Patent Publication Number: US-2022219608-A1

Title: Adjusting instrument

Description:
The invention relates to an adjusting instrument for an exterior vision unit for a vehicle. 
     Adjusting instruments for an exterior vision unit, such as an exterior mirror, exterior display and/or exterior camera, are used on vehicles, for example, automobiles. Such an adjusting instrument is generally known for the purpose of an exterior mirror unit and usually comprises a housing which is pivotable relative to a base to be coupled with the vehicle in an adjustment range, for instance between two positions, typically between a drive position and a park position. Pivoting still further from the drive position to an overfold position is also possible. In the park position, the exterior vision unit extends substantially along the vehicle, in the case of an exterior mirror unit with a mirror side facing the vehicle. In the drive position, the exterior vision unit is usually directed substantially transversely to the vehicle, and in the case of an exterior mirror unit with the mirror side facing rearwards relative to the normal driving direction. Within this context, other positions are also possible, for example a work position or drive position in which the exterior vision unit includes a different angle with respect to the vehicle, for example an angle of about 60 or about 30 degrees. In the overfold position, the vision unit extends substantially along the vehicle, in the case of an exterior mirror unit with the mirror side facing away from the vehicle. With other exterior vision units, whether or not in combination with an exterior mirror, the positions mentioned can be assumed by an exterior display and/or camera lens. An exterior display and/or camera lens may then for instance be arranged on the exterior vision unit roughly in the same position as an exterior mirror, but may also be arranged on the exterior vision unit in other positions. 
     Adjusting of the exterior vision unit may be done electrically, for instance during normal use from the park position to the drive position and vice versa. The adjusting instrument is then provided with an electric drive with which the housing can be pivoted around the base. The electric drive is usually of self-locking construction. 
     The exterior vision unit may also be adjusted under the influence of an external force, for example in case of an impact such as a collision, or in manual operation. Thus, the exterior vision unit may be moved, for instance by collision with an object, from the drive position to the overfold position, or to the park position. Also, the exterior vision unit can for instance be moved manually from the park position to the drive position, and vice versa. The electric drive is then often provided with a break coupling, so that the electric drive upon being operated under the influence of an external force exceeding a defined threshold value, can be decoupled. Thus, damage of the drive can be prevented, which is especially important when the drive is of self-locking construction. After operation under the influence of an external force, the electric drive can be re-coupled again via the coupling in an electrically driven reset movement, for instance by carrying out an electrically driven reset movement towards the park position. 
     To counteract vibrations during use, it is important for the drive position to be well defined. In practice, for this purpose, often a strong spring is used, which presses the housing onto the base continuously. 
     With electric adjustment, however, such a strong pressing down of the housing on the base is less desirable, because it necessitates a relatively powerful driving motor in carrying out the adjusting movement. Because of such spring force, furthermore, upon adjustment under the influence of an external force, the drive may be subject to relatively large forces before uncoupling takes place. As a consequence, in practice, the components in the drive train of the drive must often be made more force-resistant than is necessary for driving. From the viewpoint of costs, however, it is desirable to make the drive of lighter construction. 
     From WO2012047104, in particular the embodiment of  FIG. 10 , it is known, upon manual operation from the drive position, to transfer the uncoupling force via cooperating cam rings, and, during electric adjustment, to leave the housing free of spring force, so that the electric drive is relieved. This adjustment device provides many advantages in that the electric drive can be made of light construction, and works well in practice. 
     It is disadvantageous, however, that with electric adjustment from the park position back to the drive position, the cam rings do not always interlock properly. 
     In WO 2017074193 it has therefore been proposed to arrange for the force transmission cams, in the drive position, to be supported on the housing cam track, allowing them in and near the drive position to cooperate directly with the housing, and thereby cause the cam rings to interlock better. The housing cam track is then provided with oblique flanks near a position corresponding to the drive position. When the housing pivots from the park position to the drive position, the force transmission cams, by the movement along these oblique flanks of the housing cam track, press the housing cam ring and the base cam ring into each other. Such direct control of the interlocking of the cam rings is especially advantageous because the housing is not under spring action during electric operation. 
     Such an adjusting instrument for an exterior vision unit for a vehicle according to WO 2017074193 comprises:
         a base, comprising a foot and base shaft extending therefrom along a longitudinal axis,   a housing surrounding the base shaft, which is placed on the foot and which is pivotable in an adjustment range around the longitudinal axis of the base shaft, between a park position and an overfold position, via an intermediate drive position, which housing is provided with a housing ring, and   a drive ring surrounding the base shaft, and which is provided with three force transmission cams spaced apart along the circumference with equal interspaces, which force transmission cams cooperate with the housing ring of the housing.       

     The force transmission cams in the adjusting instrument according to WO 2017074193 cooperate with the housing ring so as, upon rotation of the drive ring relative to the housing in a first direction around the base shaft near the drive position of the housing, to move the housing from a high housing position along the base shaft downwards into a low housing position in which the housing is locked against rotation. 
     The force transmission cams in the adjusting instrument according to WO 2017074193 also cooperate with the housing ring so as, upon rotation of the drive ring, to move the drive ring along the base shaft, during an electrically driven reset movement, upwards from a low drive ring position into a high drive ring position, so that the drive ring, after it has been pivoted through action of an external force, together with the housing, relative to the base shaft, can be returned again to its initial position in the drive position by the electric drive. 
     In particular, during this electric reset movement, the force transmission cams can be transferred from the housing ring near the drive position in an axially high drive ring position onto the cam ring, so that they can thereupon, in the same axially high drive ring position, upon electrically driven adjustment of the drive ring relative to the housing near the drive position be placed on the housing ring again to put the cam rings of the housing and the base, interlocking in the drive position, under spring action. 
     While the known device offers many advantages, it also has a disadvantage. The drive ring, for the sake of the supporting stability, is provided with three cams spaced apart with mutually equal interspaces. These cams cooperate with three housing track cams spaced apart on the housing ring with mutually equal interspaces. Those housing track cams are located near the drive position, and have, in circumferential direction, on one side a run-on surface which can cooperate with the force transmission cam to move the drive ring during the reset movement axially upwards into the high drive ring position, and on the other side a second run-on surface which can cooperate with the force transmission cam to press the housing axially downwards. Thus, on the housing ring three track segments are present which are each between two housing track cams and each have a first run-on surface at one end and a second run-on surface at an opposite end. 
     Especially the first run-on surface takes up a considerable part of the available circumferential space, because the drive ring has to be able to move up the run-on surface, against the action of a spring, with a cost efficiency-wise preferably relatively weak electric motor, and without a motor current limiter for cutting the electric motor coming into operation. Consequently, with a normal, electrically driven adjusting movement, the maximum angle through which the housing of the adjusting instrument can be adjusted relative to the base is relatively small. When from the drive position the housing is being moved electrically to the park position, the first run-on surfaces limit for the reset a stroke which the housing can make when it moves to park, in that the force transmission cams run against the second run-on surfaces. 
     Due to the presence of the cams and their run-on surfaces, of the 120 degrees theoretically available for adjustment, only a more limited adjustment angle of about 70 degrees is left. In a number of cases, however, an adjustment angle of more than 70 degrees is desired. For instance, in a number of cases it is desirable to place the housing from a work position in which it is virtually perpendicular to the vehicle, to a park position in which the housing is situated practically parallel along the vehicle. In other embodiments, in which for example two or only one force transmission cam is used, likewise the theoretically available adjustment angle of 180 degrees or 360 degrees is not completely available due to the presence of the cam(s) and the run-on surfaces thereof. 
     The invention contemplates an adjusting instrument with which, while preserving the advantages mentioned, the disadvantage mentioned can be counteracted. To this end, the invention provides an adjusting instrument for an exterior vision unit for a vehicle comprising:
         a base shaft extending along a longitudinal axis,   a housing surrounding the base shaft, and which is pivotable around the longitudinal axis of the base shaft in an adjustment range, and which is provided with a housing ring, and   a drive ring surrounding the base shaft, and which is provided with a force transmission cam which can cooperate with the housing ring so as, upon rotation of the housing relative to the drive ring in a first direction around the base shaft, to move the housing via the housing ring from a high housing position along the base shaft downwards into a low housing position, and upon rotation of the drive ring relative to the housing in an opposite direction around the base shaft, to move the drive ring along the base shaft upwards from a low drive ring position into a high drive ring position,   wherein the housing ring comprises a first bottom section which is rotation-coupled with the housing, and comprises a second top section which by an underside thereof is supported on the first section and which by an upper side thereof can cooperate with the force transmission cam,   wherein the top section of the housing ring is rotatable around the base shaft relative to the bottom section,   wherein the bottom section and the top section are each provided with first run-on surfaces, which pairwise cooperate to move the drive ring via the force transmission cams axially upwards into the high drive ring position, and   wherein the top section is provided with a second run-on surface which cooperates with the force transmission cam to press the housing axially downwards.       

     By thus providing a housing ring with an articulate, rotatable top section, it is made possible that by the use of intermediate run-on surfaces, space on the upper surface of the ring can be cleared, and the run-on surface remaining on the upper surface can still be rotated out of the way. 
     By providing the top section and the bottom section each with a stop surface, which stop surfaces through pairwise cooperation limit rotation of the top section relative to the bottom section in one rotation direction, it can be achieved that in one rotation direction the free rotation of the top section of the housing ring is limited and the second run-on surface becomes operative at a predetermined place, for example near the work position. 
     Elegantly, the first run-on surfaces cooperate near a work position when the drive ring moves in a first rotation direction relative to the housing, and the second run-on surfaces cooperate near the work position when the drive ring moves in a second, opposite rotation direction relative to the housing. 
     When upon rotation of the drive ring the top section of the housing ring is, relative to the bottom section of the housing ring, carried along in rotation by the force transmission cam of the drive ring, it can be achieved that the point at which the run-on surfaces cooperate can be shifted, as a result of which the free space for adjustment and hence the adjustment angle is enlarged. 
     Advantageously, the housing, with the top section of the housing ring being carried along by the force transmission cam of the drive ring, can traverse, from a first position into a second position, an angle of more than 360 degrees divided by the number of cams of the drive ring that can cooperate with the housing ring, minus at least the angle spanned by the first run-on surface upper side. Given three cams spaced apart with, for example, equal interspaces, the angle which can be traversed is, for example, more than 70 degrees, in particular more than 75 degrees, preferably about 80 degrees, and more preferably about 90 or about 100 degrees. 
     When the first run-on surfaces at the upper side of the top section of the housing ring and the second run-on surfaces at the underside of the top section of the housing ring overlap each other in circumferential direction in each case, it can be achieved that the free space for adjustment and hence the adjustment angle is enlarged. The first and second run-on surfaces may be located axially at different positions, but may also be located radially at different distances from the longitudinal axis. 
     Advantageously, the housing and a foot provided on the base shaft are each provided with a housing cam ring and a base cam ring, respectively, which in the adjustment range interlock only in the drive position, namely so that the housing is in the low housing position, and which upon pivoting of the housing relative to the base from the drive position along the longitudinal axis move apart axially, and upon further pivoting are at least partly supported on each other, namely so that the housing is in the high housing position. 
     Also, the adjusting instrument preferably comprises a spring which surrounds the base shaft and which exerts a spring force on the drive ring along the longitudinal axis in the direction of the foot. 
     Further, the adjusting instrument advantageously comprises an electric drive unit which is included in the housing, provided with an output element for electrically adjusting the instrument, the output element cooperating with the circumference of the drive ring. 
     Also, the adjusting instrument advantageously comprises a base cam track provided on the base shaft. 
     As regards the disclosure in this application, it is noted that the technical features of the adjusting instrument described in the main claim can also be seen as an invention each independently or in combination with only one or more technical features from the main claim, the dependent claims or the description. 
     The invention also relates to an exterior vision unit for a motor vehicle, comprising an adjusting instrument, and a mirror, display and/or camera coupled with the housing. 
    
    
     
       The invention will be further elucidated on the basis of an exemplary embodiment of an adjusting instrument which is shown in drawings. In the drawings: 
         FIG. 1  shows a schematic perspective exploded view of an adjusting instrument according to the invention, seen from above; 
         FIG. 2  shows a schematic perspective exploded view of the adjusting instrument of  FIG. 1 , seen from below; 
         FIG. 3  shows a schematic cross section of the adjusting instrument of  FIG. 1  in assembled condition in the drive position; 
         FIGS. 4 a  through 4 g    show a schematic side view of the adjusting instrument of  FIG. 3  during electric adjustment from the drive position shown in  FIG. 3  to the park position and back; 
         FIG. 5  shows a schematic cross section of the adjusting instrument of  FIG. 1  in assembled condition in the park position; 
         FIGS. 6 a  through 6 g    show a schematic side view of the adjusting instrument of  FIG. 5  during manual adjustment and subsequent electric resetting from the park position shown in  FIG. 5 . 
     
    
    
     It is noted that the figures are only shown by way of exemplary embodiment and should not be considered as limiting in any way. 
       FIGS. 1 and 2  show an adjusting instrument  1  for an exterior vision unit of a vehicle. The adjusting instrument  1  comprises a base shaft  2  which extends along a longitudinal axis A. The adjusting instrument  1  furthermore comprises a housing  3  which surrounds the base shaft  2 . The housing  3  is made up of a bottom member  3   a  and a top member  3   b . The housing  3  is pivotable around the longitudinal axis A of the base shaft  2  in an adjustment range, in particular from the work position I shown in  FIGS. 1 and 2  into a park position II and back. The adjusting instrument  1  furthermore comprises a housing ring  4 , and a drive ring  5  which surrounds the base shaft  2 . 
     The housing ring  4  is of articulate construction, and comprises a bottom section  4   a  and a top section  4   b . The bottom section  4   a  is rotation-coupled with the housing  3 , and in this embodiment is integrated with the bottom member  3   a  of the housing. The top section  4   b  is rotatable relative to the bottom section  4   a  and relative to the housing  3  around the longitudinal axis A. 
     The drive ring  5  is provided with three force transmission cams  6  spaced apart with equal mutual interspaces, which can cooperate with the housing ring  4  upon rotation of the drive ring  5  relative to the housing  3 . Upon rotation of the housing  3  in a first direction around the base shaft  2  relative to the drive ring  5 , represented with the closed head of arrow P, the force transmission cams  6  can cooperate by first flanks  6   a  with second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4  to move the housing  3  via the housing ring  4  from a high housing position H along the base shaft  2  downwards into a low housing position L. The top section  4   b  is thus provided with a second run-on surface  7  which cooperates with the force transmission cam  6  to press the housing  3  axially along the longitudinal axis A downwards when, for example, upon normal, electrically driven adjustment, from the park position II the drive position I is being approached, as, for example, stepwise represented in  FIGS. 4 d   - g.    
     Upon rotation of the drive ring  5  relative to the housing  3  in an opposite direction around the base shaft  2 , i.e., in the direction of the open head of arrow P, the drive ring  5 , through cooperation with the housing ring  4 , can move upwards along the base shaft from a low drive ring position  1  into a high drive ring position h. In this embodiment, that has been realized in that second flanks  6   b  of the force transmission cams  6  engage catch surfaces  9  on the upper side  8  of the top section  4   b  of the housing ring, as a result of which the drive ring  5  carries the top section  4   b  of the housing ring  4  along in rotation ( FIG. 4 c   ). The bottom section  4   a  and the top section  4   b  are each provided with three pairs of first run-on surfaces  10   a ,  10   b , spaced apart with mutual interspaces. The first run-on surfaces  10   a ,  10   b  cooperate pairwise to move the drive ring  5  via the force transmission cams  6  supported on the upper side  8  of the housing ring  4 , axially along the longitudinal axis A upwards from the low drive ring position  1  into the high drive ring position h. Thus, for example, during an electrically driven reset movement, the drive ring  5  can move upwards along the longitudinal axis A from the low drive ring position  1  into the high drive ring position h. 
     The bottom section  4   a  and the top section  4   b  of the housing ring  4  are each provided with three sets of stop surfaces  11   a ,  11   b  spaced apart with equal interspaces and which in this embodiment are configured to be substantially standing along the longitudinal axis A. The stop surfaces  11 , through pairwise cooperation, limit rotation of the top section  4   b  relative to the bottom section  4   a  in one direction of rotation, in this case rotation in the direction of the open head of arrow P. In this embodiment, the stop surfaces  11  are operative near the work position I. 
     The second run-on surfaces  7  at the upper side  8  of the top section  4   b  of the housing ring  4  and the first run-on surfaces  10   b  at the underside  12  of the top section  4   b  of the housing ring  4  are located at different positions along the longitudinal axis A of the base shaft  2 . The housing  3  can thus, from the park position II up to the drive position I, traverse an angle of more than 70°, in particular about 80°. 
     The bottom member  3   a  of the housing  3  and a foot  13  provided on the base shaft  2  are each provided with a housing cam ring  15  and a base cam ring  14 , respectively, which in the adjustment range interlock only in the drive position, namely so that the housing  3  is in the low housing position L. Upon pivoting of the housing  3  relative to the base shaft  2  from the drive position I in the direction of the park position II, i.e., in the direction of the open arrow P, the cam rings  14 ,  15  move apart axially along the longitudinal axis A. Upon further pivoting they are at least partly supported on each other, namely so that the housing  3  is in the high housing position H. 
     The drive ring  5  and hence the force transmission cams  6 , in this example, are under action of a spring. The spring is not represented to sustain easy reference and is implemented as a helical spring which surrounds the base shaft  2  and which exerts a spring force on the drive ring  5  along the longitudinal axis A. 
     The adjusting instrument  1  of this exemplary embodiment furthermore comprises an electric drive unit, also not shown, which is included in the housing  3 , provided with an output element, for example a worm wheel, for electrically adjusting the instrument  1 , the output element cooperating with the circumference  16  of the drive ring  5 , for example via a toothing. For use as an exterior vision unit for a motor vehicle, the adjusting instrument  1  comprises a mirror, display and/or camera coupled with the housing  3 . 
     The adjusting instrument  1  is furthermore implemented with a base cam track  17  provided on the base shaft  2 . The base cam track  17  is configured for it, during normal electrically driven adjustment between the drive position I and the park position II, to serve as support for the first flanks  6   a  of the force transmission cams  6 , so that the spring force is absorbed by the base shaft  2 . The housing  3  is then free of spring force, so that the cam rings  14 ,  15  on, respectively, the foot  13  of the base shaft  2  and the underside of the bottom member  3   a  of the housing  3 , can move apart easily and housing  3  can easily rotate over foot  13  when they are supported on each other. When the angle corresponding to the drive position I has been reached, the drive ring  5  makes a stroke whereby the force transmission cams  6  go over from the base cam track  17  to the upper side  8  of the top section  4   b  of the housing ring  4 . Thus, the spring force is transmitted via the housing  3 , as a result of which the cam rings  14 ,  15  on, respectively, the base shaft  2  and the housing  3  in the drive position I are energized by the spring. When during electric adjustment from the park position II the work position/drive position I is reached, the interlocking of the cam rings  14 ,  15  is controlled by cooperation of the first flanks  6   a  of the force transmission cams  6  and the corresponding second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4 ; the housing  3  then goes over from the axially high housing position H to the axially low housing position L. 
     Illustrated in  FIGS. 4 a  through 4 g   , in a schematic side view of the adjusting instrument  1 , is the operation during electric adjustment from the drive position I to the park position II and back.  FIG. 4 a    shows, on a reduced scale, just like  FIG. 3  the adjusting instrument  1  in the work position I with the housing  3  in the low housing position L. The force transmission cams  6  of the drive ring  5  are supported by their first flanks  6   a  on the second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4 . The housing cam ring  15  and the base cam ring  14  interlock, and are under action of the spring, not represented. 
       FIG. 4 b    shows that drive ring  5 , due to the output element of the electric drive engaging the circumference  16 , has made an angular stroke relative to the housing  3 , as a result of which the first flanks  6   a  of the force transmission cams  6  have gone over onto the base cam track  17 . The spring force is now transmitted via the base shaft  2 , and the housing  3  is free of spring action. 
       FIG. 4 c    shows that upon further electric adjustment, the housing  3  can now rotate relative to the drive ring  5 . The housing cam ring  15  moves upwards out of the base cam ring  14 , and the housing  3  moves from the axially low housing position L to an axially high housing position H. At the same time, the housing  3  rotates from the drive position I around the base shaft  2  in the direction of the park position II. The top section  4   b  of the housing ring  4  cooperates via the second flanks  6   b  of the force transmission cams  6  with catch surfaces  9  on the upper side  8  of the top section  4   b  of the housing ring  4 . The top section  4   b  of the housing ring  4  is now retained by the drive ring  5 , so that it stands still relative to the base shaft  2 . The bottom section  4   a  of the housing ring  4  rotates along with the housing  3 , and rotates around the base shaft  2 . 
       FIG. 4 d    shows that upon further electric adjustment, the housing  3  remains in the axially high housing position H due to the housing cam ring  15  being supported on the base cam ring  14 . The housing  3  and the bottom section  4   a  of the housing ring  4  continue to rotate until the park position II shown in  FIG. 4 d    has been reached. In the park position II, the housing  3  runs against a stop, not represented, and the electric drive stops. The second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4  and the first run-on surfaces  10   b  on the underside  12  of the top section  4   b  of the housing ring  4  do not sit in each other&#39;s way, for they are located at different height positions along the longitudinal axis A of the base shaft  2 . The housing  3  can thus, between the drive position I and the park position II, traverse an angle of more than 70°, being about 80° in this exemplary embodiment. 
       FIG. 4 e    shows that upon electric adjustment of the housing  3  back to the drive position I, the second run-on surfaces  7  at the upper side  8  of the top section  4   b  of the housing ring  4  cooperate with the first flanks  6   a  of the force transmission cams  6  to force the cam rings  14 ,  15 , not being under spring action yet, into engagement. The housing  3  begins to move downwards along the longitudinal axis A from the axially high housing position H to the axially low housing position L. 
       FIG. 4 f    shows that the cam rings  14 ,  15  are in engagement again, and that the housing  3  is in the axially low housing position L. The position corresponding to the drive position I has been reached, and the housing  3  is now rotation-coupled with the base shaft  2 . In consequence, the housing  3  continues to stand still with respect to the base shaft  2 , and the drive ring  5  rotates making an angular stroke with respect to the housing  3  and the base shaft  2 . As a result, the first flanks  6   a  of the force transmission cams  6  go over from the base cam track  17  onto the second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4 . The stop surface  11   a  on the bottom section  4   a  of the housing  3  cooperates with the stop surface  11   b  of the top section  4   b  of the housing ring  4 , and limits rotation of the top section  4   b  of the housing ring  4  relative to the bottom section  4   a  of the housing ring  4 . Further rotation of the drive ring  5  is not possible, and the electric drive stops. The housing  3  has now come to be under spring action again, and the adjusting instrument is locked in the drive position I. 
     With the aid of the housing ring  4 , and in particular via the first run-on surfaces  10   a ,  10   b , the drive ring  5 , after it, together with the housing  3 , has been adjusted angularly around the base shaft  2  under the influence of an external force, can, with the aid of the electric drive, in a reset movement, be brought into the proper position with respect to the base shaft  2  again. This is elucidated below on the basis of  FIG. 5  and  FIGS. 6 a - g   .  FIG. 5  shows the adjusting instrument  1  in the park position II with the housing  3  in the high housing position H. The force transmission cams  6  of the drive ring  5  are supported by their first flanks  6   a  on the base cam track  17 , and transmit the spring force via the base shaft  2 . The drive ring is in the axially high drive ring position h. The housing cam ring  15  is supported on the base cam ring  14 , but the housing  3  is not under spring action.  FIGS. 6 a  through 6 g    show in a schematic side view of the adjusting instrument  1  the operation during manual adjustment from the park position II in the direction of the drive position I, and subsequent electric resetting. 
       FIG. 6 a    shows on a reduced scale, just like  FIG. 5  the adjusting instrument  1  in the park position II, where an external force is exerted manually or otherwise. For ease of reference, a part of the top section  4   b  of the housing ring  4  above the first run-on surface  10 b on the underside of the top section  4   b  of the housing ring  4  is drawn transparent. 
     In  FIG. 6 b    it can be seen that the drive ring  5  has gone up, against the action of the spring not shown, and that the force transmission cams  6  have been moved by their second flanks  6 b beyond the stops  18  on the base cam track  17 . 
     In  FIG. 6 c    it can be seen that the force transmission cams  6  of the drive ring  5  thereupon carry along by their first flanks  6   a  the top section  4   b  of the housing ring  4 . The drive ring  5  is in the axially high drive ring position h. Thereupon, in an electric reset movement, via the top section  4   b  of the housing ring  4 , the bottom section  4   a  of the housing ring  4  and hence the housing  3  is carried along to the angular position corresponding to the drive position I. When the housing  3  is in the drive position I, the housing cam ring  15  and the base cam ring  14  interlock, and the housing  3  moves from the high housing position H to the low housing position L. The drive ring  5 , which is supported via the housing ring  4  on the housing  3 , thereby comes down from the axially high drive ring position h to an axially low drive ring position  1 . The housing  3  and, rotation-coupled therewith, the bottom section  4   a  of the housing ring  4  remain standing still, but the top section  4   b  of the housing ring  4  is carried along by the force transmission cams  6 , and rotates along with the drive ring  5  driven by the electric drive. This is represented in  FIG. 6 d   . This continues until the first run-on surfaces  10   a ,  10   b  on, respectively, the upper side of the bottom section  4   a  of the housing ring  4  and the underside  12  of the top section  4   b  of the housing ring  4  cooperate. This is represented in  FIG. 6 f   . The run-on surfaces  10   a ,  10   b  have a gentle slope, which can be run up with the electric drive. Due to the relative rotation of the housing ring sections  4   a ,  4   b , the top section  4   b  of the housing ring  4  moves up along the longitudinal axis A, against the action of the spring. The drive ring  5 , which via the force transmission cams  6  is supported on the top section  4   b  of the housing ring  4 , consequently moves axially upwards along the longitudinal axis A from the low drive ring position I back to the high drive ring position h. In this high drive ring position h, the force transmission cams  6  can go over onto the base cam track  17 . As a result, the first flanks  6   a  of the force transmission cams  6  go over from the base cam track  17  onto the second run-on surfaces  7  on the upper side  8  of the top section  4   b  of the housing ring  4 . The drive gear rotates further until the first flanks  6   a  of the force transmission cams abut against stops  18 . The spring now acts via the force transmission cams  6  and the base cam track  17  on the base shaft  2 , and not on the housing  3  or housing ring  4 . Electrically driven rotation of the drive ring  5  and, being rotation-coupled therewith via the force transmission cams  6 , the top section  4   b  of the housing ring, is not possible, and the bottom section  4   a  of the housing ring  4  and the housing  3  now begin to rotate together in the direction of the park position II. The housing  3 , through cooperation of the housing cam ring  15  with the base cam ring  14 , moves axially upwards along the longitudinal axis A to the high housing position H, and the housing  3  rotates together with the bottom section  4   a  of the housing ring  4  back into the park position II. The adjusting instrument  1  is then ready again for normal electrically driven adjustment from the park position II to the drive position I as set out hereinbefore on the basis of  FIGS. 4 a - g   . The invention is not limited to the exemplary embodiment represented here. Many variants are possible. Thus, the bottom section of the housing ring may be implemented as a separate part which is supported on the housing, and which is rotation-locked therewith. Also, for example, a different number of force transmission cams may be used, for example only one or two. Also, the housing may be adjustable via the adjusting instrument between other positions than specifically a drive position and a park position, for example, between two work positions, or a number of work positions and a rest position. Such variants will be clear to one skilled in the art, and are understood to be within the scope of the invention as defined in the appended claims 
     REFERENCE NUMERALS 
     
         
           1  adjusting instrument 
           2  base shaft 
           3  housing 
           3   a  bottom member housing 
           3   b  top member housing 
           4  housing ring 
           4   a  bottom section housing ring 
           4   b  top section housing ring 
           5  drive ring 
           6  force transmission cam 
           6   a  first flank force transmission cam 
           6   b  second flank force transmission cam 
           7  second run-on surface on upper side of top section housing ring 
           8  upper side of top section housing ring 
           9  catch surface on upper side of top section housing ring 
           10   a  first run-on surface on upper side of bottom section housing ring 
           10   b  first run-on surface on underside of top section housing ring 
           11  stop surfaces 
           11   a  stop surface on bottom section housing ring 
           11   b  stop surface on top section housing ring 
           12  underside top section housing ring 
           13  foot 
           14  base cam ring 
           15  housing cam ring 
           16  circumference of drive ring 
           17  base cam track 
           18  stops on base cam track 
         A longitudinal axis 
         P arrow 
         h high drive ring position 
         l low drive ring position 
         H high housing position 
         L low housing position 
         I drive position/work position 
         II park position