Patent Publication Number: US-11029649-B2

Title: Device for timepiece, clockwork movement and timepiece comprising such a device

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application is a 35 USC § 371 US National Stage filing of International Application No. PCT/EP2017/055876 filed on Mar. 13, 2017, and claims priority under the Paris Convention to French Patent Application No. 1652134 filed on Mar. 14, 2016. 
     FIELD OF THE DISCLOSURE 
     The present invention relates to devices for timepieces, and also to clockwork movements and timepieces comprising such devices. 
     BACKGROUND OF THE DISCLOSURE 
     Devices are known for timepieces comprising a monolithic mechanism which comprises:
         a support;   at least one inertial regulating member;   an elastic suspension linking said at least one inertial regulating member to the support and having a specific overall stiffness;
 
where said at least one inertial regulating member is suited to oscillate at a frequency f relative to the support.
       

     Document US 2013/176829 A1 describes an example of such a device. 
     The known devices of this type have the disadvantage that manufacturing tolerances induce dispersions in the oscillation frequency f, and therefore in the temporal precision of the device. 
     The purpose of the present invention is especially to remedy this drawback. 
     SUMMARY OF THE DISCLOSURE 
     For this purpose, according to the invention, a device of the type in question is characterized in that the elastic suspension comprises an elastic adjustment link having a first end linked to said at least one inertial regulating member and a second end which is connected to the support by a frequency adjustment device suited to modify the position of the second end of said elastic adjustment link relative to the support, so as to change the overall stiffness of the elastic suspension and therefore said frequency f. 
     Because of these dispositions, the oscillation frequency f can be adjusted and therefore the dispersions due to the manufacturing tolerances compensated. 
     In various embodiments the mechanism according to the invention, one and/or another of the following dispositions could further be used:
         the frequency adjustment device includes a frequency adjustment member which is linked to the second end of said elastic adjustment link, where said frequency adjustment member is adjustable in position relative to the support so as to be able to deform said elastic adjustment link;   said frequency adjustment member is mounted movably relative to the support and comprises a blocking device suited to block the frequency adjustment member relative to the support;   said blocking device comprises a screw;   said frequency adjustment member is connected to the support by an eccentric link suited to be blocked by said screw;   the monolithic mechanism additionally comprises a pallet suited for engaging with an energy distribution member provided with teeth and intended to be urged by an energy storage device, where said pallet is controlled by said at least one inertial regulating member for uniformly and alternately blocking and releasing the energy distribution member, such that said energy distribution member moves stepwise under the urging of said energy storage device according to a repetitive movement cycle, and where said pallet is suited for transferring said mechanical energy to at least one inertial regulating member during this repetitive movement cycle;   the device comprises first and second inertial regulating members connected to each other so as to always have symmetrical and opposed movements;
 
The first inertial regulating member controls the pallet,
 
The second inertial regulating member controls a balancing member for moving said balancing member according to movements symmetrical and opposed to the pallet,
 
And said elastic adjustment link comprises at least one of the first and second elastic parts, with the first elastic part connecting the second inertial regulating member to the balancing member and with the second elastic part connecting said balancing member to the frequency adjustment device;
   the first and second inertial regulating members are mounted on the support in order to oscillate in translation in a first translation direction,
 
The pallet and the balancing member are elastically mounted on the support in order to oscillate in translation in a second translation direction substantially perpendicular to the first translation direction,
 
And the frequency adjustment device is suited for adjusting the position of the second end of the elastic adjustment link relative to the support at least parallel to the second translation direction;
   each of the first and second inertial regulating members is mounted on the support by two elastic suspension branches substantially perpendicular to the first translation direction,
 
Where the pallet and the balancing member are respectively mounted on the support by two elastic suspension branches substantially perpendicular to the second translation direction;
   said second elastic part of the elastic adjustment link comprises at least one U-shaped part, comprising two branches substantially parallel to the first translation direction, having free ends which are connected respectively to the frequency adjustment member and the balancing member;   the first and second inertial regulating members are connected to each other by a pivoting balancing lever;   the pallet and the balancing member are respectively linked to the first and second regulating members by first and second elastic drive branches;   the adjustment member and the support comprise facing indexes suited for visually assessing the position of the adjustment member relative to the support;   the mechanism extends along a median plane and the inertial regulating member substantially has an axial symmetry of order n about a central axis orthogonal to said median plane and fixed relative to the support, where n is an integer at least equal to 2, where said inertial regulating member comprises a number n of stiff portions connected to each other pairwise by n elastic coupling links, and where the elastic suspension comprises n elastic suspension links respectively connecting each stiff portion of the support;   the frequency adjustment device comprises a frequency adjustment member mounted substantially adjustably by pivoting around a pivoting axis and having a main body extending between a first extremity located near the pivoting axis and a second extremity adjustable in position, where the frequency adjustment member additionally comprises a lever arm which extends from the first end to opposite from the second end  153   b , where the lever arm is linked to the second end of said elastic adjustment link, and where said lever arm is shorter than the main body of the frequency adjustment member.       

     Furthermore, the invention also relates to a clockwork movement comprising the device such as described above and said energy distribution member. 
     Finally, the invention also relates to a timepiece comprising a movement such as defined above. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Other features and advantages of the invention will become apparent during the following description of two of the embodiments thereof, given as a nonlimiting example, with reference to the attached drawings. 
       In the drawings: 
         FIG. 1  is a schematic view of a timepiece which can comprise a mechanism according to an embodiment of the invention; 
         FIG. 2  is a block drawing of the movement from the timepiece from  FIG. 1 ; 
         FIG. 3  is a plane view of a part of the movement from  FIG. 2 , comprising the regulator, pallet, balancing member, frequency adjustment member and the energy distribution member, according to a first embodiment of the invention; 
         FIG. 3A  is a detailed view in section along the line A-A from  FIG. 3 ; 
         FIGS. 4 and 5  are views similar to  FIG. 3 , showing various positions of the mechanism; 
         FIG. 6  is a view similar to  FIG. 3  in another position of the frequency adjustment member; 
         FIG. 7  is a view similar to  FIG. 3  in a second embodiment of the invention; 
         FIG. 7A  is an enlarged view of the detail VII A from  FIG. 7 . 
     
    
    
     DETAILED DESCRIPTION 
     In the various figures, the same references designate identical or similar items. 
       FIG. 1  shows a timepiece  1  such as a watch, comprising:
         a case  2 ;   a clockwork movement  3  contained in the case  2 ;   generally, a winder  4 ;   a dial  5 ;   a glass  6  covering the dial  5 ;   a time indicator  7 , comprising for example two hands  7   a ,  7   b  respectively for the hours and the minutes, arranged between the glass  6  and the dial  5  and actuated by the clockwork movement  3 .       

     As shown schematically in  FIG. 2 , the clockwork movement  3  can comprise for example:
         a mechanical energy storage device  8 , generally a barrel spring;   a mechanical transmission  9  moved by the mechanical energy storage device  8 ;   the aforementioned time indicator  7 ;   an energy distribution member  10  (for example an escapement wheel);   a pallet  11  suited for sequentially retaining and releasing the energy distribution member  10 ;   a regulator  12 , which is a mechanism comprising an oscillating regulating member controlling the pallet  11  in order to move it regularly such that the energy distribution member is moved stepwise in constant time intervals.       

     The pallet  11  and the regulator  12  form a monolithic mechanism  13 , as will be explained below. 
     The clockwork movement  3  is now going to be explained in more detail with the help of  FIG. 3 , which represents a specific case where the mechanism  13  (outside of the screw blocking mechanism described below) is a monolithic system formed of a single plate  14  (usually flat) and the mobile parts are designed for moving essentially in a median plane of said plate  14 . 
     The plate  14  can be thin, for example about 0.05 mm to about 1 mm, according to the type of material for the plate  14 . 
     The plate  14  can have transverse dimensions, in the XY plane of the plate (in particular length and width, or diameter), included between about 10 mm and 40 mm. X and Y are two perpendicular axes defining the plane of the plate  14 . 
     The plate  14  can be made from any suitable stiff material preferably having a small Young&#39;s modulus for presenting good elasticity properties and a low oscillation frequency. Examples of materials that can be used to make the plate  14  include silicon, nickel, iron-nickel alloy, steel and titanium. In the case of silicon, the thickness of the plate  14  may for example be included between 0.2 mm and 0.6 mm. 
     The various members formed in the plate  14  are obtained by making openings in the plate  14  obtained by any fabrication method used in micromechanics, in particular methods used for MEMS fabrication. 
     In the case of a plate  14  of silicon, the plate can be locally hollowed and milled for example by deep reactive ion etching (DRIE) or possibly by laser cutting for small fabrication runs. 
     In the case of a plate  14  of iron-nickel, the plate could in particular be made by the LIGA method, or by laser cutting. 
     In the case of a plate  14  of steel or titanium, the plate  14  can be hollowed for example by wire electrical discharge machining (WEDM). 
     The constituent parts of the mechanism are now going to be described in more detail. Some of these parts are stiff and others (in particular those called “elastic branches”) are elastically deformable, mainly in flexion. The difference between the stiff parts and the elastic parts is the stiffness thereof in the XY plane of the plate  14 , which is due to the shape thereof and in particular the slenderness thereof. The slenderness can in particular be measured by the slenderness ratio (ratio of length to width of the part in question). For example, the stiff parts have a stiffness in the XY plane at least about 100 times higher than the elastic parts. Typical dimensions for the elastic links, for example the elastic branches which will be described below, include lengths included for example between 5 and 13 mm and widths included for example between 0.01 mm (10 μm) and 0.04 mm (40 μm), in particular about 0.025 mm (25 μm). Considering the width of the beams and the thickness of the plate  14 , the aspect ratio of these beams in longitudinal section is included between 5 and 60. The largest possible aspect ratio is preferred in order to limit the out of plane oscillation modes. 
     The plate  14  forms a fixed outer frame  15  which is fastened to a support plate  14   a , for example by screws or the like (not shown) passing through holes  15   a  of the frame  15 . The support plate  14   a  is securely joined to the case  2  of the timepiece  1 . The frame  15  can at least partially surround the energy distribution member  10 , the pallet  11  and the regulator  12 . 
     The energy distribution member  10  can be an escapement wheel rotationally mounted for example on the support plate  14   a , so as to be able to turn around a rotation axis Z 0  perpendicular to the XY plane of the plate  14 . The energy distribution member  10  is urged in a single direction of rotation  16  by the energy storage [device]  8 . 
     The energy distribution member  10  has outer teeth  17 . 
     The pallet  11  is a stiff part which can comprise a stiff body  18  extending for example parallel to the X-axis and two parallel stiff lateral arms  19 ,  20  extending for example parallel to the Y-axis on either side of the energy distribution member  10 . The arms  19 ,  20  respectively comprise two stop members  21 ,  22  shaped like fingers projecting towards each other from the arms  19 ,  20  in the X-axis direction. 
     The pallet  11  is elastically connected to the frame  15  so as to be able to move parallel to the X-axis in a translation direction O 2 . Advantageously, the pallet  11  can be connected to the frame  15  by an elastic suspension, comprising for example two elastic branches  23  substantially parallel to the Y-axis. Possibly, the elastic branches  23  can be connected to the body  18  and arranged on either side of the lateral arms  19 ,  20  by framing these lateral arms. 
     The pallet  11  can additionally comprise a stiff arm  24  extending along the Y-axis towards the regulator  12 , opposite from arm  20 . 
     The pallet  11  can additionally comprise a monostable elastic member  11   a , which can have the shape of an elastic tab whose free end comes to bear on the teeth  17  of the energy distribution member  10 . The monostable elastic member  11   a  can be connected to the stiff arm  19  of the pallet  11 , for example by an elastic suspension comprising two parallel elastic branches  11   b  extending along the Y-axis from the free end of the stiff arm  19 , in extension of the stiff arm  19  to a stiff support  11   c  which bears the monostable elastic member  11   a . The monostable elastic member  11   a  can extend along the Y-axis in the direction of the regulator  12 , from the stiff support  11   c . The monostable elastic member  11   a  serves such that the energy distribution member  10  transfers a precisely determined mechanical energy to the regulator, on each operating cycle of the clockwork movement  3 , as explained in European patent application 14/197015 (EP 3,032,350). 
     The mechanism  13  further comprises a balancing member  25  which can be formed from one part with the frame  15  and which is carried on the frame  15  for oscillating parallel to the X-axis, in the translation direction O 2 . The balancing member  25  can for example comprise:
         a stiff body  26  extending parallel to the X-axis, symmetrically to the body  18  of the pallet about an axis of symmetry Y 0  parallel to the aforementioned Y-axis;   a stiff arm  28  extending along the Y-axis towards the regulator  12 , symmetrically to the arm  24  of the pallet about the axis of symmetry Y 0 .       

     The balancing member  25  can also be inside the frame  15  and can be connected to the frame  15  by an elastic suspension, for example comprising two elastic branches  27  substantially parallel to the Y-axis and symmetric to the elastic branches  23  of the pallet  11 . Potentially, the elastic branches  23  can be connected to the body  26  of the balancing member  25 . 
     The pallet  11  and the balancing member  25  are each mounted on the frame  15  for oscillating in circular translation, with an oscillation amplitude in the translation direction O 2  and a secondary oscillation amplitude, nonzero, perpendicular to the second translation direction. Said oscillation amplitude in the translation direction O 2  is larger than the secondary oscillation amplitude of the pallet and of the balancing member, for example at least 10 times larger than the secondary oscillation amplitude of the pallet and of the balancing member. 
     The balancing member  25  can advantageously have a mass substantially identical to that of the pallet  11 , for example included between 90% and 110% of the mass of the pallet  11 . The mass of the balancing member is very close to that of the pallet but is not necessarily identical in order to allow for the fact that the stresses applied to one or the other of these members are not entirely symmetrical (for example the pallet is in contact with the energy distribution member whereas the balancing member is not). 
     The regulator  12  is a mechanical oscillator comprising first and second regulating members  29 ,  30 , each forming a stiff inertial mass, and each connected to the frame  15  by an elastic suspension which is suited so that the first and second regulating members  29 ,  30  oscillate along the Y-axis, in a translation direction O 1 . 
     The elastic suspension is formed by the set of elastic links  31 ;  36 ,  55  which connect (directly or indirectly) the first and second regulating members  29 ,  30  to the frame  15 . This elastic suspension has some overall stiffness, on which depends the oscillation frequency f of the first and second regulating members  29 ,  30 . 
     The elastic suspension of the first and second regulating members  29 ,  30  can for example comprise two elastic branches  31  for each regulating member  29 ,  30  that extend substantially along the X-axis and are connected to the frame  15 . 
     Each of the first and second regulating members  29 ,  30  is therefore mounted on the frame  15  for oscillating in circular translation, with a first oscillation amplitude in the translation direction O 1  and a secondary oscillation amplitude, nonzero, perpendicular to the translation direction O 1 . Said oscillation amplitude in the translation direction O 1  is larger than the secondary oscillation amplitude of the first and second regulating members, for example at least 10 times larger than the secondary oscillation amplitude. 
     In the example shown, the first and second regulating members  29 ,  30  can each have a C shape, with the main body  32  extending along the Y-axis between two lateral arms  33  extending towards the inside of the frame  15 . The aforementioned elastic branches  31  can advantageously be connected to the free ends of the lateral arms  33 , which would allow having elastic branches  31  that are long and therefore particularly flexible. 
     The first and second regulating members  29 ,  30  can be two parts symmetric about the aforementioned axis of symmetry Y 0 , with identical or substantially identical mass. Between them they can define a free central space  34 . 
     The first and second regulating members  29 ,  30  can be connected respectively to the pallet  11  and to the balancing member  25 , for example by elastic drive branches  36 . Thus, the first regulating member  29  commands the movements of the pallet  11  and the second regulating member  30  commands the movements of the balancing member  25 . 
     The elastic drive branches  36  can for example extend substantially along the X-axis. The elastic drive branches  36  can in particular be connected respectively to the free ends of the stiff arm  24  of the pallet and the stiff arm  28  of the balancing member. 
     Possibly, each of the first and second regulating members  29 ,  30  may comprise a notch  35  open along the X-axis between the main body  32  and the stiff arm  33  closest to the pallet  11  or balancing member  25 , and the corresponding elastic drive branch  36  may be connected to the main body  32  at the bottom of said notch  35 , which allows lengthening the elastic drive branches  36  and therefore increasing the flexibility thereof. 
     A stiff balancing lever  37 , mounted pivoting around a central rotation center P, is arranged in the free inner space  34 . The balancing lever  37  may possibly have a substantially M shape, with the central V shaped part  38  separating from the center of rotation P and two lateral arms  39 . 
     The lateral alarms  39  can be respectively connected to the first and second regulating members  29 ,  30 , for example by two elastic branches  40  extending substantially along the Y-axis. 
     The balancing lever  37  can be mounted, by an elastic suspension  43 , on a stiff support  40   a  stiffly connected to the frame  15 . The stiff support  40   a  can for example comprise an arm  41  extending along the axis of symmetry Y 0 , from the frame  15  to a head  42  which can for example extend along the X-axis by giving a T shape to the support  40   a.    
     The elastic suspension  43  can for example comprise:
         a stiff pivoting member  44  arranged inside the balancing lever  37 , comprising for example a central core  45  near the center of rotation P and extending along the X-axis between two enlarged heads  46 ;   two intermediate stiff bodies  47 ,  48  arranged on either side of the central core  45  near the center of rotation P;   two elastic branches  49  respectively connecting the free ends of the head  42  of the stiff support  41  to the stiff intermediate body  47 ;   two elastic branches  50  connecting respectively the stiff intermediate body  47  to one of the free ends of the enlarged heads  46 ;   two elastic branches  51  symmetric to elastic branches  50  connecting respectively the stiff intermediate body  48  to one of the free ends of the enlarged heads  46 ;   two elastic branches  52  connecting the stiff intermediate body  48  respectively to the ends of the central part  38  of the balancing lever.       

     The balancing lever  37  compels the first and second regulating members  29 ,  30  to move symmetrically and oppositely along the translation direction O 1 , which, via the elastic drive branches  36 , compels the pallet  11  and the balancing member  25  to move symmetrically and oppositely along the translation direction O 2 , as shown in  FIGS. 4 and 5  which show the two end-of-range positions of the mechanism  13 . 
     With these opposing movements, a dynamic balancing of the mechanism  13  is possible, in this way the sensitivity of the mechanism  13  to shocks, gravity and more generally to accelerations can be reduced. 
     The mechanism  13  further comprises a frequency adjustment device comprising a frequency adjustment member  53 , with which to finely adjust the oscillation frequency of the regulator  12 , in particular during mounting of the movement  3 . The frequency adjustment member  53  can for example be formed from a single part in the plate  14  with the other members of the aforementioned mechanism  13 . 
     The frequency adjustment member  53  is connected, directly or indirectly, to at least one other regulating member  29 ,  30  by an elastic link described as adjustment  36 ,  55 . The frequency adjustment member  53  is furthermore adjustable in position relative to the support plate  14   a  and the frame  15  so as to be able to deform the elastic adjustment link  36 ,  55  and thus apply an adjustable elastic stress on the regulating member in question, so as to influence the overall stiffness of the elastic suspension of the regulator  12 , and therefore the aforementioned frequency f. 
     The frequency adjustment member  53  can for example be connected to the frame  15  by two elastic branches  54  extending along the Y-axis. 
     In the example shown in  FIG. 3 , the elastic adjustment link  36 ,  55  comprises two elastic parts:
         a first elastic part formed by the elastic branch  36  connecting the second regulating member  30  to the balancing member  25 ;   and a second elastic part  55  connecting the balancing member  25  to the frequency adjustment member  53 .       

     The second elastic part  55  may comprise at least one U-shaped part, or be constituted by a U. In this case, the elastic link  55  can comprise two branches substantially parallel to the Y-axis which are connected to each other at an end close to the frame  15 , and whose free ends are connected respectively to the frequency adjustment member  53  and to the balancing member  25 . 
     The frequency adjustment member  53  is mounted movable relative to the frame  15  and to the support plate  14   a , at least parallel to the X-axis, for example by means of the aforementioned elastic branches  54 . The frequency adjustment member  53  comprises a blocking device  56  suited for blocking the frequency adjustment member  53  relative to the support plate  14   a , and therefore relative to the frame  15 . The blocking device can include for example a screw  56  screwed into the support plate  14   a  around an axis  58 . 
     More specifically, in the example considered, as shown in  FIGS. 3 and 3A , the frequency adjustment member  53  can be connected to the support plate  14   a  by an eccentric link, which can comprise for example a disk-shaped eccentric cam  56   c , through which the stem  56   b  of the screw  56  passes, whereas the head  56   a  of the screw  56  comes to bear on said eccentric cam  56   c  to block it. The eccentric cam  56   c  is centered on an axis  57  offset from the axis  58  of the screw  56 . 
     Advantageously, the adjustment member  53  and the frame  15  (or the support plate  14   a ) comprise facing indexes  60 ,  61  suited for visually assessing the position of the adjustment member  53  relative to the frame  15 . In the example shown, the frame  15  comprises a projection  59  comprising a rectilinear edge provided with several indexes facing the frequency adjustment member  53 , and the frequency adjustment member  53  comprises a point  61  or the like facing the indexes  60 . 
     On  FIG. 3 , the eccentric cam  56   c  is in the position where the frequency adjustment member  53  is the closest to the pallet  11  and does not impose an elastic preload on the balancing member  25 . The frequency f of the regulator  12  is then maximal. 
     The previously described mechanism operates according to the principle explained in the aforementioned European patent application 14/197015 (EP 3,032,350). In the following explanation of this operation, the concepts of top/bottom left/right are used to clarify the description in light of the orientation of the drawings from  FIGS. 3 to 5 , but these indications are not limiting. 
     In the situation from  FIG. 3 , the pallet  11  is in an extreme “right” position imposed by the elastic transmission branch  36  and the energy distribution member  10  comes to pivot under the effect of the energy storage device  8 , and during this movement the monostable elastic member  11   a  deflects and then releases by transmitting the mechanical energy thereof to the regulator  12 , as explained in the aforementioned European patent application 14/197015. The tooth  17  of the energy distribution member located towards the left in  FIG. 3  is then stopped against the stop member  21  located on the left of the pallet  11 . The elastic branches  31  are in resting position. 
     The first and second regulating members  29 ,  30  oscillate in the translation direction O 1  between the two extreme positions shown respectively in  FIGS. 4 and 5 , where the frequency f can be included for example between 20 and 30 Hz. 
     In a semi-cycle of movement, for example when the first regulating member  29  moves from the extreme “top” position of  FIG. 4  to the extreme “bottom” position from  FIG. 5 , the second regulating member  30  moves from the extreme “bottom” position from  FIG. 4  to the extreme “top” position from  FIG. 5 , because of the balancing lever  37 . During this time, the pallet  11  moves from the extreme “left” position from  FIG. 4  to the extreme “right” position from  FIG. 3  at the moment when the first and second regulating members moved to the neutral position from  FIG. 3 , and then the pallet  11  continues towards the left  5  to the extreme “left” position from  FIG. 5 , where the energy distribution member  10  again escapes and turns one step under the urging of the energy storage mechanism  8 . During this time, the balancing member  25  follows a movement symmetric and opposite to the pallet  11 . 
     The pallet  11  and the balancing member  25  therefore oscillate with a frequency  2   f  in the translation direction O 2 . 
     The operation is the same when next moving from the position from  FIG. 5  to the position from  FIG. 4 . The aforementioned steps are then repeated indefinitely. When it is necessary to perform a fine adjustment of the frequency f of the regulator, for example upon initial mounting of the movement  3  or after maintenance, an operator can loosen the screw  56  and adjust the position of the frequency adjustment member  53 , manually or by automated means, until obtaining the exact desired frequency (measured by conventional means, notably optical), possibly by guiding with the indexes  60 ,  61 . In the position from  FIG. 6 , the frequency adjustment member  53  is in the extreme position thereof farthest from the pallet  11  (meaning the position farthest to the right in  FIG. 6 ), such that the second elastic part  55  imposes a stress towards the right on the balancing member  25 , thus modifying the oscillation frequency f of the system. 
     In the second embodiment of the invention, shown in  FIGS. 7 and 7A , the above explanations relating to  FIGS. 1 and 2  remain valid. 
     The pallet  11  and the regulator  12  form an advantageously monolithic mechanism  13 , formed in a single plate  14  (usually flat) and for which the mobile parts are designed to move essentially in a median plane of said plate  14 . The explanations about the plate  14  given relating to the first embodiment remain valid in the second embodiment. 
     The plate  14  comprises frame  15  which is secured to a support plate  14   a , for example by screws or the like (not shown) passing through holes  15   a  of the support  15 . The support plate  14   a  is securely joined to the case  2  of the timepiece  1 . 
     The energy distribution member  10  can be an escapement wheel rotationally mounted for example on the support plate  14   a , so as to be able to turn around a rotation axis Z 1  perpendicular to the XY plane of the plate  14 . The energy distribution member  10  is urged in a single direction of rotation  16  by the energy storage device  8 . 
     The energy distribution member  10  has outer teeth  17 . 
     The regulating member  118  of the regulator  12  is connected to the support  15  by an elastic suspension  119  connecting said regulating member to the support. More specifically, said regulating member  118  can have substantially an axial symmetry of order n about a central axis Z′ 0  orthogonal to the XY-plane and fixed relative to the support  15 . By “have substantially an axial symmetry of order n,” it is understood that the regulating member  118  is essentially conformed to this symmetry, but that some parts of relatively negligible mass might not have this symmetry (for example parts serving to couple the pallet with the regulating member). 
     Said regulating member  118  comprises a number of stiff portions n connected together pairwise by n elastic coupling links, where n is an integer at least equal to 2. 
     The elastic suspension  119  has n elastic suspension links connecting respectively each stiff portion of the regulating member to the support  15 . 
     In particular, the elastic suspension can be provided such that the regulating member  118  is substantially mobile in rotation around the central axis Z′ 0 . 
     Advantageously, the number n is equal to 3; it can just the same be equal to 2 or more than 3. When the number n is 3 or more, each stiff portion of the regulating member  118  is connected to two adjacent stiff portions of the regulating member respectively by two elastic coupling links. 
     The regulating member  118  of the regulator  12  can have a general annular shape centered on the central axis Z′ 0  and comprise 3 stiff portions  120  connected pairwise between them by 3 elastic coupling links  121 . 
     The elastic suspension  119  which connects the regulating member  118  of the regulator  12  to the support  15  comprises 3 elastic suspension links  122  respectively linking each stiff portion  120  to the support  15  such that each stiff portion  120  is mobile with a movement at least of rotation around the central axis Z′ 0 , where the regulating member  118  has an overall movement substantially of rotation around the central axis Z′ 0 . 
     Each elastic suspension link  122  advantageously comprises at least one elastic branch  123 , for example one elastic branch  123 . Each elastic branch  123  can possibly comprise a stiff segment  123   a , for example towards the center of said elastic branch  123 . 
     Because the elastic branches  123  deflect during the rotation of the regulating member, the stiff portions  120  of the regulating member are mobile both in rotation and in radial translation about the central axis Z′ 0 . 
     The support  15  can possibly have a substantially star shape, with three branches  15   b  connected by a central part  15   c  near the axis Z′ 0 . 
     The stiff portions  120  of the regulating member  118  can each comprise a part  124  with circular-arc shape centered on the central axis Z′ 0 . The circular-arc shaped parts  124  are neighbors of each other and together form a discontinuous ring centered on the central axis Z′ 0 . 
     Each elastic branch  123  can extend substantially radially relative to the central axis Z′ 0  and connect the circular-arc shaped part  124  of one of the stiff portions  120  to the aforementioned central portion  15   c  of the support  15 . 
     The circular-arc shaped parts  124  each extend angularly between a first end  125  and a second end  126  which mutually overlap in the angular direction. For example, each first end  125  can form a first finger  125   a  extending towards the adjacent stiff portion  120  and each second end  126  can form a second finger  126   a  extending towards the adjacent stiff portion  120 , where each first finger portion  125   a  overlaps the second finger  126   a  of the adjacent stiff portion  120  towards the outside. 
     The second end  126  of each circular-arc shape part  124  can be extended substantially radially towards the inside by a stiff arm  127  terminated by a beak  128  extending angularly beyond the second end, in the direction of the adjacent stiff portion  120 . 
     Each elastic coupling link  121  may comprise at least one elastic coupling branch  121   a  (here two parallel elastic coupling branches  121   a ) extending substantially radially relative to the central axis Z′ 0  and connecting the beak  128  of each stiff portion  120  to the first end  125  of the circular-arc part  124  of the adjacent stiff portion  120 . 
     The travel of each stiff portion  120  of the regulating member can be limited by means for limiting movement relative to the support  15 , for limiting the travel, in particular angular, of the stiff portions  120  and protecting the mechanism  13  in particular in case of shock or more generally when it experiences strong accelerations. 
     These means for limiting movement can comprise a slit  129  laid-out in each circular-arc part  124  and extending angularly around the central axis Z′ 0 , and the pin  130  which is rigidly connected with the support  15  (in fact, fixed to the support plate  14 A) and which is arranged in the slit  129 . The slits  129  are shaped according to the kinetics of the stiff portions  120  during the rotational movement of the regulating member  118 . The slits  129  therefore do not have a circular shape centered on the central axis Z′ 0 , but instead here have a spiral segment shape. 
     The pallet  11  and the energy distribution member  10  can be arranged inside the regulating member  118 . 
     The pallet  11  is a stiff part which can comprise a stiff body  131  near the circular-arc part  124  of one of the stiff portions  120  of the regulating member. The pallet  11  can additionally comprise a stiff drive arm  132  which is rigidly connected with the stiff body  131  and which extends from one of said stiff bodies  131  towards one of the branches  15   b  of the support. 
     The pallet  11  is elastically connected to the support  15 , so as to be able to oscillate, for example according to a substantially rotational movement about an axis Z 2  perpendicular to the XY plane. The oscillations of the pallet  11  are commanded by the regulating body  118 . 
     For that purpose, the stiff arm  127  of one of the stiff portions  120  of the regulating member can be extended inward by an additional stiff arm  133  whose free end is connected to the free end of the stiff drive arm  132  by an elastic drive branch  134 . 
     Advantageously, the pallet  11  can be connected to the support  15  by an elastic suspension, comprising for example two elastic branches  135  for pallet suspension converging substantially towards the axis Z 2 . Possibly, the elastic branches  135  can connect the stiff body  131  to the free end  15   d  of one of the branches  15   b  of the support. 
     The pallet  11  comprises two stop members  136 ,  137 , shaped like tabs projecting substantially towards the Z 1  axis, which are suited for engaging with the energy distribution member  10 . 
     The pallet  11  is thus commanded by said regulating member  118  for regularly and alternately blocking and releasing the energy distribution member  10  by means of stop members  136 ,  137 , such that said energy distribution member  10  moves stepwise in the direction  16  under the urging of the energy storage device  8  in a cycle of repetitive movement, and said pallet  11  is further suited for transferring the mechanical energy to the regulating body  118  during this repetitive movement cycle, in a well-known way. 
     In the sample implementation, the total mass of the oscillating parts of the mechanism can be about 0.33 g and their inertia about 20.19×10 −9  kg·m 2 ; the oscillating frequency of the regulating member  118  is about 18 Hz and the rotational stiffness of the mechanism is about 2.58×10 −4  Nm/rad. Such a mechanism has a very good isochronism, which leads to a very good time precision. 
     The mechanism  13  additionally comprises a frequency adjustment device with which to adjust the aforementioned frequency f. This frequency adjustment device comprises a stiff frequency adjustment member  153 , with which to finely adjust the oscillation frequency of the regulator  12 , in particular during mounting of the movement  3 . The frequency adjustment member  153  can for example be formed from a single part in the plate  14  with the other members of the aforementioned mechanism  13 . 
     The frequency adjustment member  153  is connected, directly or indirectly, to at least one of the stiff portions  120  of the regulating member  118  by an elastic link referred to as adjustment  155 . The frequency adjustment member  153  is furthermore adjustable in position relative to the support plate  14   a  and the support  15  so as to be able to deform the elastic adjustment link  155  and thus apply an adjustable elastic stress on the regulating member  118 , so as to influence the overall stiffness of the elastic suspension of the regulator  12 , and therefore the aforementioned frequency f. 
     The frequency adjustment member  153  can have an elongated shape extending between a first end  153   a  and a second end  153   b . The frequency adjustment member  153  can be arranged inside the regulating member  118 , for example between one of the branches  15   b  of the support  15  and one of the aforementioned stiff arms  127 . The second end  153   b  can possibly have a fork shape or comprise a hole for passage for an adjustment screw  156 . The second end  153   b  can possibly be arranged facing a notched part  15   e  of the adjacent branch  15   b  of the support. 
     The frequency regulating member  153  can for example be connected to one of the branches  15   b  of the support  15  by two elastic branches  154 . The elastic branches  154  may converge towards the first end  153   a , which thus defines a pivoting axis Z 3  of the frequency adjustment member  153  (perpendicular to the aforementioned XY plane). The notched part  15   e  of the branch  15   b  adjacent to the frequency adjustment member  153  may advantageously have an edge  15   f , that is substantially circular and centered on the pivoting axis Z 3 , which may possibly be substantially in contact with the second end  153   b  of the frequency adjustment member  153  and thus contribute to guiding the frequency adjustment member  153  when the position thereof is adjusted. The notched part  15   e  of the branch  15   b  in question can possibly comprise indexes  60  such as described in the first embodiment. 
     In the example shown in  FIGS. 7 and 7A , the frequency adjustment member  153  comprises a lever arm  153   c  which extends the first end  153   a  opposite from the second end  153   b . This lever arm  153   c  can extend with some angle relative to the main body of the frequency adjustment member  153  (meaning the part included between the first and second ends  153   a ,  153   b ), for example with an angle of about 90°. The lever arm  153   c  is advantageously shorter than the main body of the frequency adjustment member  153 , for example 3 to 6 times shorter, which allows a movement of the first end  153   a  to induce a relatively smaller movement of the free end of the lever arm  153   c.    
     The elastic adjustment link  155  can connect the free end of the lever arm  153   c  to the regulating member  118 , for example to the free end of the stiff arm  127  adjacent to the frequency adjustment member  153 . 
     In the example shown, this elastic adjustment link  155  can comprise three elastic branches  155   a ,  155   b ,  155   c , comprising a first elastic branch  155   a  leaving from the free end of the lever arm  153   c  and extending to a first elbow, the second elastic branch  155   b  extending from the first elbow to a second elbow and the third elastic branch  155   c  extending from the third elbow to the free end of the aforementioned stiff arm  127 . 
     The frequency adjustment member  153  can be adjusted by pivoting the second end  153   b  thereof around the pivoting axis Z 3  and then held in position by the aforementioned adjustment screw  156 . The adjustment screw  156  can for example pass through a circular-arc shaped slot  161  arranged in the support plate  14   a . This slot can have a substantially circular-arc shape centered on the pivoting axis Z 3 . The adjustment screw  156  can for example be screwed into a nut (not shown) placed under the support plate  14   a . The adjustment and holding in position of the frequency adjustment member  153  could be done by any other means such as eccentric connection or other. 
     When it is necessary to perform a fine adjustment of the frequency f of the regulator, for example upon initial mounting of the movement  3  or after maintenance, an operator can loosen the adjustment screw  156  and adjust the position of the frequency adjustment member  153 , manually or by automated means, until obtaining the exact desired frequency (measured by conventional means, notably optical).