Timepiece escapement

Abstract

A watch escapement mechanism includes: a first escape wheel (1), a second escape wheel (2) meshing with the first escape wheel (1), and an escape fork (4) arranged to cooperate with the oscillator of the watch, wherein: the first escape wheel (1) includes a first gear train including a first locking tooth (121), the second escape wheel (2) includes a second gear train including a second locking tooth (221), and the first escape wheel (1), the second escape wheel (2) and the escape fork (4) cooperate with each other through the first locking tooth (121) and / or the second locking tooth (221).

Description

Technical Field

[0001] This invention generally relates to an escapement mechanism for mechanical watches. More specifically, it relates to an escapement mechanism comprising two escape wheels. One aspect of the invention relates to an escapement mechanism comprising an escape wheel configured to provide an impact force, particularly a tangential impact force, to the escape fork of the escapement mechanism of a watch, especially a mechanical watch. Background Technology

[0002] As shown in patent application EP4198641A1, in the prior art of escapements, the known natural escapement includes two escapement gears, each of which is configured to engage with an anchor escapement fork on one side and an impact fork mounted on the balance wheel on the other, to ensure direct engagement with one or the other of the two escapement gears. However, such escapements are bulky and contain complex mechanisms.

[0003] Document EP1367462A1 discloses an indirect double-impact escapement mechanism comprising two meshing escape wheels that cooperate with the same escape fork. In the stationary phase, the escape fork rests against the limit pin, and unlocking generates significant force and friction, which impairs overall efficiency. Furthermore, it can be noted that in document EP1367462A1, after the unlocking phase where the escape fork is locked in the stationary position by one of the two escape wheels, the other escape wheel provides the impact force to the escape fork. Therefore, precise adjustment is required to avoid any interference. However, clearance is necessary, and it mandates the specification of the escape fork's angular travel, and more generally, the specification of the escape fork's moving portion, in which the escape fork, once unlocked, does not contact either of the two escape wheels. During these angular travels or the escape fork's moving portion, the escape fork therefore does not receive impact forces from either of the two escape wheels, leading to inefficiency.

[0004] Document EP1221637A1 relates to an indirect double-impact escapement comprising two meshing escape wheels that engage with the same escape fork. Each escape wheel has a large number of teeth, while the escape fork is very small, thus requiring very precise manufacturing tolerances to ensure operation, and the escape fork cannot transfer the impact force to the balance wheel over a large angular stroke. In particular, the escape fork has a particularly limited size compared to the corresponding escape wheel size, with each escape wheel having a large number of teeth. Therefore, either the escape fork is very small, making its manufacturing complex, or the escape wheels are very large, affecting the system's compactness. Furthermore, as clearly stated in document EP1367462A1, the escapement mechanism in document EP1221637A1 cannot achieve a satisfactory impact velocity.

[0005] Document CH714200A1 discloses an escapement mechanism comprising two meshing escape wheels and cooperating with the same anchor-type escape fork. During the impact phase, the escape wheels providing the impact force pivot in the same direction as the escape fork, which leads to friction and efficiency losses. Summary of the Invention

[0006] One object of the present invention is to overcome the disadvantages of the prior art described above, and in particular to propose an escapement mechanism that is easy to manufacture and / or assemble, and / or has a compact size and / or low inertia components, and / or has high operating efficiency, and / or has improved sensitivity to shock and / or friction, and / or has a better compromise between the aforementioned limitations.

[0007] Therefore, a first aspect of the present invention relates to a watch escapement mechanism, comprising: - The first escapement wheel, which is arranged to mesh with the clock's drive gear train. - The second escapement wheel, which meshes with the first escapement wheel. - The escapement fork, which is arranged to work in conjunction with the oscillator of the clock. in: - The first escapement wheel includes a first gear train, which includes a first locking tooth. - The second escapement wheel includes a second gear train, which includes a second locking tooth. - During the first stage, namely the first stationary stage, the first escape wheel is arranged to lock the escape fork in the first stationary position using one of the first locking teeth in the first locking teeth of the first wheel gear train, followed by the second stage, namely the first impact stage. - During the third stage, the second stationary stage, the second escape wheel is arranged to lock the escape fork in the second stationary position using one of the second locking teeth in the second locking teeth of the second wheel gear train, followed by the fourth stage, the second impact stage. Its features are: - In the second phase, i.e., during the first impact phase, the first escape wheel provides impact force to the escape fork, preferably using one of the first locking teeth, and directly driving one of the second locking teeth of the second escape wheel with the other of the first locking teeth. - During the fourth stage, i.e. the second impact stage, the second escape wheel provides impact force to the escape fork, preferably using one of the second locking teeth, and is directly driven by one of the first locking teeth of the first escape wheel through the other of the second locking teeth.

[0008] According to the above embodiment, the first escape wheel and the second escape wheel cooperate with each other and each engages with the escape fork via the same locking teeth. In other words, the first wheel gear train allows the first escape wheel to cooperate with the escape fork and the second escape wheel, while the second wheel gear train allows the second escape wheel to cooperate with the escape fork and the first escape wheel. A single type of tooth (the first locking tooth) ensures contact between the first escape wheel and the escape fork and the second escape wheel, and a single type of tooth (the second locking tooth) ensures contact between the second escape wheel and the escape fork and the first escape wheel. Therefore, the structure of the first and second escape wheels can be simplified, their inertia can be reduced, and their dimensions can be designed to minimize the volume required by the escapement mechanism.

[0009] According to one embodiment, the oscillator includes an inertial element (typically a balance wheel) that exhibits oscillating motion, each oscillation including a first half-cycle (during which the balance wheel pivots or moves in a first direction of rotation or movement) and a second half-cycle (during which the balance wheel pivots or moves in a second direction of rotation or movement).

[0010] According to one embodiment, during the first half-cycle of the oscillation, a first phase, namely the first stationary phase, is followed by a second phase, namely the first impact phase, and during the second half-cycle of the oscillation, a third phase, namely the second stationary phase, is followed by a fourth phase, namely the second impact phase.

[0011] An escapement mechanism may have the following individual features or combinations thereof.

[0012] In one embodiment, the first escape wheel drives the second escape wheel only through the first locking tooth of the first wheel gear train.

[0013] In one embodiment, the second escape wheel is driven by the first escape wheel only through the second locking tooth of the second gear train.

[0014] In one embodiment, the first escape wheel and / or the second escape wheel comprises or is composed of planar gears, preferably the same planar gears. In one embodiment, each planar gear comprises only one type of tooth. In one embodiment, the first escape wheel and the second escape wheel are formed by or contain the same gear, with one gear mounted in reverse (or inverted) relative to the other. Therefore, it is generally conceivable to use the same escape gears with a single tooth train or a single type of tooth.

[0015] In one embodiment: - In the second phase, i.e., the first impact phase, the first escape wheel uses one of the first locking teeth (the tooth that contacts the escape fork during the first phase, i.e., the first stationary phase) to provide impact force to the escape fork, and directly drives one of the second locking teeth of the second escape wheel with another first locking tooth adjacent to the first locking tooth. - In the fourth phase, i.e., the second impact phase, the second escape wheel provides impact force to the escape fork using one of the second locking teeth (the tooth that contacts the escape fork during the third phase, i.e., the second stationary phase), and is directly driven by another second locking tooth adjacent to the first second locking tooth. Thus, within the same half-cycle of the oscillator, different (but adjacent) locking teeth on each escape wheel engage with the escape fork on one hand and with the other escape wheel on the other. These features allow for the separation of functions that interact separately with the escape fork and the other escape wheel, thus providing greater freedom in designing the locking tooth shape while maintaining the compactness of the escapement mechanism. In one embodiment, the first escape wheel comprises four to eight teeth, preferably six, and / or the second escape wheel comprises four to eight teeth, preferably six, with only one tooth (the adjacent tooth) driving the other escape wheel. This reduces the design difficulties arising from the clearance required to manage and avoid static indeterminacy. In other words, during the phase where the escape wheel provides the impact force, the escape wheel engages with the escape fork at a single point of contact, and also engages with the other escape wheel at a single point of contact.

[0016] In one embodiment: - Each first locking tooth includes a first recess, a second protrusion, and a distal surface starting from the tooth root. - Each second locking tooth includes a first recess, a second protrusion, and a distal surface starting from the tooth root. and: - During the first stage, i.e., the first stationary stage, or during the third stage, i.e., the second stationary stage, each distal surface of the first and second escapement wheels is arranged to contact and lock the escape fork. - During the second phase, i.e., the first impact phase, or during the fourth phase, i.e., the second impact phase, each of the second cams of the first escapement wheel is arranged to contact and drive the second cams of the second escapement wheel. - Each first recess of the first and second escape wheels is arranged to have a positive clearance or no contact with each distal surface or with each second protrusion of the second and first escape wheels, respectively. Therefore, each locking tooth of the escape wheel includes a region (distal surface) specifically for engaging with the escape fork, a region (protrusion) specifically for engaging with the other escape wheel, and a distal surface (recess) specifically for receiving the locking tooth of the other escape wheel to avoid any interference.

[0017] In one embodiment: - Each first recess has a first tooth thickness E1. - Each second protrusion has a second tooth thickness E2. and: 1.5×E1 <E2<2.5×E1。

[0018] In one embodiment: - Each distal surface of the first and second escape wheels is formed by the ends of each first locking tooth and each second locking tooth, and / or - Each distal surface of the first and second escape wheels is formed by a circular surface constituting the tooth tip, and / or - Each distal surface of the first and second escapement wheels is arranged to mate only with the escape fork.

[0019] In one embodiment: - Each distal surface of the first and second escapement wheels is arranged for, preferably only for, to engage with the escape fork and the second or first escapement wheel, respectively.

[0020] In one embodiment: - Each first locking tooth includes a first tooth tip. - Each second locking tooth includes a second tooth tip. Furthermore, each first tooth end and each second tooth end includes a first tooth side surface and a second tooth side surface, which are adjacent to each other and each has at least one first tangential direction and at least one second tangential direction, forming a convex angle Δ between them (viewed from the rotation axis of the escapement wheel in question). According to this embodiment, each locking tooth includes a first tooth side surface and a second tooth side surface at its end, with a convex angle Δ between the first tooth side surface and the second tooth side surface, thereby providing two different functional surfaces, which can further reduce the unlocking force provided by the balance wheel to unlock either of the escapement wheels.

[0021] Generally, in one embodiment, the escape fork includes: - First impact input surface and second impact input surface - First locking surface portion and second locking surface portion Furthermore, the first impact input surface and the second impact input surface are each arranged between the first locking surface portion and the second locking surface portion. In other words, the following can be defined on the escapement fork: - A locking sector angle defined by two straight lines, each line passing through the center of rotation of the escapement fork and intersecting the first locking surface portion and the second locking surface portion respectively. - An impact sector angle defined by two straight lines, each line passing through the center of rotation of the escapement fork and tangent to (or passing through) the first and second impact input surfaces, respectively. Furthermore, the locking sector angle is strictly greater than the impact sector angle.

[0022] In one embodiment, each escapement gear is arranged to apply an impact force to the escapement fork toward the outside of the escapement fork or opposite to the plane of symmetry of the escapement fork. According to this embodiment, which is the opposite of the embodiment in document EP1221637A1, the escapement fork has only one central notch defined by the first impact input surface and the second impact input surface, thus simplifying the structure while being able to transmit impact force over a large angular stroke.

[0023] In one embodiment, the escape fork includes: - First impact input surface and second impact input surface - A first locking surface portion and a first locking boss are preferably separated by a first notch, the first locking boss being disposed between the first locking surface portion and the first impact input surface. - The second locking surface portion and the second locking boss are preferably separated by a second recess, and the second locking boss is arranged between the second locking surface portion and the second impact input surface. - Such that during the first stage, i.e., the first stationary stage, the second tooth side of the first escapement wheel abuts against the first locking surface portion and / or the first locking boss of the escapement fork, and such that during the third stage, i.e., the second stationary stage, the second tooth side of the second escapement wheel abuts against the second locking surface portion and / or the second locking boss of the escapement fork. - And such that during the second phase, i.e., the first impact phase, the first tooth flank of the first escapement wheel contacts the first impact input surface, and such that during the fourth phase, i.e., the second impact phase, the first tooth flank of the second escapement wheel contacts the second impact input surface. According to this embodiment, each locking tooth that contacts the escape fork during the stationary phase can abut against two different portions of the escape fork (corresponding locking surface portions and / or locking bosses), which helps to provide a stable stationary position. Also according to this embodiment, the first locking surface portion and the first locking boss, as well as the second locking surface portion and the second locking boss, can be separated by notches, which reduces the risk of static indeterminateness, self-locking, or instability. Again according to this embodiment, the second tooth flank and the first tooth flank located at the ends of each locking tooth of the first and second escapement wheels will contact the escape fork sequentially or successively during the transition from the stationary phase to the immediately following impact phase, which can reduce the unlocking force required for the oscillator (typically the balance wheel and hairspring) to unlock the escapement mechanism.

[0024] In one embodiment, the escape fork is mounted to be pivotable and has a swing angle between a first rest position and a second rest position, between 50° and 70°, preferably between 55° and 65°, and more preferably between 57° and 63°. This swing angle is much larger than that of the escape fork in a Swiss-anchored escapement, which allows the escape wheel to deliver an impact force over a much larger angular travel, thereby maximizing the work done by either the first or second escape wheel.

[0025] In one embodiment, the first escapement wheel includes four to eight teeth, preferably six teeth, and / or the second escapement wheel includes four to eight teeth, preferably six teeth. This limited number of teeth allows for a particularly compact structure, which is an important standard, especially in dual-active half-cycle and tangentially driven escapements.

[0026] Another aspect of the invention relates to a clock that includes at least one escapement mechanism as described in the first aspect. Attached Figure Description

[0027] Other features and advantages of the invention can be more clearly understood by reading the following detailed description of embodiments of the invention, given by way of non-limiting example and illustrated in the accompanying drawings.

[0028] Figure 1 The escapement mechanism is shown, which includes a first escape wheel and a second escape wheel, an escape fork, and a balance wheel bridge of a watch oscillator. Figure 1 The escapement mechanism is shown in the first stage, namely the first stationary stage, where the escape fork is in the first stationary position, in contact with and locking the first escape wheel; Figure 2 It shows Figure 1The escapement mechanism is in the first intermediate unlocking phase immediately following the first phase, i.e., the first stationary phase; Figure 3 It shows Figure 1 The escapement mechanism is in the second stage, that is, at the beginning of the first impact stage, when the first escape wheel contacts the escape fork to provide it with impact force; Figure 4 It shows Figure 1 The escapement mechanism is in the second stage, namely the first impact stage. Figure 5 It shows Figure 1 The escapement mechanism is in the second stage, which is at the end of the first impact stage; Figure 6 It shows Figure 1 The escapement mechanism is in the third stage, namely the second stationary stage, at which time the escape fork is in the second stationary position, in contact with the second escape wheel and locking it. Figure 7 It shows Figure 1 The escapement mechanism is in the second intermediate unlocking phase, which immediately follows the third phase, i.e., the second stationary phase. Figure 8 It shows Figure 1 The escapement mechanism is in the fourth stage, which is the beginning of the second impact stage, when the second escape wheel contacts the escape fork to provide it with impact force; Figure 9 It shows Figure 1 The escapement mechanism is in the fourth stage, namely the second impact stage; Figure 10 It shows Figure 1 The escapement mechanism is in its fourth stage, which is at the end of the second impact stage; Figure 11 The first and second resting positions that the escapement fork can occupy are shown; Figure 12a and Figure 12b It shows Figure 1 Details of the escapement fork in the escapement mechanism; Figure 13 The composition is shown Figure 1 The escapement gear of the escapement mechanism, which is part of the first or second escapement wheel; Figure 14 It shows Figure 13 Details of the locking teeth of the escapement gear; Figure 15 It shows Figure 13 Details of the locking teeth of the escapement gear; Figure 16 It shows Figure 13A modified embodiment of the escapement gear; Figure 17 It shows Figure 16 Details of the locking teeth of the escapement gear; Figure 18 It shows Figure 16 Details of the locking teeth of the escapement gear; Figure 19a and Figure 19b It shows Figure 12a and Figure 12b Details of a variant embodiment of the escapement fork; Figure 20a and Figure 20b They are shown respectively Figure 1 Overall and detailed views of a variant embodiment of the escapement mechanism, particularly including the first and second escapement forks, which include... Figure 16 The escapement gear, and Figure 19a , Figure 19b The escape fork is in the first stage, that is, the first stationary position it occupies in the first stationary stage, at which time the escape fork contacts and locks the first escape wheel; Figure 21a and Figure 21b They are shown respectively Figure 20a Overall and detailed views of the escapement mechanism during the first intermediate unlocking phase immediately following the first phase, i.e., the first stationary phase; Figure 22a and Figure 22b They are shown respectively Figure 20a The escapement mechanism is in the second stage, that is, the first moment of the first impact stage, in an overall view and a detailed view, at which point the first escape wheel contacts the escape fork to provide it with impact force; Figure 23a and Figure 23b They are shown respectively Figure 20a The escapement mechanism is viewed in its overall and detailed form during the second moment of the second phase of the first impact phase. Figure 24a and Figure 24b They are shown respectively Figure 20a The escapement mechanism is viewed in its overall and detailed form during the third instant of the second phase, i.e., the first impact phase. Figure 25a and Figure 25b They are shown respectively Figure 20a The escapement mechanism is shown in the overall view and detailed view at the end of the second phase, i.e., the first impact phase. Figure 26a and Figure 26b They are shown respectively Figure 20aThe escapement mechanism is shown in the overall and detailed views during the third stage, the second stationary stage, when the escape fork is in the second stationary position, in contact with and locking the second escape wheel. Detailed Implementation

[0029] Figure 1 A watch escapement mechanism is shown, comprising: - First escapement wheel 1, which is arranged to mesh with the clock's drive gear train 99, - The second escape wheel 2, which engages with the first escape wheel 1. - Escapement fork 4, which is arranged to cooperate with the oscillator 5 of the clock.

[0030] Specifically, the first escapement wheel 1: - Can rotate around the first rotation axis A1 - Including the first escapement gear 11 and gear 13, both of which are typically press-fitted onto the first shaft defining the first rotating shaft A1. - Driven to rotate by meshing with the drive gear train 99 via gear 13. - Includes a first gear train with first locking teeth 121, each first locking tooth having a distal surface 121a.

[0031] Second escape wheel 2: - Can move around the second rotation axis A2, - Includes a second escapement gear 21, which is typically press-fitted onto a second shaft defining a second rotational shaft A2. - Includes a second gear train with second locking teeth 221, each second locking tooth having a distal surface 221a, - It is driven to rotate by engaging with the first locking tooth 121 of the first escape wheel 1 via the second locking tooth 221.

[0032] It can be noticed Figure 1 In this configuration, the first escapement gear 11 and the second escapement gear 21 are identical, only they are installed in opposite directions. Figures 13 to 15 More details of the structure of the first escapement gear 11 and the second escapement gear 21 are shown.

[0033] In particular, the first escapement gear 11 and the second escapement gear 21 are each preferably provided with six locking teeth 121, 221. More generally, the number of locking teeth 121, 221 can be between four and eight. It can be noted that a smaller number of locking teeth 121, 221 may lead to the first escapement gear 11 and the second escapement gear 21 being defined as pinions, since the Berne Dictionary defines a pinion as a toothed component that typically has 6 to 14 teeth or blades.

[0034] The locking teeth 121 and 221 are adjacent to each other, that is, the two consecutive or successive locking teeth 121 and 221 of the first escapement gear 11 and the second escapement gear 21 are separated only by a gap.

[0035] Preferably, the first escapement gear 11 and the second escapement gear 21 are identical, only assembled on their respective shafts with opposite orientations. Preferably, all locking teeth 121, 221, and in particular all distal surfaces 121a, 221a, are identical.

[0036] It can be noted that the first escapement gear 11 and the second escapement gear 21 have features such that each locking tooth 121, 221 has a first recess P1 of thickness E1 (viewed from the outside of the tooth in consideration) and a second protrusion P21, P22 of thickness E2 (viewed from the outside of the tooth in consideration) on its tooth flanks F1, F2. This feature allows the first escapement gear 11 and the second escapement gear 21 to have a smaller number of locking teeth 121, 221.

[0037] Specifically, the first recess P1 is located or substantially located between the root circle diameter DP and the pitch diameter DM, wherein the value of the pitch diameter DM corresponds to the average value of the root circle diameter DP and the first tip circle diameter DT1 (DM=(DP+DT1) / 2), and the distal surfaces 121a and 221a pass through the first tip circle diameter DT1.

[0038] In this case, Figures 1 to 15 In the illustrated embodiment, each distal surface 121a, 221a corresponds to the circular surface that forms the tip of the locking teeth 121, 221 (this circular surface is in Figure 15 (This is particularly evident in the middle). In particular, each distal surface 121a, 221a constitutes the circular end of the distal portion P3. Therefore, a circle with a diameter of DT1 can be drawn that is tangent to one or all of the surfaces 121a, 221a.

[0039] The second protrusion P21 of the tooth lateral surface F1 is located or substantially located between the pitch diameter DM and the tip circle diameter DT1, and thus includes the distal portion P3, while the second protrusion P22 of the tooth lateral surface F2 is located or substantially located between the pitch diameter DM and the tip circle diameter DT2.

[0040] The second tooth tip circle diameter DT2 is a function of the height H of the distal portion P3, which includes the distal surfaces 121a and 221a, where H = (DT1 - DT2) / 2.

[0041] The tooth thickness E of each locking tooth 121, 221, i.e., the distance separating the two tooth flanks F1, F2 in the circumferential direction perpendicular to axes A1, A2, has a maximum value E2 at or approximately at the mean diameter DM. This is the location where the derivative changes sign (i.e., an inflection point or local extremum exists), or where the slope direction changes from the first concave portion P1 to the second convex portions P21, P22. The tooth thickness E of each locking tooth 121, 221 has a minimum value E1 at the first concave portion P1. Note that 1.5 × E1 <E2<2.5×E1。

[0042] Preferably, the concave portion P1 is an arc. Preferably, the convex portions P21 and P22 are arcs.

[0043] Preferably, the first recess P1 of two adjacent teeth is located within the same arc of circle C1 (see...). Figure 13 ).

[0044] exist Figures 13 to 15 In the construction shown, it can be noted that DP ~ 0.35 × DT1. More generally, DP ≤ 0.5 × DT1, and even DP ≤ 0.4 × DT1.

[0045] exist Figures 1 to 10 In the escapement mechanism shown, the distal surfaces 121a and 221a only mate with the functional areas 41a, 41b, 43a, and 43b of the escape fork 4 to perform the corresponding rest, unlock, and impact phases. In other words, these distal surfaces 121a and 221a are not used to allow the toothed parts 11 and 21 to engage, i.e., they do not mate with the recesses P1, P21, and P22.

[0046] Figure 1 Also shown is the escapement fork 4: - It can rotate around the third rotation axis A4. - Includes a first locking device in the form of a first locking surface portion 43a for locking the first escapement wheel 1. - Includes a second locking device in the form of a second locking surface portion 43b for locking the second escape wheel 2. - Includes a first impact input device in the form of a first impact input section 41a, for receiving impact forces from the first escape wheel 1. - Includes a second impact input device in the form of a second impact input section 41b, for receiving impact forces from the second escape wheel 2. - Includes a fork-shaped member with a first fork pad 410 and a second fork pad 420, the first fork pad 410 including a first impact surface or portion 42a, and the second fork pad 420 including a second impact surface or portion 42b. - It has a plane of symmetry through the third axis of rotation A4.

[0047] The oscillator 5 includes a balance wheel 51 rotatable about a fourth rotation axis A5, and a balance wheel clamp 511 fitted with a pin 511a that engages with the fork of the escapement fork 4. The oscillator 5 also includes a resilient return element, typically a hairspring, connected to the balance wheel 51.

[0048] As will be explained below, Figures 1 to 10 The characteristic of the escapement mechanism is that the swing angle β of the escape fork is greater than 50°, usually between 55° and 60°, such as... Figure 11 As clearly shown. Figure 12a , Figure 12b Details of the different geometric features of the escapement fork 4 are shown. Specifically, the escapement fork 4 is fitted with a fork-shaped member with fork pads 410 and 420. Specifically, the fork-shaped member 400 has two first portions, namely impact portions 42a and 42b, which are arranged opposite each other and configured to transmit at least a portion of the impact force received from the first escapement wheel 1 or the second escapement wheel 2 during the impact phase to the pin 511a of the balance wheel 51. The fork-shaped member 400 includes two second portions, namely stop portions 411b and 421b, which are arranged opposite each other and each protrudes relative to one of the first portions 42a and 42b. The stop portions 411b and 421b are spaced apart from or connected to the impact portions 42a and 42b by connecting portions 411c and 421c.

[0049] These features, especially the stop portions 411b and 421b and the connecting portions 411c and 421c, are in Figure 12a Clearly visible in the middle. The large value of the swing angle β causes the stop portions 411b and 421b to protrude, and the connecting portions 411c and 421c between the stop portions 411b and 421b and the first impact surface or portion and the second impact surface or portion 42a and 42b are particularly important so that the pin 511a can pass through during unlocking (see...). Figure 1 and Figure 2 ,as well as Figure 6 and Figure 7 ).

[0050] The fork plates 410, 420 also include distal walls 412, 422 to define stop devices B1, B2 at the junctions of these walls with the stop portions 411, 421b, which are designed to engage with the clamp plate 511 in the event of an impact.

[0051] The escapement fork 4 also includes recesses 44a and 44b on opposite sides of the impact input portions 41a and 41b, adjacent to the first locking surface portion and the second locking surface portion 43a and 43b. These recesses are provided to prevent interference between the escapement wheels 1 and 2 and the escapement fork 4 outside the functional areas 41a, 41b, 43a and 43b, especially when setting the time of the watch.

[0052] It can be noticed Figure 12a In this configuration, the first impact input portion and the second impact input portions 41a and 41b are located between the first locking surface portion and the second locking surface portions 43a and 43b. Specifically, it is possible to... Figure 12a The escapement fork 4 shown is limited to the upper limit: - A locking sector angle θ1 defined by two straight lines, each line passing through the third rotation axis A4 of the escapement fork 4 and intersecting the first locking surface portion 43a and the second locking surface portion 43b respectively. - The impact sector angle θ2 is defined by two straight lines, each of which passes through the third rotation axis A4 of the escapement fork 4 and is tangent to the first impact input surface 41a and the second impact input surface 41b respectively (or passes through these first impact input surfaces and second impact input surfaces 41a, 41b). Furthermore, the locking sector angle θ1 is strictly greater than the impact sector angle θ2.

[0053] Figures 1 to 10 The different stages of the escapement mechanism maintaining the oscillation of oscillator 5 are illustrated. These stages are performed sequentially in the diagram to ensure the normal operation of the escapement mechanism.

[0054] Figure 1 The first stage, namely the first stationary stage, is shown, in which the distal surface 121a of the first escape wheel 1 contacts the first locking surface portion 43a of the escape fork 4. In this stage, the clamp 511 of the balance wheel 51 first rotates clockwise, and then rotates counterclockwise due to the elastic reset action of the elastic reset component (typically the balance spring).

[0055] Figure 2 The first intermediate stage, the "unlocking" stage, is shown, in which pin 511a acts on the second impact surface or portion 42b of the fork of the escapement fork 4 under the action of the now counterclockwise rotating balance wheel 51. This intermediate stage thus corresponds to the first unlocking stage of the balance wheel 51 or balance wheel bridge 511. In this stage, the escapement fork 4 rotates in the same pivoting direction as the first escapement wheel 1, which is clockwise in this case. This causes the distal surface 121a to leave the first locking surface portion 43a and begin to contact the first impact input portion 41a of the escapement fork 4.

[0056] Figure 3 The second stage, namely the first sub-stage of the first impact stage, is shown, in which the distal surface 121a contacts and acts on the first impact input portion 41a of the escape fork 4, causing the impact surface or portion 42a of the fork of the escape fork 4 to transmit the impact force to the pin 511a, thereby causing the balance wheel's clamp 511 to continue rotating counterclockwise. Figure 4The second stage, which is the second sub-stage of the first impact stage, is shown, in which pin 511a has just passed through the connecting line LC. Figure 5 The second stage, the third sub-stage of the first impact stage, is shown, in which pin 511a is about to lose contact with the first impact surface or portion 42a of the fork of the escapement fork 4. It can be noted that during the second stage, i.e. the first impact stage, the escapement fork 4 and the first escapement wheel 1 pivot in opposite directions of rotation.

[0057] Figure 6 The third stage, the second stationary stage, is shown, in which the distal surface 221a of the second escape wheel 2 contacts the second locking surface portion 43b of the escape fork 4. In this stage, the clamp 511 of the balance wheel 51 first rotates counterclockwise, and then rotates clockwise due to the elastic restoring action of the balance spring.

[0058] Figure 7 The second intermediate stage, the "unlocking" stage, is shown, in which pin 511a acts on the first impact surface or portion 42a of the escape fork 4 under the action of the now clockwise rotating balance wheel 51. This intermediate stage thus corresponds to the second unlocking stage of the balance wheel 51 or balance wheel bridge 511. In this stage, the escape fork 4 rotates in the same pivoting direction as the first escape wheel 1, in this case, counterclockwise. This causes the distal surface 221a to leave the second locking surface portion 43b and begin to contact the second impact input portion 41b of the escape fork 4.

[0059] Figure 8 The fourth stage, the first sub-stage of the second impact stage, is shown, in which the distal surface 221a acts on the second impact input portion 41b of the escape fork 4, causing the second impact surface or portion 42b of the fork of the escape fork 4 to transmit the impact force to the pin 511a, thereby causing the balance wheel's clamp 511 to continue rotating clockwise. Figure 9 The fourth stage, the second sub-stage of the second impact stage, is shown, in which pin 511a has just passed through the connecting line LC. Figure 10 The fourth stage, the third sub-stage of the second impact stage, is shown, in which pin 511a is about to lose contact with the second impact surface or portion 42b of the fork of the escapement fork 4. It can be noted that during the fourth stage, i.e., the second impact stage, the escapement fork 4 and the second escapement wheel 2 pivot in opposite directions of rotation.

[0060] At the end of the fourth stage, the escapement mechanism returns to its original state. Figure 1 The configuration is shown. Therefore, the operation of the escapement involves repeating these successive phases to maintain the oscillation of the balance wheel and hairspring. Thus, this operation is a cyclical process, consisting of repeating these successive phases.

[0061] Therefore, the operation of the escapement mechanism includes the following steps in sequence: - The first stage, namely the first stationary stage, in which the first escape wheel 1 and the escape fork 4 cooperate to lock their respective angular positions; - The second stage, namely the first impact stage, follows the first stage, namely the first stationary stage, in which the same first escape wheel 1 and escape fork 4 cooperate, such that the first escape wheel 1 guides the escape fork 4 to move along a predetermined angular stroke. - The third stage, namely the second stationary stage, follows the second stage, namely the first impact stage, in which the second escape wheel 2, which is kinematically connected to the first escape wheel 1, cooperates with the escape fork 4 to lock their respective angular positions. - The fourth stage, namely the second impact stage, follows the third stage, namely the second stationary stage, in which the same second escape wheel 2 cooperates with the escape fork 4, such that the second escape wheel 2 guides the escape fork 4 to move along a predetermined angular stroke. This process specifically includes: - The first intermediate stage, the "unlocking" stage, is inserted between the first stage, the first stationary stage, and the second stage, the first impact stage, in which the escape fork 4 rotates in the same direction as the first escape wheel 1.

[0062] - The second intermediate stage, the "unlocking" stage, is inserted between the third stage, the second stationary stage, and the fourth stage, the second impact stage, in which the escape fork 4 rotates in the same direction as the second escape wheel 2.

[0063] In an alternative configuration, it is entirely conceivable that the distal surfaces 121a, 221a mate with the recesses P1 and / or the protrusions P21, P22. In this way, these distal surfaces 121a, 221a would have four functions: stationary, unlocking, impact, and engagement.

[0064] Figures 16 to 18 A modified embodiment of the first escapement gear 11 and the second escapement gear 21 of the first escapement wheel and the second escapement wheel is shown, while Figure 19a , Figure 19b A variant embodiment of the escapement fork 4 is shown to provide Figures 1 to 10 An alternative embodiment of the escapement mechanism.

[0065] Combined with the above Figures 1 to 15 In the described embodiment, only the distal surfaces 121a and 221a of the distal portion P3 are functional.

[0066] exist Figures 16 to 26b In an alternative embodiment, it is proposed to configure the distal portion P3 of each locking tooth 121, 221 such that the contact surface between the escape fork 4 and the escape wheel 1 or 2 is closer to the third rotation axis A4 of the escape fork 4, particularly during the unlocking phase inserted between two consecutive stationary and impact phases.

[0067] Therefore, for the same radius R5 ( Figure 11 or Figure 20a That is, the distance from pin 511a to shaft A5 is the same. For the same fork-shaped parts 410 and 420 of the escapement fork 4, and for the same axis positions A1, A2 and A4 of the escapement wheels 1 and 2 and the escapement fork 4, the unlocking force required for the balance wheel and hairspring can still be reduced.

[0068] Therefore, such as Figure 17 and Figure 18 As shown, each distal portion P3 consists of a first portion P31 and a second portion P32, both of which are functional parts, i.e., parts that cooperate with the escapement fork 4. When viewed from axes A1 and A2, the first portion P31 forms an angle Ω between 15° and 25° with the straight line passing through axes A1 and A2 and the connection point of portions P31 and P32. When viewed from axes A1 and A2, these portions P31 and P32 form a convex angle Δ, which is strictly less than 180°, typically between 135° and 150°. Figure 17 and Figure 18 In this, each of the first part P31 and the second part P32 is a plane, but it can also be conceived as a curved surface, in which case at least one tangent of each part P31 and P32 forms a convex angle Δ, which is strictly less than 180° and usually between 135° and 150°.

[0069] Therefore, when viewed from axes A1 and A2, portions of P31 and P32 form a V-shape, just as when viewed from the outside of the escapement fork 4. Figure 12a , Figure 12b The locking surfaces 43a and 43b of the central escapement fork 4 are the same as parts 43a1, 43a2 and 43b1, 43b2.

[0070] Figure 16 Escapement gears 11 and 12 with such locking teeth 121 and 221 are shown. Figure 17 and Figure 18 Details of a specific locking tooth are shown. Figure 19a and Figure 19b An escapement fork 4 that engages with such escapement gears 11, 12 is shown.

[0071] Figure 20a and Figure 20b The escapement mechanism in its first stage, i.e., the first stationary stage, is shown (equivalent to...). Figure 1 Part Two, P32, on surface portions 43a1, 43a2 and 43b1, 43b2 (in...) Figure 19bThe two contact areas at (see and shown in detail) mate with the escape fork 4. In this particular configuration, portions 43a1 and 43b1 are planar, while portions 43a2 and 43b2 are hemispherical and protrude from portions 43a1 and 43b1, or at least, portions 43a1 and 43b1 are separated from portions 43a2 and 43b2 by notches or recesses. The shape of these portions ensures that the resultant force F between the escape wheels passes through or substantially through the third axis of rotation A4 of the escape fork 4.

[0072] The first unlocking phase (after the first stationary phase) is initiated by contact between pin 511a and part 42b, causing relative displacement of part P32 relative to parts 43a1 and 43a2 (the escape fork 4 continues to rotate in the same pivoting direction as the first escape wheel 1), until it reaches... Figure 21a , Figure 21b The configuration shown corresponds to the moment when the impact phase begins. In this configuration, part P31 momentarily contacts part 43a2, and then engages with impact input part 41a during the second phase, i.e., the first impact phase.

[0073] Figure 22a and Figure 22b The contact between the upstream portion 42a of the connecting wire LC and the pin 511a is shown. Figure 23a and Figure 23b The contact between the downstream portion 42a of the connecting wire LC and the pin 511a is shown. In these illustrations, the first portion P31 mates with portion 41a, and then the second portion P32 takes over. Figure 24a , Figure 24b The contact between the second part P32 and part 41a continues until the distal surface 121a contacts the end of part 41a, where the end coincides with the end of part 43a2. Figure 25a , Figure 25b ).

[0074] The third stage, the second stationary stage, follows, in which the locking teeth 221 of the escapement gear 21 engage with portions 43b1 and 43b2 of the escapement fork 4. Figure 26a , Figure 26b ).

[0075] Industrial applications The escapement mechanism according to the present invention can be used in industrial applications.

[0076] It is understood that various obvious modifications and improvements can be made to the various embodiments of the invention described in this specification that are applicable to those skilled in the art without departing from the scope of the invention.

[0077] Specifically, the escape wheel can be a "solid" wheel (without notches) or a wheel with notches. The same applies to the escape fork. Furthermore, escape wheels can be the same or different in shape (same or different tooth systems, single and / or composite structures, one-piece and / or assembled types, same or different numbers of teeth are conceivable), or they can be the same or different in material.

Claims

1. A watch escapement mechanism, comprising: The first escapement wheel (1) is arranged to mesh with the drive gear train (99) of the clock. The second escape wheel (2) engages with the first escape wheel (1). The escapement fork (4) is arranged to cooperate with the oscillator of the clock. in: The first escapement wheel (1) includes a first gear train, which includes a first locking tooth (121). The second escapement wheel (2) includes a second gear train, which includes a second locking tooth (221). During the first stage, i.e., the first stationary stage, the first escape wheel (1) is arranged to lock the escape fork (4) in the first stationary position using one of the first locking teeth (121) in the first gear train, followed by the second stage, i.e., the first impact stage. During the third stage, namely the second stationary stage, the second escape wheel (2) is arranged to lock the escape fork (4) in the second stationary position using one of the second locking teeth (221) in the second gear train, followed by the fourth stage, namely the second impact stage. Its features are: During the second phase, i.e., the first impact phase, the first escape wheel (1) provides an impact force to the escape fork (4), preferably using one of the first locking teeth (121), and directly driving one of the second locking teeth (221) of the second escape wheel (2) with the other first locking tooth (121). During the fourth stage, i.e. the second impact stage, the second escape wheel (2) provides impact force to the escape fork (4), preferably using one of the second locking teeth (221), and is directly driven by one of the first locking teeth (121) of the first escape wheel (1) through the other second locking tooth (221).

2. The escapement mechanism according to claim 1, wherein, The first escape wheel (1) drives the second escape wheel (2) only through the first locking tooth (121) of the first gear train.

3. The escapement mechanism according to any one of claims 1 or 2, wherein, The second escape wheel (2) is driven by the first escape wheel (1) only through the second locking tooth (221) of the second wheel gear train.

4. The escapement mechanism according to any one of claims 1 to 3, wherein, The first escape wheel (1) and / or the second escape wheel (2) include or are composed of planar gears, preferably the same planar gears.

5. The escapement mechanism according to any one of claims 1 to 4, wherein: During the second phase, i.e., the first impact phase, the first escape wheel (1) provides impact force to the escape fork (4) using one of the first locking teeth (121), and directly drives one of the second locking teeth (221) of the second escape wheel (2) with a first locking tooth adjacent to the first locking tooth (121). During the fourth phase, i.e. the second impact phase, the second escape wheel (2) provides impact force to the escape fork (4) using one of the second locking teeth (221), and is directly driven by one of the second locking teeth (221) adjacent to the second locking tooth in the second locking teeth (221).

6. The escapement mechanism according to any one of claims 1 to 5, wherein: Each first locking tooth (121) includes a first recess (P1), a second protrusion (P21, P22) and a distal surface (121a) from the tooth root. Each second locking tooth (221) includes a first recess (P1), a second protrusion (P21, P22) and a distal surface (221a) from the tooth root. in: During the first phase, i.e., the first stationary phase, or during the third phase, i.e., the second stationary phase, each distal surface (121a, 221a) of the first escapement wheel (1) and the second escapement wheel (2) is arranged to contact and lock the escapement fork (4). During the second phase, i.e., the first impact phase, or during the fourth phase, i.e., the second impact phase, each of the second protrusions (P21, P22) of the first escapement wheel (1) is arranged to contact and drive the second protrusions of the second escapement wheel (2). Each first recess (P1) of the first escapement wheel (1) and the second escapement wheel (2) is arranged to have a positive gap or no contact with each distal surface (121a, 221a) or with each second protrusion (P21, P22) of the second escapement wheel (2) and the first escapement wheel (1).

7. The escapement mechanism according to claim 6, wherein: Each first recess (P1) has a first tooth thickness E1. Each second protrusion (P21, P22) has a second tooth thickness E2. And among them: 1.5×E1 <E2<2.5×E1。 8. The escapement mechanism according to any one of claims 6 or 7, wherein: Each distal surface (121a, 221a) of the first escapement wheel (1) and the second escapement wheel (2) is formed by the ends of each first locking tooth (121) and each second locking tooth (221), and / or Each distal surface (121a, 221a) of the first escapement wheel (1) and the second escapement wheel (2) is formed by a circular surface constituting the tooth tip, and / or Each distal surface (121a, 221a) of the first escape wheel (1) and the second escape wheel (2) is arranged to engage only with the escape fork (4).

9. The escapement mechanism according to any one of claims 6 or 7, wherein: Each distal surface (121a, 221a) of the first escapement wheel (1) and the second escapement wheel (2) is arranged to engage with the escapement fork (4) and the second escapement wheel (2) or the first escapement wheel (1), respectively.

10. The escapement mechanism according to any one of claims 1 to 9, wherein: Each first locking tooth (121) includes a first tooth tip, Each second locking tooth (221) includes a second tooth tip, Furthermore, each of the first tooth tip and each of the second tooth tips includes a first tooth lateral surface and a second tooth lateral surface, the first tooth lateral surface and the second tooth lateral surface are adjacent and each has at least one first tangential direction and at least one second tangential direction, forming a convex angle Δ between them.

11. The escapement mechanism according to claim 10, The escape fork (4) mentioned therein includes: First impact input surface (41a) and second impact input surface (41b). The first locking surface portion (43a1) and the first locking boss (43a2) are preferably separated by a first notch, and the first locking boss (43a2) is arranged between the first locking surface portion (43a1) and the first impact input surface (41a). The second locking surface portion (43b1) and the second locking boss (43b2) are preferably separated by a second notch, and the second locking boss (43b2) is arranged between the second locking surface portion (43b1) and the second impact input surface (41b). During the first stage, i.e., the first stationary stage, the second tooth side of the first escape wheel (1) abuts against the first locking surface portion (43a1) and / or the first locking boss (43a2) of the escape fork (4), and during the third stage, i.e., the second stationary stage, the second tooth side of the second escape wheel (2) abuts against the second locking surface portion (43b1) and / or the second locking boss (43b2) of the escape fork (4). Furthermore, during the second phase, i.e. the first impact phase, the first tooth side of the first escape wheel (1) contacts the first impact input surface (41a), and during the fourth phase, i.e. the second impact phase, the first tooth side of the second escape wheel (2) contacts the second impact input surface (41b).

12. The escapement mechanism according to any one of claims 1 to 11, wherein the escape fork (4) is mounted to be pivotable and has a swing angle between the first rest position and the second rest position between 50° and 70°, preferably between 55° and 65°, and more preferably between 57° and 63°.

13. The escapement mechanism according to any one of claims 1 to 12, wherein the first escape wheel (1) comprises four to eight teeth, preferably six teeth, and / or the second escape wheel (2) comprises four to eight teeth, preferably six teeth.

14. A clock comprising at least one escapement mechanism according to any one of claims 1 to 13.

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