Speed ​​regulating machine

Abstract

To provide a speed control escapement that can acquire stable accuracy of measuring time due to a large amplitude of a speed controller.SOLUTION: A speed control escapement 2 includes: a balance wheel 31 which makes reciprocating rotation at a regular cycle; a driving wheel 41 for an intermittent transmission device 4 connected to the balance wheel 31 coaxially; a driven wheel 42 for the intermittent transmission device 4 engaged with the driving wheel 41; a regulation leverage (a pallet 54) engaged with the escape wheel 7 to regulate the rotation of the escape wheel 7; and a swing stone 52 engaged with the regulation leverage, the swing stone integrally rotating with the driven wheel 42. With the structure, no swing abnormality occurs even when an amplitude of the balance wheel exceeds approximately 340° and this leads to realization of an exceptionally large amplitude.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present invention relates to a speed regulating escapement for use in a mechanical timepiece. [Background technology]

[0002] (isochronous) In mechanical watches, the rotation of the barrel containing the power spring is accelerated by a speed-increasing wheel train, and the speed-regulating escapement rotates the wheel train at a fixed cycle to measure time. As the speed-regulating escapement rotates back and forth, it is subject to viscous resistance due to friction of the sliding surfaces and air disturbances, so the vibration of the speed-regulating escapement alone will dampen and eventually stop. In reality, the escapement replenishes energy to the speed-regulating escapement as needed with each escapement, allowing the speed-regulating escapement to maintain its amplitude. In this invention, the rotational position at a certain point in the oscillation cycle of the balance is referred to as the "oscillation angle," and the maximum oscillation angle (single amplitude) of the balance is referred to as the "amplitude" to distinguish between the two.

[0003] During the escapement release process and energization process, which are necessary for the governor to continue vibrating, the time when the force and moment are generated does not strictly coincide with the free state of the governor. Therefore, the governor is subjected to external forces that disturb the free vibration. The effect on the rate that occurs in this case is generally called "escapement error," and escapement error is calculated from Airy's law. It is known that this escapement error generally decreases in proportion to the square of the amplitude of the balance. The free state of the governor mentioned above refers to the state in which the hairspring of the governor is in a free state.

[0004] In addition, the deviation of the center of gravity of the governor relative to the rotating shaft is called "unbalanced weight" and affects the isochronism in the vertical position. The effect on the rate caused by this is generally called "vertical isochronism", and this effect is expressed as follows, with amplitude as a variable: The amplitude crosses the horizontal axis (zero timing error) for the first time at 220°. It is defined by the first kind of Bessel function. Vertical isochronism is the function of the balance amplitude change in the region where the amplitude is 220° or less. Large timing error In the range of 220° or more, the larger the amplitude of the balance, the greater the sensitivity to changes in amplitude. Timing errors are significantly reducedTherefore, it is recommended that the amplitude of the balance be kept at 220° or more at the end of the mainspring's operating time.

[0005] In addition, the clock can be displayed in a flat or upright position. Timing accuracy The main cause of the "balance difference", which is the difference between the two, is said to be the difference in friction between the tenons that support the balance shaft in the flat and upright positions. In other words, in the flat position, the tenons are supported in the thrust direction by the bridge jewel, so the distance from the balance's center of rotation to the sliding surface is small, whereas in the upright position, the tenons are supported in the radial direction by the hole jewel, so the distance is greater than in the flat position, and friction torque increases. As a result, the amplitude in the upright position decreases, and this difference affects isochronism. In other words, if the initial amplitude can be increased, the final swing angle will also increase, and the balance difference will decrease. restraint This becomes possible.

[0006] Therefore, in order to improve timekeeping accuracy, including escapement error, vertical isochronism, and vertical difference, it is effective to increase the amplitude of the balance. (See Non-Patent Document 1 below.)

[0007] (Prior art 1) However, in conventional escapements such as the club-tooth lever escapement (Swiss lever escapement) or the Tedent escapement, if the amplitude of the balance is set large, the impulse jewel that rotates integrally with the balance stem interferes with the regulating lever (pallet fork, Tedent lever, etc.), causing a problem called "impingement," so the amplitude of the balance could not be set to approximately 340° or more (see, for example, Patent Document 1 below).

[0008] (Prior art 2) Another prior art is the "Benoit tourbillon" invented by Achille Hubert Benoit. Note that the Benoit tourbillon does not have a carriage (cage), so it is different from the tourbillon.

[0009] The Benoit tourbillon is different from conventional escapements in that the escape wheel and the balance are in elastic contact via a hairspring, and when the escape wheel rotates, the torque is transmitted around the balance arbor by the escape wheel's division angle via the hairspring to maintain vibration. The Benoit tourbillon has the advantage of having no frictional resistance during escapement and no free spinning of the escape wheel, which causes loss of energy transmission. In addition, since it does not have an impulse jewel, there is no impulse hit, and the amplitude of the balance can be expanded to the elastic limit of the hairspring. The Benoit tourbillon uses an anchor-shaped regulating lever to regulate the escape wheel, which rotates alternately under the alternating torque of the hairspring, to perform escapement. In the following explanation of the operation of the Benoit tourbillon, the direction in which the escape wheel rotates when relaxing the power spring is defined as the positive rotation direction.

[0010] First, when the balance rotates in the opposite direction to the forward rotation of the escape wheel, the escape wheel receives a torque in the reverse direction from the hair spring and rotates in the reverse direction. When the escape wheel rotates in the reverse direction, one of the pawls on the regulating lever engages with the escape wheel and locks it. After the escape wheel is locked, the balance starts to oscillate freely, and when it reverses at a first amplitude, the torque of the hair spring that locks the escape wheel decreases. When the torque of the hair spring decreases below the forward torque of the escape wheel, the escape wheel disengages from the pawl of the regulating lever and starts to rotate forward. When the regulating lever is returned to the neutral position by a thin spring, the other pawl locks the escape wheel that rotates forward. The balance again transitions to free oscillation, and when it reverses at a second amplitude, the torque of the hair spring that locks the escape wheel decreases. When the torque of the hairspring eventually becomes greater than the forward torque of the escape wheel, the escape wheel disengages from the pawl and is rotated in the reverse direction by the hairspring, thus starting the next operating cycle.

[0011] However, it is known that the Benoit tourbillon does not sustain vibration and has an unstable isochronism due to the following reasons (see Non-Patent Document 2 below).

[0012] The first problem is that the vibration does not continue. Benoit's tourbillon aims to bias the balance by twisting the hairspring through the forward rotation of the escape wheel, but this is not realized. This is because the escape wheel receives torque from the speed-increasing gear train and gradually increases its angular velocity from a stopped state, while the balance instantly overtakes the escape wheel at its maximum angular velocity. In this case, the escape wheel does not bias the balance through the hairspring, but rather the balance biases the escape wheel through the hairspring. As a result, Benoit's tourbillon supplements the energy of the balance to the escape wheel, instead of giving energy to the balance, and the balance stops even though the torque of the main spring is sufficiently large.

[0013] The second problem is that the timing accuracy is unstable. In the Benoit tourbillon, the angle at which the escape wheel rotates during escapement varies depending on the direction of rotation of the balance, so the torque of the hairspring, which acts as an external disturbance, is generated asymmetrically with respect to the free vibration of the balance. If an external torque asymmetric with respect to the free vibration is generated near the center of the free vibration due to escapement, the effect on timing accuracy is kept small based on Airy's theorem. However, since the Benoit tourbillon escapes at an oscillation angle where the torque of the hairspring and the torque of the speed-up train are balanced, an external torque asymmetric with respect to the free vibration is generated at an oscillation angle that is far removed from the free state of the governor. This makes it impossible to reduce the escapement error. Moreover, the torque at which the escapement operates is directly affected by the torque of the power spring. This makes it impossible to obtain stable timing accuracy with the Benoit tourbillon. (See Non-Patent Document 3)

[0014] (Prior art 3) The "free spring impulse escapement" (see Patent Document 3 below) invented by Sigmund Riefler is known as a regulating escapement that solves the first problem of the Benoit tourbillon. The escapement in Patent Document 3 transmits force to the balance via a hairspring, just like the Benoit tourbillon, but the hairspring is elastically connected to a regulating lever, and when the hairspring is twisted to transmit torque to the balance using the oscillation of the regulating lever, the escape wheel's division angle is further divided into two for forward and reverse rotation of the balance, so that the hairspring can always be twisted in the opposite direction for either direction of reciprocating rotation of the balance, which is an improvement over the Benoit tourbillon.

[0015] In the escapement of Patent Document 3, the regulating lever can twist the hairspring in the opposite direction in either rotation direction of the balance, so that the hairspring can be twisted by the oscillation angle of the regulating lever to reliably impart elastic energy. This makes it possible to replenish energy to the governor, allowing it to continue vibrating.

[0016] However, the escapement of Patent Document 3 has a problem that the torsion angle of the hairspring is limited to a small oscillation angle of the regulating lever due to the structure using the regulating lever to twist the hairspring, and therefore it is not possible to impart a sufficient torsion angle to the hairspring. As a result, it is not possible to supply sufficient energy to the governor, and it is not possible to obtain the desired amplitude of approximately 340° or more.

[0017] Furthermore, the escapement of Patent Document 3 generates friction loss torque because the pawl of the regulating lever pressed against the escape tooth is frictionally slid by the hairspring to engage and disengage when the escapement is released. Therefore, disturbance torque is generated at an oscillation angle far removed from the free state of the governor, and coupled with the problem of small amplitude, there is a problem that stable timekeeping accuracy cannot be obtained.

[0018] (Prior art 4) As another prior art, a speed-adjusting escapement is known in which the impulse jewel is moved away from the balance wheel in a club-tooth lever escapement to avoid collision with the pallet fork (see Patent Document 4 below).

[0019] The escapement in Patent Document 4 connects the balance stem and an axis spaced from the balance stem with an endless track that can move in a reciprocating manner, and has an impulse jewel on the endless track. This makes it possible to avoid strikes by moving the impulse jewel to a position where it does not interfere with the pallet fork when the amplitude of the balance swings approximately 340° or more.

[0020] However, in the speed-governing escapement of Patent Document 4, the endless track itself and the multiple driven wheels that guide the endless track are constantly moving in conjunction with the movement of the balance, so internal friction in the endless track itself and friction between the driven wheels are constantly occurring. This causes a problem of preventing the free vibration of the speed governor. In addition, there is a problem of the quality factor (Q value) of the speed governor decreasing due to friction loss. This causes a problem of consuming a lot of energy, and a problem of needing to replenish a lot of energy to maintain a large amplitude. This causes a problem of shortening the duration of the mainspring. [Prior art documents] [Patent documents]

[0021] [Patent Document 1] JP 2010-217166 A [Patent Document 2] French Patent Application Publication No. 3008200 [Patent Document 3] DE 50739 A1 [Patent Document 4] JP 2020-85819 A

[0022] [Non-Patent Document 1] Shoichiro Komaki (2014) “§2.9 Escapement error”, Mechanical Watch Course, University of Tokyo Press, p. 76, p. 102-110. [Non-Patent Document 2] George Daniels(2011) “Tourbillon Carriages”(UK), WATCHMAKING, 2011 edition, p. 300-302. [Non-Patent Document 3] R. Daners (1986) “Un tourbillon d'apr▲e▼s A.-H. Beno▲i▼t” (Switzerland), Chronom▲e▼trophilia, No. 21, p. 47-54. Summary of the Invention [Problem to be solved by the invention]

[0023] The problem to be solved by the invention is to provide a governor and escapement that has a large amplitude and can provide stable timekeeping accuracy. [Means for solving the problem]

[0024] The most important feature of the present invention is that by providing an intermittent transmission device in the regulating escapement, it is possible to achieve a large amplitude of more than approximately 340° and an escapement using a regulating lever and impulse jewel.

[0025] (1) The regulating escapement of the present invention comprises a balance which rotates back and forth at a constant period, a balance stem which is coaxially connected to the balance, a driving wheel of an intermittent transmission which is coaxially connected to the balance stem, a driven wheel of the intermittent transmission which engages with the driving wheel, a regulating lever which engages with an escape wheel and regulates rotation of the escape wheel, and an impulse jewel which rotates integrally with the driven wheel and engages with the regulating lever.

[0026] According to the speed-regulating escapement of the present invention, the regulating lever can be oscillated at a predetermined oscillation angle of the balance to effect escapement. Furthermore, even if the amplitude of the balance exceeds approximately 340°, no oscillation occurs because the intermittent transmission rotates. Furthermore, as long as the amplitude of the balance does not exceed the range in which the driven wheel rotates once, theoretically, it is possible to increase the amplitude of the balance up to the elastic limit of the hairspring. Therefore, compared to conventional escapements in which oscillation occurs, the amplitude can be significantly increased, and timekeeping accuracy can be improved.

[0027] (2) Furthermore, the regulating escapement according to the present invention comprises a balance which rotates back and forth at a constant cycle, a balance stem coaxially connected to the balance, a driving wheel of an intermittent transmission which is coaxially connected to the balance stem, an escape wheel which is arranged coaxially with the balance stem and fixed to the main plate so as not to rotate, a carrier supported coaxially with the balance stem, a hair spring which elastically contacts the balance stem and the carrier, a regulating lever which is supported on the carrier and engages with the escape wheel and regulates the rotation of the carrier, a driven wheel of the intermittent transmission which is supported on the carrier and engages with the driving wheel, and an impulse jewel which rotates integrally with the driven wheel and engages with the regulating lever.

[0028] According to the speed-regulating escapement of the present invention, the regulating lever can be oscillated at a predetermined oscillation angle of the balance to effect escapement. Also, since the entire speed-regulating escapement can be rotated at a constant cycle in the rotation direction of the balance while oscillating the balance at a large amplitude exceeding approximately 340°, vertical isochronism in various vertical positions can be averaged. Furthermore, since the hairspring can be twisted by a constant angle for each escapement, it also functions as a constant force device and can equalize the energy given to the speed-regulating mechanism. As a result, the timekeeping accuracy can be further improved.

[0029] (3) Furthermore, in the speed-regulating escapement according to the present invention, the angle by which the carrier rotates in the opposite direction to the balance wheel during escapement may be set to be larger than the angle by which the carrier rotates in the same direction as the balance wheel.

[0030] In this case, it is possible to improve the efficiency of energy supply from the carrier to the balance, which in turn makes it possible to maintain a large amplitude of the balance and improve timekeeping accuracy.

[0031] (4) Furthermore, in the speed-regulating escapement according to the present invention, the torque that the carrier receives from the speed-increasing gear train may be set to be greater than the torque generated by the hair spring when the oscillation angle of the balance rotating in the opposite direction to the carrier is at its maximum.

[0032] In this case, when the balance has its maximum swing angle in the direction opposite to the direction of rotation of the carrier, it is possible to prevent the carrier from being unwound by the torque generated in the hairspring, thereby suppressing the inhibition of free vibration that deteriorates timekeeping accuracy.

[0033] (5) Furthermore, the speed-regulating escapement according to the present invention may be set so that when the balance rotates in the same direction as the carrier, the point at which the carrier rotates is completed before the hairspring becomes free, and when the balance rotates in the opposite direction to the carrier, the point at which the carrier rotates is set after the hairspring becomes free.

[0034] In this case, since it is possible to eliminate the section during rotation of the carrier where the carrier relaxes the hairspring and reduces the energy held by the governor, it is possible to improve the efficiency of energy replenishment to the balance by the rotation of the carrier, and thus it is possible to maintain a large amplitude of the balance.

[0035] (6) In the speed-regulating escapement according to the present invention, the intermittent transmission device may be a Geneva mechanism.

[0036] In this case, machining is simple and there are no special curves, so high precision can be obtained with general machine tools. In addition, since it is a positive motion type and has good acceleration and deceleration kinetics during intermittent transmission, reliable and smooth intermittent operation can be obtained.

[0037] (7) In the speed-regulating escapement according to the present invention, the driving wheel of the Geneva mechanism may be configured as a single layer.

[0038] In this case, the driving wheel of the Geneva mechanism, which is normally made up of two layers of a pin gear and a lock gear, can be made into a single layer, allowing the intermittent transmission to be made thinner.

[0039] (8) In the regulating escapement according to the present invention, the impulse jewel may be provided on the driven wheel of the Geneva mechanism.

[0040] In this case, since there is no need to provide a pallet seat to hold the pallet jewel, the driven wheel can also function as the pallet seat, making it possible to form the intermittent transmission in a thin configuration.

[0041] (9) In the speed regulating escapement according to the present invention, the impulse jewel may be provided on the teeth portion of the driven wheel of the Geneva mechanism.

[0042] In this case, the outermost diameter of the driven wheel can be made smaller than when the impulse jewel is held in phase with the groove of the driven wheel, thereby making it possible to reduce the size of the intermittent transmission device.

[0043] (10) In the speed controlling escapement according to the present invention, the outer end position of the hairspring may be attached so as to be angularly adjustable about the balance stem with respect to the engagement phase of the intermittent transmission device.

[0044] In this case, the free state of the governor can be adjusted in the assembled state relative to the operating angle of the escapement, making it easy to adjust the rate. Effect of the Invention

[0045] According to the present invention, the amplitude of the governor can be maintained large and escapement can be achieved at a predetermined oscillation angle, resulting in an escapement, movement, and timepiece with stable timekeeping accuracy. [Brief description of the drawings]

[0046] [Figure 1] A front view illustrating a timepiece according to the present invention. [Diagram 2] FIG. 1 is a front view showing a movement according to a first embodiment; [Diagram 3] FIG. 1 is a rear view showing an extension escapement according to a first embodiment; [Figure 4] FIG. 1 is a partial front view showing a speed governor according to a first embodiment; [Diagram 5] FIG. 1 is a perspective view showing an intermittent transmission and an escapement according to a first embodiment; [Figure 6] FIG. 1 is a side view showing an intermittent transmission and an escapement according to a first embodiment; [Figure 7] FIG. 1 is a front view showing a reference state of an intermittent transmission and an escapement according to a first embodiment; [Figure 8] FIG. 8 is an explanatory diagram showing the vicinity of the intermittent transmission device corresponding to FIG. 7. [Figure 9] An explanatory diagram showing the escapement and its surroundings corresponding to FIG. 7. [Figure 10] FIG. 11 is an explanatory diagram showing a state before a first stop release step in the first embodiment; [Figure 11] FIG. 11 is an explanatory diagram showing a state after a first stop release step in the first embodiment; [Figure 12] FIG. 11 is an explanatory diagram showing a state of a first biasing step in the first embodiment; [Figure 13] FIG. 1 is an explanatory diagram showing a state before a first idling step in the first embodiment; [Figure 14] FIG. 11 is an explanatory diagram showing a state after a first idling step in the first embodiment. [Figure 15] FIG. 11 is an explanatory diagram showing a first amplitude state in the first embodiment. [Figure 16] FIG. 11 is an explanatory diagram showing a state before a second idling step in the first embodiment. [Figure 17] FIG. 11 is an explanatory diagram showing a state after a second idling step in the first embodiment. [Figure 18] FIG. 11 is an explanatory diagram showing a state after a second stop release step in the first embodiment; [Figure 19] FIG. 11 is an explanatory diagram showing a state of a second energizing step in the first embodiment; [Figure 20] FIG. 11 is an explanatory diagram showing a state before a third idling step in the first embodiment. [Figure 21] FIG. 11 is an explanatory diagram showing a state after a third idling step in the first embodiment. [Figure 22] FIG. 11 is an explanatory diagram showing a state of a second amplitude in the first embodiment; [Figure 23] FIG. 11 is an explanatory diagram showing a state before a fourth idling step in the first embodiment. [Figure 24] FIG. 11 is an explanatory diagram showing a state after a fourth idling step in the first embodiment. [Diagram 25] FIG. 1 is an explanatory diagram showing a state before one cycle ends in the first embodiment; [Figure 26] Graph showing angles of the balance and driven wheel according to the first embodiment [Figure 27] Graph showing escapement error when the pawl is engaged in the first embodiment [Figure 28] Graph showing escapement error when the prongs are in motion in the first embodiment [Figure 29] FIG. 11 is a front view showing a reference state of the expansion escapement according to the second embodiment; [Diagram 30] FIG. 11 is a perspective view showing a movement according to a third embodiment; [Diagram 31] FIG. 11 is a perspective view showing a speed control escapement according to a third embodiment. [Diagram 32] Exploded view of the speed regulator escapement according to the third embodiment [Diagram 33] FIG. 35 is an explanatory diagram showing a section line AA of a cross-sectional view corresponding to FIG. 34. [Diagram 34] 34 is a cross-sectional view of the speed governor escapement according to the third embodiment taken along the line AA shown in FIG. [Diagram 35] FIG. 11 is a perspective view showing a movement according to a third embodiment; [Diagram 36] 35, but from the opposite side. [Figure 37] 49 is a perspective view of the components shown in the operation explanatory diagrams according to the third embodiment shown in FIGS. 38 to 48 ; [Figure 38] FIG. 13 is an explanatory diagram showing a state before a first stop release step in the third embodiment; [Figure 39]FIG. 13 is an explanatory diagram showing a state in which the first stop release step is completed in the third embodiment; [Diagram 40] FIG. 13 is an explanatory diagram showing a state in which the first rotation step is completed in the third embodiment. [Diagram 41] FIG. 13 is an explanatory diagram showing a state after a first idling step in the third embodiment. [Diagram 42] FIG. 13 is an explanatory diagram showing a state of a first amplitude in the third embodiment; [Diagram 43] FIG. 13 is an explanatory diagram showing a state after a second idling step in the third embodiment. [Diagram 44] FIG. 13 is an explanatory diagram showing a state in which the second stop release step is completed in the third embodiment; [Diagram 45] FIG. 13 is an explanatory view showing a state in which the second rotation step is completed in the third embodiment. [Diagram 46] FIG. 13 is an explanatory diagram showing a state after a third idling step in the third embodiment. [Figure 47] FIG. 13 is an explanatory diagram showing a state of a second amplitude in the third embodiment. [Figure 48] FIG. 13 is an explanatory diagram showing a state after a fourth idling step in the third embodiment. [Figure 49] A graph showing the angle between the balance and the carrier assembly when energy is lost in the first rotation process in the third embodiment. [Figure 50] Graph showing the angle between the balance and the carrier assembly when energy is lost in the second rotation process in the third embodiment. [Figure 51] Graph showing the angle between the balance and the carrier assembly when the energy loss in the first rotation process is suppressed in the third embodiment. [Figure 52] Graph showing the angle between the balance and the carrier assembly when the energy loss in the second rotation process is suppressed in the third embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0047] (First embodiment) A first embodiment of the present invention will be described below in chronological order with reference to the drawings. Note that in this embodiment, a mechanical timepiece will be described as an example of a timepiece.

[0048] Generally, the mechanical body that includes the driving parts of a watch is called the "movement". When the dial and hands are attached to this movement and it is placed inside a watch case, it is called a finished watch. Of the two sides of the base plate that makes up the base of a watch, the side with the dial is called the "back side" of the movement. In addition, of the two sides of the base plate, the side that faces when the back cover is opened is called the "front side" of the movement.

[0049] As shown in FIG. 1, the completed timepiece 1 of this embodiment includes, within a case 10, a movement 11, a dial 14 that indicates the time, a minute hand 15b, and an hour hand 15c.

[0050] As shown in Fig. 2, the movement 11 has a main plate 13 that constitutes a base plate. Fig. 2 is a front view of the movement 10 as seen from the front side. On the front side of the main plate 13, a speed-increasing train wheel 16 is provided, which is made up of a barrel 16a that houses a power spring, a second wheel 16b, a third wheel 16c, a fourth wheel 16d, and an escape wheel 7. Furthermore, the speed-regulating escapement 2 according to the present invention is journaled by the main plate 13 and a train bridge (not shown) while engaging with the speed-increasing train wheel 16. Note that parts other than the speed-regulating escapement, such as the back train wheel, winding and time setting devices, are not shown in the illustration.

[0051] As shown in FIG. 3, the speed-controlling escapement 2 includes an escapement 5 that regulates the rotation of the speed-increasing train wheel 16, a speed governor 3 that regulates the rotation speed of the speed-increasing train wheel 16, and an intermittent transmission 4 that is interposed between the escapement 5 and the speed governor 3 and engages with the escapement 5 and the speed governor 3. In the escapement according to the present invention, the intermittent transmission 4 and the escapement 5 work together to perform escapement operation, so the portion including the intermittent transmission 4 and the escapement 5 is referred to as an extended escapement 45. In this embodiment, a club-tooth lever escapement is used for the escapement 5. FIG. 3 is a rear view of the speed-controlling escapement 2 as viewed from the back side.

[0052] (hairspring) 4 is a partial front view of the regulating escapement 2 of this embodiment, with the balance stud 17 omitted. The inner end of the hair spring 36 is fixed at the inner end point 36a of the collet 34 by a first wedge 35, and the outer end is fixed at the outer end point 36b of the balance stud 37 by a second wedge 38. This embodiment shows an example in which a winding hair spring is used, and the spiral portion from the inner end point 36a to the bending start point 36c is formed in an arc shape displaced in the axial direction of the balance stem 32 from the bending start point 36c to the outer end point 36b. In the present invention, the direction in which the balance 31 is located on the axis of the balance stem 32 as viewed from the main plate 13 is defined as the up direction.

[0053] 4, the angle between the inner end point 36a and the outer end point 36b of the hair spring 36 in the direction from the inner end to the outer end of the hair spring 36 with respect to the center of the balance shaft 32 is called the "winding angle" and indicated by the symbol α. Similarly, the angle between the bending start point 36c of the hair spring 36 and the outer end point 36b is called the "wind-up angle" and indicated by the symbol β.

[0054] In this embodiment, in order to minimize the radial elastic force generated in the tenon of the balance shaft 32, the external winding angle β is set to approximately 245° in accordance with the Phillips condition, and the inside is formed into a curve in accordance with the Grossmann condition so that the hair spring 36 expands and contracts without eccentricity around the balance shaft 32. The other spiral portions are formed into a spiral shape along an Archimedes curve.

[0055] In this embodiment, the winding angle α of the hair spring 36 is set to approximately 90°. In general, when the winding angle α is 0° or 180°, the effect of the amplitude on the even chronology is maximum, and the closer the winding angle α is to 90°, the more the effect of the amplitude can be suppressed. Also, the larger the amplitude, the greater the effect on the even chronology. Thus, when the amplitude is significantly greater than approximately 340° as in the present invention, the effect of the amplitude on the even chronology can be effectively minimized by setting the winding angle α to 90°. In this embodiment, an example in which a wound hair spring is used has been shown, but a flat hair spring may also be used, and the winding angle α in that case is handled in the same manner as described above.

[0056] 5 is a diagram showing the escapement 5 and intermittent transmission 4 of the speed regulating escapement 2, with the balance 31 and collet 34 omitted. The escapement 5 is made up of an escape wheel 7, an anchor 54 which serves as a regulating lever, a pair of throttle pins 58, and an impulse jewel 52. The intermittent transmission 4 is made up of a driving wheel 41 and a driven wheel 42. Note that in this embodiment, an example is shown in which a Geneva mechanism is used for the intermittent transmission 4.

[0057] The escape wheel 7 and the escape pinion 72 are integrally connected to the escape wheel arbor 71. The torque transmitted from the speed-increasing train wheel 16 is transmitted to the escape tooth 73 by the escape pinion 72. Tapered tenons are formed on both axial ends of the balance arbor 32, the driven wheel arbor 43, the pallet arbor 54a, and the escape wheel arbor 71. The balance arbor 32, the driven wheel arbor 43, the pallet arbor 54a, and the escape wheel arbor 71 are journaled between the main plate 13 and a train wheel bridge (bearing) (not shown) via the tenons. The pallet 54 includes an inserting pawl 55 and an extending pawl 56 integrally connected to it, and regulates the rotation of the escape wheel 7 by alternately engaging with and disengaging from the escape tooth 73 as the pallet 54 swings.

[0058] (Intermittent transmission device) In this embodiment, in order to achieve a thinner structure, a finger-piece type Geneva mechanism used in a winding stop device for a timepiece's power spring is adopted instead of a system in which a driving wheel 41 of the intermittent transmission device 41 is composed of a commonly used pin wheel and lock wheel. The driving wheel 41 is coaxially connected to the balance arbor 32 and rotates around the balance arbor 32. The driven wheel 42 is coaxially connected to the driven wheel arbor 43 and rotates around the driven wheel arbor 43.

[0059] The driving wheel 41 has a convex finger 41a, a stop surface 41b, and two recesses 41c. In this embodiment, the amplitude of the balance is 660°. The driven wheel 42 (geneva wheel) of the intermittent transmission device 4 has five teeth so as to be compatible with the amplitude of 660°. The driven wheel 42 has five grooves 42a, the same number as the number of teeth, ten impact surfaces 42b, which is twice the number of teeth, and five stop surfaces 42c, the same number as the number of teeth. However, the number of teeth of the driven wheel 42 is not limited to five, and the number of teeth is appropriately changed depending on the amplitude.

[0060] The driven wheel 42 rotates when the finger 41a of the driving wheel 41 engages with the impact surface 42b of the driven wheel 42, and stops without rotating when the stop surface 41b of the driving wheel 41 engages with the stop surface 42c of the driven wheel 42. The impulse jewel 52 is connected to the driven wheel 42 so as to protrude from the driven wheel 42 so as to engage with the pallet 54e. In the example of FIG. 5, the impulse jewel 52 is provided at the center of the teeth of the driven wheel 42. As a result, the impulse jewel 52 rotates back and forth together with the driven wheel 42, and during the process, it releasably engages with the impact surfaces 541f and 542f of the pallet box 54f that form the recess of the pallet 54e at the tip of the pallet 54. The gap (box tip clearance) between the finger 41a of the driving wheel 41 and the groove 42a of the driven wheel 42 is set to a very small gap amount, for example, about 10 microns.

[0061] In this embodiment, when the regulating escapement 2 is housed in the movement 11, the balance arbor 32, the driven wheel arbor 43, the pallet arbor 54a, and the escape wheel arbor 71 are arranged on a single straight line on the movement 11. This allows the balance arbor 32 and the escape wheel arbor 71 to be as far apart as possible, and allows a design in which they are less likely to interfere with each other even when the balance 31 has a large diameter. In addition, since the number of teeth of the driven wheel 42 is set to an odd number and the impulse jewel 52 is provided on the tooth 42d of the driven wheel 42, in the above-mentioned straight line arrangement, the engagement between the impulse jewel 52 and the pallet arbor 54e and the engagement between the finger 41a of the driving wheel 41 and the groove 42a can be simultaneously generated.

[0062] (Pendulum stone and ankle box) As shown in Figs. 6 and 8, the small flange 51b is coaxially connected to the driven wheel axle 43. The small flange 51b has a curved recess 51c formed on the inside in the radial direction at a position corresponding to the impulse jewel 52. The recess 51c functions as a relief portion to prevent the tip 54h from contacting the small flange 51b when the impact surfaces 541f and 542f of the pallet box 54f and the impulse jewel 52 are engaged. In addition, the portion of the outer circumferential surface of the small flange 51b other than the recess 51c is made to be in sliding contact with the tip 54h provided below the pallet 54e, and has a safety function to prevent malfunction of the escapement 5 caused by external disturbance. Fig. 6 is a side view of the right side of the expansion escapement 45, and Fig. 8 is a front view of the intermittent transmission device 4.

[0063] (Material of sliding parts) At least one of the impulse jewel 52, the pallet 55, the pallet 56, the driving wheel 41, the driven wheel 42, and the bearings (radial bearings and thrust bearings) not shown, including the sliding parts during escapement, is made of an artificial gemstone such as a ruby ​​or a lubricant. Agent They are made of sintered metal, which is a porous body that can be impregnated with water, or metal coated with DLC (Diamond-Like Carbon) or other materials, which give them low friction and wear resistance. This ensures smooth escapement action with little wear over the long term.

[0064] (Axis and direction of rotation) 7 is a front view showing the free state of the governor 3, i.e., the free state of the hairspring 36, and showing the state in which the driving wheel 41, driven wheel 42, and pallet fork 54, among the components that make up the expansion escapement 45, are in their reference state (the rotation angle of each element is 0°). In the reference state, the finger 41a of the driving wheel 41 faces the groove 423a of the driven wheel 42, and the impulse jewel 52 faces the pallet box 54f.

[0065] In describing the escapement operation of the first embodiment, the rotation axis and the rotation direction are defined as follows with reference to FIG. 7. The driving wheel 41, which rotates integrally with the balance 31, reciprocates around the axis O1 in a first rotation direction M1 and a second rotation direction M2 that are opposite to each other. The driven wheel 42 rotates around the axis O2 in a third rotation direction M3 and a fourth rotation direction M4 that are opposite to each other. The anchor 54 oscillates around the axis O3 in a fifth rotation direction M5 and a sixth rotation direction M6 that are opposite to each other. The escape wheel 7 rotates around the axis O4 in a seventh rotation direction M7, but is very slightly reversed to an eighth rotation direction M8 in the escapement stop release process. Also, a straight line drawn by projecting a plane including the axis O1 to the axis O4 onto a front view is defined as a straight line CL.

[0066] Also, reference numerals corresponding to the various parts of the intermittent transmission 4 are shown in Fig. 8, and reference numerals corresponding to the various parts of the escapement 5 are shown in Fig. 9. Figs. 8 and 9 are detailed explanatory diagrams of the reference state shown in Fig. 7. In the reference state, the finger 41a of the driving wheel 41 engages with the groove 423a of the driven wheel 42 while being positioned on a straight line CL. Also, the impulse jewel 52 engages with the pallet box 54f while being positioned on a straight line CL. Also, these engagements are in opposite positions across the driven wheel arbor 43.

[0067] (Explanation of escapement mechanism) The escapement operation for one cycle in the first embodiment will be described below in chronological order with reference to Figures 10 to 25. Figures 10 to 25 are front views showing the expansion escapement 45.

[0068] Fig. 10 is an operation explanatory diagram before the first stop release step in the first embodiment, and shows the state before the stop state of the escape wheel 7 is released by the extending pawl 56. Fig. 10 shows a state in which the rotation angle of the balance 31 is at -90° with respect to the free state of the governor 3.

[0069] In the expansion escapement 45, the impulse jewel 52 is in a position rotated 36° in the M4 direction with respect to the center line CL by the previous escapement operation. Also, the pallet fork 54 has swung in the M6 ​​direction with respect to the center line CL, and the pallet rod 54d is held down by the stop pin 58a. Also, since the stop surface 41b of the driving wheel 41, which rotates together with the balance 31 in the M1 direction, is engaged with the stop surface 423c of the driven wheel 42, the driven wheel 42 has stopped rotating.

[0070] The escape wheel 7 receives torque in the M7 direction, but the stop surface 56a of the protruding claw 56 on the pallet fork 54 engages the stop surface 732a of the escape tooth 732, so the escape wheel 7 is restricted to a stopped state. In addition, the stop surfaces that press against each other are not perpendicular to the direction of rotation but slightly angled, so the pallet fork 54 is subjected to a "pulling" action of receiving torque in the M6 ​​direction due to the torque of the escape wheel 7, and is pressed down by the dowel pin 58a. Due to this pulling action, even if a disturbance is input to the pallet fork 54, the pallet rod 54d can be maintained in a pressed state without being separated from the dowel pin 58a.

[0071] FIG. 11 is an explanatory diagram showing the first stop release step. FIG. 11 shows a state in which the balance 31 has rotated in the M1 direction from the state shown in FIG. 10. The finger 41a of the driving wheel 41 is accommodated in the groove 423a of the driven wheel 42 and engages with the impact surface 424b. In addition, the stop surface 422c and the stop surface 423c are accommodated in the recess 41c of the driving wheel 41, respectively, so that the engagement between the stop surface 41b of the driving wheel 41 and the stop surface 423c of the driven wheel 42, which was engaged in FIG. 10, is released. As a result, the driven wheel 42 rotates in the M3 direction.

[0072] As the driven wheel 42 rotates, the impulse jewel 52 engages with and presses the impact surface 541f of the pallet fork 54. This causes the pallet fork 54 to swing in the M5 direction. The escapement 5 was in a stopped state with the protruding pawl 56 engaged with the escape tooth 732 until the first stop release step, but due to the swing of the pallet fork 54, the amount of engagement between the stop surface 56a of the protruding pawl 56 and the stop surface 732a of the escape tooth 732 decreases, and when the locking corner 56b of the protruding pawl 56 passes the tip 732b of the escape tooth 732, the stop of the escape wheel is released.

[0073] In the first stop release process, when the engagement between the protruding pawl 56, which is set to apply a pull, and the escape tooth 732 is released, the escape wheel 7 is wound back very slightly in the M8 direction. This causes the governor 3 to lose a very small amount of its stored energy.

[0074] Fig. 12 is an explanatory diagram showing the first biasing step. Fig. 12 shows a state in which the balance 31 has rotated in the M1 direction from the state shown in Fig. 11. After the first stop release step, the impact surface 732c of the escape tooth 732 of the escapement 5 slides against and presses against the impact surface 56c of the projection 56. As a result, the escape wheel 7 starts to rotate in the M7 direction.

[0075] The impact surface 56c of the protruding claw 56 is pressed by the impact surface 732c of the escape tooth 732, so that the pallet fork 54 is biased in the M5 direction and the swing is accelerated. As a result, the impulse jewel 52, which had been pressing the impact surface 541f of the pallet box 54f, disengages from the impact surface 541f and engages with the opposing impact surface 542f, transitioning to a state in which it is biased by the pallet fork 54. As a result, the driven wheel 42 is biased in the M3 direction.

[0076] As the driven wheel 42 accelerates, the finger 41a, which had been pressing the impact surface 424b of the driven wheel 42, disengages from the impact surface 424b and engages with the opposing impact surface 423b, transitioning to a state in which it is pushed by the driven wheel 42. As a result, the driving wheel 41 is biased in the M1 direction. As a result, the torque from the power spring is transmitted to the governor 3 via the speed-increasing wheel train 16, the escapement 5, and the intermittent transmission 4, and the governor 3 can obtain energy that is significantly greater than the amount lost in the first stop release process.

[0077] FIG. 13 is an explanatory diagram showing the state before the first idling stroke. FIG. 13 shows the state in which the balance 31 has rotated in the M1 direction from the state shown in FIG. 12. After the first urging stroke, the impulse jewel 52 is released from the pallet box 54f as the driven wheel 42 rotates. When the driven wheel 42 rotates further, the stop surface 422c of the driven wheel 42 and the stop surface 41b of the driving wheel 41 engage with each other, so that the driven wheel 42 maintains a state in which its rotation is stopped even if the balance 31 continues to rotate. Note that the engagement between the stop surface 422c of the driven wheel 42 and the stop surface 41b of the driving wheel 41 is not in a mutually pressing relationship due to an external force, and is separated in a fluid lubricated state via the lubricating oil present on the engagement surface, so that the energy held by the speed governor 3 is not significantly lost.

[0078] After the pallet fork 54 swings in the M5 direction, the pallet rod 54d is pressed against the stop pin 58b. Since the stop surface 735a of the escape tooth 735 presses against the stop surface 55a of the recessed jaw 55, the pallet rod 54d maintains its pressed state against the stop pin 58b by the pulling action.

[0079] Fig. 14 is an explanatory diagram showing the state after the first idling stroke. Fig. 14 shows the state in which the balance 31 has rotated in the M1 direction from the state shown in Fig. 13 and has rotated 360° or more in the M1 direction with respect to the free state of the governor 3.

[0080] After the finger 41a of the driving wheel 41 engages with the impact surface 422b of the driven wheel 42, the driven wheel 42 is rotated by one tooth in the M3 direction. At the same time, the impulse jewel 52 also rotates by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, it has no effect on the escapement 5, and is also not affected by either the driven wheel 42 or the escapement 5. In the present invention, the rotation of the driven wheel 42 that has no effect on the escapement is referred to as "idling."

[0081] During idling, sliding friction occurs at the engagement portion, and the governor 3 loses an extremely small amount of its stored energy. Here, the friction caused by idling is called "idling friction" and the energy loss caused by idling friction is calledThis is called "idling loss". This idling loss is small enough compared to the energy obtained by each energizing step that it does not have a significant effect on reducing the amplitude. The effect of this idling loss on isochronism will be described later.

[0082] After the first idling stroke, the balance 31 continues to rotate without hitting anything, but since the stop surface 41b of the driving wheel 41 and the stop surface 421c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0083] FIG. 15 is an explanatory diagram showing the state where the first amplitude is reached. FIG. 15 shows the state where the balance 31 rotates in the M1 direction from the state shown in FIG. 14, and rotates 660° in the M1 direction with respect to the free state of the governor 3. After the balance 31 reaches the maximum swing angle at the first amplitude, it reverses from the M1 direction to the M2 direction. Note that in this embodiment, the states of FIG. 15 and FIG. 22 described later are shown as the first amplitude and the second amplitude, respectively, but the amplitude is not limited to 660° and may be expanded to a range permitted by the elasticity of the hairspring 36 and to a range where the impulse jewel 52 does not come into contact with the spur 541g or 542g of the pallet fork 54c. In addition, when the amplitude is further expanded, the number of teeth of the driven wheel 42 can be appropriately changed to accommodate an even greater number of idling revolutions.

[0084] Fig. 16 is an explanatory diagram showing the state before the second idling stroke. Fig. 15 shows the state in which the balance 31 reverses its rotation direction to the M2 direction after the maximum swing angle in the M1 direction shown in Fig. 15. In addition, since the stop surface 41b of the driving wheel 41 and the stop surface 421c of the driven wheel 42 are engaged, the rotation of the driven wheel 42 remains stopped. When the balance 31 rotates further, the finger 41a of the driving wheel 41 engages with the impact surface 421b while being accommodated in the groove 422a of the driven wheel 42.

[0085] Fig. 17 is an explanatory diagram showing the state after the second idling step, in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 16.

[0086] After the finger 41a of the driving wheel 41 engages with the impact surface 421b of the driven wheel 42, it rotates the driven wheel 42 by one tooth in the M4 direction. At the same time, the impulse jewel 52 also rotates by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small amount of idling loss.

[0087] After the second idling stroke, the balance 31 continues to rotate in the M2 direction, but since the stop surface 41b of the driving wheel 41 and the stop surface 422c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0088] Fig. 18 is an explanatory diagram showing the state before the second stop release step. Fig. 18 shows the state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 17. The finger 41a of the driving wheel 41 is housed in the groove 423a of the driven wheel 42 and engages with the impact surface 423b.

[0089] As the driven wheel 42 rotates, the impulse jewel 52 engages with and presses the impact surface 542f of the pallet fork 54. This causes the pallet fork 54 to swing in the M6 ​​direction. The escapement 5 was in a stopped state with the plunger 55 engaged with the escape tooth 735 until the second stop release step, but due to the swing of the pallet fork 54, the amount of engagement between the stop surface 55a of the plunger 55 and the stop surface 735a of the escape tooth 735 decreases, and when the rocking corner 55b of the plunger 55 passes the tip 735b of the escape tooth 735, the stop of the escape wheel is released.

[0090] In the second release process, as in the first release process, when the engagement between the pawl 55, which is set to apply a pull, and the escape tooth 735 is released, the escape wheel 7 is wound back very slightly in the M8 direction. This causes the governor 3 to lose very little energy.

[0091] Fig. 19 is an explanatory diagram showing the second biasing step. Fig. 19 shows a state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 18. After the second stop release step, the escapement 5 presses the impact surface 735c of the escape tooth 735 while sliding against the impact surface 55c of the set pawl 55. As a result, the escape wheel 7 starts to rotate in the M7 direction.

[0092] The impact surface 55c of the recessed claw 55 is pressed by the impact surface 735c of the escape tooth 735, so that the pallet fork 54 is biased in the M6 ​​direction and the swing is accelerated. As a result, the impulse jewel 52, which had been pressing the impact surface 542f of the pallet box 54f, disengages from the impact surface 542f and engages with the opposing impact surface 541f, transitioning to a state in which it is biased by the pallet fork 54. As a result, the driven wheel 42 is biased in the M4 direction.

[0093] As the driven wheel 42 accelerates, the finger 41a, which had been pressing against the impact surface 424b of the driven wheel 42, disengages from the impact surface 424b and engages with the opposing impact surface 423b, transitioning to a state in which it is pushed by the driven wheel 42. As a result, the driving wheel 41 is biased in the M1 direction. As a result, the torque from the power spring is transmitted to the governor 3 via the speed-increasing wheel train 16, the escapement 5, and the intermittent transmission 4, and the governor 3 can obtain energy greater than the amount lost in the second stop release process.

[0094] Fig. 20 is an explanatory diagram showing the state before the third idling step. Fig. 20 shows the state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 19. After the second urging step, the balance 31 continues to rotate, but since the stop surface 41b of the driving wheel 41 and the stop surface 423c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again maintains the stopped state.

[0095] After the pallet fork 54 swings in the M5 direction, the pallet rod 54d is pressed against the stop pin 58a. Since the stop surface 733a of the escape tooth 733 presses against the stop surface 56a of the protruding claw 56, the pallet rod 54d maintains its pressed state against the stop pin 58a by the pulling action.

[0096] The impulse jewel 52, which rotates integrally with the driven wheel 42, is released from the pallet box 54f as the driven wheel 42 rotates. When the driven wheel 42 rotates further, the stop surface 423c of the driven wheel 42 engages with the stop surface 41b of the driving wheel 41, maintaining the stopped state. When the balance 31 rotates further, the finger 41a of the driving wheel 41 engages with the impact surface 425b while being housed in the groove 424a of the driven wheel 42.

[0097] Fig. 21 is an explanatory diagram showing the state after the third idling stroke. Fig. 21 shows the state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 20, and has rotated 360° or more in the M2 direction with respect to the free state of the governor 3.

[0098] After the finger 41a of the driving wheel 41 engages with the impact surface 425b of the driven wheel 42, the driven wheel 42 is rotated by one tooth in the M4 direction. At the same time, the impulse jewel 52 also rotates by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small idling loss.

[0099] After the third idling stroke, the balance 31 continues to rotate without hitting anything, but since the stop surface 41b of the driving wheel 41 and the stop surface 424c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0100] Fig. 22 is an explanatory diagram showing the state when the second amplitude is reached. Fig. 22 shows the state when the balance 31 rotates in the M2 direction from the state shown in Fig. 21, and rotates 660° in the M2 direction with respect to the free state of the governor 3. After the maximum swing angle is reached, the rotation direction of the balance 31 reverses from the M2 direction to the M1 direction.

[0101] Fig. 23 is an explanatory diagram showing the state before the fourth idling stroke. Fig. 23 shows the state in which the balance 31 reverses its rotation direction to the M1 direction after the maximum swing angle in the M2 direction shown in Fig. 22. In addition, since the stop surface 41b of the driving wheel 41 and the stop surface 424c of the driven wheel 42 are engaged, the rotation of the driven wheel 42 remains stopped. When the balance 31 rotates further, the finger 41a of the driving wheel 41 engages with the impact surface 426b while being accommodated in the groove 424a of the driven wheel 42.

[0102] Fig. 24 is an explanatory diagram showing the state after the fourth idling step, in which the balance 31 has rotated in the M1 direction from the state shown in Fig. 23.

[0103] After the finger 41a of the driving wheel 41 engages with the impact surface 426b of the driven wheel 42, it rotates the driven wheel 42 by one tooth in the M3 direction. At the same time, the impulse jewel 52 also rotates by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small idling loss.

[0104] After the fourth idling stroke, the balance 31 continues to rotate in the M1 direction, but since the stop surface 41b of the driving wheel 41 and the stop surface 423c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0105] Fig. 25 is an explanatory diagram showing the state before one cycle is completed, in which the balance 31 has rotated in the M1 direction from the state shown in Fig. 24.

[0106] As the balance 31 rotates, the finger 41a of the driving wheel 41 is again accommodated in the groove 423a of the driven wheel 42 and engages with the impact surface 424b, transitioning to the first stop release step in the next cycle. The speed controlling escapement 2 shown in this embodiment performs the escapement operation in this manner.

[0107] (Effect of Amplitude) Generally, the quality factor (Q value) is used as an index to indicate the quality of a regulator escapement. The quality factor indicates the degree of influence of disturbances on timekeeping accuracy, and the higher the value, the better the regulator is, being less susceptible to disturbances. The quality factor of conventional escapements, such as the club-tooth lever escapement, is said to be around 100 to 300.

[0108] The quality factor Q is given by the following formula 1.

[0109]

number

[0110] Here, E is the energy held by the governor, and can be expressed by the torsional spring constant k of the hairspring and the amplitude A of the governor. Also, ΔE represents the energy lost by the governor. The quality factor is dimensionless.

[0111] Additionally, timing error (daily rate) is known as an index of the quality of timekeeping accuracy. Timing error is a value obtained by measuring the accuracy of a watch over a short period of time and converting it into a gain or loss per day, with the sign δ and the unit being seconds per day. A gain in timing error is indicated by a plus (+) and a loss in timing error by a minus (-). Apart from the effects of temperature changes and changes in position, timing accuracy is mainly affected by external vibrations and the operation of the escapement.

[0112] The general formula for the timing error δ is given by the following Equation 2 based on Airy's theorem. (See Non-Patent Document 1.)

[0113]

number

[0114] Here, k is the torsional spring constant of the hairspring, T is the governor period, f(θ) is the external torque generated in the governor, and θ is the oscillation angle at which the external torque f(θ) generated in the governor occurs. Note that the unit of δ is seconds / period.

[0115] The above-mentioned formula 1 expressing the quality factor and formula 2 expressing the timing error include the energy reserve of the governor. Coefficient (kA2 / 2) These include: In order to improve the quality factor and reduce the timing error δ, it is most effective to increase the amplitude A, which is a factor that affects them exponentially. In conventional escapements, the amplitude could not be increased to more than approximately 340° due to the problem of swinging, but with the speed-controlling escapement 2 of the present invention, swinging does not occur, so it is possible to obtain an amplitude that far exceeds approximately 340°. For example, based on Equation 1 and Equation 2, when the amplitude A is doubled, the quality factor is improved fourfold and the timing error δ is reduced to one-quarter.

[0116] (Effect of idling) FIG. 26 shows the change in angle between the balance 31 and the driven wheel 42 in this embodiment. A graph showing the phase of tempura 31 on the horizontal axis. The solid line 91 is the balance 31. Rotation angle The dashed line 92 indicates the driven wheel 42. Rotation angle The horizontal axis represents 0 radians to 2π radians. to corresponds to one period of vibration.

[0117] Point 91a indicates the time of the first stop release process and the first energizing process, point 91b indicates the time of the first idling process, point 91c indicates the time of the first amplitude, point 91d indicates the time of the second idling process, point 91e indicates the time of the second stop release process and the second energizing process, point 91f indicates the time of the third idling process, point 91g indicates the time of the second amplitude, point 91h indicates the time of the fourth idling process, and point 91g indicates the end of the cycle.

[0118] The points 91b and 91d, and the points 91f and 91h, where slip occurs, are located in phases symmetrical to 0 radians and π radians, which are phases corresponding to the free state of the governor 3. Idle The friction torques are equal in magnitude and act in opposite directions. In other words, the friction torque during idling is always generated symmetrically and in equal amounts with respect to the free state of the governor 3. This relationship also applies when the amplitude is made larger and the number of idling events increases. The effect of these torques during idling on the rate is explained next.

[0119] Figures 27 and 28 are Tenshin 32 The disturbance torque (solid line 94) generated in Timing error (Dash line 95) A graph showing Figure 27 So what is the rotation angle of Tenshin 32 in the M2 direction? Figure 28 So what is the rotation angle of Tenshin 32 in the M1 direction? of Horizontal axis to the right show. In both figures, Solid line 94 occurs at center 32 Disturbance Torque, dashed line 95 is Disturbance Torque-induced timing errors degree Represents. Also , the sign of the torque is Tenshin 32 Energizing Will be This case is considered positive.

[0120] Where: According to Airy's theorem, in both figures, when disturbance torque occurs in the first and third quadrants, the timing error according to the present invention is delayed, and when disturbance torque occurs in the second and fourth quadrants, the timing error is advanced. Also, according to formula 2, the effect on the timing error increases in proportion to the swing angle. .

[0121] 27 and 28, line 94a indicates the torque generated when the escapement is released, lines 94b and 94c indicate the torque generated when the heel of the escape tooth presses against the impact face of the pallet stone, line 94d indicates the torque generated when the impact face of the escape tooth presses against the let-off corner of the pallet stone, and lines 94e and 94f indicate the torque generated when the intermittent transmission 4 is running idly. The timing error shown by dashed line 95 is caused by the operation of the escapement, and is therefore called the "escapement error" to distinguish it from other timing errors.

[0122] Here, the intermittent transmission device 4 Idling friction torque Although the amount of 94e and 94f is very small, they occur at a large swing angle relative to the free state of the governor 3, so when viewed individually, they have a large effect on isochronism. However, as mentioned above, Idling friction torque Since the delay in the third quadrant and the advance in the fourth quadrant always occur symmetrically and equally with respect to the free state of the governor 3, be offset That is, the intermittent transmission device 4 Each idling friction torque occurs symmetrically with respect to the free state of the governor 3, it has no effect on the timing error.

[0123] In order to cancel out the timing error, it is necessary to set the idling to occur in a symmetrical phase with respect to the free state of the governor 3. In the governor escapement 2 according to this embodiment, the outer end of the hairspring 36 is connected to a hairspring holder 62 whose angle is adjustable around the balance shaft 32. The phase of governor 3 relative to This allows for proper adjustment, which can accurately cancel out the timing error that occurs each time the wheel spins.

[0124] Furthermore, the torques 94a, 94b, 94c, and 94d generated by the escapement 5 are the same as those of a conventional club-tooth lever escapement, but since the amplitude of the balance 31 of the speed controlling escapement 2 according to this embodiment is much greater than approximately 340°, the escapement error decreases inversely proportional to the square of the rate of increase in the amplitude based on formula 2. This makes it possible to improve timekeeping accuracy significantly compared to conventional club-tooth lever escapements.

[0125] (effect) Therefore, with the speed controlling escapement according to the first embodiment of the present invention, even when the amplitude of the balance exceeds approximately 340°, no oscillation occurs, and a significantly larger amplitude than that of conventional escapements can be realized. This allows the quality factor (Q value) to be significantly increased, and timekeeping accuracy to be significantly improved. Furthermore, since oscillation can be achieved in an oscillation angle range where the effect of amplitude changes on timekeeping errors is low, the flatness difference can be improved. Furthermore, since an intermittent transmission is used in the mechanism for eliminating oscillation, the large amplitude can be realized with little energy loss.

[0126] In addition, the improved accuracy of the timekeeping mechanism allows the frequency to be reduced, which in turn allows the speed at which the mainspring relaxes to be slowed down, thereby lengthening the operating time.

[0127] In this embodiment, a case has been presented in which a Geneva mechanism is used for the intermittent transmission device 4, but a commonly known intermittent transmission device, for example, an intermittent gear or a cam device, may also be used.

[0128] In this embodiment, the balance arbor 32, the driven wheel arbor 43, the pallet arbor 54a, and the escape wheel arbor 71 are arranged in a straight line when viewed from above the movement. time As long as the fingers 41a engage with the impact surface 42b, they do not need to be arranged in a straight line, and the arrangement may be changed as appropriate depending on the design of the movement.

[0129] Second embodiment Next, a second embodiment of the present invention will be described with reference to Fig. 29. In this second embodiment, the escapement 5 is the club-tooth lever escapement in the first embodiment. of In this embodiment, the escapement is replaced with a detent escapement (latch escapement or chronometer escapement) with less friction loss. The configuration is the same as that of the first embodiment except for the extension escapement 45. The configurations, actions, and effects that are not described in the following embodiments are omitted because they are the same as those in the first embodiment.

[0130] Figure 29 is a front view showing the free state of governor 3, i.e., the free state of hairspring 36, in which, among the components that make up expansion escapement 45, driving wheel 41, driven wheel 42, and detent arm (latch) 59 serving as a regulating lever are at their reference positions (the rotation angle of each element is 0°).

[0131] In this embodiment, the impulse wheel 51, which is a component of the escapement 5, is coaxially coupled to the driven wheel 42 of the intermittent transmission device 4. In the reference state, the finger 41a of the driving wheel 41 engages with the groove 423a of the driven wheel 42, and the impulse jewel 52 engages with the detent arm 59. The groove 423a in the driven wheel 42 corresponds to the groove located directly opposite the impulse jewel 52 with respect to the driven wheel arbor 43.

[0132] In this embodiment, since a detent escapement is used, only when the driven wheel 42 rotates in the M4 direction, the impulse jewel 52 swings the detent arm 59 in the M6 ​​direction, and the escape wheel 7 rotates by one tooth in the M7 direction. Also, when the driven wheel 42 rotates in the M3 direction, the impulse jewel 52 is pushed toward the detent arm 59, so the detent arm 59 but No swing, escape wheel 7 too Except for the fact that escapement operation is performed only in the M4 direction of the driven wheel 42, the operating principle of the expansion escapement 45 is the same as that of the first embodiment, and therefore a description thereof will be omitted.

[0133] (effect) Therefore, the speed-control escapement according to the second embodiment of the present invention can achieve a significantly larger amplitude than in a conventional detent escapement without causing the balance to strike. This allows a high quality factor to be obtained, and timekeeping accuracy to be significantly improved. Furthermore, since the escapement can oscillate in an oscillation angle range where the effect of amplitude changes on timekeeping errors is low, the flatness difference can be improved. Furthermore, since an intermittent transmission is used in the mechanism for eliminating strikes, the large amplitude can be achieved with little energy loss.

[0134] In addition, the improved accuracy of the timekeeping mechanism allows the frequency to be reduced, which in turn allows the speed at which the mainspring relaxes to be slowed down, thereby lengthening the operating time.

[0135] Third embodiment Next, a third embodiment of the present invention will be described with reference to the drawings. In the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and their description will be omitted. In the first embodiment, the rotation shaft of the parts constituting the speed regulating escapement 2 is journaled on the main plate 13, but in the third embodiment, the speed regulating escapement 2 is mounted on one carrier assembly 6, and the carrier assembly 6 is intermittently rotatable around the carrier axle 67 at a constant cycle. In the first and second embodiments, the speed regulating escapement 2 is biased via the intermittent transmission device 4, but in the third embodiment, as described below, the speed regulating escapement 2 is biased via the hairspring 36. In the present embodiment, the amplitude of the balance is 660°.

[0136] 30 is a perspective view of a movement 11 equipped with a speed regulating escapement 2 of the third embodiment, as viewed from the front side. Note that parts other than the speed regulating escapement, such as the speed-increasing gear train 16, the back gear train, and the winding and time setting devices mounted on the main plate 13, are not shown. The speed regulating escapement 2 is provided on the front side of the main plate 13. A balance shaft 32 provided in the speed regulating escapement 2 is journaled by a balance bridge 17 fixed to the main plate 13.

[0137] Fig. 31 is a perspective view showing only the regulating escapement 2, and Fig. 32 is a side view of the regulating escapement 2 disassembled into subassembly levels. The regulating escapement 2 is composed of subassemblies: a governor 3, a carrier assembly 6, and a carrier receiver 8. This allows for easy assembly of each subassembly. , decomposition, and This allows adjustment work to be done.

[0138] The governor 3 includes a balance shaft 32 supported by a journal, a balance 31 coaxially connected to the balance shaft 32, a collet 34, a hairspring 36, a driving wheel 41 of the intermittent transmission device 4, a bearing 19, and a bearing 33. The carrier assembly 6 also includes a bearing 33. 42 driven wheels and the escapement 5 in an operable manner. In addition, the carrier bridge 8 is fixed to the main plate 13, and the escape wheel 7 is fixed coaxially thereto.

[0139] 32 is a common center line of the balance axle 32 and the carrier axle 67, and the speed governor 3, the carrier assembly 6, and the carrier support 8 are coaxially assembled on the axis O1. The hair spring 37 connected to the outer end of the hair spring 36 is loosely inserted into a hole of a fastening portion 62d connected to the tip of the hair spring support 62 held by the carrier assembly 6, and is held down by a set screw 62e. As a result, the hair spring 36 elastically contacts the speed governor 3 and the carrier assembly 6, and can twist the hair spring 36 when the carrier assembly 6 rotates.

[0140] FIG. 33 is a plan view of the speed controlling escapement 2. FIG. 34 shows a cross-sectional view taken along the line AA in FIG. 33. The balance 31 and the collet 34 are coaxially coupled to the balance stem 32, and the inner rings of the bearings 19 and 33 are fitted to both ends of the balance stem 32. The outer ring of the bearing 19 is fitted to an arm 18 which is a component of the balance bridge 17, and the outer ring of the bearing 33 is fitted to an axle box provided above the carrier stem 67. The inner rings of the bearings 68a and 68b are fitted to the carrier stem 67, and the outer rings of the bearings 68a and 68b are fitted to the carrier bridge 8. In other words, the balance stem 32 and the carrier stem 67 are supported so as to be rotatable independently of each other. The carrier 61 and the carrier arbor 67, and the carrier arbor 67 and the carrier pinion 69 are each press-coupled to each other, and the torque and rotation from the speed-increasing gear train 16 are transmitted to the carrier 61 via the carrier pinion 69 and the carrier arbor 67.

[0141] (Carrier Assembly) The axis O2 shown in FIG. 34 indicates the center line of the driven wheel axle 43, and the axis O3 indicates the center line of the pallet axle 54a which is the pivot axis of the pallet axle 54 as a regulating lever. and axis O3 Parallel to is The driven wheel 42 is coaxially coupled to the driven wheel arbor 43, and the inner rings of the bearings 64a and 64b are fitted to the driven wheel arbor 43. The outer rings of the bearings 64a and 64b are fitted to both ends of a driven axle box 63 pressed into the carrier 61.

[0142] A swing set 51 is fitted non-rotatably below the driven wheel arbor 43 using a key 44, and the swing set 51 is locked to the driven wheel arbor 43 by a wedge 53a that passes through the driven wheel arbor 43. The swing set 51 has a large flange 51a and a small flange 51a in the axial direction. A swing jewel 52, not shown in the cross-sectional view of FIG. 34, is connected to the large flange 51a so as to protrude below the large flange 51a.

[0143] Furthermore, the pallet fork 54 is fitted into the pallet fork arbor 54a via a pressed collar 54c. Furthermore, the inner rings of bearings 66a and 66b are fitted into the pallet fork arbor 54c. Furthermore, the outer rings of the bearings 66a and 66b are fitted into an pallet fork chock 65 that is pressed into the carrier 61. Note that since operation is not impeded even if the angle of the pallet fork 54 is misaligned relative to the pallet fork arbor 54a, the pallet fork 54 is locked by a wedge 54c that passes through the pallet fork arbor 54a without a key.

[0144] 35 and 36 are perspective views of the regulating escapement 2 of this embodiment as seen from above and below, respectively, and do not show the balance 31, the hairspring 36, and the carrier bridge 8. The pallet fork 54 is disengaged from the impulse jewel 52, and is aligned along the axis O3 The carrier assembly 6 receives torque from the speed-increasing gear train 16, but the insertion pawls 55 and the projection pawls 56 provided on the pallet fork 54 alternately engage with and disengage from the escape tooth 73 of the escape wheel 7 as the pallet fork 54 oscillates, periodically restricting the rotation of the carrier assembly 6.

[0145] The small flange 51b has a curved recess 51c formed radially inward at a portion radially corresponding to the impulse jewel 52. The recess 51c functions as a relief portion that prevents the tip 54h from contacting the small flange 51b when the impact surfaces 541f and 542f of the pallet box 54f engage with the impulse jewel 52. In addition, the outer peripheral surface of the small flange 51b, except for the recess 51c, is made slidable by the tip 54h provided below the pallet 54e, and functions as a safety device that prevents malfunction of the escapement 5 caused by external disturbances.

[0146] A dowel pin 58 is pressed into the pallet rod 54d and swings integrally with the pallet rod 54d. The dowel pin 58 engages with a regulating groove 61c provided below the carrier 61, and regulates the swing range of the pallet 54. The swing range is set to ensure the minimum gap required for the impulse jewel 52 and the pallet box 54f to be engaged and disengaged. In addition, when the dowel pin 58 is held down by the regulating groove 61c, the gap between the tip 54h and the small flange 51b is set small enough that they do not slide against each other.

[0147] The hair holder 62 includes a gripping portion 62b and an arm portion 62c extending from the gripping portion 62b. The gripping portion 62b has a radially reduced rigidity due to the notch 62a, and grips the carrier axle 67 by elastic force. This allows the hair holder 62 to be appropriately adjusted in angle about the axis O1, enabling adjustment of the angle between the intermittent transmission device 4 and the free state of the governor 3. The frictional force of the gripping portion 62b is set to be sufficiently large relative to the maximum torque generated in the hair spring 36, so that the gripping portion 62b is immobile when the governor escapement 2 is in operation.

[0148] FIG. 37 is a perspective view of elements used to explain the operation of this embodiment shown in FIG. 38 to FIG. 48. The rotation axis and rotation direction of each element are defined using FIG. 37. The driving wheel 41, which rotates integrally with the balance 31, rotates back and forth about the axis O1 in a first rotation direction M1 and a second rotation direction M2 that are opposite to each other. The driven wheel 42 reciprocates about the axis O2 in a third rotation direction M3 and a fourth rotation direction M4 that are opposite to each other. The pallet fork 54 oscillates in a fifth rotation direction M5 and a sixth rotation direction M6 that are opposite to each other about the axis O3. O4 is the center line of the fastening portion 62d. O4The three axes rotate in a seventh rotation direction M7 in accordance with the rotation of the carrier stem 67 around the axis O1, but are very slightly reversed to an eighth rotation direction M8 in the escapement stop release process. The reference state (where the rotation angle of each element is 0°) in this embodiment is defined as a state in which the finger 41a of the driving wheel 41 faces the groove 423a of the driven wheel 42, and the impulse jewel 52 faces the pallet box 54f, as shown in Figure 37. In the reference state, the governor 3 is set to a free state.

[0149] (Explanation of escapement mechanism) Hereinafter, the third embodiment of the present invention will be described in chronological order with reference to the drawings. Note that Figures 38 to 48 are front views of the component configuration shown in Figure 37 as viewed from above.

[0150] Fig. 38 is an operation explanatory diagram showing the state before the first stop release step in the third embodiment, and shows the state before the stopped state of the carrier assembly 6 is released by the extending claws 56. Fig. 38 shows the state in which the rotation angle of the balance 31 is at -90° with respect to the free state of the governor 3.

[0151] The extension escapement 45 is in the previous working cycle and the impulse jewel 52 Connecting O2 and O3 The ankle 54 is rotated 36° in the M4 direction with respect to the center line CL. In a swung position , the dowel pin 58a is in the regulating groove Wall 61c. Also, the stop surface 41b of the driving wheel 41, which rotates in the M1 direction together with the balance 31, is engaged with the stop surface 423c of the driven wheel 42, and the driven wheel 42 is in a state where it has stopped rotating.

[0152] The carrier assembly 6 receives torque in the M7 direction from the speed-increasing gear train 16, but the projection 56 of the pallet fork 54 is stopped by the stop surface 731a of the escape tooth 731, so the carrier assembly 6 is restricted to a rotation-stopped state. In addition, when the projection 56 of the pallet fork 54 presses against the stop surface 731a of the escape tooth 731, a "pulling" action is generated on the pallet fork 54 in the M6 ​​direction. Due to this pulling action, even if an external disturbance is input to the pallet fork 54, the stem pin 58a will not rotate in the regulating groove. Wall It is possible to maintain the restrained state without moving away from 61c.

[0153] FIG. 39 is an explanatory diagram showing the state after the first stop release step. FIG. 39 shows the state in which the balance 31 has rotated in the M1 direction from the state shown in FIG. 38. The finger 41a of the driving wheel 41 is accommodated in the groove 423a of the driven wheel 42 and engages with the impact surface 424b. In addition, the stop surface 422c and the stop surface 423c are accommodated in the recess 41c of the driving wheel 41 which rotates together with the balance 31 in the M1 direction, so that the engagement between the stop surface 41b of the driving wheel 41 and the stop surface 423c of the driven wheel 42 which had been engaged is released. As a result, the driven wheel 42 rotates in the M3 direction.

[0154] As the driven wheel 42 rotates, the impulse jewel 52 engages with and presses the impact surface 541f of the pallet fork 54. This causes the pallet fork 54 to swing in the M5 direction. The escapement 5 was in a stopped state with the protruding pawl 56 engaged with the escape tooth 731 until the first stop release step, but due to the swing of the pallet fork 54, the protruding pawl 56 disengages from the stop surface 731a of the escape tooth 731, and the stop of the carrier assembly 6 is released. In addition, the recessed pawl 55 of the pallet fork 54 enters between the escape teeth, and an interference amount with the escape tooth 733 is provided. When the pallet rod 54d swings further, the stop pin 58a engages with the regulating groove 61c, and the escape tooth 733 is again stopped.

[0155] In the first release step, when the projection 56, which is set to apply a pulling force, is disengaged from the escape tooth 731, it performs the work of extremely slightly rewinding the carrier assembly 6 in the M8 direction. This causes the governor 3 to lose an extremely small amount of its stored energy.

[0156] Fig. 40 is an explanatory diagram showing the state after the first rotation step. Fig. 40 shows a state in which the balance 31 has rotated in the M1 direction from the state shown in Fig. 39. Immediately after the protruding pawl 56 and the escape tooth 731 are disengaged from each other in the first stop release step, the carrier assembly 6 starts rotating in the M7 direction.

[0157] The carrier assembly 6 receives the torque of the speed-increasing gear train 16, and performs angular acceleration in the M7 direction until the engagement of the engagement pawl 55 with the escape tooth 733 causes the rotation to stop. The fastening portion 62d also rotates integrally with the carrier assembly 6. On the other hand, the balance rotates in the M1 direction at almost the maximum angular velocity, and overtakes the carrier assembly 6 which is angularly accelerating in the M7 direction. Therefore, in the first rotation process, the carrier assembly 6 cannot twist the hair spring 36 so as to impart elastic energy to the hair spring 36. Therefore, in the first rotation process, it is preferable to minimize the energy loss of the speed governor 3. Therefore, the rotation angle of the carrier assembly 6 in the first rotation process is set to the minimum angle for the engagement of the engagement pawl 55 with the escape tooth 733. After the first rotation process, the rotation of the fastening portion 62d stops, and the outer end position of the hair spring 36 stops, causing the speed governor 3 to start free vibration.

[0158] FIG. 41 is an explanatory diagram showing the state after the first idling step. FIG. 41 shows the state in which the balance 31 rotates in the M1 direction from the state shown in FIG. 40, and rotates 450° in the M1 direction with respect to the free state of the governor 3. As the balance 31 rotates in the M1 direction, the driven wheel 42 rotates by one tooth in the M3 direction. Note that the idling is the same as in the first embodiment, so a description thereof will be omitted. After the first idling step, the balance 31 continues to rotate without hitting anything, but since the stop surface 41b of the driving wheel 41 and the stop surface 421c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again maintains a stopped state.

[0159] FIG. 42 is an explanatory diagram of the first amplitude. FIG. 42 shows a state in which the balance 31 rotates in the M1 direction from the state shown in FIG. 14, and rotates 660° in the M1 direction with respect to the free state of the governor 3. After the first maximum oscillation angle is reached, the rotation direction of the balance 31 reverses from the M1 direction to the M2 direction. Note that in this embodiment, the states of FIG. 42 and FIG. 47 (described later) are exemplified as the first amplitude and the second amplitude, respectively, but the amplitude is not limited to 660° and may be expanded to a range permitted by the elasticity of the hairspring 36 and to a range in which the impulse jewel 52 does not come into contact with the spur 541g or 542g of the pallet fork 54c. In addition, when the amplitude is further expanded, the number of teeth of the driven wheel 42 can be appropriately changed to accommodate an even greater number of idling revolutions.

[0160] Fig. 43 is an explanatory diagram showing the state after the second idling step, in which the balance 31 has made one rotation in the M2 direction after the first amplitude shown in Fig. 42.

[0161] The finger 41a of the driving wheel 41 engages with the groove 421a of the driven wheel 42, and then rotates the driven wheel 42 by one tooth in the M4 direction. This causes the impulse jewel 52 to rotate by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small amount of idling loss.

[0162] After the second idling step, the balance 31 continues to rotate in the M2 direction, but since the stop surface 41b of the driving wheel 41 and the stop surface 422c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0163] FIG. 44 is an explanatory diagram showing the state after the second stop release step. FIG. 44 shows the state in which the balance 31 has rotated in the M2 direction from the state shown in FIG. 43. The finger 41a of the driving wheel 41 is accommodated in the groove 423a of the driven wheel 42 and engages with the impact surface 423b. In addition, the stop surface 422c and the stop surface 423c are accommodated in the recess 41c of the driving wheel 41, which rotates together with the balance 31 in the M2 direction, so that the engagement between the stop surface 41b of the driving wheel 41 and the stop surface 422c of the driven wheel 42 is released. As a result, the driven wheel 42 rotates in the M4 direction.

[0164] As the driven wheel 42 rotates, the impulse jewel 52 engages with and presses the impact surface 542f of the pallet fork 54. This causes the pallet fork 54 to swing in the M6 ​​direction. The escapement 5 was in a stopped state with the recessed pawl 55 engaged with the escape tooth 733 until the second stop release step, but due to the swing of the pallet fork 54, the recessed pawl 55 disengages from the escape tooth 733, and the stop of the carrier assembly 6 is released. In addition, the protruding pawl 56 of the pallet fork 54 enters between the escape teeth, providing an interference amount with the escape tooth 732. When the pallet rod 54d swings further, the stop pin 58a engages with the regulating groove 61c, and the escape tooth 732 is again held in a stopped state.

[0165] In the second release process, as in the first release process, when the engagement between the recessed pawl 55, which is set to apply a pull, and the escape tooth 733 is released, the carrier assembly 6 is very slightly rewound in the M8 direction. This causes the governor 3 to lose a very small amount of its stored energy.

[0166] Fig. 45 is an explanatory diagram showing the state after the second rotation step. Fig. 45 shows a state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 44. Immediately after the engaging pawl 55 and the escape tooth 733 are disengaged from each other in the second stop release step, the carrier assembly 6 starts rotating in the M7 direction.

[0167] The carrier assembly 6 receives the torque of the speed-increasing gear train 16, and performs angular acceleration in the M7 direction until the interference between the protruding pawl 56 and the escape tooth 732 causes the rotation to stop. The fastening portion 62d also rotates integrally with the carrier assembly 6. On the other hand, the balance rotates in the M2 direction at almost the maximum angular velocity, and moves away from the carrier assembly 6 which is angularly accelerating in the M7 direction. Therefore, in the second rotation process, the carrier assembly 6 can twist the hairspring 36 so as to impart elastic energy to the hairspring 36. That is, the amount of elastic energy required to maintain the vibration of the speed governor 3 can be replenished by elastically deforming the hairspring 36 so as to reduce its diameter. Therefore, the rotation angle of the carrier assembly 6 in the second rotation process is set to be larger than that in the first rotation process. This makes it possible to compensate for the energy loss of the speed governor 3 that occurs during the escapement operation. After the second rotation step, the rotation of the fastening portion 62d stops and the outer end position of the hairspring 36 stops, so that the speed governor 3 starts free vibration.

[0168] Fig. 46 is an explanatory diagram showing the state after the third idling stroke. Fig. 46 shows the state in which the balance 31 has rotated in the M2 direction from the state shown in Fig. 45 and has rotated 360° or more in the M2 direction with respect to the free state of the governor 3.

[0169] The finger 41a of the driving wheel 41 engages with the groove 423a of the driven wheel 42, and then rotates the driven wheel 42 by one tooth in the M4 direction. This causes the impulse jewel 52 to rotate by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small amount of idling loss.

[0170] After the third idling stroke, the balance 31 continues to rotate without hitting anything, but since the stop surface 41b of the driving wheel 41 and the stop surface 424c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0171] Fig. 47 is an explanatory diagram showing the state when the second amplitude is reached. Fig. 47 shows the state when the balance 31 rotates in the M2 direction from the state shown in Fig. 46, and rotates 660° in the M2 direction with respect to the free state of the governor 3. After the maximum swing angle is reached, the rotation direction of the balance 31 reverses from the M2 direction to the M1 direction.

[0172] The second amplitude is a state in which the rotation direction M2 of the balance 31 is opposite to the rotation direction M7 of the carrier assembly 6 and has the maximum oscillation angle, so the torque with which the hairspring 36 twists the carrier assembly 6 in the M8 direction is also maximum.

[0173] At this time, if the torque generated in the hairspring 36 in the M8 direction is greater than the torque in the carrier assembly 6 in the M7 direction, the hairspring 36 will rewind the carrier assembly 6 in the M8 direction, disrupting the free vibration of the governor 3 and deteriorating the timekeeping accuracy. Therefore, in this embodiment, in the second amplitude state in which the balance 31 has the maximum oscillation angle in the direction opposite to the rotational direction of the carrier assembly 6, the torque in the M7 direction that the carrier assembly 6 receives from the speed-up gear train 16 is set to be greater than the torque in the M8 direction generated in the hairspring 36. This makes it possible for the carrier assembly 6 to continue free vibration without being rewound by the hairspring 36.

[0174] Fig. 48 is an explanatory diagram showing the state after the fourth idling stroke. Fig. 48 shows a state in which the balance 31 has made one rotation in the M1 direction after the second amplitude shown in Fig. 47.

[0175] The finger 41a of the driving wheel 41 engages with the groove 423a of the driven wheel 42, and then rotates the driven wheel 42 by one tooth in the M4 direction. This causes the impulse jewel 52 to rotate by the same angle, but since the impulse jewel 52 does not engage with the pallet box 54, the driven wheel 42 spins freely. At this time, the governor 3 generates a very small amount of idling loss.

[0176] After the fourth idling stroke, the balance 31 continues to rotate in the M1 direction, but since the stop surface 41b of the driving wheel 41 and the stop surface 423c of the driven wheel 42 engage with each other, the rotation of the driven wheel 42 again remains stopped.

[0177] As the balance 31 rotates, the finger 41a of the driving wheel 41 again engages with the groove 422a of the driven wheel 42, and transitions to the first stop release step in the next cycle. The speed controlling escapement 2 shown in the third embodiment according to the present invention performs escapement operation in this manner.

[0178] (Phase of rotation) 49 to 52 are graphs showing the rotation angles of balance 31 and carrier assembly 6 in the first and second pivot strokes, with the horizontal axis representing time and the vertical axis representing the oscillation angle of balance 31. FIG. 49 shows the case where energy is lost in the first pivot stroke, FIG. 50 shows the case where energy is lost in the second pivot stroke, FIG. 51 shows the case where energy loss is suppressed in the first pivot stroke, and FIG. 52 shows the case where energy loss is suppressed in the second pivot stroke. In each figure, the angle of balance 31 is shown by a solid line 96, and the angle of carrier assembly 6 is shown by a dashed line 97. Also, The sign of the rotation angle is positive in the M1 direction of the balance 31 and the M7 direction of the carrier assembly 6. For ease of explanation, the angle of the carrier assembly 6 before rotation in each rotation process will be set to 0°.

[0179] Figure 49 shows the first rotation process, in which t1 indicates the time when the first stop is released, t2 indicates the time when the oscillation angle of the balance 31 which is freely vibrating becomes zero, t3 indicates the time when the relative angle between the carrier assembly 6 and the balance 31 becomes zero, and t4 indicates the time when the first rotation process is completed. At time t3, the hairspring 36 is in a free state. .

[0180] Arrow 98a indicates the angle and direction of carrier assembly 6 relative to balance 31. In other words, balance 31 receives torque in the direction of arrow 98a, the amount of torque being calculated by multiplying the torsion angle of hair spring 36, indicated by the length of arrow 98a, by torsion spring constant k. Also, at time t3, point 96c on line 96 and point 97c on line 97 coincide with each other, and hair spring 36 is in a free state.

[0181] From point 97a of first stop release to point 97d of first rotation completion, the carrier assembly 6 receives torque from the speed-increasing gear train 16 and performs angular accelerated motion up to angle Φ1. However, since the carrier assembly 6 leads the balance 31 only in the section from t1 to t3, the hairspring 36 is energized and energy can be replenished.

[0182] On the other hand, in the section from t3 to t4, the balance 31 rotating at the maximum angular velocity overtakes the carrier assembly 6 undergoing angular acceleration and takes the lead, so that the carrier assembly 6 is pulled by the balance 31 via the hairspring 36. In other words, in the section from t3 to t4 in the first rotation process, part of the energy held by the balance 31 is consumed in accelerating the carrier assembly 6, The restoring force of the hairspring 36 is reduced by the amount that the carrier assembly 6 rotates, resulting in a loss of energy stored in the governor 3. .

[0183] Therefore, in the first rotation stroke, it is preferable to suppress the loss of the energy stored in the balance 31, minimize the section in which energy is lost, and maximize the section in which energy can be replenished. Therefore, as shown in Figure 51, it is preferable to generate the first stop release point t1 earlier and set the first rotation completion point 97d (time t4) of the carrier assembly 6 before points 96c and 97c (time t3) at which the hairspring 36 is in the free state. This makes it possible to replenish energy to the governor 3 throughout the entire section of the first rotation stroke without reducing the energy stored in the balance 31.

[0184] Next, FIG. 50 shows the second rotation process, and t5 is the time when the second stop is released. t6 is the time when the relative angle between the carrier assembly 6 and the balance 31 becomes zero, and t7 is the time when the swing angle of the balance 31, which is freely vibrating, becomes zero. , t8 indicates the time when the second rotation process is completed. At time t6, the hairspring 36 is in a free state. .

[0185] Arrow 98 b indicates the angle and direction of the carrier assembly 6 relative to the balance 31. That is, the balance 31 receives a torque in the direction of arrow 98b whose magnitude is calculated by multiplying the torsion angle of the hair spring 36 represented by the length of arrow 98b by the torsion spring constant k. Also, at time point t6, point 96f on line 96 and point 97f on line 97 coincide with each other, and the hair spring 36 is in a free state.

[0186] From the second stop release point 97e to the second rotation completion point 97h, the carrier assembly 6 receives torque from the speed-increasing gear train 16 and performs angular accelerated motion up to an angle Φ2, but in the section from t6 to t8, the balance 31 rotates in the opposite direction to the carrier assembly 6, so that the relative angle between the carrier assembly 6 and the balance 31 can be easily obtained. In other words, the hairspring 36 can be effectively twisted, so that the energy held in the governor 3 can be effectively replenished.

[0187] On the other hand, Time From t5 Time In the section up to t6, the torsion angle of the hairspring 36 is the same as the rotation angle of the carrier assembly 6. decrease In addition, the balance 31 supplies a part of its energy to the carrier assembly 6. Time From t5 Time In the t6 section, A part of the energy stored in the balance 31 is consumed in accelerating the carrier assembly 6, and the restoring force of the hairspring 36 is reduced by the amount that the carrier assembly 6 rotates, resulting in a loss of energy stored in the governor 3. .

[0188] Therefore, it is preferable to suppress the loss of the energy stored in the balance 31 in the second rotation process as well, to minimize the section in which the energy is lost, and to maximize the section in which the energy can be replenished. t5 The hairspring 36 is further delayed at points 96f and 97f (time t6 , time t7It is preferable to provide the second stop release point 97e (time point t5) of the carrier assembly 6 after the second stop release point 97e (time point t5). This makes it possible to replenish energy to the governor 3 throughout the entire second rotation stroke without reducing the energy held by the balance 31.

[0189] In addition, the stop release in the first rotation process and the second rotation process phase The adjustment can be made by adjusting the engagement between the escape tooth 73 and the recessed and projecting pawls 55 and 56, but this adjustment method is not limited to this and the shape of the parts of the escapement 5 may also be adjusted.

[0190] In the speed-controlling escapement 2 according to this embodiment, the outer end of the hairspring 36 37 attached to the is held by a hair holder 62 whose angle can be adjusted around the balance shaft 32. This makes it possible to adjust the relative angle between the intermittent transmission 4 and the free state of the governor 3, and accurately cancels out timing errors that occur each time the intermittent transmission 4 goes through an idling stroke.

[0191] (effect) Therefore, the speed control escapement according to this embodiment 2 According to this, even when the amplitude of the balance exceeds approximately 340°, no oscillation occurs, and a much larger amplitude than that of conventional escapements can be realized. This allows the quality factor (Q value) to be significantly increased, and timekeeping accuracy to be significantly improved. In addition, since oscillation can be achieved in an oscillation angle range where the effect of amplitude changes on timekeeping errors is low, the flatness difference can be improved. In addition, since an intermittent transmission is used in the mechanism for eliminating oscillation, the large amplitude can be realized with little energy loss.

[0192] Furthermore, since most of the energy is replenished in the second rotation stroke in which the balance 31 rotates in the opposite direction to the rotation direction of the carrier assembly 6, the hair spring 36 can be reliably twisted in the direction of reducing its diameter even if the rotation speed of the carrier assembly 6 is slower than that of the balance 31. Also, the rotation angle of the carrier in the second rotation stroke is set large. As a result, energy can be reliably and sufficiently replenished to the governor 3, and a large amplitude can be maintained.

[0193] Furthermore, if the first rotation stroke is completed before the hairspring 36 reaches its free state, and the second rotation stroke is set to start after the hairspring 36 reaches its free state, the loss of energy stored in the speed governor 3 in each stop / release stroke can be minimized, maximizing the efficiency of replenishing energy from the escapement 5 to the speed governor 3. This further improves the efficiency of the speed regulating escapement 2, and makes it possible to extend the operating time of the power spring.

[0194] In addition, the amount of energy supplied from carrier assembly 6 to balance 31 depends on the torsion angle of hairspring 36, and is therefore determined by rotation angles Φ1 and Φ2 of carrier assembly 6. In other words, escapement 5 and hairspring 36 function as a constant force device, making it possible to stabilize the oscillation angle of balance 31.

[0195] Also 、 According to the speed-governing escapement of this embodiment, 2 Since the carrier assembly 6 equipped with the above-mentioned components can be rotated at a constant period around the axis O1, the vertical isochronism in various vertical positions can be averaged, thereby improving the vertical isochronism.

[0196] These improvements in timekeeping accuracy allow the movement frequency to be reduced, which in turn reduces the rate at which the barrel relaxes, allowing the mainspring to operate for longer. [Industrial Applicability]

[0197] It can also be applied to mechanical stopwatches. [Explanation of symbols]

[0198] 1...watch, 10...case, 11...movement, 12...crown, 13...main plate, 14...dial, 15...hands, 16...speed-increasing gear train, 17...balance bridge, 18...arm, 19...bearing, 2...governing escapement, 3...governing mechanism, 31...balance, 32...balance shaft, 33...bearing, 34...balance ball, 35...first wedge, 36...hairspring, 37... stud, 38... second wedge, 4... intermittent transmission device, 41... driving wheel, 41a... finger, 41b... stop surface, 41c... recess, 42... driven wheel, 42a... radial groove, 42b... impact surface, 42c... stop surface, 43... driven wheel stem, 44... key, 45... extension escapement, 5... escapement, 51... pendulum seat, 51a... large rib, 51b... small rib, 51c... 52...pivot stone, 53a...third wedge, 53b...fourth wedge, 54...ankle, 54a...ankle true, 54b...ankle body, 54c...collar, 54d...ankle rod, 54e...ankle second, 54f...ankle box, 54g...spur, 54h...tip, 55...insertion claw, 55a...stopping surface, 55b...locking corner, 55c...impact surface, 55d...let-off corner, 56...outer claw, 56a...stopping surface, 56b...locking corner, 56c...impact surface, 56d...let-off corner, 58...thrust pin, 59...detent arm, 6...carrier assembly, 61...carrier, 61a...follower true arm, 61b...ankle true arm, 61c...regulating groove Wall , 62...bearing support, 62a...notch, 62b...gripping portion, 62c...arm portion, 62d...fastening portion, 62e...set screw, 63...driven axle box, 64a...bearing, 64b...bearing, 65...ankle axle box, 66a...bearing, 66b...bearing, 67...carrier arbor, 67a...axle box portion, 68a...bearing, 68b...bearing, 68c...spacer, 69...carrier pinion, 7...escape wheel, 71...escape wheel arbor, 72...pinion, 73...escape tooth, 73a...stop surface, 73b...tooth tip, 73c...impact surface, 73d...tooth heel, 8...carrier support

Claims

1. A balance that rotates back and forth at a constant cycle, a balance stem coaxially connected to said balance; a driving wheel of an intermittent transmission device coaxially connected to the balance shaft; an escape wheel that is arranged coaxially with the balance shaft and is fixed to the main plate so as not to rotate; A carrier supported coaxially with the balance shaft; a hairspring that elastically contacts the balance shaft and the carrier; a regulating lever that is journalled on the carrier and engages with the escape wheel to regulate rotation of the carrier; a driven wheel of an intermittent transmission device journalled on the carrier and engaged with the driving wheel; A pendulum stone that rotates integrally with the driven wheel and engages with a regulating lever; A speed regulator comprising:

2. 2. The speed-regulating escapement according to claim 1, wherein an angle by which the carrier rotates in a direction opposite to that of the balance wheel during escapement is set to be larger than an angle by which the carrier rotates in the same direction as that of the balance wheel.

3. 3. The speed-regulating escapement according to claim 1 or 2, characterized in that the torque that the carrier receives from the speed-increasing gear train is set to be larger than the torque generated by the hairspring when the oscillation angle of the balance wheel rotating in the opposite direction to the carrier is at its maximum.

4. 4. The speed controlling escapement according to claim 1, wherein the time when the carrier rotates when the balance wheel rotates in the same direction as the carrier is set to be completed before the time when the hairspring becomes free, and the time when the carrier rotates when the balance wheel rotates in the opposite direction to the carrier is set to be started after the time when the hairspring becomes free.

5. 2. The speed governor according to claim 1, wherein the intermittent transmission is a Geneva mechanism.

6. 6. The speed regulator escapement according to claim 5, wherein the driving wheel of the Geneva mechanism is constructed of a single layer.

7. 7. The speed-regulating escapement according to claim 5, wherein the impulse jewel is provided on the driven wheel of the Geneva mechanism.

8. 8. The speed-regulating escapement according to claim 7, wherein the impulse jewel is provided on a tooth portion of the driven wheel of the Geneva mechanism.

9. 9. The speed-controlling escapement according to claim 1, wherein an outer end position of the hairspring is attached so as to be angularly adjustable around the balance stem with respect to an engagement phase of the intermittent transmission device.

10. A timepiece movement equipped with the speed regulating escapement according to any one of claims 1 to 9.

11. A mechanical watch equipped with the watch movement according to claim 10.

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