Escapement mechanism for timepiece

Abstract

An escapement mechanism (10 ') comprising: a first escapement wheel (1') comprising a plurality of first locking surfaces (121a ') and a first drive gear (111') forming a first main drive gear, a second escapement wheel (2 ') comprising a plurality of second locking surfaces (221a') and a second drive gear (211 ') forming a second main drive gear, an inertia member, a pallet (4') comprising: a locking surface portion (43a '), the locking surface part is arranged to be in contact with the first escapement wheel (1 ') and the second escapement wheel (2'), pulse receiving equipment and pulse transmitting equipment, and is characterized in that the second main driving gear is meshed with the first main driving gear and is matched with the escapement fork (4 ') in the same plane.

Description

Technical Field

[0001] The present invention relates generally to escapements for timepieces equipped with an inertial member such as a balance wheel, and in particular to a double active half-period tangentially driven escapement. Background Art

[0002] In the prior art of dual active semi-periodic escapement mechanisms, for example, a dual active semi-periodic tangentially driven escapement mechanism proposed in World Patent WO2013182243A1 is known, which includes a single escape wheel and two pallet forks that cooperate with each other and with the escape wheel. On the other hand, in order to make the space occupied comparable to that of a traditional escapement mechanism (such as a Swiss lever escapement mechanism), this system requires the manufacture and assembly of complex small-sized components.

[0003] Also known is European patent EP1367462A1, which relates to an indirect double-impulse escapement with a lock arranged between two escape wheels. In this document, the dimensions of the lock are particularly limited compared to the corresponding dimensions of the escape wheels, each of which has a large number of teeth. As a result, the dimensions of the lock are very small, which makes its manufacture complex, or the dimensions of the escape wheels are large, which affects the compactness of the system. Finally, the direction of the contact force between a given tooth of either of the two escape wheels and the first or second locking means of the lock makes it necessary to use a dowel pin or a washer, especially in the event of a collision.

[0004] Patent CH712631A1 relates to an escapement mechanism comprising two escapement gears and a balance wheel that interacts with the two escapement gears and an oscillator. Summary of the invention

[0005] The object of the present invention is to solve the above-mentioned defects of the prior art. Specifically, a double active half-cycle tangential drive escapement mechanism is first proposed, whose components are easier to manufacture and / or assemble, and / or occupy less space, and / or operate robustly.

[0006] To this end, a first aspect of the present invention may relate to an escapement mechanism of a timepiece movement, comprising:

[0007] a first escape wheel, mounted rotatably about a first axis, arranged to mesh with a gear train of a timepiece movement, such as a power gear train, to receive power, and comprising a plurality of first locking surfaces and a first drive gear,

[0008] - a second escape wheel, mounted to rotate about a second axis of rotation, comprising a plurality of second locking surfaces and a second drive gear,

[0009] - an inertial member, mounted to rotate about a third axis of rotation, arranged to exhibit oscillations, each oscillation comprising a first half-period and a second half-period,

[0010] - Pallet fork, mounted to rotate about a fourth axis, comprising:

[0011] a first locking surface portion arranged to come into contact with one of the plurality of first locking surfaces to lock the rotation of the first escape wheel,

[0012] a second locking surface portion arranged to be in contact with one of the plurality of second locking surfaces to lock the rotation of the second escape wheel,

[0013] - pulse receiving means arranged to receive a first pulse from the first escape wheel during a first half-period of the oscillation of the inertial element, and to receive a second pulse from the second escape wheel during a second half-period of said oscillation of the inertial element,

[0014] - a pulse transmission device, arranged to transmit at least a part of the first pulse or the second pulse to the inertial member,

[0015] Features:

[0016] - a plurality of first locking surfaces and a first drive gear form a first main drive gear,

[0017] - a plurality of second locking surfaces and a second drive gear forming a second main drive gear,

[0018] The second main drive gear meshes with the first main drive gear to transmit power from the first escapement wheel to the second escapement wheel in the inner plane.

[0019] And wherein the first main driving gear and the second main driving gear are arranged to cooperate with the escapement fork in the same plane.

[0020] According to the above embodiment, the escapement mechanism comprises a single pallet fork and two escape wheels. Unlike the world patent WO2013182243A1 which comprises two pallets indexed angularly to each other, the above embodiment does not provide any indexing due to the single pallet fork. In addition, a particularly compact assembly can be obtained, since the pallet fork is rotatably mounted to alternately lock the first or second escape wheel: the first or second escape wheel can be mounted or arranged side by side, in particular symmetrically with respect to the plane through which the respective axes of rotation of the inertial piece and the pallet fork pass.

[0021] It can be noted that according to the escapement mechanism of the above embodiment, during the same swing (reciprocating) of the inertial member, two pulses are transmitted to the inertial member to maintain its swing. In fact, the escapement fork can:

[0022] - receiving a first pulse from the first escape wheel and transmitting it to the inertial element during the first half of the cycle of the inertial element (for example the outward stroke constituting the first half of the oscillation), and

[0023] A second pulse from the second escape wheel may be received and transmitted to the inertial element during its second half-period (for example the return stroke constituting the second half of said oscillation).

[0024] In this embodiment, the cooperation between the two escape wheels and the cooperation between each escape wheel and the pallet fork are performed on the same plane, although the overall thickness of the escapement mechanism is reduced and the parts are easy to manufacture because of the flat design without protrusions.

[0025] The invention can be defined by the following features taken alone or in combination.

[0026] In one embodiment, the inertial part comprises a balance wheel. In particular, the inertial part may comprise a balance wheel, a balance wheel shaft and a bridge with pins, which are connected to a hairspring.

[0027] In one embodiment, the first locking surface portion is arranged to lock the rotation of the first escapement wheel, ie the escapement movement of the first escapement wheel, and / or the second locking surface portion is arranged to lock the rotation of the second escapement wheel, ie the escapement movement of the second escapement wheel.

[0028] In one embodiment, the escapement has no stops or washers to limit the displacement of the pallets beyond the nominal locking position.

[0029] In one embodiment, the first locking surface portion is arranged so that a first force exerted on the pallet fork by the first escapement wheel locked by the first locking surface portion passes substantially near the fourth rotation axis, in particular, passes through the fourth rotation axis, and the second locking surface portion is arranged so that a second force exerted on the pallet fork by the second escapement wheel locked by the second locking surface portion passes substantially near the fourth rotation axis, in particular, passes through the fourth rotation axis.

[0030] In one embodiment, the first force exerted on the pallet fork by the first escape wheel locked by the first locking surface portion passes substantially in the vicinity of the fourth rotation axis, in particular through the fourth rotation axis, thereby ensuring that the pallet fork is not subjected to a tipping torque during the static phase. In other words, the first force exerted on the pallet fork by the first escape wheel locked by the first locking surface portion passes substantially in the vicinity of the fourth rotation axis, in particular through the fourth rotation axis, thereby ensuring a stable static position of the pallet fork during the static phase. In the static phase, the pallet fork is only engaged with the first escape wheel.

[0031] In one embodiment, the second force exerted on the pallet fork by the second escape wheel locked by the second locking surface portion passes substantially near the fourth rotation axis, in particular through the fourth rotation axis, thereby ensuring that the pallet fork is not subjected to a tipping torque during the static phase. In other words, the second force exerted on the pallet fork by the second escape wheel locked by the second locking surface portion passes substantially near the fourth rotation axis, in particular through the fourth rotation axis, thereby ensuring a stable static position of the pallet fork during the static phase. In the static phase, the pallet fork is only engaged with the second escape wheel.

[0032] In one embodiment, the pallet fork is mounted in a freely rotatable connection. In one embodiment, the pallet fork is mounted in a freely rotatable connection on a bridge and / or on a plate of a timepiece. In one embodiment, the pallet fork has no elastic return means and / or the escapement has no elastic return means connected or engaged with the pallet fork to keep or return it to a rest position (and of course, there is also an elastic member (conventional hairspring) of the oscillator connected to the inertial element, the continuous movement of which causes the release of the escape wheel and the subsequent movement of the pallet fork). In other words, the displacement of the pallet fork is caused by the inertial element and / or the first escape wheel and / or the second escape wheel. In particular, when the escapement is operating normally, the displacement of the pallet fork is caused only by the inertial element and / or the first escape wheel and / or the second escape wheel.

[0033] In one embodiment, the escapement is not a direct impulse escapement. In other words, in one embodiment, the first escape wheel and / or the second escape wheel do not cooperate directly with the inertia piece (or oscillator member usually formed by a balance wheel / balance spring combination).

[0034] It can be noted that the escapement according to the above-described embodiment provides greater operational safety, since the first or second locking force passes through the fourth axis of rotation: in the locked position (or in the stationary phase), the pallet fork is not subjected to a tipping torque, which allows a stable locked position to be obtained without providing a stop or washer which is usually required to limit the travel of the pallet fork, especially in the event of a crash. Naturally, this type of escapement can also be provided with a stop or washer.

[0035] In one embodiment, the first locking surface portion is arranged so that a first friction cone formed around a force application point of the first escapement wheel on the escapement fork includes, or contains, or passes through a fourth rotation axis, and / or the second locking surface portion is arranged so that a second friction cone formed around a force application point of the second escapement wheel on the escapement fork includes, or contains, or passes through a fourth rotation axis.

[0036] In one embodiment, the first locking surface portion has a first normal direction passing through the fourth rotation axis or substantially passing through the fourth rotation axis, and the second locking surface portion has a second normal direction passing through the fourth rotation axis or substantially passing through the fourth rotation axis.

[0037] In one embodiment:

[0038] a first straight line passes through the fourth rotation axis and through the contact point between the first escape wheel and the first locking surface portion in the first locking phase, and

[0039] a second straight line passes through the fourth rotation axis and through the contact point between the second escape wheel and the second locking surface portion in the second locking phase,

[0040] They form an acute angle α. In other words, a triangle can be formed, which contains:

[0041] - the fourth axis of rotation for the first vertex,

[0042] a contact point between the first escape wheel and the first locking surface portion for a second vertex,

[0043] - a contact point between the second escape wheel and the second locking surface portion for the third vertex. In one embodiment, the triangle is acute at its first vertex. This configuration allows ensuring a short travel of the pallet fork between a first locking position (of the pallet fork), in which the first escape wheel is locked (by the pallet fork), and a second locking position (of the pallet fork), in which the second escape wheel is locked (by the pallet fork). This provides a compact assembly.

[0044] In one embodiment, the angle α is in the range of 60° to 80°.

[0045] In one embodiment:

[0046] The pulse receiving device of the pallet fork comprises:

[0047] - a first pulse input arranged to receive a first pulse of the first escape wheel during a first half-period of the balance wheel,

[0048] - a second pulse input arranged to receive a second pulse of the second escape wheel during a second half-period of the balance wheel,

[0049] in:

[0050] - the first pulse input portion is adjacent to the first locking surface portion, the second pulse input portion is adjacent to the second locking surface portion,

[0051] And / or:

[0052] The first pulse input portion is separated from the first locking surface portion by a first fork, and the second pulse input portion is separated from the second locking surface portion by a second fork.

[0053] In one embodiment:

[0054] - a third straight line passes through the fourth rotation axis and through the contact point between the first escape wheel and the first pulse input part during the first pulse phase, and

[0055] a fourth straight line passes through the fourth rotation axis and the contact point between the second escape wheel and the second pulse input during the second pulse phase,

[0056] They form an acute angle γ.

[0057] In one embodiment, the angle γ is in the range of 50° to 70°.

[0058] In one embodiment, angle γ is smaller than angle α.

[0059] In one embodiment:

[0060] - the first escape wheel comprises a plurality of first locking teeth, each locking tooth comprising one of a plurality of first locking surfaces, wherein each first locking tooth is arranged between two first drive teeth of the first drive gear,

[0061] The second escape wheel comprises a plurality of second locking teeth, each locking tooth comprising one of a plurality of second locking surfaces, wherein each second locking tooth is arranged between two second drive teeth of the second drive gear.

[0062] In one embodiment:

[0063] - each first locking tooth comprises at least one first transverse drive surface, preferably with a circular involute profile, designed to mesh with a second drive tooth,

[0064] - each second locking tooth comprises at least one second transverse drive surface, preferably with a circular involute profile, designed to mesh with the first drive tooth,

[0065] In one embodiment, the first locking tooth and the second locking tooth are asymmetrical.

[0066] In one embodiment, the head diameters ( DT2 ) of the first locking tooth and the second locking tooth are respectively larger than the head diameters ( DT1 ) of the first and second driving teeth.

[0067] In one embodiment: 1.1.DT1≤DT2≤1.3.DT1.

[0068] In one embodiment, the tooth thickness (e2) of the first locking tooth and the second locking tooth is greater than the tooth thickness (e1) of the first and second driving teeth, respectively.

[0069] In one embodiment: 1.8.e1≤e2≤2.5.e1.

[0070] In one embodiment, the first escape wheel and / or the second escape wheel respectively include 3 to 8 first locking teeth and 3 to 8 second locking teeth, and preferably include 4 or 5 first locking teeth and 4 or 5 second locking teeth.

[0071] In one embodiment:

[0072] - the first escapement wheel forms or comprises a first escapement gearwheel, and / or

[0073] The second escape wheel forms or comprises a second escape gear.

[0074] A second aspect of the present invention may relate to an escapement mechanism of a timepiece movement, comprising:

[0075] a first escape wheel, mounted rotatably about a first axis, arranged to mesh with a gear train of a timepiece movement, such as a power gear train, to receive power, and comprising a plurality of first locking surfaces and a first drive gear,

[0076] a second escape wheel, mounted to rotate about a second axis of rotation, comprising a plurality of second locking surfaces and a second drive gear meshing with the first drive gear to transmit power from the first escape wheel to the second escape wheel,

[0077] - an inertial member, mounted to rotate about a third axis of rotation, arranged to exhibit oscillations, each oscillation comprising a first half-period and a second half-period,

[0078] - Pallet fork, mounted to rotate about a fourth axis, comprising:

[0079] a first locking surface portion arranged to come into contact with one of the plurality of first locking surfaces to lock the rotation of the first escape wheel,

[0080] a second locking surface portion arranged to be in contact with one of the plurality of second locking surfaces to lock the rotation of the second escape wheel,

[0081] - pulse receiving means arranged to receive a first pulse from the first escape wheel during a first half-period of the oscillation of the inertial element, and to receive a second pulse from the second escape wheel during a second half-period of said oscillation of the inertial element,

[0082] - a pulse transmission device, arranged to transmit at least a part of the first pulse or the second pulse to the inertial member,

[0083] It is characterized in that the first locking surface portion is arranged so that a first force exerted on the escapement fork by the first escapement wheel locked by the first locking surface portion basically passes near the fourth rotation axis, in particular, passes through the fourth rotation axis, and that the second locking surface portion is arranged so that a second force exerted on the escapement fork by the second escapement wheel locked by the second locking surface portion basically passes near the fourth rotation axis, in particular, passes through the fourth rotation axis.

[0084] According to the above-described embodiment, the escapement mechanism comprises a single pallet fork and two escape wheels. Unlike the world patent WO2013182243A1, which comprises two pallet forks angularly indexed to one another, the above-described embodiment does not provide any indexing due to the presence of only a single pallet fork. In addition, a particularly compact assembly can be obtained, since the pallet fork is mounted in rotation to alternately lock the first or second escape wheel: the first or second escape wheel can be mounted or arranged side by side, in particular symmetrically with respect to the plane through which the respective axes of rotation of the inertial piece and the pallet fork pass. Finally, it can be noted that the escapement mechanism according to the above-described embodiment provides greater operational safety, since the first or second locking force passes through the fourth axis of rotation: in the locked position (in the stationary phase), the pallet fork is not subjected to a tipping torque, which allows a stable locked position to be obtained and advantageously does not require the provision of a stop or washer that is usually required to limit the travel of the pallet fork, especially in the event of a collision.

[0085] It can be noted that according to the escapement mechanism of the above embodiment, during the same swing (reciprocating) of the inertial member, two pulses are transmitted to the inertial member to maintain its swing. In fact, the escapement fork can:

[0086] - receiving, during a first half-cycle of the inertial element (for example the outward stroke constituting the first half of the oscillation), a first pulse from the first escape wheel and transmitting it (at least partially) to the inertial element, and

[0087] - A second pulse from the second escape wheel may be received and (at least partially) transmitted to the inertial element during a second half-period of the inertial element (for example the return stroke constituting the second half of said oscillation).

[0088] The invention can be defined by the following features taken alone or in combination.

[0089] In one embodiment, the inertial part comprises a balance wheel. In particular, the inertial part may comprise a balance wheel, a balance wheel shaft and a bridge with pins, which are connected to a hairspring.

[0090] In one embodiment, the first locking surface portion is arranged to lock the rotation of the first escapement wheel, ie the escapement movement of the first escapement wheel, and / or the second locking surface portion is arranged to lock the rotation of the second escapement wheel, ie the escapement movement of the second escapement wheel.

[0091] In one embodiment, the escapement has no stops or washers to limit the displacement of the pallets beyond the nominal locking position.

[0092] In one embodiment, the first locking surface portion is arranged so that a first friction cone formed around a force application point of the first escapement wheel on the escapement fork includes, or contains, or passes through a fourth rotation axis, and / or the second locking surface portion is arranged so that a second friction cone formed around a force application point of the second escapement wheel on the escapement fork includes, or contains, or passes through a fourth rotation axis.

[0093] In one embodiment, the first locking surface portion has a first normal direction passing through the fourth rotation axis or substantially passing through the fourth rotation axis, and the second locking surface portion has a second normal direction passing through the fourth rotation axis or substantially passing through the fourth rotation axis.

[0094] In one embodiment:

[0095] a first straight line passes through the fourth rotation axis and through the contact point between the first escape wheel and the first locking surface portion in the first locking phase, and

[0096] a second straight line passes through the fourth rotation axis and through the contact point between the second escape wheel and the second locking surface portion in the second locking phase,

[0097] They form an acute angle α. In other words, a triangle can be formed, which contains:

[0098] - the fourth axis of rotation for the first vertex,

[0099] a contact point between the first escape wheel and the first locking surface portion for a second vertex,

[0100] - a contact point between the second escape wheel and the second locking surface portion for the third vertex. In one embodiment, the triangle is acute at its first vertex. This configuration allows ensuring a short travel of the pallet fork between a first locking position (of the pallet fork), in which the first escape wheel is locked (by the pallet fork), and a second locking position (of the pallet fork), in which the second escape wheel is locked (by the pallet fork). This provides a compact assembly.

[0101] In other words, the present invention may relate to an escapement mechanism of a watch movement, comprising:

[0102] a first escape wheel, mounted rotatably about a first axis, arranged to mesh with a gear train of a timepiece movement, such as a power gear train, to receive power, and comprising a plurality of first locking surfaces and a first drive gear,

[0103] - a second escape wheel, mounted to rotate about a second axis of rotation, comprising a plurality of second locking surfaces and a second drive gear meshing with the first drive gear,

[0104] an inertial member, such as a balance wheel, mounted to rotate about a third axis of rotation and arranged to exhibit oscillations, each oscillation comprising a first half-period and a second half-period,

[0105] - Pallet fork, mounted to rotate about a fourth axis, comprising:

[0106] a first locking surface portion arranged to come into contact with the plurality of first locking surfaces in order to lock the movement of the first escape wheel,

[0107] a second locking surface portion arranged to be in contact with a plurality of second locking surfaces to lock the movement of the second escape wheel,

[0108] - pulse receiving means arranged to receive a first pulse from the first escape wheel during a first half-period of the oscillation of the balance wheel and to receive a second pulse from the second escape wheel during a second half-period of said oscillation of the balance wheel,

[0109] - a pulse transmission device, arranged to transmit at least a part of the first pulse or the second pulse to the inertial member,

[0110] Features:

[0111] a first straight line passes through the contact point between the first escape wheel and the first locking surface portion and through the point through which the fourth rotation axis passes, and

[0112] a second straight line passes through the point of contact between the second escape wheel and the second locking surface portion and through the point through which the fourth rotation axis passes,

[0113] They form an acute angle α.

[0114] In one embodiment, the angle α is in the range of 60° to 80°.

[0115] In one embodiment, the plurality of first locking surfaces and the plurality of second locking surfaces are arranged to cooperate with the pallet fork in a first plane (referred to as the locking plane), and the first drive gear is arranged to cooperate with the second drive gear in a second plane (referred to as the drive plane, parallel to and different from the locking plane) to transmit power from the first escape wheel to the second escape wheel. In one embodiment, the first escape wheel and / or the second escape wheel may be formed by two superimposed parts: the first layer includes the drive gears and the second layer includes the locking surfaces. The cooperation between the two escape wheels and the cooperation between each escape wheel and the pallet fork are carried out on different planes.

[0116] In one embodiment:

[0117] - a plurality of first locking surfaces and a first drive gear form a first main drive gear,

[0118] - a plurality of second locking surfaces and a second drive gear forming a second main drive gear,

[0119] - a second main drive gear meshing with the first main drive gear to transmit power from the first escapement wheel to the second escapement wheel in the inner plane,

[0120] And the first main drive gear and the second main drive gear are arranged to cooperate with the escapement fork in the same plane. In this embodiment, the cooperation between the two escapement wheels and the cooperation between each escapement wheel and the escapement fork are performed on the same plane, although the overall thickness of the escapement mechanism is reduced, and the parts are easy to manufacture because of the flat design without protrusions.

[0121] In one embodiment:

[0122] - the first escape wheel comprises a plurality of first locking teeth, each locking tooth comprising one of a plurality of first locking surfaces, said first locking teeth preferably being asymmetrical,

[0123] the second escape wheel comprises a plurality of second locking teeth, each locking tooth comprising one of a plurality of second locking planes, said second locking teeth being preferably asymmetrical,

[0124] And each first locking tooth is configured to cooperate with the second drive gear, and / or each second locking tooth is configured to cooperate with the first drive gear to transmit power from the first escapement wheel to the second escapement wheel.

[0125] In one embodiment:

[0126] - the first escape wheel comprises a plurality of first locking teeth, each locking tooth comprising one of a plurality of first locking surfaces,

[0127] - the second escape wheel comprises a plurality of second locking teeth, each locking tooth comprising one of a plurality of second locking planes,

[0128] The first locking tooth and the second locking tooth are asymmetrical.

[0129] In one embodiment, the first escape wheel and / or the second escape wheel respectively include 3 to 8 first locking teeth and 3 to 8 second locking teeth, and preferably include 4 or 5 first locking teeth and 4 or 5 second locking teeth.

[0130] In one embodiment:

[0131] The pulse receiving device of the pallet fork comprises:

[0132] - a first pulse input arranged to receive a first pulse of the first escape wheel during a first half-period of the balance wheel,

[0133] - a second pulse input arranged to receive a second pulse of the second escape wheel during a second half-period of the balance wheel,

[0134] and:

[0135] - the first pulse input portion is adjacent to the first locking surface portion, the second pulse input portion is adjacent to the second locking surface portion,

[0136] And / or:

[0137] The first pulse input portion is separated from the first locking surface portion by a first fork, and the second pulse input portion is separated from the second locking surface portion by a second fork.

[0138] In one embodiment:

[0139] - a third straight line passes through the fourth rotation axis and through the contact point between the first escape wheel and the first pulse input part during the first pulse phase, and

[0140] a fourth straight line passes through the fourth rotation axis and the contact point between the second escape wheel and the second pulse input during the second pulse phase,

[0141] They form an acute angle γ.

[0142] In one embodiment, the angle γ is in the range of 50° to 70°.

[0143] In one embodiment, angle γ is smaller than angle α.

[0144] In one embodiment:

[0145] - the first locking surface portion is concave, and / or

[0146] - The second locking surface portion is concave.

[0147] In one embodiment:

[0148] the first locking surface portion comprises at least two first secondary locking surface portions, being V-shaped (or "V") or "U"-shaped, preferably being V-shaped with an obtuse angle βa, and preferably the angle βa is in the range of 140°-170°,

[0149] The second locking surface portion comprises at least two second auxiliary locking surface portions, and is V-shaped (or "V") or "U"-shaped, preferably V-shaped with an obtuse angle βb, and preferably the angle βb is in the range of 140°-170°.

[0150] In one embodiment:

[0151] - the first escapement wheel forms or comprises a first escapement gearwheel, and / or

[0152] The second escape wheel forms or comprises a second escape gear.

[0153] A third aspect of the present invention relates to a timepiece comprising the escapement mechanism according to the first or second aspect. BRIEF DESCRIPTION OF THE DRAWINGS

[0154] Other features and advantages of the present invention will become more apparent from the following detailed description of embodiments of the invention, which are described by way of non-limiting examples and illustrated in the accompanying drawings.

[0155] Figure 1 A general view of a timepiece oscillator with an escapement mechanism in a first embodiment of the present invention is shown, in particular comprising a first escapement wheel, a second escapement wheel and an escapement fork;

[0156] Figure 2 Shows Figure 1 A view of the escapement in cooperation with the balance cock during the rest phase;

[0157] Figure 3 Shown without the balance cock Figure 2 A magnified view of the escapement in the

[0158] Figure 4 Shows Figures 1 to 3 A view of the pallet fork of the escapement in FIG.

[0159] Figure 5 Shows Figure 4 Details of the pallet fork;

[0160] Figure 6 Shows Figures 1 to 3 A view of the second escape wheel of the escapement in FIG.

[0161] Figure 7 Shows Figure 2 View of the escapement in transition from the rest phase to the impulse phase;

[0162] Figure 8 Shows Figure 7 View of the escapement during the impulse phase;

[0163] Fig. 9 The escapement mechanism of the second embodiment is shown, which differs in some respects from the Figures 1 to 3 The escapement mechanism cooperates with the balance bridge and particularly comprises a first escape wheel, a second escape wheel and an escape fork;

[0164] Fig.10 Shows Fig. 9 A view of the first escape wheel of the escapement in FIG.

[0165] Fig.11 Shown without the balance cock Fig. 9 Illustration of the escapement in the . DETAILED DESCRIPTION

[0166] Figures 1 to 8 A double active half-cycle tangentially driven escapement 10 in a first embodiment is shown, ie, in the pulse phase of the escapement, either one of the first and second escape wheels in contact with the pallet fork and the pallet fork rotate in opposite directions.

[0167] Figure 1 A full view of a movement 100 is shown, which includes an escapement 10 disposed between the movement gear train (here the power gear train 99) and the oscillator 5 of the movement, the oscillator being in the form of a balance wheel 51 connected to a hairspring. The escapement 10 mainly includes:

[0168] - Pallet fork 4,

[0169] - First escape wheel 1,

[0170] - Second escape wheel 2.

[0171] Please refer to the following text Figure 2 As explained, the escapement 10 cooperates with the resonator 5 via a pin embedded in the bridge 511 of the balance wheel 51. As for the power gear train 99, Figure 1 It is shown that the first escape wheel 1 is in contact with the power wheel 3 of the power gear train 99 , and in particular, is in contact with the gear 31 of the power gear train 99 via a pinion 13 integrally connected to the first escape wheel 1 .

[0172] As is known, the function of escapement 10 of the invention is to maintain the oscillation of a regulating member, that is to say of balance 51 of oscillator 5 .

[0173] Specifically, in detail Figure 2 As shown, the first escape wheel 1 is rotatably mounted around the first rotation axis A1, meshes with the power gear train 99 of the watch movement to receive power, and includes a plurality of first locking surfaces 121a (see FIG. 1 ) arranged on the first locking teeth 121. Figure 2 and Figure 3 ) and the first driving gear 111. It can be noted that the first locking tooth 121 and the first driving gear 111 are arranged on parallel and different planes.

[0174] The second escape wheel 2 is rotatably mounted around the second rotation axis A2, and includes a plurality of second locking surfaces 221a provided on the second locking teeth 221 and a second driving gear 211 meshing with the first driving gear 111. It can be noted that the second locking teeth 221 and the second driving gear 211 are arranged on parallel and different planes.

[0175] The pallet fork 4 is rotatably mounted around the fourth axis A4 and comprises pulse receiving devices of the following forms:

[0176] a first pulse input 41 a arranged to receive a first pulse of the first escape wheel 1 during a first half-period of the balance 51 ,

[0177] A second pulse input 41 b is arranged to receive a second pulse of the second escape wheel 2 during the second half-period of the balance 51 .

[0178] The pallet 4 also comprises an impulse transmission device, with first and second impulse transmission devices in the form of a first impulse surface 42a and a second impulse surface 42b, respectively, which form an escapement fork, such as a lock or a lever of a known lever escapement mechanism. The shape of the escapement fork cooperates with a pin 511a on the bridge 511 of the balance wheel 51.

[0179] Finally, the pallet 4 includes:

[0180] a first locking surface portion 43a, arranged to be in contact with the plurality of first locking surfaces 121a, so as to lock the rotation of the first escape wheel 1,

[0181] A second locking surface portion 43 b is arranged to be in contact with the plurality of second locking surfaces 221 a to lock the rotation of the second escape wheel & pinion 2 .

[0182] The first and second escape wheels 1, 2, in particular comprising first and second escape gears 12, 22 respectively, are designed to cooperate with the pallet fork 4 so as to provide pulses to the balance with hairspring and thus allow it to maintain its oscillation about the third axis of rotation A3, as described below. In addition, the first and second escape wheels 1, 2 are meshed with each other through first and second gears 11, 21 respectively, in particular through first and second drive gears formed by teeth 111 and 211 respectively.

[0183] Advantageously, Figure 1 The power wheel 3 in the power gear train 99 can be in direct contact with the second hand wheel (not shown) of the power gear train 99. In fact, this configuration allows the first and second escapement wheels 1, 2 to generate a rotation speed, which allows the number of teeth of the first and second escapement gears 12, 22 to be limited, and thus allows the use of first and second escapement wheels 1, 2, each of which has a size substantially the same as that of the pallet fork 4, so that the double active semi-periodic escapement has a compact size, which is substantially similar to that of the Swiss lever escapement.

[0184] In particular, the first and second escape wheels 1, 2 can be inscribed in a cylinder centered on the axis A1, A2, respectively, and the diameters of the cylinders are D1, D2, which are the same as the diameter D4 of the cylinder centered on the fourth axis A4 (in which the escapement fork 4 can be inscribed) ( Figure 3 ).exist Figure 3 In the particular construction shown, diameter D4 is greater than diameter D1 or D2. In addition, axes A1, A2, A4 define respective ends of a generally equilateral triangle.

[0185] In such Figures 1 to 8 In the variant of our construction shown, D4 is approximately equal to 1.4.D1 or 1.4.D2 (D1 and D2 are equal). More generally, D4 is preferably between D1 and 2.D1, or between D2 and 2.D2.

[0186] "An element is inscribed in a cylinder of diameter D centered on an axis" means that diameter D is the smallest diameter centered on the axis such that the element is contained in the cylinder.

[0187] Figure 4 4 shows a detailed top view of the pallet fork 4 in a plane. The figure particularly highlights the angle α, which separates the first straight line S1 connecting the first locking surface portion 43a and the fourth rotation axis A4 from the second straight line S2 connecting the second locking surface portion 43b and the fourth rotation axis A4. In particular, when the escapement mechanism 10 is in a stationary phase, at the contact area between the first locking surface portion 43a and the first locking tooth 121 (in particular the end 121a), in particular at the contact point 431a (see Figure 5 ), the first straight line S1 connects the fourth rotation axis A4 and the first locking surface portion 43a. In particular, when the escapement is in a stationary stage (see Figure 3 ), at the contact area between the second locking surface portion 43b and the second locking tooth 221 (particularly the end portion 221a), particularly at the contact point 431b (see Figure 5 ), a second straight line S2 connects the fourth rotation axis A4 and the second locking surface portion 43b.

[0188] In one exemplary embodiment, the angle α is approximately equal to 70°. More generally, the following value range can be envisaged: 60°≤α≤80°.

[0189] Preferably, and in the embodiment shown, the first and second locking surface portions 43a, 43b are concave, that is to say they are formed by a continuous or discontinuous V-shaped surface when viewed from either escape wheel. Thus, in particular, the points 431a, 431b are defined by the concave points of the "V" ( Figure 5 ).

[0190] These surfaces have straight or curved continuous or discontinuous parts, Figure 4 As highlighted with bold lines in FIG. 4 , angles βa, βb are formed at each surface 43a, 43b. If the first and second locking surface portions 43a, 43b are curved, the angles βa, βb can be determined by the tangents of the locking surface portions. Advantageously, the angles βa, βb are obtuse angles. Preferably, the angles βa, βb are approximately equal to 170°. More generally, the angles βa, βb are preferably between 140° and 175°. Studies conducted by the applicant have shown that this angle range represents a good compromise between good locking security, minimal or no recoil at the end of the pulse, and minimal energy loss during release. The angle βa may be equal to or different from the angle βb.

[0191] Furthermore, the first and second locking surface portions 43a, 43b are perpendicular to the normal lines ( Figure 5 ) is inclined. For example, the first surface portion 43a1 may form an angle βa1 of approximately 6° with the normal to the straight line S1. For example, the second surface portion 43a2 may form an angle βa2 of approximately 8° with the normal to the straight line S1. For example, the first surface portion 43b1 may form an angle βb1 of approximately 6° with the normal to the straight line S2. For example, the second surface portion 43b2 may form an angle βb2 of approximately 8° with the normal to the straight line S2. If the first and second locking surface portions 43a, 43b are curved, the angles βa1, βa2, βb1, βb2 may be determined by tangents to the surface portions.

[0192] from Figure 5 It can be noted that the first and second locking surface portions 43a, 43b are adjacent to the first and second pulse input portions 41a, 41b, respectively. In fact, at the first fork 44a separating the two adjacent functional surfaces, the first locking surface portion 43a is engaged with the first pulse input portion 41a. Similarly, at the second fork 44b separating the two adjacent functional surfaces, the second locking surface portion 43b is engaged with the second pulse input portion 41b.

[0193] In the static phase of the escapement, the ends 121a, 221a of the first and second locking teeth 121, 221 are designed to be placed in the first and second locking surface portions 43a, 43b, respectively, more specifically in the "V-shape" formed by the first and second locking surface portions 43a, 43b. Advantageously, the ends 121a, 221a are in the form of rounded surfaces.

[0194] As an example, Figure 2 2 shows a stationary phase, wherein the end 221a of the second locking tooth 221 abuts against the second locking surface portion 43b, more specifically, within the "V-shape" formed by the same second locking surface portion. In this configuration, the pin 511a can be rotated in the first rotation direction (eg Figure 2The pin 511a is disengaged from the first pulse surface 42a under the rotation of the balance wheel 51 until the pin 511a rotates in the second rotation direction (as shown by the arrow). Figure 7 As shown by the arrow, under the action of the rotation of the balance wheel 51, it contacts the same first pulse surface 42a again and can therefore be released.

[0195] Figure 7 4 shows a release phase, in which the end 221a of the second locking tooth 221 leaves the second locking surface portion 43b under the action of the pin 511a, which guides the pulse surface 42a until the end 221a passes the second fork 44b and contacts the second pulse input portion 41b, so that the end 221a can send a pulse to the escapement fork 4 through the second pulse input portion 41b, and the escapement fork 4 can therefore send a pulse to the pin 511a through the second pulse surface 42b, as shown in FIG. Figure 8 This pulse phase lasts until a subsequent rest phase (not shown) during which the end 121 a of the first locking tooth 121 of the first escape wheel 1 comes into contact with the first locking surface portion 43 a of the pallet 4 .

[0196] Therefore, the second pulse input portion 41b can receive the pulse generated by the end 221a of the second locking tooth 221 of the second escape wheel 2. The pallet fork 4 also includes a first partial pulse input portion 41a, which can receive the pulse generated by the end 121a of the first locking tooth 121 of the first escape wheel 1. When viewed from any escape wheel, the first and second pulse input portions 41a, 41b are preferably convex, such as Figure 5 As shown in the plan view in . Each of the first and second pulse input parts 41a, 41b particularly includes a cylindrical part, in particular a cylindrical part whose directrix is ​​a circular asymptote. The first and second pulse input parts 41a, 41b are preferably matched with the rounded surfaces 121a, 221a of the first and second locking teeth 121, 221 having an asymmetric profile. This shape of the locking teeth allows the geometry of the surfaces 121a, 221a and 41a, 41b to be optimized to transmit torque to the oscillator 5. In particular, the asymmetric first and second locking teeth 121, 221 allow a number of feasible geometric shape options to be provided to the first and second pulse input parts 41a, 41b.

[0197] like Figure 4 As shown, the angle γ can be constructed, which separates:

[0198] - a third straight line S3, tangent to the first pulse input portion 41a and passing through the fourth rotation axis A4,

[0199] - A fourth straight line S4, tangent to the second pulse input portion 41b and passing through the fourth rotation axis A4. Preferably, the angle γ is an acute angle (see Figure 4). Preferably, the first and second pulse input parts 41a, 41b are tangent within the angular range of the separation surfaces 43a, 43b. Therefore, γ is much smaller than α. In a configuration variant, the angle γ is approximately equal to 60°. More generally, the following numerical range can be designed: 50°≤γ≤70°.

[0200] Pallet 4 may be symmetrical relative to a plane P perpendicular to the plane of the drawing and passing through fourth axis of rotation A4, in particular if surfaces 41a, 42a, 43a and 41b, 42b, 43b are identical. Manufacturing is easier and the parts can be mounted in either direction during assembly. Of course, pallet 4 may not be symmetrical relative to plane P.

[0201] Figures 9 to 11 An escapement 10' is shown in a second embodiment. The operation of the second embodiment is identical in all respects to that of the escapement in the first embodiment, but the construction differs in certain respects described below and the reference numerals are changed by simply adding the following prime: '.

[0202] In this second embodiment, the first escape wheel 1 ′ and the second escape wheel 2 ′ are in the form of a flat part, here a single escape wheel.

[0203] In detail, the first escape wheel 1' is rotatably mounted around the first rotation axis A1' and is arranged to mesh with the power gear train of the watch movement (not shown) to receive power, and includes a plurality of first locking surfaces 121a' arranged on the first locking teeth 121', and a first drive gear 111' which integrally forms the first main drive gear. As shown above, the first main drive gear is substantially flat, that is, the first locking teeth 121' and the first drive gear 111' are arranged on the same plane. Finally, it can be noted that the first locking teeth 121' have an asymmetric profile, while the first drive gear 111' has a symmetric profile.

[0204] The second escape wheel 2' is then mounted to rotate about the second axis A2' and comprises a plurality of second locking surfaces 221a' arranged on the second locking teeth 221' and a second drive gear 211' which integrally forms the second main drive gear. As shown above, the second main drive gear is substantially flat, that is to say the second locking teeth 221' and the second drive teeth 211' are arranged on the same plane. Finally, it can be noted that the second locking teeth 221' have an asymmetrical profile, while the second drive gear 211' has a symmetrical profile.

[0205] The first main driving gear (including the first driving gear 111 ′ and the first locking tooth 121 ′) and the second main driving gear (including the second driving gear 211 ′ and the second locking tooth 221 ′) cooperate with each other on the one hand, and cooperate with the escapement fork 4 ′ described below on the other hand.

[0206] On the one hand, the first drive gear 111' and the second drive gear 211' are designed to allow them to mesh together. The first drive gear 111' is also designed to allow it to mesh with the second locking tooth 221', and the second drive gear 211' is also designed to allow it to mesh with the first locking tooth 121'. Therefore, the first escape wheel 1' and the second escape wheel 2' have synchronous movement.

[0207] On the other hand, the first locking tooth 121' and the second locking tooth 221', like the first and second locking teeth 121, 221 of the first and second escape wheels 1, 2 of the first embodiment, include end portions forming first and second locking surfaces 121a', 221a' respectively, each end portion being in the form of a rounded surface and designed to cooperate with the first and second locking surface portions 43a', 43b' and the pulse receiving device of the escapement fork 4'.

[0208] In particular, the following points may be noted:

[0209] - the first drive gear 111 ′ and the second drive gear 211 ′ are specifically designed to allow the first and second escapement wheels 1 ′, 2 ′ to mesh,

[0210] - The first locking tooth 121' and the second locking tooth 221' are specifically designed to cooperate with the escapement fork 4', but can also be designed to allow the first and second escapement wheels 1', 2' to mesh. In particular, the first locking tooth 121' is designed to cooperate with the first pulse input portion 41a' and the first locking surface portion 43a' of the escapement fork 4' in sequence. Similarly, the second locking tooth 221' is designed to cooperate with the first pulse input portion 41b' and the second locking surface portion 43b' of the escapement fork 4' in sequence.

[0211] In the second embodiment, the head diameter DT2 of the first locking tooth 121' and the second locking tooth 221' is larger than the tooth diameter DT1 of the first driving gear 111' and the second driving gear 211'. Fig.10 As shown. In this way, the teeth of the first drive gear 111 'and the second drive gear 211 'do not interact or interfere with the pallet fork 4 '. In a specific construction variant, the diameter DT2 can be about 1.2.DT1. More generally, the following value range can be designed: 1.1.DT1≤DT2≤1.3.DT1.

[0212] In the second embodiment, the thickness e2 of the first locking tooth 121' and the second locking tooth 221' is advantageously different from the tooth thickness e1 of the first driving gear 111' and the second driving gear 211'. Preferably, the thickness e2 of the first locking tooth 121' and the second locking tooth 221' is greater than the tooth thickness e1 of the first driving gear 111' and the second driving gear 211', as shown in FIG. Fig.10In a specific configuration variation, the thickness e2 may be approximately 1.9.e1. Preferably, the following numerical range may be designed: 1.8.e1≤e2≤2.5.e2.

[0213] "Thickness" is the measured distance between the two flanks of a given tooth measured at a diameter DP which corresponds to or substantially coincides with the pitch diameter of the associated gear.

[0214] In this way, the angular indexing of the first and second escape wheels 1', 2' is easily performed without risk of error. In particular, during assembly, a given first locking tooth 121' can only be housed between two consecutive teeth of the second drive gear 211' and vice versa. The distribution of the teeth of the first and second main drive gears around their respective axes means that only one angular indexing configuration can be adopted between the first and second escape wheels 1', 2'.

[0215] In this particular construction variant, the first and second escape wheels 1 ′, 2 ′ respectively comprise:

[0216] - ten teeth of the first drive gear 111 ' and ten teeth of the second drive gear 211 ', and

[0217] Five first locking teeth 121 ′ and five second locking teeth 221 ′.

[0218] In particular, two consecutive teeth of the first driving gear 111 ′ and two consecutive teeth of the second driving gear 211 ′ are respectively disposed between two consecutive teeth of the first locking tooth 121 ′ and the second locking tooth 221 ′.

[0219] Advantageously, the first and second escape wheels 1 ′, 2 ′ are identical and can be respectively reversed during assembly of the escapement mechanism 10 ′.

[0220] Therefore, the escapement mechanism in the second embodiment is particularly advantageous in its compactness (the escape wheel is simplified to an escape gear) and simplicity of assembly (each escape wheel is not obtained by assembly and the escape wheel does not need to be assembled with the error correction system).

[0221] As regards the dimensions in the plane of the elements of the escapement mechanism 10 ′ of the second embodiment, these dimensions are comparable to those of the elements of the mechanism of the first embodiment (see Figure 3 and Fig.11 ). In particular, diameter D4 is approximately equal to 1.3.D1 or 1.3.D2 (D1 and D2 are equal). More generally, D4 is preferably between D1 and 2.D1, or between D2 and 2.D2.

[0222] Industrial Applications

[0223] The escapement according to the invention can be used in industrial applications.

[0224] It will be understood that various modifications and improvements apparent to those skilled in the art can be made to the various embodiments of the invention described in this specification without departing from the scope of the invention.

[0225] In particular, it can be noted that, no matter which embodiment, the pallet fork can be an integral component or obtained by assembly. In particular, the locking device can be attached to the pallet fork, for example, and the locking device is disc-shaped and can be made of a specific material.

[0226] Preferably, the escape wheel in the first embodiment can be assembled between the integrated engagement gear and the integrated escape gear.

[0227] Preferably, each escape wheel in the second embodiment may be in the form of an integral gear.

[0228] Regardless of the embodiment, the pallet fork and / or the escape wheel, in particular the escape gear, may comprise in whole or in part single-crystalline silicon (regardless of orientation), polycrystalline silicon, amorphous silicon, amorphous silicon dioxide, doped silicon, regardless of the type and degree of doping, or porous silicon. It may also comprise silicon carbide, glass, ceramic, quartz, ruby ​​or sapphire. Alternatively, it may be made of a metal or a metal alloy, in particular a metal alloy that is at least partially amorphous. For example, such components may comprise Ni or NiP. Advantageously, alloys such as those described in patent application WO2017102661 may be used. It is also possible to manufacture all or part of these parts from an amorphous metal alloy (for example, it may be designed to manufacture all or part of these parts from a metallic glass).

[0229] Preferably, the escapement is designed to cooperate with a balance with a hairspring, with a frequency of 3 or 4 Hz, or even higher, such as 5, 6, 8 or 10 Hz.

[0230] Of course, the escapement can be used to maintain the oscillation of any type of oscillator, whether it is the balance-with-sprung type oscillator mentioned above or any other type of oscillator, such as an inertial member guided and elastically reset by a flexible sheet.

Claims

1. An escapement mechanism (10') for a watch movement, comprising: - a first escape wheel (1'), which is mounted to rotate about a first rotation axis (A1'), is arranged to mesh with a gear train of the watch movement, such as a power gear train (99), to receive power, and comprises a plurality of first locking surfaces (121a') and a first drive gear (111'), - a second escape wheel (2') mounted in rotation about a second rotation axis (A2') and comprising a plurality of second locking surfaces (221a') and a second drive gear (211'), an inertial element, which is mounted in rotation about a third axis of rotation (A3') and is arranged to exhibit oscillations, each oscillation comprising a first half-period and a second half-period, - a pallet fork (4'), which is rotatably mounted around a fourth rotation axis (A4'), comprising: a first locking surface portion (43a') arranged to be in contact with a plurality of first locking surfaces (121a') in order to lock the rotation of the first escape wheel (1'), a second locking surface portion (43b') arranged to be in contact with a plurality of second locking surfaces (221a') in order to lock the rotation of the second escape wheel (2'), - pulse receiving means arranged to receive a first pulse from said first escape wheel (1') during a first half-period of the oscillation of said inertial element, and to receive a second pulse from said second escape wheel (2') during a second half-period of the oscillation of said inertial element, - a pulse transmission device, the pulse transmission device being arranged to transmit at least a part of the first pulse or the second pulse to the inertial member, Features: - the plurality of first locking surfaces (121a') and the first drive gear (111') form a first main drive gear, - a plurality of second locking surfaces (221a') and a second drive gear (211') form a second main drive gear, The second main driving gear meshes with the first main driving gear to transmit power from the first escapement wheel (1') to the second escapement wheel (2') in the inner plane, And wherein the first main driving gear and the second main driving gear are arranged to cooperate with the pallet fork (4') in the same plane.

2. The escapement mechanism (10') according to claim 1, wherein the first locking surface portion (43a') is arranged so that a first force exerted on the escapement fork (4') by the first escapement wheel (1') locked by the first locking surface portion (43a') passes substantially near the fourth rotation axis (A4'), in particular, passes through the fourth rotation axis (A4'), and the second locking surface portion (43b') is arranged so that a second force exerted on the escapement fork (4') by the second escapement wheel (2') locked by the second locking surface portion (43b') passes substantially near the fourth rotation axis (A4'), in particular, passes through the fourth rotation axis (A4').

3. The escapement mechanism (10') according to any one of claims 1 or 2, wherein: a first straight line (S1) passes through the fourth rotation axis (A4') and through the contact point between the first escape wheel (1') and the first locking surface portion (43a') in the first locking phase, and a second straight line (S2) passing through said fourth rotation axis (A4') and passing through the contact point between said second escape wheel (2') and said second locking surface portion (43b') in the second locking phase, They form an acute angle α.

4. Escapement mechanism (10') according to claim 3, wherein said angle α is within an angular value range of 60° to 80°.

5. The escapement mechanism (10') according to any one of claims 1 to 4, wherein: The pulse receiving device of the pallet fork (4') comprises: a first pulse input (41a') arranged to receive a first pulse of the first escape wheel (1') during a first half-period of the balance wheel, a second pulse input (41b') arranged to receive a second pulse of the second escape wheel (2') during a second half-period of the balance wheel, in: - the first pulse input portion (41a') is adjacent to the first locking surface portion (43a'), and the second pulse input portion (41b') is adjacent to the second locking surface portion (43b'), And / or: The first pulse input portion (41a') is separated from the first locking surface portion (43a') by a first fork, and the second pulse input portion (41b') is separated from the second locking surface portion (43b') by a second fork.

6. The escapement mechanism (10') according to claim 5, wherein: - a third straight line (S3) passes through the fourth rotation axis (A4') and the contact point between the first escape wheel (1') and the first pulse input part (41a') in the first pulse phase, and - a fourth straight line (S4) passes through the fourth rotation axis (A4') and the contact point between the second escape wheel (2') and the second pulse input part (41b') in the second pulse phase, They form an acute angle γ.

7. Escapement mechanism (10') according to claim 6, wherein said angle γ is within an angular value range of 50° to 70°.

8. Escapement mechanism (10') according to claim 6 or 7 as appended to claim 3 or 4, wherein the angle γ is smaller than the angle α.

9. The escapement mechanism (10') according to claims 1 to 8, wherein: - the first escape wheel (1') comprises a plurality of first locking teeth (121'), each of the locking teeth comprising one of a plurality of first locking surfaces (121a'), wherein each of the first locking teeth (121') is arranged between two first driving teeth of the first driving gear (111'), -The second escape wheel (2') comprises a plurality of second locking teeth (221'), each of the locking teeth comprising one of a plurality of second locking planes (221a'), wherein each of the second locking teeth (221') is arranged between two second driving teeth of the second driving gear (211').

10. The escapement mechanism (10') according to claim 9, wherein: - each of said first locking teeth (121') comprises at least one first transverse driving surface, preferably with a circular involute profile, designed to mesh with said second driving tooth, - Each of said second locking teeth (221') comprises at least one second transverse driving surface, preferably with a circular involute profile, designed to mesh with said first driving tooth.

11. The escapement mechanism (10') according to any one of claims 9 or 10, wherein the first locking tooth (121') and the second locking tooth (221') are asymmetrical.

12. The escapement mechanism (10') according to any one of claims 9 to 11, wherein the head diameter (DT2) of the first locking tooth (121') and the second locking tooth (221') is respectively larger than the head diameter (DT1) of the first and second driving teeth, and preferably in: 1.1.DT1≤DT2≤1.3.DT1, And / or wherein the tooth thickness (e2) of the first locking tooth (121') and the second locking tooth (221') is respectively greater than the tooth thickness (e1) of the first and second driving teeth, and preferably in: 1.8.e1≤e2≤2.5.e1.

13. An escapement mechanism (10') according to any one of claims 9 to 12, wherein the first escapement wheel (1') and / or the second escapement wheel (2') respectively include 3 to 8 first locking teeth (121') and 3 to 8 second locking teeth (221'), and preferably include 4 or 5 first locking teeth (121') and 4 or 5 second locking teeth (221').

14. The escapement mechanism (10') according to any one of claims 1 to 13, wherein: - the first escape wheel (1') forms or comprises a first escape gear (12'), and / or The second escape wheel (2') forms or comprises a second escape gear (22').

15. A timepiece comprising an escapement (10') according to any one of the preceding claims.

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