Patent Document

TECHNICAL FIELD 
   The present invention relates to an axial adjusting device. In particular, the invention concerns an axial adjusting device with a spring support during the return motion. 
   BACKGROUND OF THE INVENTION 
   The invention relates to an axial adjusting device having two discs which are rotatable relative to one another and coaxially supported relative to one another. Between the two discs, balls are guided in pairs of ball grooves in the discs. The depth of the pairs of ball grooves is variable across the circumference of the discs. One of the discs is axially supported and one is axially displaceable against resilient returning forces of the spring mechanism. At least one of the discs can be driven rotatably by a motor via a gear drive. 
   In this embodiment, a rotatingly driven disc can, at the same time, constitute the axially displaceable disc, but this is an exception. Normally, the supported disc is rotatingly driven and the axially displaceable disc which, in turn, is supported thereon via the balls, is held in a rotationally fast way. 
   For the purpose of actuating the axial adjusting device, the motor is driven in a first direction of rotation, with the at least one disc coupled to the motor via reduction stages being rotated and with the axially displaceable disc which, in turn, supports itself on the axially supported disc, being axially displaced against resilient returning forces of the spring mechanism. 
   As a result of the discs rotating relative to one another, the balls, which rest in pairs of ball grooves against end positions and which, at the same time, are positioned therein in the deepest groove portions, run towards shallower groove portions. As a result, the discs are pushed away from one another. 
   If the motor is driven in the opposite direction or is switched so as to be current-free, the displaceable disc is pushed back by the resilient returning forces applied thereto by the spring means and the at least one rotatably drivable disc is rotated back actively by the motor or as a result of the effect of the balls in the ball grooves until the balls in their pairs of ball grooves stop against the end positions simultaneously. As a result of the balls stopping in this way against the ends of the ball grooves, the rotating masses of this system, i.e., the rotatable one of the discs, the gears of the gear drive and the shaft of the motor with the rotor mass, are stopped abruptly. 
   Even elastic deformation of the motor shaft caused by the pulse generated as a result of the rotating masses stopping abruptly, can lead to tooth fracture at the pinion or at the set of gears. This is because, when the motor shaft is bent, the points of force application in the toothings move outwardly, resulting in loads acting on the pinion or the set of gears exceeding the design loads. 
   SUMMARY OF THE INVENTION 
   It is therefore an object of the present invention to provide a design which is able to accommodate, in a damage-free way, the pulse generated when the above-mentioned rotating masses are braked after the balls have been stopped. 
   According to a first solution, there is provided a second spring mechanism which—during the return motion of the discs, after the balls have reached their end positions in the ball grooves, which end positions are determined by the greatest groove depth—permit the drivable disc to overshoot against the resilient returning forces of the second spring mechanism. As a result of the second spring mechanism, it is ensured that, up to a limited extent, it is possible for the current-free motor or, optionally, for the electrically braked motor, to continue to rotate without being overloaded, with the rotating masses then being spring suspended and, preferably, additionally, being braked by a damping process. 
   According to one embodiment, one of the gears of the gear drive comprises hub elements and gear rim elements which are separate from one another and which are resiliently supported relative to one another by the second spring mechanisms. The second spring mechanisms are helical pressure springs which are positioned in the hub and gear rim elements in the circumferential direction. 
   According to a further embodiment, the undriven disc of the discs is held by a holding element in the housing in a rotationally fast way. The holding element is supported by a second spring mechanism so as to be resiliently deflectable. The holding element, in particular, is a holding pin which is radially displaceable relative to the disc, and which engages a resting trough at the disc edge and is resiliently supported in the housing via pressure springs. 
   According to another embodiment, in the region following the end position determined by the greatest groove depth, the ball grooves comprise a rising run-out portion. The second spring mechanism is provided for returning the axially displaceable disc. In particular, the spring mechanism can be formed by helical pressure springs arranged so as to extend in an axis-parallel way relative to the disc. 
   According to a second solution, there is provided a second spring mechanism which, during the return motion of the discs, prior to the balls reaching end positions in the ball grooves, corresponding to a greatest groove depth, is resiliently pretensioned against a returning force. In this way, it is ensured that even before the balls stop against end positions in the ball grooves, the rotating masses are resiliently spring-suspended and, in particular, the spring movement is additionally dampened. There is no need for any overshooting after the end positions have been reached. The first solution, above, may also be combined with the second solution, herein. 
   In a further embodiment, the second spring mechanism is formed by a leaf spring which is fixed to one of the discs and whose free end co-operates with a stop at the other one of the discs. For dampening purposes, the free end of the leaf spring can slide along the other one of the discs before the end stop is reached. 
   According to a still further embodiment, the second spring mechanism is formed by an elastic rubber or plastic element which is fixed to one of the discs and co-operates with a stop at the other one of the discs. In particular, the rubber or plastic element can include suitable internal damping means. 
   Preferred embodiments of the invention are illustrated in the drawings and will be described below. Other advantages and features of the invention will become apparent upon reading the following detailed description and appended claims, and upon reference to the accompanying drawings. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     For a more complete understanding of this invention, reference should now be made to the embodiments illustrated in greater detail in the accompanying drawings and described below by way of examples of the invention. 
     In the drawings: 
       FIG. 1  is an axial section through an inventive device according to a first embodiment with spring mechanisms in a multi-disc gear. 
       FIG. 2  shows a multi-disc gear according to  FIG. 1  in the form of a detail
         A) in an axial view;   B) in an axial section along line A—A; and   C) in an axial section along line B—B.       
       FIG. 3  shows an inventive device according to a second embodiment with elastically resilient holding pins:
         A) in an axial section; and   B) in an axial view.       
       FIG. 4  shows a holding pin as an enlarged detail in a design which is modified as compared to  FIG. 3 . 
       FIG. 5  is an axial section through an inventive device according to a third embodiment with a ball groove shape co-operating with the spring mechanism. 
       FIG. 6  shows one of the discs according to  FIG. 5  in the form of a detail:
         A) in an axial view;   B) with a ball groove shape according to  FIGS. 1–4 ; and   C) with a ball groove shape according to  FIG. 5 .       
       FIG. 7  shows an inventive device according to a fourth embodiment with spring mechanisms which act between the discs, in a first variant
         A) in an axial section; and   B) in an axial view.       
       FIG. 8  shows the two discs with a leaf spring according to  FIG. 7  in the form of a detail:
         A) in an axial section along line C—C of  FIG. 8B ;   B) in an axial view; and   C) in a perspective view.       
       FIG. 9  shows an inventive device according to a fourth embodiment with spring mechanisms which act between the discs, in a second variant,
         A) in an axial section; and   B) in an axial view.       
       FIG. 10  shows the two discs according to  FIG. 9  in the form of a detail:
         A) in an axial section along line A—A of  FIG. 10B ;   B) in an axial view;   C) in a perspective view; and   D) in the form of a detail along line C—C of  FIG. 10B .       
   

   DETAILED DESCRIPTION OF THE INVENTION 
     FIG. 1  shows an axial setting device according to the present invention in a mounted condition. The end of a motor shaft  12  projects from a housing  13  of the driving motor  11 . The motor housing  13  is inserted into a centering bore  101  in a housing wall  102  in bore  103 . A shaft journal  14  with a driving pinion  15  is positioned on the shaft end  12 . A bearing journal  18  on which a sleeve pinion  19  is directly supported via two needle bearings  41 ,  42  is inserted into the housing wall  102 . A multi-part gear  20  engaging the pinion  15  is pressed on to the sleeve pinion  19 . Further details regarding the gear  20  will be described below. Via its toothing, the sleeve pinion  19  engages a tooth segment  22  which is firmly connected to a first disc  24  of the adjusting device. Via a needle bearing  23 , the first disc  24  is rotatably supported on the projection of the cover  25  on which it is axially supported via an axial bearing  26 , a disc  27  and a securing ring  28 . The rotatingly drivable first disc  24  co-operates with a second disc  29  which is slidingly supported on a projection at the first disc  24  and which, via an axial bearing  30  and a disc  31 , is supported on a first spring mechanism in the form of pressure springs  33  in the coupling cover  25 . The helical pressure springs  33  are arranged so as to extend in an axis-parallel way relative to the second disc  29 . Pressure pins  32  forming the setting members are positioned in the pressure springs  33 . In the faces of the first and second discs  24 ,  29  which face one another, there are provided pairs of grooves  34 ,  39  whose depth is circumferentially variable and in which there run balls  35  held in a ball cage  36 . Each of the grooves  34 ,  39  extends from a first stop with the greatest groove depth to a second stop with the smallest groove depth. 
   The second disc  29  comprises a radial projection  37  with a guiding claw  38 . The guiding claw  38 , in a longitudinally displaceable way, slides on a holding pin  40  which is firmly inserted in a bore  105  in a housing wall  106  and which, in this way, holds the axially displaceable second disc  29  in a rotationally fast way. 
     FIG. 2  shows the gear  20  in the form of an enlarged detail, with the individual parts being described jointly below. The gear  20  comprises two hub discs  51 ,  52  which are pressed directly on to the sleeve pinion  19 . Between the two, a gear rim  53  is axially fixed but rotationally movable, while allowing the required axial play. Both the hub discs  51 ,  52  and the gear rim  53  comprise window openings  54 ,  55  and inner apertures  56  respectively, which, in the circumferential direction, all have approximately the same length and into which there are jointly inserted second spring mechanisms such as helical pressure springs  57  which are held in position by the window openings  54 ,  55  and inner apertures  56  respectively and are supported on the ends of the openings  54 ,  55  and apertures  56  respectively. Consequently, when the hub discs  51 ,  52  are rotated relative to the gear rim  53 , the helical pressure springs  57  are axially shortened. Such shortening generates a returning force which acts against the relative rotation. 
   If the adjusting device is adjusted positively by the driving motor  11 , this causes the first disc  24  to rotate, as a result of which the balls  35  running from deeper ball groove regions to shallower ball groove regions axially displace the second disc  29  on the cover projection against a returning force of the springs  33 . The cover  25  normally forms part of a coupling carrier of a locking coupling in a differential drive. When the adjusting device is returned, the first disc  24  is rotated back by the driving motor  11  in the opposite direction until the balls  35  reach the end positions in the ball grooves  34 ,  39 . The resulting abrupt braking of the first disc  24  is not directly transmitted to the rotor mass of the driving motor because the gear  20 , while the pressure springs  57  are being shortened, permits overshooting so that only the relatively small mass of the sleeve pinion  19  is braked in an uncushioned way, whereas the greater rotor mass is cushioned. The driving motor is normally a frequency-modulated electric motor. 
     FIG. 3  shows an axial setting device in accordance with the present invention in a mounted condition.  FIG. 3B  shows an axial view of the device of  FIG. 3A .  FIGS. 3A and 3B  will be described jointly below. The end of a motor shaft  12  projects from a housing  13  of the driving motor  11 . The motor housing  13  is inserted into a centering bore  101  in a housing wall  102 . A shaft journal  14  with a driving pinion  15  is positioned on the shaft end  12 . A bearing journal  18  on which a sleeve pinion  19  is directly supported via two needle bearings  41 ,  42  is inserted into the housing wall  102  in bore  103 . A gear  20  engaging the pinion  15  is pressed on to the sleeve pinion  19 . Via its toothing, the sleeve pinion  19  engages a tooth segment  22  which is firmly connected to a first disc  24  of the adjusting device. Via a needle bearing  23 , the first disc  24  is rotatably supported on the projection of the cover  25  on which it is axially supported via an axial bearing  26 , a disc  27  and a securing ring  28 . The rotatingly drivable first disc  24  cooperates with a second disc  29  which is slidingly supported on a projection at the first disc  24  and which, via an axial bearing  30  and a disc  31 , is supported on a first spring mechanism in the form of pressure springs  33  in the coupling cover  25 . The helical pressure springs  33  are arranged so as to extend in an axis-parallel way relative to the second disc  29 . Pressure pins  32  forming the setting members are positioned in the pressure springs  33 . In the faces of the first and second discs  24 ,  29  which face one another, there are provided pairs of grooves  34 ,  39  whose depth is circumferentially variable and in which there run balls  35  held in a ball cage  36 . Each of the grooves  34 ,  39  extends from a first stop with the greatest groove depth to a second stop with the smallest groove depth. 
   The second disc  29  comprises a radial projection  37  with a guiding groove  38 ′. The guiding groove  38 ′, in a longitudinally displaceable way, slides on a multi-part holding pin  60  which, by way of a semi-spherical head  63 , engages the guiding groove  38 ′ and which, in this way, holds the axially displaceable second disc  29  in a rotationally fast way. The holding pin  60  is supported in a sleeve member  61  so as to extend radially relative to the disc axis and is resiliently supported thereon via plate pressure springs  66 . The sleeve member  61 , by way of a thread  62 , is directly threaded into a bore  105  in the housing wall  106 . 
   If the adjusting device is adjusted positively by the driving motor  11 , this causes the first disc  24  to rotate, as a result of which the balls  35  running from deeper ball groove regions to shallower ball groove regions axially displace the second disc  29  on the cover projection against a returning force of the springs  33 . The cover  25  normally forms part of a coupling carrier of a locking coupling in a differential drive. When the adjusting device is returned, the first disc  24  is rotated back by the driving motor  11  in the opposite direction until the balls  35  reach the end positions in the ball grooves  34 ,  39 . The resulting braking of the first disc  24  is cushioned in that the first disc  24  and the second disc  29  overshoot, with the plate springs  66  being shortened, so that the entire gear drive is braked in a cushioned way, i.e. in particular also the rotor mass. The cone of the holding pin  60  rises in the wedge-shaped guiding groove  38 ′ which, towards one side, rises steeply. Via the balls resting against the end stops, the two discs  24 ,  29  remain firmly coupled. The driving motor is normally a frequency-modulated electric motor. 
     FIG. 4  shows the resilient holding pin  60 ′ in a second embodiment in the form of an enlarged detail. The holding pin  60 ′ is resiliently supported via two helical pressure springs  64 ,  65  in the sleeve member  61 . Instead of the semi-spherical head, there is provided a cone  63 ′. 
     FIG. 5  shows an axial setting device according to the present invention in a mounted condition. The end of a motor shaft  12  projects from a housing  13  of the driving motor  11 . The motor housing  13  is inserted into a centering bore  101  in a housing wall  102 . A shaft journal  14  with a driving pinion  15  is positioned on the shaft end  12 . A bearing journal  18  on which a sleeve pinion  19  is directly supported via two needle bearings  41 ,  42  is inserted into the housing wall  102  in bore  103 . A gear  20  engaging the pinion  15  is pressed on to the sleeve pinion  19 . By way of its toothing, the sleeve pinion  19  engages a tooth segment  22  which is firmly connected to a first disc  24  of the adjusting device. Via a needle bearing  23 , the first disc  24  is rotatably supported on the projection of the cover  25  on which it is axially supported via an axial bearing  26 , a disc  27  and a securing ring  28 . The rotatingly drivable first disc  24  cooperates with a second disc  29  which is slidingly supported on a projection at the first disc  24  and which, via an axial bearing  30  and a disc  31 , is supported on a first spring mechanism in the form of pressure springs  33  in the cover  25 . The helical pressure springs  33  are arranged so as to extend in an axis-parallel way relative to the second disc  29 . Pressure pins  32  forming the setting members are positioned in the pressure springs  33 . In the faces of the first and second discs  24 ,  29  which face one another, there are provided pairs of grooves  34 ,  39  whose depth is circumferentially variable and in which there run balls  35  held in a ball cage  36 . 
   The second disc  29  comprises a radial projection  37  with a guiding claw  38 . The guiding claw  38 , in a longitudinally displaceable way, slides on a holding pin  40  which is firmly inserted in a bore  105  in a housing wall  106  and which, in this way, holds the axially displaceable second disc  29  in a rotationally fast way. 
     FIG. 6  shows the second disc  29  of  FIG. 5  in an axial view, with the projection  37  and the guiding claw  38  being shown in the form of details. This illustration shows the shape of the ball grooves  39  in detail. They extend from a first axial stop region  71  with a greater depth at the end A to a second axial stop  72  with a smaller depth at the end B. In a plan view, the ball grooves in the first disc  24  are identical, so that pairs of grooves can be made to overlap with their respective first ends A, with the ball resting against the first end stops A and with the discs being in their closest positions. A rotation of the discs relative to one another causes the balls in both grooves of a pair of grooves to run towards the ends B, as a result of which the axially movable second disc  29  moves away from the axially supported first disc  24 . 
     FIG. 6B  shows the track shape according to  FIGS. 1 to 4 , wherein the ball stops  71 ,  72  are provided at the shallowest point A and at the flattest point B of the ball groove  39  and comprise the shape of a spherical cup. 
     FIG. 6C  shows the ball groove shape according to  FIG. 5 , wherein the deepest point of the ball groove  39  at the end A does not form the stop. Instead, there is provided a rising run-out portion  73  which, if the discs are rotated further beyond their end position, again causes the discs to move away from one another, so that the pressure springs  33  are shortened once again, as a result of which the rotor mass and the entire rotational mass of the drive are cushioned by the returning force of the pressure springs  33  when overshooting their end positions. 
     FIG. 7A  shows an inventive axial adjusting device in a mounted condition. The end of a motor shaft  12  projects from a housing  13  of the motor  11 . The motor housing  13  is inserted into a centering bore  101  in a housing wall  102 . A shaft journal  14  with a driving pinion  15  is positioned on the shaft end  12 . A bearing journal  18  on which a sleeve pinion  19  is directly supported via two needle bearings  41 ,  42  is inserted into the housing wall  102  in a bore  103 . A gear  20  engaging the pinion  15  is pressed on to the sleeve pinion  19 . Via its toothing, the sleeve pinion  19  engages a tooth segment  22  which is firmly connected to a first disc  24  of the adjusting device. Via a needle bearing  23 , the first disc  24  is rotatably supported on the projection of the cover  25  on which it is axially supported via an axial bearing  26 , a disc  27  and a securing ring  28 . The rotatingly drivable first disc  24  cooperates with a second disc  29  which is slidingly supported on a projection at the first disc  24  and which, via an axial bearing  30  and a disc  31 , is supported on a first spring mechanism in the form of pressure springs  33  in the cover  25 . The helical pressure springs  33  are arranged so as to extend in an axis-parallel way relative to the second disc  29 . Pressure pins  32  forming the setting members are positioned in the pressure springs  33 . In the faces of the first and second discs  24 ,  29  which face one another, there are provided pairs of grooves  34 ,  39  whose depth is circumferentially variable and in which there run balls  35  held in a ball cage  36 . Each of the grooves  34 ,  39  extends from a first stop with a greatest groove depth to a second stop with the smallest groove depth. 
   The second disc  29  comprises a radial projection  37  with a guiding claw  38 . The guiding claw  38 , in a longitudinally displaceable way, slides on a holding pin  40  which is firmly inserted in a bore  105  in a housing wall  106  and which, in this way, holds the axially displaceable second disc  29  in a rotationally fast way. 
   The plan view of  FIG. 7B  shows that, at the projection  37  of the second disc  29 , there is affixed a leaf spring  81  whose free end cooperates with a stop curve  82  at the tooth segment  22  of the first disc  24 . Initially, the end of the leaf spring  81  slides along the stop curve  82  while generating friction forces until it stops at a stop  83  at the tooth segment  22 , with the leaf spring being shorted during further rotation. In this embodiment, effective engagement of the leaf spring at the stop  83  takes place prior to the balls having reached the end stops in the ball grooves. 
     FIGS. 8A ,  8 B and  8 C show additional views of the first and second discs  24 ,  29  of  FIGS. 7A and 7B . In  FIGS. 8A–8C , any details which are identical to those shown in  FIG. 7  have been given the same reference numbers. To that extent, reference is made to the above description. Further details do not need to be mentioned. 
     FIG. 9  shows an axial setting device according to the present invention in a mounted condition. The end of a motor shaft  12  projects from a housing  13  of the motor  11 . The motor housing  13  is inserted into a centering bore  101  in a housing wall  102 . A shaft journal  14  with a driving pinion  15  is positioned on the shaft end  12 . A bearing journal  18  on which a sleeve pinion  19  is directly supported on the journal  18  via two needle bearings  41 ,  42  is inserted into the housing wall  102  in a bore  103 . A gear  20  engaging the pinion  15  is pressed on to the pinion sleeve  19 . Further details regarding the gear  20  will be given below. Via its toothing, the sleeve pinion  19  engages a tooth segment  22  which is firmly connected to a first disc  24  of the adjusting device. Via a needle bearing  23 , the first disc  24  is rotatably supported on the projection of the cover  25  on which it is axially supported via an axial bearing  26 , a disc  27  and a securing ring  28 . The rotatingly drivable first disc  24  cooperates with a second disc  29  which is slidingly supported on a projection at the first disc  24  and which, via an axial bearing  30  and a disc  31 , is supported on a first spring mechanism in the form of pressure springs  33  in the coupling cover  25 . The helical pressure springs  33  are arranged so as to extend in an axis-parallel way relative to the second disc  29 . Pressure pins  32  forming the setting members are positioned in the pressure springs  33 . In the faces of the first and second discs  24 ,  29  which face one another, there are provided pairs of grooves  34 ,  39  whose depth is circumferentially variable and in which there run balls  35  held in a ball cage  36 . Each of the grooves  34 ,  39  extends from a first stop with a greatest groove depth to a second stop with a smaller groove depth. 
   The second disc  29  comprises a radial projection  37  with a guiding claw  38 . The guiding claw  38 , in a longitudinally displaceable way, slides on a holding pin  40  which is firmly inserted in a bore  105  in a housing wall  106  and which, in this way, holds the axially displaceable second disc  29  in a rotationally fast way. 
   In the plan view of  FIG. 9B , the leaf spring between the two discs explained with reference to  FIG. 7B  is replaced by a resilient element  91  which is fixed to the projection  37  of the second disc  29  and which is acted upon by a buffer web  92  affixed by bolts  93 ,  94  to the disc segment  22 . The buffer web  92  effectively stops against the resilient element  91  even before the balls have reached the end stops in the ball grooves. The resilient element  91  is preferably elastic rubber or plastic having internal damping. 
     FIGS. 10A–10D  show additional views of the first and second discs  24 ,  29  of  FIGS. 9A and 9B . In addition to the details previously discussed with respect to  FIGS. 9A and 9B ,  FIG. 10D  shows a bolt  95  which holds the resilient element  91  at the projection  27 . 
   When the disc  24  is rotated back by the driving motor  11 , the spring mechanisms of the devices according to  FIGS. 7 to 10  ensure that, even before the end stops in the ball grooves are reached, the rotor mass and the entire rotational mass of the drive are braked relative to the second disc  29 , held in a rotationally fast way, before the end stops in the ball grooves are reached. Thereafter, the effect of the spring elements will be to achieve a certain amount of turning back from the end stops to the extent that this is possible relative to the returning force of the helical pressure springs  33 . 
   From the foregoing, it can be seen that there has been brought to the art a new and improved axial adjusting device. While the invention has been described in connection with one or more embodiments, it should be understood that the invention is not limited to those embodiments. Thus, the invention covers all alternatives, modifications, and equivalents be included in the spirit and scope of the appended claims.

Technology Category: 2