member  4  is further pushed down until an outer peripheral portion of the inner hub  11  in contact with the pressing member  4  is depressed by a certain distance. 
     In  FIG. 16A  on the left, the axial member  16  of the clutch hub  1  before runout correction (before pressing) is not perpendicular to the horizontal armature surface  141  (inclination θ 1 ). In this state, the clutch hub  1  suffers from runout. In this case, the end surface of the cylindrical pressing member  4  is in contact with an outer peripheral edge portion of the upper surface of the inner hub  11 , the outer peripheral edge portion being located on an inner peripheral side of the armature  14  placed on the retainer plate  22 , which corresponds to an outer peripheral side with reference to the contact position at which the inner hub  11  contacts the locating portion  31 . 
     As shown in  FIG. 16B  on the right, when the pressing member  4  is descended as it is, the outer peripheral portion of the inner hub  11  is depressed. Accordingly, deformation can be caused in the plate surface of the inner hub  11  at the contact position, at which the inner hub  11  contacts the locating portion  31 . In other words, as shown in the figure, the plate surface of the inner hub  11  is bent and deformed in the cross section passing through the contact position, and inclined with respect to the horizontal plane. Accordingly, the axial member  16  is relatively displaced toward the fixing member  3 . As a result, the angle between the horizontal armature surface  141  and the axial member  16  (inclination θ 2 ) is increased. 
     Accordingly, the inclination θ 2  is permitted to form substantially a right angle by appropriately setting the amount of depression of the pressing member  4  according to the amount of runout measured in advance, thereby correcting the runout caused in the armature surface  141 . However, the amount of deformation of the sheet-metal inner hub  11  is the sum of the amount of elastic deformation and the amount of plastic deformation. The amount of elastic deformation, which rebounds after removing the load, is not reflected in the amount of correction. For this reason, as the amount of runout becomes larger, the amount of depression is increased. At the same time, the amount of depression of the pressing member  4  (amount of depression) is determined, taking account of the amount of rebound after deformation. This relationship is shown in  FIG. 17B  on the right. 
     Specifically, as shown in  FIG. 17A  on the left, the amount of runout is ranked into several stages. After that, an amount of depression required for permitting the inclination θ 2  after correction to form a right angle is preset for each rank. Then, based on the measurement performed by the runout measurement section  72 , the pressing member  4  is driven so as to achieve the amount of depression corresponding to the rank. The axial member  16  of the clutch hub  1 , which is held by the chuck members  61 , is able to slide between the pair of claws  63  as the amount of inclination of the axial member  16  changes in the course of correcting runout. Therefore, the operation of correction will not be prevented. 
     After that, at steps S 5  and S 6  of  FIG. 7 , the delivery member  78  transfers the clutch hub  1  after correction to the runout check section  74  to check whether the runout of the armature surface  141  has become equal to or less than a specified value. The configuration of the runout check section  74  is similar to that of the runout measurement section  72 . If the runout is equal to or less than a specified value, control proceeds to step S 7  where the clutch hub  1  is conveyed from the discharge conveyor  75  for the subsequent steps. Then, at step S 8 , the armature surface  141  is subjected to finishing grinding using a well-known grinding device. 
     In the finishing grinding of the armature surface  141 , the runout that has remained after the correction of runout is removed. In the present embodiment, since the surface runout is substantially completely corrected by the runout correction section  73 , only a little time and work is required for the finishing grinding. Thus, comparing with the runout correction using the conventional grinding, the processing time is remarkably shortened. Accordingly, productivity is greatly enhanced, and the clutch hub  1  having high quality can be manufactured. 
     The deformation processing apparatus for correcting surface runout  73  according to the present embodiment can be effectively used in the process of manufacturing clutch hubs of not only the air conditioners for automobiles but also various power transmission devices. Further, surface runout of a clutch hub is efficiently corrected by configuring the deformation processing system  50  for correcting surface runout, which includes the deformation processing apparatus for correcting surface runout  73 .