Pallet for timepiece escapement

Abstract

An escapement fork for a timepiece escapement mechanism (10, 10 '), comprising a fork (400, 400'); according to the invention, the fork has two first portions (411a, 421a; 411a ', 421a'), i.e. Pulse portions, which are arranged opposite one another and are arranged so as to generate a pulse from at least one escape wheel (1, 2; 1 ', 2') to an inertia member, characterized in that the fork member (400; 400 ') comprises two second portions (411b, 421b; 411b ', 421b'), i.e. A stop portion, which second portions are arranged opposite each other, each second portion being arranged relative to the first portion (411a, 421a; 411a ', 421a'), and each second portion is arranged to abut against the inertial member when the timepiece movement is impacted in a stationary phase.

Description

Escapement fork used in watch escapement mechanisms Technical Field

[0001] The present invention relates generally to an escapement mechanism for a watch movement, and more specifically to an escapement fork for such an escapement mechanism. Background Technology

[0002] In the prior art of escapements, known documents CH44855A and EP3754433A1 disclose various anchor-type escapements with a tipless anchor shaft and a fork-shaped component that engages with the balance wheel plate to provide an anti-tipping safety device. However, these systems are bulky, mainly because the anchor shaft must be long enough to ensure sufficient movement of the fork-shaped component to engage and disengage with the balance wheel plate pin, even though the inherent anchor shaft angular travel of these types of escapements is very small. Furthermore, note that such Swiss-anchored escapements are inevitably subject to friction during the pulse phase, as the anchor shaft and escape wheel rotate in the same direction during the pulse phase. Summary of the Invention

[0003] To address the aforementioned shortcomings of the prior art, one objective of this invention is to specifically provide an escapement mechanism whose components can improve upon known escapement mechanisms, namely, having advantages such as high operational performance, and / or good efficiency, and / or operational safety, and / or excellent shock resistance, and / or reduced overall space occupation.

[0004] Therefore, a first aspect of the present invention relates to an escapement fork of a watch movement, the watch movement comprising: an escapement mechanism including an escapement fork and at least one escape wheel; a oscillator including at least one inertial element having a drive portion, such as a tooth or pin, and an elastic reset device connected to the inertial element; the escapement fork comprising: a locking device configured to lock the at least one escape wheel of the escapement mechanism in a stationary phase; a pulse receiving device configured to receive a pulse from the at least one escape wheel in a pulse phase; and a fork-shaped member having two first portions, namely pulse portions, the first portions being disposed opposite each other and configured to transmit at least a portion of the pulse received from the at least one escape wheel to the drive portion of the inertial element in the pulse phase; characterized in that the fork-shaped member comprises two second portions, namely stop portions, the second portions being disposed opposite each other, each second portion being protruding relative to one of the first portions, and each second portion being configured to abut against the inertial element when the watch movement is impacted in a stationary phase.

[0005] In the above embodiments, the escape fork includes a fork-shaped member that mates with the drive portion of the inertial member. This fork-shaped member protrudes relative to the pulse portion (also referred to as the pulse surface portion or pulse surface) to form a second portion called the stop portion. These second protrusions form bulges or protrusions extending from the first portion. Such protruding second portions allow for abutment against the inertial member, even when the locking mechanism is compact and / or there is a large angular offset between two adjacent rest positions, such as in the case of a tangentially driven escapement.

[0006] An escapement fork may have the following individual features or combinations thereof.

[0007] In one embodiment, the fork-shaped member includes two lugs, each extending along a longitudinal direction, wherein each lug has a first width E1 at a first portion and a second width E2 at a second portion, wherein E2 > E1, preferably E2 > 1.1E1, preferably E2 > 1.2E1, and preferably E2 > 1.3E1, in a direction perpendicular to its respective longitudinal direction. According to this configuration, the lateral dimension of the lugs (relative to their longitudinal direction) gradually increases from the first portion to the second portion. In one embodiment, each second portion protrudes inward into the fork-shaped member. In other words, each second protrusion may selectively reduce the width of the lug opening separating the two lugs, or may reduce the width of the lug opening by a diffuser portion, which is generally known in the prior art.

[0008] In one embodiment, each second part includes at least: a distal stop formed at the free end of the fork, specifically at the free end of the lug of the fork; and a radial surface oriented substantially perpendicular to the pivot direction of the escapement fork, wherein: the distal stop is configured to abut against the fork during an additional upward or downward angle stroke of the inertial member, preferably during an additional upward or downward angle stroke of the inertial member and at this time the drive portion is in a non-engaged or non-disengaged phase with the fork, if the watch movement is impacted; and / or the radial surface is configured to abut against the drive portion of the inertial member during an additional upward or downward angle stroke of the inertial member, preferably during an additional upward or downward angle stroke of the inertial member and at this time the drive portion is in an engaged or disengaged phase with the fork, if the watch movement is impacted. According to this embodiment, each second part can be divided into two functional parts. The first functional component refers to the distal or end component, which, upon impact, can abut against the inertial component (rather than the drive portion) when the drive portion of the inertial component disengages from the fork. The second functional component refers to a radial, lateral, or internal component located between the first functional component and the first portion, which can abut against the drive portion of the inertial component when impacted while the drive portion of the inertial component is engaging or disengaging from the fork.

[0009] In one embodiment, each first part is connected to the second part via a third part, i.e., a connecting portion. Preferably, the third part has a slope reversal point and / or a groove. Specifically, at the third part (i.e., the connecting portion), a change in the sign of the derivative (i.e., the presence of an inflection point or local extremum) or a change in the slope direction during the transition from the first part to the second part can be anticipated. In one embodiment, each first part is adjacent to a second part, and the transition between each first part and the corresponding second part forms or defines the third part.

[0010] In one embodiment, the angle δ formed by the first tangent of the first portion and the second tangent of the second portion (which protrudes from the first portion) is less than 180° when the first portion and the protruding second portion are viewed from inside the fork. Specifically, the first tangent may be tangent to the first portion at the intersection of the second tangent and the first portion. More specifically, a plane of symmetry for the fork structure may be defined, and the second tangent may be parallel or substantially parallel to said plane of symmetry.

[0011] In one embodiment, each first portion preferably includes at least one plane and at least one curved surface, both of which are located away from the pivot of the escapement fork. Preferably, the at least one curved surface may include a circular or arcuate cross-section, a circular profile, or an arcuate profile.

[0012] In one embodiment, each second portion includes at least one curved surface. In another embodiment, each second portion includes a circular or arcuate cross-sectional surface or a circular or arcuate profile.

[0013] In one embodiment: the locking device and / or pulse receiving device are located at a radial distance R41 from the escape fork pivot, and the second part, i.e. the stop part, is located at a radial distance R41 from the escape fork pivot, wherein R4>R41, preferably R4>1.4R41, and more preferably R4>1.8R41.

[0014] In particular, the radial distance R41 is between: the first radial distance Ra41 of the escapement fork shaft, from which the pulse receiving device extends; and the second radial distance Ra43 of the escapement fork shaft, where one end of the locking device is located.

[0015] In one embodiment, the escape fork is characterized in that: the escape fork is planar or composed of planar components, and / or the escape fork has no tip, and / or the escape fork is a single-piece structure or assembled from at least two components, which may be made of silicon, manufactured by etching a wafer, or manufactured by metal growth in an electroplating mold, or manufactured by conventionally cutting a metal plate, or manufactured by metallic glass or amorphous materials, and may be without additional blades.

[0016] In one embodiment, the pulse receiving device is configured to receive tangential pulses from the at least one escape wheel.

[0017] In one embodiment, the escape fork is symmetrical or substantially symmetrical with respect to a center plane located between or at an opening between the two lugs and passing through the pivot of the escape fork.

[0018] In one embodiment, the escape fork is configured to cooperate with two escape wheels.

[0019] A second aspect of the invention relates to an adjustment device for a watch movement, comprising: an escapement mechanism including the escape fork described in the first aspect and at least one escape wheel, the at least one escape wheel being configured to mesh with a gear train, such as a power gear train, in the watch movement to receive power; a oscillator including an inertial element having a drive portion, such as a tooth or pin, and a resilient reset device connected to the inertial element; and two external stops, the two external stops being, for example, formed by a limiting pin or a washer, wherein, in a stationary phase, the fork of the escape fork is configured to abut against one of the two external stops and the drive portion when the oscillator rebounds or reverses. Specifically, when the oscillator rebounds or reverses, a first lug of the fork is designed to contact the drive portion, and a second lug of the fork is designed to contact one of the two external stops.

[0020] In one embodiment, a triangle with the axles of the escape fork, the first escape wheel, and the second escape wheel at its apex on the axle of the locking wheel has an angle less than 120°, preferably less than 90°, and more preferably less than 80°. In one embodiment, the escape fork is not positioned between the axles of the first and second escape wheels. In one embodiment, the axle of the escape fork is located within a triangle, the apexes of which are the axles of the escapement mechanism moving part and the oscillator, respectively. In one embodiment, a circle can be defined centered on the axle of the escape fork, passing through the axles of the first and second escape wheels, and at least one portion passing through the oscillator or balance wheel. In one embodiment, the stopper does not have an elongated or highly elongated shape, and its length is generally less than twice the maximum width of the stopper. In one embodiment, the portion of the escape fork furthest from its center of rotation is positioned at a radius approximately equal to the maximum width of the escape fork: the overall shape of the escape fork is compact and uniform (without significant protrusions), thereby limiting its moment of inertia (which is greatly affected by the square of the distance from the axle).

[0021] In one embodiment, the escapement is not a direct-pulse escapement. In other words, the at least one escape wheel never directly engages with the inertial element. In one embodiment, the stop wheel is the only component of the escapement that directly engages with the inertial element. In one embodiment, from a functional perspective, the escape fork constitutes the only component of the escapement located between the at least one escape wheel and the inertial element.

[0022] A second aspect of the invention relates to an adjustment device for a watch movement, comprising: an escapement mechanism including the escape fork described in the first aspect and at least one escape wheel, the at least one escape wheel being configured to mesh with a gear train in the watch movement, such as a power gear train, to receive power; and an oscillator including an inertial element having a driving portion, such as a tooth or pin, and an elastic reset device connected to the inertial element, wherein the escape fork is rotatably mounted and has an oscillating motion between two consecutive stationary positions with an amplitude greater than 30°, preferably greater than 40°, more preferably greater than 45°. In this escapement mechanism, the impulse is generally tangential. In other words, under the action of the impulse, the escape fork and the escape wheel transmitting the impulse rotate in opposite directions. This reduces sensitivity to friction.

[0023] In one embodiment, the escapement mechanism includes: a first escapement wheel, rotatably mounted about a first rotating shaft, configured to mesh with a gear train of a clock movement, and including a plurality of first stop surfaces and a first drive gear for cooperating with a locking device of an escapement fork; a second escapement wheel, rotatably mounted about a second rotating shaft, including a plurality of second stop surfaces for cooperating with the locking device of the escapement fork and a second drive gear meshing with the first drive gear to transmit power from the first escapement wheel to the second escapement wheel.

[0024] In one embodiment, when the first escapement wheel transmits a pulse to the escapement fork, the pulse is a tangential pulse. In one embodiment, when the second escapement wheel transmits a pulse to the escapement fork, the pulse is a tangential pulse. In one embodiment, the pulse phase applied by the first escapement wheel to the blocking moving member occurs within the first alternating period of the oscillation, while the pulse phase applied by the second escapement wheel to the blocking moving member occurs within the second alternating period of the oscillation.

[0025] In one embodiment: The driving part is arranged at a position with a radial distance R5 from the axis of the inertial member, and the second part, i.e., the stop part, is arranged at a position with a radial distance R41 from the axis of the escapement fork, where 0.8R5 < R4 < 1.2R5, preferably 0.9R5 < R4 < 1.1R5. According to this embodiment, the escapement fork is significantly more compact than the anchor of a Swiss anchor escapement mechanism.

[0026] In one embodiment: The driving part is semi-circular, and / or the inertial member includes a cylindrical side surface that forms a stop wall configured to abut against one of the two second parts, i.e., the stop parts, when the clock movement is impacted during a stationary phase, where: The driving part is arranged at a position with a radial distance R5 from the axis of the inertial member, and the stop wall is arranged at a position with a radial distance R6 from the axis of the inertial member, where preferably R5 > R6, preferably R5 > 1.2R6, preferably R5 > 1.3R6.

[0027] A third aspect of the present invention may relate to a clock including the adjusting device described in the second aspect.

[0028] A fourth aspect of the invention, which may exist independently or in combination with the foregoing aspects, relates to an escapement mechanism for a watch movement, comprising: a first escape wheel, rotatably mounted about a first axis, configured to mesh with a gear train of the watch movement, such as a power gear train, to receive power, and including a plurality of first locking surfaces and a first drive gear; a second escape wheel, rotatably mounted about a second axis, including 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; an inertial element, rotatably mounted about a third axis, configured to oscillate, each oscillation including a first half-cycle and a second half-cycle; and an escapement mechanism. The fork, rotatably mounted about a fourth pivot, includes: a first locking surface portion configured to contact one of a plurality of first locking surfaces to lock rotation of the first escape wheel; a second locking surface portion configured to contact one of a plurality of second locking surfaces to lock rotation of the second escape wheel; a pulse receiving device configured to receive a first pulse from the first escape wheel during a first half-cycle of the oscillation of the inertial member, and a second pulse from the second escape wheel during a second half-cycle of the oscillation of the inertial member; and a pulse transmission device configured to transmit at least a portion of the first pulse or the second pulse to the inertial member.

[0029] In one embodiment, the first blocking surface region is configured such that the first force exerted on the escape fork by the first escape wheel by the first blocking surface region is transmitted generally near the fourth pivot, and particularly through the fourth pivot.

[0030] In one embodiment, the second blocking surface portion is configured such that the second force exerted by the second escape wheel on the escape fork by the second blocking surface portion passes generally near the fourth pivot, and particularly through the fourth pivot.

[0031] In one embodiment, the first escape wheel and / or the second escape wheel may be a single-plane, integral, one-piece, or integrally formed component. In one embodiment, multiple first stop surfaces and a first drive gear may be disposed on the same plane. In one embodiment, multiple second locking surfaces and a second drive gear may be disposed on the same plane.

[0032] In one embodiment, the first escape wheel and / or the second escape wheel may be a dual-plane assembly, such as consisting of two independent gears, or a multi-stage assembly. In one embodiment, multiple first locking surfaces and a first drive gear may be arranged on two different planes. In one embodiment, multiple second locking surfaces and a second drive gear may be arranged on two different planes.

[0033] In the above embodiments, the escapement mechanism can improve operational safety because the first or second locking force acts on or substantially acts on the fourth pivot: when in the locked position (or stationary state), the escape fork does not experience overturning torque, thereby achieving a stable locked position.

[0034] It can be noted that, according to the escapement mechanism of the above embodiment, two pulses are transmitted to the inertial member during the same swing (round trip) of the inertial member to maintain its swing. In fact, the escape fork can: receive a first pulse from the first escape wheel during the first half-cycle of the inertial member (e.g., the outward stroke constituting the first half of the swing) and transmit it to the inertial member, and can receive a second pulse from the second escape wheel during the second half-cycle of the inertial member (e.g., the return stroke constituting the second half of the swing) and transmit it to the inertial member.

[0035] In one embodiment, the first force applied to the escape fork by the first escape wheel, locked by the first locking surface, passes substantially near the fourth pivot, and particularly through the fourth pivot, thereby ensuring that the escape fork is not subjected to overturning torque during the stationary phase. In other words, the first force applied to the escape fork by the first escape wheel, locked by the first locking surface, passes substantially near the fourth pivot, and particularly through the fourth pivot, thereby ensuring a stable stationary position of the escape fork during the stationary phase. During this stationary phase, the escape fork engages only with the first escape wheel.

[0036] In one embodiment, the second force applied to the escape fork by the second escape wheel, locked by the second locking surface, passes substantially near the fourth pivot, and particularly through the fourth pivot, thereby ensuring that the escape fork is not subjected to overturning torque during the stationary phase. In other words, the second force applied to the escape fork by the second escape wheel, locked by the second locking surface, passes substantially near the fourth pivot, and particularly through the fourth pivot, thereby ensuring the stable stationary position of the escape fork during the stationary phase. During this stationary phase, the escape fork engages only with the second escape wheel.

[0037] In one embodiment, the escape fork is mounted in a rotatable manner. In another embodiment, the escape fork is mounted in a rotatable manner on the watch bridge and / or plate. In one embodiment, the escape fork lacks a resilient return mechanism, and / or the escapement mechanism lacks a resilient return mechanism connected to or engaged with the escape fork to hold or return it to a rest position (along with the resilient element of the oscillator (a conventional hairspring) connected to the inertial element, which releases the escape wheel and subsequently moves the escape fork through the continuous movement of the inertial element). In other words, the displacement of the escape fork is caused by the inertial element and / or the first escape wheel and / or the second escape wheel. In particular, when the escapement mechanism is operating normally, the displacement of the escape fork is caused only by the inertial element and / or the first escape wheel and / or the second escape wheel.

[0038] In one embodiment, the escapement is not a direct pulse escapement. In other words, in one embodiment, the first escape wheel and / or the second escape wheel do not directly engage with the inertial element (or the oscillating mechanism typically formed by a balance wheel / hairspring combination).

[0039] In one embodiment, the inertial element includes a balance wheel. Specifically, the inertial element may include a balance wheel, a balance wheel shaft, and a clamp with pins, which are connected to a hairspring.

[0040] In one embodiment, the first locking surface is configured to lock the rotation of the first escape wheel, i.e., the escapement movement of the first escape wheel, and / or the second locking surface is configured to lock the rotation of the second escape wheel, i.e., the escapement movement of the second escape wheel.

[0041] In one embodiment, the first locking surface portion is configured such that the first friction cone formed by the point of application of the force applied to the escapement fork around the first escape wheel includes, or contains, or passes through the fourth pivot, and / or the second locking surface portion is configured such that the second friction cone formed by the point of application of the force applied to the escapement fork around the second escape wheel includes, or contains, or passes through the fourth pivot.

[0042] In one embodiment, the first locking surface portion has a first normal direction passing through or substantially passing through the fourth pivot axis, and the second locking surface portion has a second normal direction passing through or substantially passing through the fourth pivot axis.

[0043] In one embodiment: a first straight line passes through the fourth pivot and the point of contact between the first escape wheel and the first locking surface during the first locking phase, and a second straight line passes through the fourth pivot and the point of contact between the second escape wheel and the second locking surface during the second locking phase, forming an acute angle α. In other words, a triangle can be formed comprising: the fourth pivot with respect to a first vertex, the point of contact between the first escape wheel and the first locking surface with respect to a second vertex, and the point of contact between the second escape wheel and the second locking surface with respect to a third vertex. In one embodiment, the triangle has an acute angle at its first vertex. This configuration allows for a short travel of the escape fork between a first locking position and a second locking position, in which the first escape wheel is locked and the second escape wheel is locked. This provides a compact assembly and is advantageously symmetrical with respect to the planes through which the respective pivots of the inertial element and the escape fork pass.

[0044] In one embodiment, the pulse receiving device of the escapement fork includes: a first pulse input unit configured to receive a first pulse from the first escapement wheel during the first half-cycle of the balance wheel, and a second pulse input unit configured to receive a second pulse from the second escapement wheel during the second half-cycle of the balance wheel.

[0045] In one embodiment, the first pulse input portion is adjacent to the first locking surface portion, and the second pulse input portion is adjacent to the second locking surface portion.

[0046] In one embodiment, the first pulse input section is separated from the first locking surface section via a first fork, and the second pulse input section is separated from the second locking surface section via a second fork.

[0047] In one embodiment: the third straight line passes through the fourth shaft and the contact point between the first escape wheel and the first pulse input in the first pulse phase, and the fourth straight line passes through the fourth shaft and the contact point between the second escape wheel and the second pulse input in the second pulse phase, forming an acute angle γ.

[0048] In one embodiment, the angle γ is in the range of 50° to 70°.

[0049] In one embodiment, angle γ is smaller than angle α. In other words, the first and second pulse input portions are located between the first and second locking surface portions.

[0050] In another embodiment, angle γ can be greater than angle α. In other words, the first and second locking surface portions are located between the first and second pulse input portions. This design symmetrically distributes the displacement caused by any gaps that may occur on the respective axes of the escape wheel. Attached Figure Description

[0051] 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.

[0052] Figure 1 shows an adjustment device for a watch movement, comprising: on one hand, an escapement mechanism including a fork, a first escape wheel, and a second escape wheel; on the other hand, an oscillator including an inertial element with a drive section; Figure 2 shows details of the escape fork in Figure 1; Figure 3 shows details of the escape fork in Figure 2; Figure 4 shows details of the escape fork in Figure 2; Figure 5 shows the state of the adjustment device shown in Figure 1 when the escapement mechanism is in a stationary phase, at which point the escapement mechanism is impacted, causing the escape fork to rotate angularly in a first direction S1; Figure 6 shows the state of the adjustment device shown in Figure 1 when the escapement mechanism is in a stationary phase, at which point the impact causes the escape fork to rotate angularly in a second direction S2; Figure 7 shows a virtual adjustment device with the same configuration as Figure 6, including a virtual escape fork; Figure 8 shows the adjustment device shown in Figure 6 to illustrate the swing range of the escape fork, particularly the lug area of ​​the escape fork; Figure 9 shows the adjustment device shown in Figure 1 when the oscillator is in a return swing state, and the escapement mechanism is in a stationary phase; Figure 10 shows the adjustment device in Figure 1... The details of the device are shown to illustrate the total tilt angle when the escape fork occupies two consecutive stationary positions; Figure 11 shows a highly simplified fork member of the first variant design of the escape fork, particularly the fork member of the escape fork of the regulating device in Figure 1; Figure 12 shows an extremely simplified fork member of the second variant implementation, particularly the fork member of the escape fork of the regulating device in Figure 1; Figure 13 shows a variant of the regulating device shown in Figure 1, which specifically includes a third implementation variant of the escape fork of the regulating device in Figure 1, which is suitable for the stationary phase of the escapement mechanism; Figure 14 shows the state of the regulating device shown in Figure 13 in the escapement mechanism pulse phase (immediately following the stationary phase shown in Figure 13); Figure 15 shows the state of the regulating device shown in Figure 13 in the escapement mechanism rest phase after the pulse phase shown in Figure 14; Figure 16 shows the state of the regulating device shown in Figure 13 in the escapement mechanism pulse phase after the stationary phase shown in Figure 15; Figure 17 shows details of the escape fork in Figure 13; Figure 18 shows in detail the locking mechanism locking device and pulse receiving device of the regulating device shown in Figure 13. Detailed Implementation

[0053] Figure 1 shows an adjustment device for a watch movement, comprising: an escapement 10 including a locking moving part 4, a first escape wheel 1 and a second escape wheel 2; a oscillator 20 including an inertial element (here, a balance wheel 51) that rotates about a third axis A5 and has a drive portion (here, a pin 511a) located on a tray 511 of the balance wheel 51; and a resilient reset mechanism (not shown) connected to the balance wheel 51 (typically a coil spring or a flexible element).

[0054] The two external stops are, in this example, made up of limit pins 91 and 92, but limit rods may also be used.

[0055] Specifically, the escapement mechanism 10 includes: a first escape wheel 1, rotatably mounted about a first pivot A1, configured to mesh with the gear train of the watch movement, and including a plurality of first stop surfaces and a first drive gear for cooperating with a locking device of the escape fork (4; 4'); and a second escape wheel (2; 2'), rotatably mounted about a second pivot (A2; A2'), including a plurality of second stop surfaces for cooperating with a locking device of the escape fork (4; 4') and a second drive gear (4; 4') meshing with the first drive gear to transmit power from the first escape wheel (1; 1') to the second escape wheel (2; 2').

[0056] An escapement fork (4'), rotatably mounted about a fourth pivot (A4'), includes: a locking device configured to lock at least one escape wheel (1, 2; 1', 2') of the escapement mechanism (10; 2') in a stationary phase; a pulse receiving device for receiving pulses from the first escape wheel 1 or the second escape wheel 2 in a pulse phase; and a fork-shaped member 400 with lugs 410, 420.

[0057] Figure 2 shows the second locked position of the escapement mechanism in Figure 1. The escape fork 4 shown in Figure 2 includes: a blocking device, in this example consisting of first and second blocking surface regions 43a and 43b, which lock the first escapement movement 1 or the second escapement movement 2 respectively via the first locking surface 121a and the second locking surface 221a during the stationary phase; a pulse receiving device, in this example consisting of a pulse input section 41a and a pulse input section 41b, the former used to receive the first pulse of the first escapement wheel 1 during the first reciprocating cycle of the balance wheel 51, and the latter used to receive the second pulse of the second escapement wheel 2 during the second reciprocating cycle of the balance wheel 51; the latter is used to receive the second pulse from the second escapement wheel 2 during the second oscillation cycle of the balance wheel 51; the fork-shaped member 400 is equipped with two fork lugs 41. 0, 420, each fork lug includes inner walls 411, 421, respectively equipped with: the first two portions 411a, 421a, referred to as pulse portions, are arranged opposite each other for transmitting at least a portion of the received pulse to the pin 511a of the balance wheel 51 during the pulse phase; the fork members (400; 400') include two second portions (411b, 421b; 411b', 421b'), i.e., stop portions, the second portions are arranged opposite each other, each second portion protruding relative to one of the first portions (411a, 421a; 411a', 421a'), and each second portion is configured to abut against the inertial element when the watch movement is impacted during the stationary phase. It is understood that during normal operation of the escapement 10 (especially in the absence of impact), only the first two portions 411a, 421a contact or engage with the pin 511a. During normal operation, the second parts 411b and 421b do not interact with either the pin 511a or the balance plate 511.

[0058] More specifically, as shown in Figures 2, 3, and 4, each lug 410, 420 includes inner walls 411, 421, which have: a first portion 411a, 421a, called the pulse portion, extending from the bottom of the fork-shaped structure for engaging with the pin 511a on the balance wheel plate 511 of the balance wheel 51; and a second portion 411b, 421b, called the stop portion, located at the free end of each lug, with its endpoints B1, B2 forming a stop device, particularly a line, edge, or surface, which can be used to engage with the wall 511b of the platform 511. The first and second portions can be connected by a third portion 411c, 421c (i.e., the connecting portion) to maintain continuity between the second and first portions.

[0059] It should be noted that the first stamping portions 411a and 421a can be a single plane or curved surface, or they can be composed of multiple continuous or discontinuous surfaces. In the embodiment shown in FIG4, the first pulse portions 411a and 421a are particularly composed of a first planar surface 411a1 and 421a1 and a second curved surface 411a2 and 421a2 (in the shape of an arc), the second surface having a radius of curvature R1 and being continuously formed with the first surface.

[0060] The second portions 411b and 421b can be a single plane or a curved surface, or they can be composed of multiple continuous or discontinuous surfaces. In the embodiments shown in Figures 2 to 4, the second portions 411b and 421b are in the shape of a single curved surface 411b and 421b (arc-shaped), having a radius of curvature R2 and vertices S1 and S2. The surfaces 411b and 421b are connected at endpoints B1 and B2 to the distal walls 412 and 422 of the blocking movement member 4, which are opposite to the periphery or wall 511b of the tray 511 during the additional arcuate movement of the oscillator. The distal walls 412 and 422 are located between the inner walls 411 and 421 and the outer walls 413 and 423 of each lug 410 and 420. Each outer wall 413 and 423 partially defines the outline of the escapement fork 4 and extends along the longitudinal directions D410 and D420, respectively. In general, the longitudinal directions D410 and D420 can be regarded as the longitudinal directions of the lugs 410 and 420.

[0061] The second portions 411b and 421b constitute protrusions extending from the inner walls 411 and 421 of each lug 410 and 420. To describe these protrusions, the lug portions 410 and 420 can be considered to have a thickness E2 at the second portion 411b, and at 421b, particularly at the ends B1 and B2, the thickness E2 is strictly greater than the thickness E1 measured at the first protruding portions 411a and 421a, the thicknesses being measured perpendicularly to the longitudinal directions D410 and D420.

[0062] In a specific structure, the thickness E2 reaches its maximum value at the vertices S1 and S2 of the second portions 411b and 421b. At these vertices, contact may occur between the second portions 411b and 421b and the platform pin 511a.

[0063] In a specific structure, the thickness E2 measured at vertices S1 and S2 is approximately equal to 1.5.E1. More generally, it can be considered that E2>E1, or even E2>1.1.E1, or even E3>1.2.E1, or even E3>1.3.E1.

[0064] As can be seen from Figure 4, the radius of curvature R2 is smaller than the radius of curvature R1. In a specific structure, R1 is approximately 5.R2. More generally, it can be considered that R2 < R1, even 2.R2 < R1, and even 4.R2 < R1.

[0065] In addition, it can be considered that when observing from the inside of the fork-shaped member 400, the first pulse segments 411a, 421a and the second pulse segments 411b, 421b form a protruding angle δ, and the angle is strictly less than 180°. Specifically, a first tangent T1 can be constructed to be tangent to the first segments 411a, 421a, and a second tangent T2 can be constructed to be tangent to the second segments 411b, 421b. When observing from the inside of the fork-shaped member, these two tangents form the protruding angle δ. In particular, the first tangent T1 can be tangent to the first part at the intersection of the second tangent T2 and the first part. More specifically, the symmetric plane of the fork can be defined, and the second tangent T2 can be parallel or substantially parallel to the symmetric plane of the fork. In particular, a first tangent T1 tangent to the first parts 411a, 421a and a second half-line D2 passing through B1, B2 can also be constructed, and when observing from the inside of the fork, they form the protruding angle δ.

[0066] In the schematic diagram shown in Figure 4, the second tangent T2 is substantially parallel to the symmetric plane P4 of the fork, and the angle δ formed by T1 and T2 is approximately 160°. The angle can vary between 70° and 179° according to the relative positions of the tangents T1 and T2. More generally, a half-line D1 passing through at least one point of the first parts 411a, 421a and a half-line D2 passing through at least one point of at least one of the second parts 411b, 421b (especially B1 and B2) can be determined, and when observing from the inside of the fork-shaped member, they form the protruding angle δ.

[0067] In the configuration of the escape fork 4 shown in Figures 2 to 4, the following points can be noted: the escape fork 4 is symmetrical with respect to the plane P4; the escape fork 4 is a planar component, containing only layers; the escape fork 4 has no tip; the first and second pulse input sections 41a and 41b are located between the first and second locking surface sections 43a and 43b; the second portions 411b and 421b are located at a distance or radius R4 from the fourth rotating shaft A4, while the first blocking surface portions 43a and 43b and / or the first and second pulse inlet portions 41a and 41b are located at a distance R4 from the fourth rotating shaft A4. At a distance or radius of 1, and R4>R41, preferably R4>1.4R41, preferably R4>1.8R41; angle γ is less than angle α; angle γ is defined as: the angle between the straight line S3 connecting the first pulse input segment 41a and the fourth rotating shaft A4 and the straight line S4 connecting the second pulse input segment 41b and the fourth rotating shaft A4, and angle α is defined as: angle α is particularly highlighted in the figure, which separates the first straight line S1 connecting the first locking surface part 43a and the fourth rotating shaft A4 from the second straight line S2 connecting the second locking surface part 43b and the fourth rotating shaft A4.

[0068] Returning to Figure 1, it can be noted that the escapement mechanism 10 is a double-tangential pulse type. The escapement mechanism 10 shown in Figure 1 has the following characteristics: its operational safety benefits from the locking force F generated by the contact between the first escapement moving part 1 and the locking moving part 4 during the stationary phase shown in Figure 1, which passes (or substantially passes) through the fourth pivot A4 of the locking moving part 4, particularly through the first and second locking concave areas, which are specially designed to provide good locking safety. Therefore, during a given stationary phase, the escapement fork 4 is not subjected to overturning torque, thus achieving a stable locked position.

[0069] In the event of a severe impact, such as when a watch is dropped, a limiting device can be used to restrict the angular travel of the escapement fork 4, thereby further improving operational safety. The limiting device functions when the escapement fork 4 is normally secured by its first and second locking surface areas.

[0070] Figure 5 shows the state of the adjustment device shown in Figure 1 when the escapement mechanism is stationary, at which point the impact causes the locking moving part to rotate angularly in the first direction S1. In this case, a first external stop, such as limit pins 91 and 92 or a stop, can be provided to limit the angular travel of the escape fork in the given first direction S1. Therefore, even in the event of an accidental impact, the travel of the escape fork 4 will be limited in the rotational direction S1.

[0071] Figure 6 shows the adjustment device shown in Figure 1 in the stationary phase of the escapement mechanism, where the impact causes the escape fork to rotate angularly in the second direction S2. In this case, to further improve operational safety, measures can be taken to prevent the teeth of the first escapement moving member 1, which normally contacts the first locking surface portion 43a of the escape fork 4, from contacting the adjacent pulse inlet portion, which could otherwise cause the escape fork 4 to move unexpectedly before the release phase of the balance wheel 51.

[0072] Therefore, it is recommended to form second portions 411b and 421b, referred to as stop portions, at the free ends of each lug 410, 420 of the escapement fork 4. These two second portions 411b, 421b are characterized by small protruding ends extending from the inner walls of each lug 410, 420, with the inner wall of 420 protruding as far away as possible from the contact area between the fourth pivot A4 of the escapement fork 4 and the stop wall 511b of the escapement fork 4 and the balance wheel plate 511 (whose oscillation is maintained by the escapement mechanism). Thus, the angular oscillation of the escapement fork 4 is minimized, and the escapement mechanism stop teeth, which normally contact the first and second surface stop portions 43a, 43b of the escapement fork 4, cannot contact the adjacent pulse input portions 41a, 41b. It should be noted that for the same escapement fork lug angle, due to its greater distance from the fourth pivot A4 of the escapement fork 4, the protruding portions of the lugs 410, 420 will experience greater displacement relative to other portions of the escapement fork 4.

[0073] Figure 7 shows a virtual adjustment device with the same configuration as Figure 6, including a virtual escapement fork. Compared to Figure 6, the escapement mechanism 10 shown in Figure 7 adopts the same configuration as Figure 6, but is equipped with a virtual stopper 4F, whose free end of the lug has no protrusion, and whose inner wall is only shaped for the pulse function. In this case, the stopper tooth or stop surface of the escape wheel may contact the pulse inlet portion, as shown in the area indicated by the dashed circle at the bottom of the figure.

[0074] Figure 8 illustrates the adjustment mechanism shown in Figure 6 to demonstrate the range of motion of the escapement fork, particularly the lug region. The second parts 411b and 421b (i.e., the limiting sections), working in conjunction with the disc pin 511a, also have the advantage of minimizing lug displacement; that is, minimizing the degree of accidental lug movement that the escapement fork 4 might experience when the pin 511a engages or disengages from the fork member 400. As shown in Figure 8, the tautness occurs at the end or beginning of the stationary phase. The possible contact between the second portions 411b and 421b, i.e. the stop portions, and the disc pin 511a, ensures that the blocking teeth or stop surfaces (typically with the first and second locking surface portions 43a, 43b) cannot contact the adjacent pulse inlet portions 41a, 41b.

[0075] Overall, the second parts 411b and 421b, i.e., the stop portions, also have free ends of the extended lugs 410 and 420, thereby preventing the stopper 4 from flipping over, because when the balance wheel oscillates additionally, or in other words, when the balance wheel pin is not between the two lugs, the lugs 410 and 420 may still contact the balance wheel plate wall. Figure 9 shows the adjustment device shown in Figure 1, where the oscillator is swinging back while the escapement is stationary. The overall structure ensures that the escape fork 4 rotates in the first direction S1 until it contacts the limit pin 91.

[0076] Therefore, the lugs 410, 420 with protrusions replace the anti-reverse function known in the prior art. This characteristic of the tips is enhanced by the approximately 50° tilt angle β of the blocking movement 4 of the escapement 10, which is much higher than the approximately 15° tilt angle of a conventional Swiss anchor escapement. This allows the tenon 511a to disengage from the plate of the fork 400, while allowing the lugs 410, 420 to engage with the baffle 511b of the balance wheel plate 511 during the additional curvature of the balance wheel 51 and the more general curvature of the oscillator. Figure 10 shows details of the adjusting device in Figure 1 to illustrate the total tilt angle β when the escapement fork 4 occupies two consecutive rest positions.

[0077] Figure 11 shows a simplified embodiment 400A of the fork-shaped part 400 of the escapement fork 4 of the adjustment device in Figure 1. In this extremely simplified first embodiment, it can be observed that the first half-line D1 coincides with the first segments 411a and 421a, while the second half-line D2 passes only through a single point on the second segments 411b and 421b, which may correspond to points B1 and B2, or may not.

[0078] Figure 12 shows a highly simplified fork 400B in a second implementation of the escapement fork 400 of the adjusting device in Figure 1. In this extremely simplified second embodiment, it can be noted that the first half-line D1 coincides with the first portions 411a and 421a, and the second half-line D2 coincides with the second portions 411b and 421b, thus passing through the points corresponding to B1 and B2.

[0079] Regardless of the variant used, referring to Figures 2, 3, 4, 11, and 12, the inner walls 411 and 421 (especially the stops B1 and B2) are symmetrically distributed with respect to the plane P4 of the fourth pivot A4 of the escapement fork 4. More generally, the lugs 410 and 420 are symmetrically distributed with respect to the plane P4, that is, the wall surfaces 412 and 422, as well as the outer wall surfaces 413 and 423, are also symmetrically distributed with respect to said plane.

[0080] Preferably, the platform pin 511a is crescent-shaped so that it can engage with the second portions 411b and 421b, thereby minimizing the oscillation of the lugs, while allowing it to be inserted into the fork and engage with either of the first portions 411a and 421a, thereby allowing the balance wheel 51 to be released and to transmit impulse to the balance wheel during its alternating motion.

[0081] During normal operation of the escapement mechanism 10, the first parts 411a and 421a engage only with pin 511a. In the event of a strong impact, parts 411b and 421b are designed to engage with the tray wall 511b via stop devices B1 and B2, or with the tray pin 511a via their respective apexes S1 and S2. The outer walls 413 and 423 are designed to engage only with limit pins 91 and 92 (or alternative limit pins), or with pin 511a when the oscillator rebounds.

[0082] Due to the unique nature of the double tangential pulse escapement mechanism, particularly the use of two escape wheels, the stop wheel 4 has a considerable tilt angle β, approximately 50°. Therefore, the displacement of the 400-type fork is particularly significant compared to that of the Swiss anchor fork, even though the current escape fork 4 is extremely compact, comparable in size to the two escape wheels and the balance wheel tray 511. Consequently, the functional space of the escapement mechanism in the watch can be reduced.

[0083] In the specific structure shown in Figure 10, the radius R5 separating the pin 511a from the third axis A5 of the balance wheel is approximately equal to the radius R4 of the small circle C4 centered on axis A4, and the balance wheel blocking member 4 can be embedded in the circle.

[0084] In another embodiment, the body or fork-shaped structure of the escapement fork 4 can be extended to maximize the displacement of the free ends of the lugs 410 and 420 while limiting the tilt of the escapement fork 4.

[0085] Figure 13 illustrates a variant of the regulating device shown in Figure 1, specifically including a third embodiment of the locking movement component of the regulating device of Figure 1, which is suitable for the stationary phase of the escapement mechanism. In this third embodiment, a new blocking movement component geometry is shown, characterized by first and second blocking surface portions 43a', 43b' between the two pulse inlet surfaces 41a', 41b', as shown in Figures 17 and 18.

[0086] As described below, this escape fork 4' ensures that the reaction forces of the given escape wheel relative to the escape fork 4' and the other escape wheel are located on opposite sides of the plane passing through the respective axes of the escape fork and the given escape wheel.

[0087] The advantage of this structure lies in its working principle, which enables optimized control of assembly clearance, especially considering that the pivots of the two escape wheels will move symmetrically relative to the plane passing through the respective axes of the stop wheel and balance wheel (at different working stages).

[0088] This control over the assembly gap conforms to the definition of a robust escapement.

[0089] Figure 13 shows an adjustment device similar to those in Figures 1 to 10 for the movement of a clock, including: an escapement 10' comprising an escape wheel 4', a first escape wheel 1', and a second escape wheel 2'; a oscillator 20' comprising an inertial element (here, a balance wheel) having a drive portion (here, a pin 511a') located on a tray 511' of the balance wheel 51; and a resilient reset mechanism (not shown) connected to the balance wheel (typically a coil spring or a flexible element); two external stops, which are, for example, limit pins (91, 92; 91', 92') or washers; Figures 13 to 16 show a speed regulating device including the escapement 10'; and Figures 17 and 18 present in detail a third special variant of the escapement fork 4'. Please note that the shape of the fork 400' of the escapement fork 4' is independent of the shape of the first and second locking surface portions 43a', 43b' and the first and second pulse input portions 41a', 41b' of the escapement fork 4'.

[0090] Figure 18 shows in detail the first and second concave regions of the blocking structures 43a' and 43b', which are formed by surfaces 43a1', 43a2' and 43b1', 43b2' respectively, forming obtuse V-shaped structures βa' and βb' with an included angle of approximately 165°.

[0091] The figure particularly highlights angle α, which separates the first straight line S1 connecting the first locking surface 43a and the fourth rotating shaft A4 from the second straight line S2 connecting the second locking surface 43b and the fourth rotating shaft A4.

[0092] Specifically, the first straight line S1' passes through the intersection of connecting surfaces 43a1' and 43a2', and the second straight line S2' passes through the intersection of connecting surfaces 43b1' and 43b2'. In the illustrated construction variant, the angle α' is an acute angle, approximately 55°. More broadly, the following numerical range can be designed: 50° ≤ α ≤ 70°.

[0093] The figure particularly highlights angle α, which separates the first straight line S1 connecting the first locking surface 41a and the fourth rotating shaft A4 from the second straight line S2 connecting the second locking surface 43b and the fourth rotating shaft A4.

[0094] Specifically, the third straight line S3' intersects the first pulse input portion 41a', and the fourth straight line S4' intersects the second pulse input portion 41b'. In the illustrated variant, the angle γ' is an acute angle, approximately 65°. More broadly, the following numerical range can be designed: 60° ≤ γ ≤ 80°.

[0095] Please note that the escapement fork 4' shown in Figure 18 differs from the escapement fork 4' shown in Figure 2: here, the first and second concave regions of the blocking components 43a' and 43b' are positioned between the first and second pulse input regions 41a' and 41b'. Therefore, angle α' is smaller than angle γ' (while in Figure 2, angle α is larger than angle γ).

[0096] With this special 4' escapement fork configuration, the escapement mechanism 10' shown in Figures 13 to 16 has the following characteristics: it is driven by a first escape wheel 1' (particularly including a pinion 13' driven along a first direction S1), and the moving part is located on the right side of the plane P45' through the respective axes of the moving part 4' and the balance wheel or oscillator 51'. This distinguishes it from the escapement mechanism 10 in Figure 1, which is equipped with the first escape wheel 1 (particularly including a pinion 13 driven along a first direction S1) located on the left side of the plane P45 through the respective axes of the moving part 4 and the balance wheel 51. Gears 11' and 21' are the same as gears 11 and 21 in Figure 1, the only difference being that gears 11' and 21' are mounted in reverse on their respective axes A1' and A2' relative to the arrangement of gears 11 and 21 on their respective axes A1' and A2'.

[0097] Figure 13 illustrates the operating state of the escapement 10': the second escapement movable part 2' abuts against the second blocking surface region 43b' of the blocking movable part 4', thereby generating a reaction force F24' pointing in the direction of axis A4'. The engagement between the first and second escape wheels 1', 2' also generates a reaction force F12'. The vector distribution of these reaction forces is shown on both sides of the plane P24' passing through the respective axes of rotation of the movable part 2' and the movable part 4'. By evaluating the force applied to the second escape wheel 2' in this stationary phase, and noting that the part is locked or pressed against the second locking surface region 43b', it can be inferred that the mounting clearance of the second movable escapement 2' relative to the second axis A2' has been eliminated, thereby allowing or causing the second movable escapement 2' to move to the left of Figure 13, generally along direction D21' (the movement of the second escape wheel 2' along direction D21' can be simply summarized as the second escape wheel 2' swinging or rotating about the fulcrum of the second escape wheel 2' on the escape fork 4').

[0098] Figure 14 shows the state of the escapement mechanism 10' when the second escapement actuator 2' engages with the second pulse input section 41b' to transmit a pulse to the locking actuator 4'. This causes the reaction force F24' to no longer pass through the fourth pivot A4', thus changing its direction. The vectors of the reaction forces F24' and F12' are still distributed on both sides of the plane P24'. By summarizing the forces applied to the second escape wheel 2' during the stroke phase and recording the stroke force F24' and support force F12' applied to the second stroke inlet section 41b' respectively, it can be inferred that the installation clearance of the second escape wheel 2' relative to the second pivot A2' is compensated, allowing or causing the second escape wheel 2' to always move to the left of Figure 14, approximately along direction D22'.

[0099] Therefore, any installation clearance of the second escape wheel 2' relative to the second pivot A2' is compensated, and during the stationary or stroke phases involving the second escape wheel 2', it is always permitted or caused the second escape wheel 2' to move to the left of FIG. 13 or FIG. 14.

[0100] Figure 15 illustrates the operating state of the escapement mechanism 10': the first escapement moving part 1' abuts against the first blocking surface region 43a' of the blocking moving part 4', thereby generating a reaction force F14' pointing in the direction of the fourth axis A4'. The meshing between the first and second escape wheels 1' and 2' also generates a reaction force F12' (very weak) and / or at least one makes contact when stationary. The schematic vectors of these reaction forces are distributed on both sides of the plane P14' through the respective axes of the moving parts 1' and 4'. It should also be noted that the first escape wheel 1' is continuously subjected to torque from the drive gear set via the pinion 13'. By evaluating the force applied to the first escape wheel 1' during this stationary phase, and noting that it is stuck or pressed against the first locking surface area 43a', it can be inferred that the mounting clearance of the first escape wheel 1' relative to the first pivot A1' has been eliminated, thereby allowing or causing the first escape wheel 1' to move to the right of FIG. 15, roughly along direction D11' (the movement of the first escape wheel 1' along direction D11' can be briefly summarized as: due to the torque applied to the first escape wheel 1', the first escape wheel 1' swings or rotates about its fulcrum on the escape fork 4').

[0101] Figure 16 illustrates the operating state of the escapement mechanism 10': when the first escapement moving part 1' transmits a pulse to the blocking moving part 4' in cooperation with the first pulse input segment 41a', it causes the reaction force F14' to be redirected, and the force no longer acts through the fourth shaft A4'. The meshing between the first and second escape wheels 1' and 2' also generates a (very weak) reaction force F12' and / or at least one contact point during the pulse phase. Furthermore, note that the first escape wheel 1' continuously bears the torque of the drive gear set through the pinion 13'. The vectors representing the reaction forces F14' and F12' remain on either side of the plane P14'. By evaluating the force applied to the first escapement actuator 1' during the stroke phase, and recording the stroke force F14' acting on the first stroke inlet section 41a' and the torque acting on the first escapement actuator 1', it can be inferred that the installation clearance of the first escapement wheel 1' relative to the first shaft A1' has been eliminated, allowing or causing the first escapement wheel 1' to always move to the right of FIG. 16, approximately along direction D12'.

[0102] Therefore, any installation clearance of the first escape wheel 1' relative to the first pivot A1' is compensated, and during the stationary or stroke phases involving the first escape wheel 1', the first escape wheel 1' is always allowed or caused to move to the right in the direction shown in Figure 15 or Figure 16.

[0103] Whether in the stationary phase (Figures 13 and 15) or the stroke phase (Figures 14 and 16), the escapement pistons 1' and 2' will move symmetrically relative to plane P45' (but at different stages). Specifically, when the first and second escapement wheels 1' and 2' successively abut against the first and second stop surfaces 43a' and 43b', the displacement amplitudes D11' and D21' of the first and second escapement wheels 1' and 2' are the same, while the directions of displacement D11' and D21' are opposite. When 2' successively abuts against the first and second stop surface regions 43a' and 43b', respectively, the displacement amplitudes D11' and D21' of the first and second moving parts 1' and 2' are the same, and the directions of displacement D11' and D21' are symmetrical relative to plane P45'. In particular, when the first and second movable escapement mechanisms 1' and 2' sequentially contact the first and second pulse inlet portions 41a' and 41b', the displacements D12' and D22' of the first and second movable escapement mechanisms 1' and 2' are of the same magnitude, and the displacement directions of D12' and D22' are symmetrical with respect to the plane P45'.

[0104] Precise control of the displacement of the first and second escape wheels 1', 2' relative to their bearings controls the assembly clearance, meeting the requirements for designing a robust escapement mechanism. Note that this clearance compensation is independent of the operational safety provided by the second portion, the stop portion, which forms a protrusion or projection relative to the first portions 411a', 421a' (i.e., the stamped portion of the fork 400'). Therefore, the escape fork 4' may or may not include a fork 400' similar to or identical to the fork 400 previously described in Figures 2 through 4.

[0105] Therefore, the escapement fork 4' enables the design of a particularly robust and shock-resistant escapement mechanism.

[0106] Industrial applications The escapement fork and its manufacture described in this invention can be used in industrial applications.

[0107] 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.

Claims

1. An escapement fork for a watch movement (4; 4'), the watch movement includes: an escapement (10; 10'), the escapement including an escape fork (4; 4') and at least one escape wheel (1, 2; 1', 2'), a oscillator (20; 20'), the oscillator including at least one inertial element having a drive portion, such as a tooth or pin (511a; 511a'), and a resilient reset device connected to the inertial element, the escape fork (4; 4') including: a locking device configured to lock the at least one escape wheel (1, 2; 1', 2') of the escapement mechanism (10; 10') in a stationary phase, a pulse receiving device configured to receive pulses from the at least one escape wheel (1, 2; 1', 2') in a pulse phase, and a fork-shaped member (400; 4'). 00'), the fork-shaped member has two first portions (411a, 421a; 411a', 421a'), namely pulse portions, the first portions being disposed opposite each other and configured to transmit at least a portion of the pulses received from the at least one escapement wheel (1, 2; 1', 2') to the drive portion of the inertial member during the pulse phase, characterized in that the fork-shaped member (400; 400') includes two second portions (411b, 421b; 411b', 421b'), namely stop portions, the second portions being disposed opposite each other, each second portion being convex relative to one of the first portions (411a, 421a; 411a', 421a'), and each second portion being configured to abut against the inertial member when the watch movement is impacted during the stationary phase.

2. The escapement fork (4; 4') according to claim 1, wherein, The fork-shaped member (400; 400') includes two lugs (410, 420; 410', 420'), each lug extending along a longitudinal direction (D410, D420; D410', D420'), wherein each lug (410, 420; 410', 420') has, in a direction perpendicular to its respective longitudinal direction (D410, D420; D410', D420'), a first width E1 at a first portion (411a, 421a; 411a', 421a'), and a second width E2 at a second portion (411b, 421b; 411b', 421b'), wherein E2 > E1, preferably E2 > 1.1E1, preferably E2 > 1.2E1, preferably E2 > 1.3E1.

3. The escapement fork (4; 4') according to claim 1 or 2, wherein, Each second part (411b, 421b; 411b', 421b') includes at least: a distal stop end formed at the free end of the fork (400; 400'), specifically at the free end of the lugs (410, 420; 410', 420') of the fork (400; 400'); and a radial surface oriented substantially perpendicular to the pivoting direction of the escapement fork (4; 4'), wherein: the distal stop end is configured such that, preferably during the additional ascent or descent angle travel of the inertial member, the inertial member enters... During the additional upward or downward angle travel of the inertial element, and during this time the drive portion and the fork (400; 400') are in a non-engaged or non-disengaged phase, if the watch movement is impacted, the distal stop end abuts against the inertial element, and / or the radial surface is configured such that during the additional upward or downward angle travel of the inertial element, preferably during the additional upward or downward angle travel of the inertial element and during this time the drive portion and the fork (400; 400') are in an engaged or disengaged phase, if the watch movement is impacted, the radial surface abuts against the drive portion of the inertial element.

4. The escapement fork (4; 4') according to any one of claims 1 to 3, wherein, Each first part (411a, 421a; 411a', 421a') is connected to the second part (411b, 421b; 411b', 421b') via a third part (411c, 421c; 411c', 421c'), the third part being the connecting part. Preferably, a tilt reversal point and / or groove are provided at the third part.

5. The escapement fork (4; 4') according to any one of claims 1 to 4, wherein, When the first portion (411a, 421a; 411a', 421a') and the second portion (411b, 421b; 411b', 421b') are observed to protrude from inside the fork-shaped member (400; 400'), the first tangent of the first portion (411a, 421a; 411a', 421a') and the second tangent of the second portion (411b, 421b; 411b', 421b') form an angle δ of less than 180° with the second tangent of the second portion, and the second portion is protruding relative to the first portion.

6. The escapement fork (4; 4') according to any one of claims 1 to 5, wherein, Each first part (411a, 421a; 411a', 421a') includes at least one plane and at least one curved surface, preferably said plane being remote from the pivot (A4; A4') of the escapement fork (4; 4').

7. The escapement fork (4; 4') according to any one of claims 1 to 6, wherein, Each second part (411b, 421b; 411b', 421b') includes at least one surface.

8. The escapement fork (4; 4') according to any one of claims 1 to 7, wherein: The locking device and / or pulse receiving device are located at a radial distance R41 from the pivot of the escape fork (4; 4'). The second part (411b, 421b; 411b', 421b'), i.e. the stop part, is located at a radial distance R41 from the pivot of the escape fork (4; 4'), wherein R4>R41, preferably R4>1.4R41, and more preferably R4>1.8R41.

9. The escapement fork (4; 4') according to any one of claims 1 to 8, characterized in that: The escapement fork is planar or composed of planar components, and / or the escapement fork has no tip, and / or the escapement fork is a single piece or assembled from at least two components.

10. An adjusting device (10') for a watch movement, comprising: Escapement mechanism (10; 10'), said escapement mechanism comprising an escapement fork (4; 4') according to any one of claims 1 to 9 and at least one escape wheel (1, 2; 1', 2'), said at least one escape wheel being arranged to mesh with a gear train in a watch movement, such as a power gear train, to receive power; a rocker (20; 20'), said rocker comprising an inertial member having a driving portion, such as teeth or pins (511a; 511a'), and an elastic restoring device connected to the inertial member, two external stops, said two external stops being constituted by, for example, limit pins (91, 92; 91', 92') or washers, wherein, in the stationary phase, the fork member (400; 400') of the escapement fork (4; 4') is arranged to abut against one of the two external stops and the driving portion when the rocker (20; 20') rebounds or rebounds in the reverse direction.

11. An adjusting device (10') for a watch movement, comprising: Escapement mechanism (10; 10'), said escapement mechanism comprising an escapement fork (4; 4') according to any one of claims 1 to 9 and at least one escape wheel (1, 2; 1', 2'), said at least one escape wheel being arranged to mesh with a gear train in a watch movement, such as a power gear train, to receive power; a rocker (20; 20'), said rocker comprising an inertial member having a driving portion, such as teeth or pins (511a; 511a'), and an elastic restoring device connected to the inertial member, wherein the escapement fork (4; 4') is rotatably mounted and has a swinging movement with an amplitude greater than 30°, preferably greater than 40°, more preferably greater than 45° between two consecutive stationary positions.

12. The adjusting device according to any one of claims 10 to 11, wherein, Said escapement mechanism (10; 10') comprises: a first escape wheel (1; 1'), rotatably mounted about a first axis of rotation (A1; A1'), arranged to mesh with a gear train of a watch movement and comprising a plurality of first stop surfaces and a first driving gear for cooperating with a locking device of the escapement fork (4; 4'), a second escape wheel (2; 2'), rotatably mounted about a second axis of rotation (A2; A2'), comprising a plurality of second stop surfaces for cooperating with a locking device of the escapement fork (4; 4') and a second driving gear (4; 4') meshing with the first driving gear to transmit power from the first escape wheel (1; 1') to the second escape wheel (2; 2').

13. The adjusting device according to any one of claims 10 to 12, wherein: The driving portion is arranged at a radial distance R5 from the axis of rotation of the inertial member, and a second portion (411b, 421b; 411b', 421b'), i.e., a stop portion, is arranged at a radial distance R41 from the axis of rotation of the escapement fork (4; 4'), wherein 0.8R5 < R4 < 1.2R5, preferably 0.9R5 < R4 < 1.1R5.

14. The adjusting device according to any one of claims 10 to 13, wherein: The drive section is crescent-shaped, and / or the inertial element includes a cylindrical side surface forming a stop wall, which is configured to abut against one of the two second sections (411b, 421b; 411b', 421b'), i.e., the stop section, when the watch movement is subjected to an impact during the stationary phase. The drive section is located at a radial distance R5 from the axis of rotation of the inertial element, and the stop wall is located at a radial distance R6 from the axis of rotation of the inertial element. Preferably, R5 > R6, more preferably R5 > 1.2R6, and more preferably R5 > 1.3R6.

15. A clock, comprising an adjusting device according to any one of claims 10 to 14.

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