Detent escapement and mechanical timepiece.

专利摘要:
A detent escapement (100) of the present invention includes an escape wheel (110), a beam (120) having a pulse pallet (122) and a release pallet (124), and a detent (130) having a pallet of rest (132). A straight line that passes through a center of rotation of the trigger and a center of rotation of the balance defines a reference line of rotation. The clearance pallet is fixed to a position which, in a state where the balance is in the neutral position, is shifted in the opposite direction to the escape wheel relative to the rotational reference line so that the total sum of influences that advance the diurnal march of the timepiece, including the sum of the influence on the rotary movement of the pendulum which is generated by a "pulse before the neutral" and the influence on the rotary movement of the pendulum which is generated by a "resistance after neutral", and the sum total of the influences that delay the diurnal march of the timepiece, including the sum of the influence on the rotary movement of the pendulum which is generated by a "forward resistance" the "dead point" and the influence on the rotary movement of the pendulum which is generated by a "pulse after the neutral" balance each other.
公开号:CH704885B1
申请号:CH01639/12
申请日:2010-08-31
公开日:2016-01-29
发明作者:Masayuki Koda；Hiroki Uchiyama；Takashi Niwa
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

Technical area
[0001] The present invention relates to a detent escapement and a timepiece in which the detent escapement is incorporated. Particularly, the present invention relates to a detent escapement which is arranged to decrease the error due to the escapement and to a mechanical timepiece in which a detent escapement configured as indicated above is incorporated.
Prior art
[0002] In the prior art, the detent escapement "(chronometer escapement) is a known type of escapement for a mechanical timepiece. As representative embodiments of the detent escapement, conventionally the spring detent escapement and the pivoted detent escapement are widely known (eg, refer to NPL 1 below).
[0003] With reference to FIG. 20, the conventional spring detent escapement 800 includes an exhaust mobile 810, a balance wheel 820, a detent lever 840, and a leaf spring 830. An impulse vane 812 is attached to a large plate of the balance wheel 820 A rest paddle 832 is attached to the trigger lever 840. A release paddle 824 is attached to the large platen 816. The impulse paddle 812 and the release paddle 824 are configured to be able to contact. with the tooth 812 of the exhaust mobile 810.
[0004] With reference to FIG. 21, the conventional swiveling detent escapement 900 includes an escapement mobile 910, a balance wheel 920, a detent lever 930, and a spiral spring 940. An impulse vane 912 is attached to a large plate of the balance 920 A rest pallet 932 is attached to the trigger lever 930. A release pallet 924 is attached to the large platen 916.
[0005] Unlike the lever escapement which is widely used today, a common advantage to the escapements of the types shown in FIGS. 20 and 21 is that the power loss (transmission torque) in the escapement can be reduced, since the power is transmitted directly from the escapement mobile to the balance.
[0006] In addition, the conventional detent escapement includes an exhaust mobile (1), a balance, a detent (11) which supports a stop pawl (21), and a large plate (5) which is attached to the balance. The detent escapement includes a hairspring (12), the inner end of which is integrated into the detent (11) (for example, refer to PTL 1 below).
Citation list
Patent literature
[0007] [PTL 1] Japanese translation of PCT Patent Publication No. 2009-510,425 (Pages 5-7 and Fig. 1)
Non-patent literature
[0008] [NPL 1] Pages 39 to 47, "The Practical Watch Escapement", Première Impression Limitée, 1994 (First Edition), written by George Daniel
Summary of the invention
Problem to be solved by the invention
[0009] In a mechanical timepiece, the error due to the escapement is one of the factors which affects isochronism, and this applies to the lever escapement as well as to the direct impulse type escapement represented by the trigger exhausts mentioned above. Based on the Airy formula, when the escapement transmits energy to the balance by means of a pulse or resistance, an escapement error is generated relative to a free oscillation of the balance.
[0010] When the balance oscillates freely as a result of the return force of a hairspring, the impulse and the resistance due to the escapement can be classified as "impulse before neutral", "resistance before neutral" , "Pulse after neutral", and "resistance after neutral". Here, "neutral" means the "center of oscillation of the balance" when the balance is freely oscillating. That is, "center of oscillation" denotes a position which is at the exact center between a position of rotation when the balance wheel is turned to the extreme in a first direction (for example, clockwise. 'a clock: rotation to the right) and a position of rotation when the balance is turned to the extreme in a second direction (for example, counterclockwise: rotation to the left) which is a direction contrary to the first direction.
[0011] "Resistance before neutral" is the fact that a force is applied in a direction opposite to the direction of advance of the balance before the balance passes through neutral (center of oscillation of the balance). In other words, "resistance before neutral" occurs when one end of a leaf spring makes contact with the balance release pallet and applies resistance to the balance before the balance has passed through the balance. neutral point (center of oscillation of the balance).
A "pulse before neutral" is the fact that a force is applied relative to the direction of advance of the balance before the balance has passed through neutral (center of oscillation of the balance). In other words, an "impulse before neutral" occurs when the tooth of the escapement mobile is in contact with the impulse pallet of the balance and applies a force relative to the direction of advance of the front balance. that the balance has passed through neutral (center of oscillation of the balance).
[0013] A "pulse after neutral" is the fact that a force is applied in the direction of advance of the balance wheel after the balance wheel has passed through neutral point (center of oscillation of the balance wheel). In other words, an "impulse after neutral" occurs when the tooth of the escape wheel presses the impulse pallet of the balance and applies a force in the direction of advance of the balance after the balance has passed. by the neutral point (center of oscillation of the balance).
A "resistance after the neutral point" is the fact that a force is applied in the direction opposite to the direction of advance of the balance wheel after the balance wheel has passed through neutral point (center of oscillation of the balance wheel) . In other words, “resistance after neutral” occurs when the end of the leaf spring contacts the balance release pallet and applies resistance to the balance after the balance has passed through neutral. (center of oscillation of the balance) and returns in the direction of neutral (center of oscillation of the balance). In addition, "resistance after neutral" occurs when one end of a leaf spring contacts the balance release pallet and applies resistance to the balance after the balance has passed through neutral ( balance center of oscillation), then returned to neutral (balance center of oscillation), and the balance passed through neutral again (balance center of oscillation).
[0015] In general, when there is no disturbance, it is known that the period of oscillation of the balance wheel is constant, due to the "isochronism of the pendulum", regardless of the amplitude of the balance wheel. On the other hand, when the balance is positioned at a position that is separate from neutral (center of oscillation), the influence that the disturbance has on the period of oscillation of the balance is great. In addition, the momentum that occurs when the balance passes through neutral (center of oscillation of the balance) has no effect on the period of oscillation of the balance. In addition, the resistance that occurs when the balance passes through neutral (center of oscillation of the balance) does not influence the period of oscillation of the balance.
[0016] In the following, the "Airy formula" is described. With reference to FIG. 22, when there is no disturbance applied to the balance, the period of oscillation of the balance is constant, due to the "isochronism of the pendulum", regardless of the amplitude of the balance. A "pulse before neutral" (pulse before passing through the center of oscillation) reduces the period of oscillation and changes the diurnal rate ("timing rate") (second / day) of the timepiece in the direction plus (forward). In addition, a "resistance after neutral" (resistance after passing through the center of oscillation) also changes the diurnal rate (seconds / day) of the timepiece in the plus (forward) direction. On the other hand, a "resistance before neutral" (resistance before passing through the center of oscillation) changes the daytime (seconds / day) of the timepiece in the minus (lag) direction. In addition, a "pulse after neutral" (pulse after passing through the center of oscillation) changes the daytime (second / day) rate of the timepiece in the minus (delay) direction.
[0017] In addition, the further the position at which the disturbance is applied is from the center of oscillation of the balance, the greater the influence on the period of oscillation of the balance due to the disturbance. In addition, when the disturbance is applied to the center of oscillation of the balance, the disturbance does not influence the period of oscillation of the balance. In addition, the error due to the escapement changes depending on the angle of oscillation of the balance (that is, the input torque of the balance). Essentially, transmission efficiency of the escapement is improved, an escapement mechanism which can transfer and receive kinetic energy in a range of narrow oscillation angles in the vicinity of a center of oscillation of the balance wheel is provided , and therefore, an elementary performance such as daytime running of the mechanical timepiece can be improved.
[0018] Therefore, the elimination of the change in daytime rate that accompanies the change in the swing angle of the balance is a problem to be solved.
[0019] An object of the present invention is to provide a detent escapement which is arranged to further reduce error due to the exhaust than the detent escapement in the prior art.
Solution to the problem
[0020] In general, the error due to the exhaust (the static error due to the exhaust) is indicated by the following equation.SEE = Rd - RnHere,SEE: static error due to the escape (seconds / day);Rd: daytime running (second / day) for a constant oscillation angle (arbitrary constant torque) with the driving escapement;Rn: day rate (timing rate ") (second / day) in the case of free oscillations of the balance.
In the present invention, by correcting a position of the center of oscillation of the balance, the total sum of the influence on the diurnal rate generated by the Pulse before neutral ", the influence on the daytime rate generated by "resistance before neutral", the influence on daytime running generated by a "pulse after neutral", and the influence on daytime running generated by "resistance after neutral" is configured to be smaller than the detent escapement of the prior art. That is to say, by correcting the position of the center of oscillation of the balance wheel, the present invention is arranged to suppress a change of a period in a case where the escapement operates in a period of free damped oscillation of the balance. pendulum.
For example, a correction of the position of the center of oscillation of the balance can be obtained by determining a corrective quantity to be somewhat different, by simulation, by preparing an approximate equation (linear approximate equation), and calculating the correcting amount (angle) of the position of the center of oscillation of the balance. Alternatively, in correcting the position of the balance center of oscillation, by preparing a prototype escapement of the same size or larger to test and set a corrective amount to be somewhat different, an appropriate corrective amount (angle) may be obtained from the test results. In this way, by performing a correction of the position of the center of oscillation of the balance, the error due to the escapement can be significantly reduced compared to the detent escapement of the prior art. In addition, in this way, by performing a correction of the position of the center of oscillation of the balance, an isochronism curve can be improved compared to the detent escapement of the prior art.
[0023] The present invention relates to a detent escapement for a timepiece, which includesan escapement unit having teeth forming a set of teeth,a balance having an impulse vane to cooperate with each tooth of the teeth and a release vane, anda trigger formed by a blade and having a rest pallet to cooperate with each tooth of the teeth,wherein a "resistance before neutral" is the fact that one end of a leaf spring contacts the balance release pallet and applies resistance to the balance before the balance passes through neutral,in which a "pulse before neutral" is the fact that the tooth of the escape wheel is in contact with an impulse paddle of the balance and applies a force relative to a direction of advance of the balance before the balance goes through neutral,wherein an "impulse after neutral" is the fact that the tooth of the escape wheel pushes the impulse paddle of the balance and applies a force relative to a direction of advance of the balance after the balance has passed through the dead point,wherein "resistance after neutral" is when the end of the leaf spring contacts the balance release pallet and applies resistance to the balance after the balance has passed through neutral, and the causes the end of the leaf spring to contact the balance release pallet and apply resistance to the balance after the balance has passed through neutral, then returned to neutral, then returned through point dead, andwherein a rotational reference line is a straight line which passes through the center of rotation of the blade and the center of rotation of the balance.
In the detent escapement of the present invention, in a state where the balance is positioned in neutral, the release pallet is offset in the direction opposite to the exhaust mobile relative to the reference line of rotation so that the total sum of the influences which cause the diurnal rate of the timepiece to advance, including the sum of the influence on the rotary movement of the balance which is generated by a "pulse before neutral" and the influence on the rotary movement of the balance which is generated by a "resistance after the neutral point", and the total sum of the influences which delay the daytime running of the timepiece, including the sum of the influence on the rotary movement of the balance which is generated by a "resistance before neutral" and the influence on the rotary movement of the balance which is generated by a "pulse after neutral", balance each other. With this configuration, the error due to the escapement can be reduced compared to the conventional spring detent escapement. In addition, according to this configuration, an isochronism curve can be improved compared to the detent escapement of the prior art.
In the detent escapement of the present invention, it is preferable that the release pallet is fixed at a position in which, in a state where the pendulum is positioned in neutral, the release pallet is rotated between 10 ° and 50 ° relative to the reference line of rotation in the direction opposite to the exhaust mobile. In this configuration, an error due to the escapement can be further reduced compared to the conventional spring detent escapement.
[0026] Further, in the detent escapement of the present invention, it is preferable that the release pallet is fixed at a position in which, in a state where the rocker (120) is positioned in neutral, the pallet clearance is rotated 20 ° to 30 ° relative to the reference line of rotation in the direction opposite to the exhaust mobile. Under this configuration, the error due to the escapement can be significantly reduced compared to the conventional spring detent escapement.
In addition, in the present invention, in a mechanical timepiece including a mainspring which forms a drive source for the mechanical timepiece, a cog which is driven by a torque when the mainspring is armed, and an exhaust to control the rotation of the gear train, the exhaust is according to the present invention.
In the mechanical timepiece of the present invention, it is preferable that the balance includes a hairspring, an outer end of the hairspring is fixed to a stud which is provided to be able to rotate relative to a balance bridge, and the mechanical timepiece is arranged to make it possible to change the position of the release pallet and the position of the impulse pallet with respect to the reference line of rotation by turning the eyebolt relative to the balance bridge. In addition, it is preferable that the mechanical timepiece of the present invention additionally includes a range indicating means for indicating a range over which the stud can be rotated.
[0029] According to this configuration, a thin mechanical timepiece, which can be easily adjusted, can be produced compared to the conventional spring detent escapement. Furthermore, in the mechanical timepiece of the present invention, the error due to the escapement can be compared to the detent escapement of the prior art.
Advantageous effects of the invention
[0030] Since the detent escapement of the present invention is configured to apply energy to the balance from the escapement mobile in a range of a narrow oscillation angle in the vicinity of the position where the balance passes the neutral point (center of oscillation), an error due to the escapement of the mechanical timepiece can be reduced compared to the conventional spring detent escapement. In addition, in the detent escapement of the present invention, the isochronism curve can be improved compared to the detent escapement of the prior art. Further, in the mechanical timepiece of the present invention, an error due to the escapement can be reduced compared to the detent escapement of the prior art.
Brief description of the drawings
[0031] FIG. 1 is a plan view showing the structure of an escapement in one embodiment of a detent escapement of the present invention. fig. 2 is a sectional view showing a single leaf spring fixing peg and an eccentric leaf spring peg in the embodiment of the detent escapement of the present invention. fig. 3 is a sectional view showing a hairspring fixing peg and an eccentric hairspring peg in the embodiment of the detent escapement of the present invention. fig. 4 is a sectional view showing the hairspring fixing pin and a horizontal hairspring screw in the embodiment of the detent escapement of the present invention. fig. 5 is a sectional view showing an eccentric adjustment pin in the embodiment of the detent escapement of the present invention. fig. 6 is a partial sectional view showing a concave receiving portion for receiving the hairspring in the embodiment of the detent escapement of the present invention. fig. 7 is a plan view showing a structure such as a front gear and the escapement in one embodiment of a mechanical timepiece which uses the detent escapement of the present invention. fig. 7A is a perspective view showing the structure such as the front gear and the escapement in the embodiment of the mechanical timepiece which uses the detent escapement of the present invention. fig. 8 is a plan view showing an escapement mobile and a portion of a balance in the embodiment of the detent escapement of the present invention. fig. 9 is a (first) plan view showing an operational state of the escapement in the embodiment of the detent escapement of the present invention. fig. 10 is a (second) plan view showing an operational state of the escapement in the embodiment of the detent escapement of the present invention. fig. 11 is a (third) plan view showing an operational state of the escapement in the embodiment of the detent escapement of the present invention. fig. 12 is a (fourth) plan view showing an operational state of the escapement in the embodiment of the detent escapement of the present invention. fig. 13 is a (fifth) plan view showing an operating state of the escapement in the detent escapement embodiment of the present invention. fig. 14 is a (sixth) plan view showing an operational state of the escapement in the detent escapement embodiment of the present invention. fig. 15 is a (seventh) plan view showing an operational state of the escapement in the detent escapement embodiment of the present invention. fig. 16 is a graph showing the test results of a ten times size model of the escapement in the detent escapement embodiment of the present invention. fig. 17 is a graph showing the results of a simulation in the embodiment of the detent escapement of the present invention. fig. 18 are torque graphs and plan views of the balance showing changes in position of a pulse and resistance due to a neutral position adjustment in the detent escapement. fig. 19 is graphs showing changes in position of a pulse and resistance due to the neutral position adjustment in the detent escapement. fig. 20 is a perspective view showing the structure of the conventional spring detent escapement. fig. 21 is a perspective view showing the structure of the conventional pivoted detent escapement. fig. 22 is a principle view for explaining the Airy formula. fig. 23 is a (first) plan view showing a state of operation of the escapement in a neutral position in which daytime running is delayed in the conventional detent escapement. fig. 24 is a (second) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 25 is a (third) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 26 is a (fourth) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 27 is a (fifth) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 28 is a (sixth) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 29 is a (seventh) plan view showing the operational status of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 30 is an (eighth) plan view showing the operational status of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 31 is a (first) plan view showing the operational status of the exhaust in the neutral position in which daytime running is delayed. fig. 32 is a (second) plan view showing the operational state of the exhaust in the neutral position in which daytime running is delayed. fig. 33 is a (third) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 34 is a (fourth) plan view showing the operational state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 35 is a (fifth) plan view showing the operational state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 36 is a (sixth) plan view showing the operating state of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement. fig. 37 is a (seventh) plan view showing the operational status of the escapement in the neutral position in which daytime running is delayed in the conventional detent escapement.
Description of embodiments
[0032] Hereinafter, embodiments of the present invention will be described with reference to the drawings. In general, a movement body including a driving part of a timepiece is called a "movement". A state where a dial and hands are mounted on the movement and inserted into a timepiece case to achieve a finished product is called "complete". Among the two sides of a plate which forms a support for the timepiece, the side on which a timepiece case glass is arranged, that is to say the side on which the dial is arranged is called the “rear side” of the movement, “crystal side”, or “dial side”. Among the two sides of the plate, the side on which a back case of a timepiece case is disposed, i.e. the side opposite the dial is called the "front side" of the movement or "side. rear of box ”. A cog that is incorporated into the "front side" of the movement is called a "front cog". A cog that is incorporated into the "rear side" of the movement is called a "rear cog".
(1) Configuration of the detent escapement of the present invention
[0033] With reference to FIGS. 1, 7 and 8, a movement 300 of the timepiece includes a detent escapement 100 of the present invention. The detent escapement 100 of the present invention includes an exhaust mobile 110, a balance 120, and a detent formed by a blade 130 which has a rest pallet 132 including a contact plane 132B which is capable of entering into. contact with a tooth 112 of the exhaust mobile 110.
The balance 120 includes a balance axis 114, a wheel 115, a large plate 116, and a hairspring 118. The impulse pallet 122 is fixed to the large plate 116. A release pallet 124 is attached to the large plate 116. The impulse vane 122 is arranged to be able to come into contact with each tooth 112 of the exhaust mobile 110.
[0035] With reference to FIGS. 1 and 9c, a straight line which passes through the center of rotation 130A of the blade 130 and the center of rotation 120C of the balance 120 in a state where the balance 120 is positioned at a center of oscillation is defined as a reference line 120D rotation. The release pallet 124 is arranged to be fixed at a position which, in a state where the rocker 120 is positioned at the center of oscillation, is offset in the direction opposite to the exhaust mobile 110, relative to the reference line. of rotation 120D, so that the total sum of the influences which advance the diurnal rate of the timepiece, including the sum of the influence on the rotary movement of the balance wheel 120 which is generated by the "impulse before neutral "And the influence on the rotary movement of the balance 120 which is generated by a" resistance after the neutral point ", and the total sum of the influences which delay the daytime running of the timepiece, including the sum of the influence on the rotary motion of the balance 120 which is generated by a "resistance before neutral" and the influence on the rotary movement of the balance wheel 120 which is generated by a "pulse after neutral", balance each other.
[0036] It is preferable that the release pallet 124 is fixed between a position in which the release pallet is rotated by 10 ° relative to the reference line of rotation 120D and a position in which the release pallet is rotated by 50 ° relative to the reference line of rotation 120D, in the direction opposite to the exhaust mobile 110. In addition, it is even better when the release pallet 124 is fixed at a position in which the release pallet is. rotated by 20 ° to 30 ° with respect to the reference line of rotation 120D in the direction opposite to the exhaust mobile 110. That is to say, in FIG. 1, an angle DTN between a straight line 120F which connects the center of rotation of the balance 120 and a contact surface of the release vane 124 to each other and the reference line of rotation 120D is preferably 10 ° at 50 °, and, even better, from 20 ° to 30 °. On the other hand, in the detent escapement of the prior art, the release vane 124 is fixed to be positioned on the rotational reference line (the DTN angle is 0 °).
[0037] A single leaf spring 140 capable of contacting the release vane 124 is provided on the leaf 130. The leaf spring 140 may be in the form of a leaf spring of an elastic material such as a stainless steel. The leaf spring 140 includes a base portion 140B, a deformable spring portion 140D, and a release vane contact portion 140G. It is preferable that the direction of the thickness of the plate of the deformable spring portion 140D of the leaf spring 140 is the direction perpendicular to the axial line 130A of the center of rotation of the blade 130.
With reference to FIGS. 1, 7, 7A and 8, the escape wheel 110 includes an escape wheel 109 and an escape pinion 111. The tooth 112 is formed on the outer circumferential part of the escape wheel 109. For example, as shown in fig. 1, fifteen copies of the tooth 112 are formed on the outer circumferential part of the escape wheel 109. The escape mobile 110 is incorporated in the movement to rotate relative to the plate 170 and a gear bridge (not shown ). An upper portion of the exhaust pinion shaft 111 is supported to rotate relative to the cog bridge (not shown). A lower portion of the exhaust pinion shaft 111 is supported to rotate relative to the plate 170.
The balance 120 is incorporated into the movement to rotate relative to the plate 170 and a balance bridge 180. An upper end of the balance axis 114 is supported to rotate relative to the balance bridge 180. One end balance shaft 114 is supported to rotate relative to plate 170. An inner end of hairspring 118 is attached to collar 172 which is attached to balance shaft 114. An outer end of hairspring 118 is attached to an eyebolt 175 which is attached to a eyebolt 174. The eyebolt 174 is supported to rotate only through a predetermined angle with respect to the balance bridge 180. The eyebolt 174 and the eyebolt 175 are fully rotated. relative to each other, and in this way the eyebolt is rotated relative to the balance bridge of the release pallet 124 based on the rotational reference line 120D. Therefore, the position of the release vane and the position of the impulse vane 122 can be changed relative to the rotation reference line. That is to say, according to this configuration, the position of the release pallet 124 relative to the position of the center of oscillation of the balance 120 is adjusted, and a correction of the position of the center of oscillation of the balance 120 can be done by adjusting the position of the pulse paddle 122.
[0040] In addition, it is preferable that rotatable range indicating means for indicating a range over which a movable eyebolt 175 can be rotated are provided. For example, the rotary range indicating means may be presented by a marking 183 which is provided on the balance bridge 180. The marking 183 can be formed at a multitude of positions. For example, as shown in fig. 7, the marking 183 may be arranged to include a short scale on a delay side, a scale having an intermediate length on the delay side, a scale indicating a reference, a scale having an intermediate length on the advance side, and a short graduation on the advance side. The markings 183 may be provided on the balance bridge 180 or may be provided on other parts such as the cog bridge or the barrel bridge. The markings 183 may be a graduation or an engraving and may be presented by an outline shape such as the balance bridge 180 or the gear bridge, or a cut shape.
A racket 176 for adjusting the daytime rate ("timing rate") of the timepiece is supported to be rotated only by a predetermined angle relative to the balance bridge 180. A racket pin 177 which is fixed racquet 176 is in contact with the vicinity of the outer end of hairspring 118. The position at which racquet pin 177 contacts hairspring 118 is changed by turning racquet 176, and therefore daytime walking. of the timepiece can be adjusted.
The blade 130 is incorporated into the movement to rotate relative to the plate 170 and the gear bridge (not shown). The blade 130 includes a blade body 134 and a blade axle 136. An upper portion of the blade axle 136 is supported to rotate relative to the cog bridge (not shown). A lower end of the axis of the blade 136 is supported to rotate relative to the stage 170. Alternatively, the blade 130 can be incorporated into the movement 300 to rotate relative to the stage 170 and a blade bridge (not shown). ). In this configuration, the upper end of the blade axis 136 is supported to rotate relative to a blade bridge (not shown). A spring support protrusion 130D is provided on the end of the leaf 130 near the balance 120. A release paddle contact portion 140G of the leaf spring 140 is arranged to contact the spring support protrusion 130D. .
The blade 130 is arranged to rotate in two directions, namely a direction in which the rest pallet 132 approaches the exhaust mobile 110 and a direction in which the rest pallet 132 moves away from the exhaust mobile 110. A spring 150 for applying, to the blade 130, a force which turns the blade 130 in the direction in which the rest pallet 132 approaches the exhaust mobile 110, is provided. The spring 150 may be a leaf spring of an elastic material such as stainless steel. The spring 150 includes a base portion 150B and a deformable spring portion 150D. It is preferable that the direction of the thickness of the deformable spring portion 150D of the spring 150 is in a direction perpendicular to the axis of rotation 130A of the blade 130.
The spring 150 is arranged to apply a force to the blade 130 in a level perpendicular to the axis of rotation 110A of the exhaust mobile 110. The leaf spring 140 and the spring 150 are arranged in a position in a direction which is symmetrical with respect to the center of rotation 130A of the blade 130. The direction in which the spring 150 applies a force to the blade 130 is a direction in which a part of the blade 130, on which the rest pallet 132 is planned, approach the mobile escape 110.
[0045] According to this configuration, since the spring 150 always applies a force to the blade 130, the blade 130 can return directly to the initial position shown in FIG. 1. In addition, the detent escapement of the present invention is arranged so that the spring 150 applies the force returning the blade to the initial position, which corresponds to the "pull" operation in the lever, lever escapement. 130. Therefore, the detent escapement of the present invention includes features which are not easily subjected to the influence of disturbance compared to the conventional spring detent escapement.
It is preferable that the detent escapement 100 of the present invention is configured so that the leaf spring 140 and the spring 150 include a part which is positioned in a level perpendicular to the axis of rotation 110A of the mobile d exhaust 110. According to this configuration, a thin detent escapement can be realized compared to the conventional spring detent escapement.
With reference to FIGS. 1 and 2, the leaf spring 140 is fixed to the leaf body 134 by the fixing pin 137 of the leaf spring. The eccentric pin 138 of the leaf spring for adjusting the position of the end of the leaf spring 140 is fixed to the blade body 134. The eccentric pin 138 of the leaf spring includes an eccentric shaft portion 138F, a head portion. 138H, and a fixing part 138K. The fixing part 138K is inserted to rotate in a fixing hole of the stage 170. For example, an eccentric amount of the eccentric shaft part 138F can be set to about 0.1mm to 2mm. A 138M drive groove is provided on the 138H head portion. The eccentric shaft portion 138F of the eccentric pin 138 of the leaf spring is disposed in an opening 140J of the leaf spring 140. By turning the eccentric shaft portion 138F of the eccentric pin 138 of the leaf spring, the spring of blade 140 can rotate along the upper surface of blade body 134 relative to the axial line of the center of the leaf spring fixing pin 137 as the center of rotation.
As a modification, with reference to FIG. 4, a horizontal screw 146 of the leaf spring for adjusting the position of the end of the leaf spring 140 can be provided. A support hole portion 140E of the leaf spring 140 is supported between the horizontal screw 146 of the leaf spring and a support nut 147 of the leaf spring. A screw part of the horizontal screw 146 of the leaf spring is arranged to be screwed into a female screw part which is provided on a vertical wall part 130V of the blade 130. According to this configuration, adjust the force that applies. on the leaf spring 140 at the end of the blade 130 can be carried out easily.
With reference to FIGS. 1 and 3, the spring 150 is fixed to the plate 170 by a fixing pin 157 of the balance spring. An eccentric peg 158 of the hairspring for adjusting the position of the end of the spring 150 is attached to the plate 170 (i.e., a bracket). The hairspring eccentric peg 158 includes an eccentric shaft portion 158F, a head portion 158H, and an attachment portion 158K. The fixing part 158k is inserted and fixed to a fixing hole of the plate 170. For example, the eccentric amount of the eccentric shaft part 158F can be set to about 0.1mm to 2mm. A 158M drive groove is provided on the 158H head portion. The eccentric shaft portion 158F of the hairspring eccentric pin 158 is disposed in an opening 150J of the spring 150. By turning the eccentric shaft portion 158F of the hairspring eccentric pin 158, the spring 150 can rotate along the spring 150. upper surface of the plate 170 with the axial line of the center of the fixing pin 157 of the hairspring as the center of rotation.
[0050] As a modification, the spring 150 can be arranged to be fixed relative to the plate 170 (i.e., a support) using a horizontal fixing screw (not shown) of the spring. The horizontal screw for fixing the spring may be arranged to be similar to the structure of the horizontal screw 146 of the leaf spring shown in FIG. 4. According to this configuration, the intensity of the force applied to the blade 130 can be easily adjusted. In addition, according to this configuration, since the added resistance to the balance 120 can be controlled, a control of an oscillation angle of the balance 120 can be performed.
Referring to FIGS. 1 and 5, an eccentric adjustment pin 162 for adjusting the initial position of the blade 130 is provided to rotate at the stage 170 (i.e., a holder). The eccentric adjustment pin 162 includes an eccentric shaft portion 162F, a head portion 162H, and an attachment portion 162K. The fixing part 162K is inserted to rotate at the fixing hole of the plate 170. For example, the amount of eccentricity of the eccentric shaft part 162F can be set to about 0.1mm to 2mm. The 158M drive groove is provided on the 162H head part. The eccentric shaft portion 162F of the eccentric adjustment pin 162 is arranged to contact the surface side portions of the blade 130. By turning the eccentric shaft portion 162F of the eccentric adjustment pin 162, the initial part of the blade 130 can be easily adjusted.
With reference to FIG. 1, an eccentric slip prevention peg 164 for preventing slippage of blade 130 is provided on stage 170 (i.e., a holder). The eccentric slip prevention peg 164 may be arranged to be similar to the structure of the eccentric adjustment peg 162 shown in FIG. 5. For example, the eccentric amount of the eccentric shaft portion of the slip prevention eccentric pin 164 can be set to about 0.1mm to 2mm. According to this configuration, even when the blade moves considerably parallel to the support surface by disturbance, slippage of the hairspring from the blade can effectively be prevented. By turning the eccentric shaft portion of the slip prevention eccentric pin 164, the range of motion of the blade 130 can be easily adjusted.
Referring to FIGS. 1 and 2, a receiving concave portion 130G for receiving the spring 150 is provided on the side surface of the leaf 130. A leaf contacting a portion of the spring 150 is received in the receiving concave portion 130G. In this configuration, although the spring 150 moves considerably up and down from the surface of the stage 170 (i.e., a support), slippage of the spring 150 from the leaf 130 can effectively be prevented.
Referring to FIG. 1, because the eccentric slip prevention peg 164 is provided, although the blade 130 moves considerably parallel to the surface of the stage 170 by disturbance, slippage of the spring 150 from the blade 130 can be effectively prevented.
(2) Operation of the detent escapement of the present invention
[0055] Then, with reference to FIGS. 9 to 15, the operation of the detent escapement of the present invention will be described. In fig. 9 to 15, (a) in the drawings is a plan view showing the operating state of the detent escapement, and (b) in the drawings is a view showing the impulse (torque) and resistance ( torque), with the influence on the advance of the day gear and the influence on the delay of the day gear due to the "impulse before neutral", "resistance before neutral", "impulse after neutral point ”, and“ resistance after neutral ”. Fig. 9c is a partial plan view showing a configuration in which the release vane 124 is fixed at the position which is offset in the opposite direction of the exhaust mobile 110 from the rotational reference line 120D. In fig. 9b to 15b, the horizontal axis indicates an angle of rotation of the balance 120 and the vertical axis indicates the impulse (torque) and resistance (torque) which are applied to the balance 120. Here, the influence on the advance of daytime walking is represented by hatching increasing diagonally towards the right, and the influence on the delay of daytime walking is represented by hatching decreasing diagonally towards the right. In addition, in fig. 9b to 15b, the "dead center" of the swing of the balance 120 (center of oscillation of the balance) is represented by a vertical line (solid line). In fig. 9b to 15b, a position of maximum amplitude of the balance 120 is represented by a white circle. In fig. 9b to 15b, a current position of the balance 120 is represented by a vertical line (thick solid line).
(2-1) First operation
[0056] With reference to FIG. 9a, the balance 120 performs a free oscillation, and therefore, the large plate 116 rotates in the direction of an arrow A1 (counterclockwise). With reference to FIG. 9b, the balance 120 rotates counterclockwise towards neutral (center of oscillation) from the position shown in FIG. 9a.
(2-2) Second operation
Referring to FIG. 10a, the release pallet 124 which is attached to the large platen 116 rotates in the direction of arrow A1 (counterclockwise) and the release pallet contacts the release pallet contact portion 140G leaf spring 140. Subsequently, the release vane 124 rotates in the direction of arrow A1 (counterclockwise), the leaf spring 140 is pressed to the release vane 124, and the release spring blade presses spring support protrusion 130D. In this way, the blade 130 rotates in the direction of an arrow A2 (clockwise). The end of the tooth 112 of the exhaust mobile 110 slides on the contact plane 132B of the rest pallet 132. According to the operation in which the blade 130 rotates in the direction of the arrow A2 (clockwise direction). a watch), the blade body 134 is separated from the eccentric adjustment pin 162. Referring to FIG. 10b, the balance 120 receives "resistance before neutral", and therefore receives the influence in which daytime walking is delayed. The amount by which daytime walking is delayed in the state shown in fig. 10a is smaller than the amount of which daytime walking is delayed due to Pulse after Neutral "in a state shown in fig. 11a which is generated after the state of FIG. 10a.
(2-3) Third operation
[0058] With reference to FIG. 11a, the end of the tooth 112 of the exhaust mobile 110 comes into contact with the contact plane 132B of the rest pallet 132. The exhaust mobile 110 is driven by the front gear which is driven in rotation by the torque when a mainspring is armed and the exhaust mobile 110 is driven. The exhaust mobile 110 rotates in a direction of an arrow A4 (clockwise), the end of the tooth 112 of the exhaust mobile 110 comes into contact with the impulse paddle 122, and the torque is transmitted to the balance 120. If the large chainring 116 rotates upward at a predetermined angle in the direction of arrow A1 (counterclockwise), the release pallet 124 is separated from the part. release paddle contact contact 140G of the leaf spring 140. The blade 130 is rotated in the direction of arrow A3 (counterclockwise) by the spring force of the spring 150 and returns to the original position. The end of the tooth 112 of the exhaust mobile 110, which is in contact with the contact plane 132B of the rest pallet 132, is slid from the rest pallet 132 (the exhaust mobile 110 is released). The blade 130 is rotated in the direction of arrow A3 (counterclockwise) by the spring force of the spring 150 and the blade body 134 is pushed behind in the direction of the eccentric adjustment pin 162. The balance wheel 120 receives the "pulse before neutral" and therefore receives the influence in which the daytime gear is advanced. The amount by which daytime walking is advanced in the state shown in fig. 11a is greater than the amount of which daytime walking is delayed due to the "pulse after neutral" in the state shown in fig. 10a.
(2-4) Fourth operation
[0059] With reference to FIG. 12a, continuously, the end of the tooth 112 of the exhaust mobile 110 is in contact with the impulse pallet 122, the rotational torque is transmitted to the balance 120, and the balance 120 passes through neutral (center of oscillation) and rotates. The blade body 134 of the blade 130 contacts the eccentric adjustment pin 162 by the spring force of the spring 150. The balance 120 receives a "pulse after neutral", and therefore receives the influence. in which daytime walking is delayed. The amount by which daytime walking is delayed in the state shown in fig. 12a balances the amount by which daytime walking is advanced due to the "pulse after neutral" in the state described above shown in fig. 11a.
(2-5) Fifth operation
Referring to FIG. 13a, the balance 120 performs a free oscillation in the direction of arrow A1 (anti-clockwise), and consequently, the end of the next tooth 112 of the exhaust mobile 110 falls on the plane of contact 132B of the rest pallet 132. With reference to FIG. 13b, the balance 120 oscillates more freely, and as a result, the balance 120 goes through its position of maximum amplitude. In this way, the large platen 116 rotates in a direction (clockwise) opposite to the direction of arrow A1.
(2-6) Sixth operation
[0061] With reference to FIG. 14a, the release vane 124 attached to the large platen 116 rotates in a direction of an arrow A5 (clockwise) and contacts a release vane contact portion 140G of the leaf spring 140. The release vane 124 rotates in the direction of arrow A5 (clockwise) and the leaf spring 140 is pressed against the release vane 124. At this time, the leaf spring 140 is separated from the leaf. spring support protrusion 130D of the leaf 130. Therefore, only the leaf spring 140 is pushed in a direction of an arrow A6 (counterclockwise) by the release pallet 124 in a state where the blade 130 is stationary. With reference to FIG. 14b, the balance 120 receives "resistance after neutral," and therefore receives the influence in which daytime walking is advanced. The amount by which daytime walking is advanced in the state shown in fig. 14a balances the amount of which daytime walking is delayed due to the "pulse after neutral" in the state described above shown in fig. 10a.
(2-7) Seventh operation
[0062] With reference to FIG. 15a, if the large platen 116 rotates upward at a predetermined angle in the direction of arrow A5 (clockwise), the release vane 124 is separated from the release vane contact portion 140G of the spring. blade 140. In this way, the leaf spring 140 returns to the original position and the balance 120 performs a free oscillation. With reference to a fig. 15b, the pendulum 120 more freely oscillates, and therefore the pendulum 120 rotates in the direction of the next maximum amplitude position.
(2-8) Repeat the operation
[0063] Hereinafter, similarly, the operations from the state shown in FIG. 9 in the state shown in FIG. 15 can be repeated. As described above, the amount by which daytime walking is delayed in the state shown in fig. 12a balances the amount by which daytime walking is advanced due to the "pulse after neutral" in the state shown in fig. 11a. In addition, the amount of which the daytime walking is delayed in the state shown in fig. 14a is balanced with the amount by which the diurnal rate is advanced due to the "momentum after neutral" in the state described above shown in fig. 10a. Further, preferably, the total sum of the amount by which daytime walking is delayed in the state shown in fig. 12a and the amount of which daytime walking is delayed in the state shown in fig. 14a is configured to swing with the total sum of the quantity by which the diurnal rate is advanced in the state shown in fig. 11a, the amount by which daytime walking is advanced in the state shown in fig. 14a, and the amount by which daytime walking is advanced in the state described above shown in fig. 10a. Depending on the configuration, the detent escapement of the present invention can be configured so that the error due to the exhaust decreases significantly compared to the conventional detent escapement.
(2-9) Preferred configuration of the detent escapement of the present invention
[0064] In the detent escapement of the present invention, it is preferable that the release vane 124 is fixed at a position towards the direction which is away from the exhaust mobile 110 based on the rotational reference line 120D. Further, in the detent escapement of the present invention, it is preferable that the release vane 124 is fixed between a position in which the release vane is rotated 10 ° from the rotational reference line 120D and a position wherein the release vane is rotated 50 ° from the rotational reference line 120D towards the direction which is away from the exhaust mobile 110. Further, in the detent escapement of the present invention, it is still preferable that the release pallet 124 is fixed at a position in which the release pallet is rotated approximately 30 ° from the rotational reference line 120D towards the direction which is away from the exhaust mobile 110.
(3) Detent escapement operation of comparison example 1
Next, an operation of a detent escapement of Comparison Example 1 will be described with reference to FIGS. 23 to 30. The detent escapement configuration of Comparative Example 1 corresponds to the configuration of the conventional detent escapement, and includes a balance wheel that is configured in a neutral position in which daytime running is delayed. In fig. 23 to 30, (a) in the drawings is a plan view showing the operating state of the detent escapement, and (b) in the drawings is a view showing the pulse (torque) and resistance ( torque), with the influence on the advance of the day gear and the influence on the delay of the day gear due to the "impulse before neutral", "resistance before neutral", "impulse after neutral point ”, and“ resistance after neutral ”.
[0066] With reference to FIG. 23c, a straight line passing through a 130CG center of rotation of a 130G blade with a 120CG center of rotation of a 120G balance wheel as a starting point in a state where the 120G balance wheel is positioned at a center of oscillation is set as the 120DG rotation reference line. Fig. 23c is a partial plan view showing a configuration in which the release pallet 124G is fixed at a position on the rotational reference line 120DG. In fig. 23b to 30b, the horizontal axis indicates an angle of rotation of the 120G balance and the vertical axis indicates the momentum (torque) and resistance (torque) that are applied to the 120G balance. Here, the influence on the diurnal gait advance is represented by hatching increasing diagonally to the right, and the influence on the diurnal gait delay is represented by the hatching decreasing diagonally to the right. In addition, in fig. 23b to 30b, the "neutral point" of the 120G balance wheel oscillation (balance center of oscillation) is represented by a vertical line (solid line). In fig. 23b to 30b, a maximum amplitude position of the 120G balance wheel is represented by a white circle. In fig. 23b to 30b, a current position of the balance 120G is represented by a vertical line (thick solid line).
(3-1) First operation
[0067] With reference to FIG. 23a, the 120G balance wheel oscillates freely, and therefore, a large chainring 116G rotates in a direction of an arrow A1 (counterclockwise). With reference to FIG. 23b, the 120G balance wheel rotates counterclockwise towards neutral (center of oscillation) to a position shown in fig. 9a.
(3-2) Second operation
Referring to FIG. 24a, the release pallet 124G which is attached to the large platen 116G rotates in the direction of arrow A1 (counterclockwise) and the release pallet contacts the release pallet contact portion of the 140G leaf spring.
(3-3) Third operation
Referring to FIG. 25a, subsequently, the release vane 124G rotates in the direction of arrow A1 (counterclockwise), the leaf spring 140G is pressed against the release vane 124G, and the leaf spring presses the protrusion spring support. In this way, the blade 130G rotates in the direction of the arrow A2 (clockwise). The end of the tooth of the exhaust mobile 110 slides on the contact plane of the rest pallet 112G. According to the operation in which the 130G blade rotates in the direction of the arrow A2 (clockwise), the blade body is separated from the eccentric adjustment pin. With reference to FIG. 25b, the 120G balance receives "resistance after neutral," and therefore, the balance receives the influence in which daytime walking is advanced. The amount by which daytime walking is delayed in the state shown in fig. 25a is smaller than the amount of which daytime walking is delayed due to "pulse after neutral" in a state shown in fig. 26a which is generated after the state of fig. 25a.
(3-4) Fourth operation
Referring to FIG. 26a, the end of the tooth of the exhaust mobile 110G comes into contact with the contact plane of the rest pallet 112G. The 110G mobile exhaust is driven by the front gear, which is driven by torque when the mainspring is charged and the 110G exhaust mobile is driven. The 110G exhaust mobile rotates in the direction of the arrow A4 (clockwise), the tooth end of the 110G exhaust mobile comes into contact with the 112G impulse paddle, and the torque of rotation is transmitted to the 120G balance. If the large chainring 116G rotates upward at a predetermined angle in the direction of arrow A1 (counterclockwise), the release vane 124G is separated from the release vane contact portion of the leaf spring. 140G. The blade 130G rotates in the direction of arrow A3 (counterclockwise) by the spring force of the spring 150G and returns to the original position. The end of the tooth of the 110G exhaust mobile, which contacts the contact plane B of the 112G rest pallet, is slid from the 112G rest pallet (the 110G exhaust mobile is released). The blade 130G rotates in the direction of arrow A3 (counterclockwise) by the spring force of the spring 150G and the blade body is pushed behind towards the eccentric adjustment pin. The 120G balance receives the "pulse after neutral" and therefore receives the influence in which daytime walking is delayed. The amount by which daytime walking is delayed in the state shown in fig. 26a is greater than the amount of which the diurnal rate advances due to "resistance after neutralization" in the state shown in fig. 25a.
(3-5) Fifth operation
Referring to FIG. 27a, the 120G balance wheel freely oscillates in the direction of arrow A1 (counterclockwise), and therefore the 120G balance wheel rotates to the maximum amplitude position of the 120G balance wheel.
(3-6) Sixth operation
[0072] With reference to FIG. 28a, the 120G balance oscillates more freely, and as a result, the 120G balance wheel passes through the maximum amplitude position of the 120G balance. In this way, the large chainring 116G rotates in the direction of arrow A5 (clockwise). The release vane 124G which is attached to the large chainring 116G rotates in the direction of arrow A5 (clockwise) and the release vane contacts the release vane contact portion of the leaf spring. 140G. The release vane 124G rotates in the direction of arrow A5 (clockwise) and the leaf spring 140G is pressed to the release vane 124G. At this time, the leaf spring 140G is separated from the leaf spring support protrusion 130G. Therefore, only the leaf spring 140G is pushed towards the direction of arrow A6 (counterclockwise) by the release pallet 124G in a state where the leaf 130G is stationary. With reference to FIG. 28b, the 120G balance receives "resistance before neutral," and therefore receives the influence in which the speed of time is retarded.
(3-7) Seventh operation
[0073] With reference to FIG. 29a, the balance 120G performs a free oscillation in the direction of the arrow A5 (clockwise), and consequently, the end of the next tooth of the exhaust mobile 110G falls on the contact plane of the 112G rest pallet. The end of the tooth of the 110G exhaust mobile comes into contact with the 112G impulse paddle, the rotational torque is transmitted to the 120G balance, and the 120G balance passes through neutral (center of oscillation) and turns . The blade body of the 130G blade contacts the eccentric adjustment pin by the spring force of the 150G spring. The 120G balance receives "resistance after neutral," and therefore receives the influence in which daytime walking is advanced. The amount by which daytime walking is advanced in the state shown in fig. 29a is smaller than the amount by which daytime walking is advanced due to "pulse after neutral" in the state described above shown in fig. 26a.
(3-8) Eighth operation
[0074] With reference to FIG. 30a, the 120G balance wheel more freely oscillates, and therefore the 120G balance wheel rotates in the direction of the next dead center.
(3-9) Repeating an operation
[0075] Hereinafter, similarly, the operations from the state shown in FIG. 23 until the state shown in fig. 30 are repeated. As described above, the amount by which daytime walking is delayed in the state shown in fig. 26a is greater than the amount by which daytime walking is advanced due to the "resistance after neutralization" in the state shown in fig. 25a. In addition, as described above, the amount of which the daytime walking is delayed in the state shown in fig. 26 (a) is greater than the amount by which daytime walking is advanced due to "resistance after neutralization" in the state shown in fig. 28a. In addition, a value which adds the amount by which the daytime march is delayed in the state shown in fig. 26a and the amount of which daytime walking is delayed due to "resistance before neutral" in the state shown in fig. 28a is greater than a value which adds up the amount by which the diurnal rate is advanced due to "resistance after neutral" in the state shown in fig. 25a and the amount by which daytime walking is advanced due to "resistance after neutralization" in the state shown in fig. 29a. Therefore, in the detent escapement of Comparison Example 1, the influence in which the daytime running is delayed is large, and an error due to the escapement is major compared to the detent escapement of the present. invention.
(4) Operation of the detent escapement of Comparison Example 2
Next, an operation of a detent escapement of a comparison example 2 will be described with reference to FIGS. 31 to 37. The configuration of a detent escapement of Comparison Example 2 includes a balance that is configured in a neutral position in which daytime gear is advanced. In fig. 31 to 37, (a) in the drawings is a plan view showing the operating state of the detent escapement of the comparative example, and (b) in the drawings is a view showing the pulse ( torque) and resistance (torque), with the influence on the advance of the daytime running and the influence on the delay of the daytime running due to the "pulse before neutral", "resistance before the point dead "," pulse after neutral ", and" resistance after neutral ". Fig. 31c is a partial plan view showing a configuration in which a release pallet 124H is fixed at the 60 ° position in a counterclockwise direction from a rotational reference line 120DH in a position towards a remote direction of a 110H exhaust mobile based on the 120DH rotation reference line. In fig. 31b to 37b, a horizontal axis indicates an angle of rotation of a 120H balance and a vertical axis indicates the impulse (torque) and resistance (torque) which are applied to the 120H balance. Here, the influence on the diurnal gait advance is represented by hatching increasing diagonally to the right, and the influence on the diurnal gait delay is represented by the hatching decreasing diagonally to the right. In addition, in fig. 31b to 37b, the "dead center" of the 120H balance wheel oscillation (center of oscillation of the balance) is represented by a vertical line (solid line). In fig. 31b to 37b, a position of maximum amplitude of the 120H balance wheel is represented by a white circle. In fig. 31b to 37b, a current position of the 120H balance wheel is represented by a vertical line (thick solid line).
(4-1) First operation
[0077] With reference to FIG. 31a, the 120H balance wheel performs a free oscillation, and therefore a large 116H chainring rotates in the direction of the arrow A1 (counterclockwise). With reference to FIG. 31b, the 120H balance wheel rotates counterclockwise to neutral (center of oscillation) from the position shown in fig. 31a.
(4-2) Second operation
Referring to FIG. 32a, the release pallet 124H which is attached to the large platen 116H rotates in the direction of arrow A1 (counterclockwise) and the release pallet contacts a contact portion of the release pallet d. 'a 140H leaf spring. Subsequently, the 124H release vane rotates in the direction of arrow A1 (counterclockwise), the 140H leaf spring is pressed against the 124H release vane, and the leaf spring presses the supporting protrusion. spring. In this way, the blade 130H rotates in the direction of the arrow A2 (clockwise). The end of the tooth of the 110H escapement unit slides on the contact plane of the 132H rest pallet. According to the operation in which the 130H blade rotates in the direction of the arrow A2 (clockwise), the blade body is separated from the eccentric adjustment pin. With reference to FIG. 32b, the 120H balance receives "resistance before neutral," and therefore the balance receives the influence in which daytime walking is delayed. The amount by which daytime walking is delayed in the state shown in fig. 32a is smaller than the amount by which daytime walking is advanced due to a "pulse before neutral" in a state shown in fig. 33a which is generated after the state of fig. 32a.
(4-3) Third operation
Referring to FIG. 33a, the end of the tooth of the exhaust mobile 110H comes into contact with the contact plane of the rest pallet 132H. The 110H mobile exhaust is driven by the front gear which is driven by the torque when the mainspring is charged and the 110H mobile exhaust is driven. The 110H exhaust mobile rotates in the direction of the arrow A4 (clockwise), the tooth end of the 110H exhaust mobile comes into contact with the 122H pulse vane, and the torque rotation is transmitted to the 120H balance. If the large chainring 116H rotates upward at a predetermined angle in the direction of arrow A1 (counterclockwise), the release vane 124H is separated from the release vane contact portion of the leaf spring. 140H. The 130H blade is rotated in the direction of the arrow A3 (counterclockwise) by the spring force of a 150H spring and returns to the original position. The end of the tooth of the exhaust mobile 110H, which comes into contact with the contact plane of the rest pallet 132H, is away from the rest pallet 132H (the exhaust mobile 110 is released) . The blade 130H is turned in the direction of arrow A3 (counterclockwise) by the spring force of the spring 150H and the blade body is pushed back towards the eccentric adjustment pin. The 120H balance receives a "push before neutral" and therefore the balance receives the influence in which daytime gear is advanced. The amount by which daytime walking is advanced in the state shown in fig. 33a is greater than the amount of which daytime walking is delayed due to "resistance before neutral" in the state shown in fig. 32a.
(4-4) Fourth operation
[0080] With reference to FIG. 34a, continuously, the end of the tooth of the exhaust mobile 110H is in contact with the pulse paddle 122H, the rotational torque is transmitted to the 120H balance, and the 120H balance goes through neutral (center of oscillation) and rotates. The blade body of the 130H blade contacts the eccentric adjustment pin by the return force of the 150H spring.
(4-5) Fifth operation
[0081] With reference to FIG. 35a, the 120H balance wheel performs a free oscillation in the direction of the arrow A1 (anti-clockwise), and consequently, the end of the next tooth of the exhaust mobile 110H falls on the contact plane of the 132H rest pallet.
(4-6) Sixth operation
[0082] With reference to FIG. 36b, the 120H balance oscillates more freely, and as a result, the 120H balance crosses at the maximum amplitude position of the 120H balance. In this way, the large chainring 116H rotates in the direction (clockwise) opposite to the direction of arrow A1. The release vane 124H which is attached to the large chainring 116H rotates in the direction of arrow A5 (clockwise) and the release vane contacts the release vane contact portion of the leaf spring. 140H. The 124H release vane rotates in the direction of arrow A5 (clockwise) and the 140H leaf spring is pressed to a 124H release vane. At this time, the leaf spring 140H is separated from the leaf spring support protrusion 130H. Therefore, only the leaf spring 140H is pushed towards the direction of arrow A6 (counterclockwise) by the release vane 124H in a state where the leaf 130H is stationary. With reference to FIG. 36b, the 120H balance receives "resistance after neutral," and therefore receives the influence in which the speed of time is advanced. The amount by which daytime walking is advanced in the state shown in fig. 36a is smaller than the amount by which daytime walking is advanced due to a "pulse before neutral" in the state described above shown in fig. 33a.
(4-7) Seventh operation
Referring to FIG. 37a, if the large chainring 116H rotates upward at a predetermined angle in the direction of arrow A5 (clockwise), the release vane 124H is separated from the spring release vane contact portion. 140H blade. In this way, the leaf spring 140H returns to the original position and the balance 120H performs a free oscillation. With reference to FIG. 37b, the 120H balance wheel performs more free oscillation, and therefore the 120H balance wheel rotates to the next maximum amplitude position.
(4-8) Repeating an operation
[0084] Hereinafter, similarly, the operations of the state shown in FIG. 31 in the state shown in fig. 37 can be repeated. As described above, the amount by which daytime walking is delayed in the state shown in fig. 33a is greater than the amount by which daytime walking is delayed in the state shown in fig. 32a. In addition, the amount of which the daytime walking is delayed in the state shown in fig. 33a is greater than the amount by which daytime walking is delayed in the state shown in fig. 36a. In addition, the amount by which daytime walking is advanced in the state shown in fig. 33a is greater than a value which adds up the quantity of which the diurnal rate is delayed in the state shown in fig. 32a and the value of an influence in which the daytime walking is delayed in the state shown in fig. 36a. Therefore, in the detent escapement of Comparison Example 2, the influence in which the daytime running is advanced is large, and an error due to the escapement is major compared to the detent escapement of the present. invention.
(5) Comparison and review results of a detent escapement operation of the present invention and an example comparison operation
With reference to FIGS. 18a and 19a, in the detent escapement of Comparative Example 1 corresponding to the configuration of the conventional detent escapement, the influence in which daytime running is delayed is greater than the influence in which running daytime is advanced. In the configuration of Comparison Example 1, generally, in the case where a significant delay in daytime running is generated, after the balance wheel passes through the neutral position, the resistance (torque) which is applied to the balance wheel by the output of the blade and the impulse (torque) which are applied to the balance from the escapement mobile are generated and terminated. On the other hand, in the configuration of Comparison Example 1, the resistance (torque) which is applied to the balance by the leaf spring output is generated before the balance passes through the neutral position.
Referring to FIGS. 18b and 19b, an embodiment (corrected example) of the detent escapement of the present invention is configured so that the influence in which daytime walking is delayed is equal to the influence in which daytime walking is advanced. That is, in the embodiment of the present invention, generally, the influence in which daytime walking is delayed and the influence in which daytime walking is advanced are fully compensated. In the embodiment of the present invention, the resistance (torque) that is applied to the balance is generated by the exit of the blade, and the resistance ends before the balance goes through the neutral position. In the impulse (torque) which is applied to the balance from the escapement rotor, the balance passes through the neutral position in the row in which the impulse (torque) is generated. On the other hand, in the embodiment of the present invention, the resistance (torque) which is applied to the balance by the output of the leaf spring is generated after the balance passes through the neutral position.
With reference to FIGS. 18c and 19c, in the detent escapement of Comparison Example 2 including the balance in which the release pallet is fixed at the position of 60 ° counterclockwise from the reference line of rotation in the position towards the direction away from the exhaust mobile based on the rotation reference line, the influence in which the daytime walking is delayed is smaller than the influence in which the daytime walking is advanced. In the configuration of Comparison Example 2, generally, in the case where a significant advance of the daytime gear is generated, before the balance wheel crosses in the neutral position, the resistance (torque) which is applied to the balance wheel by the output of the blade and the impulse (torque) which is applied to the balance from the escape wheel set are generated and terminated. On the other hand, in the configuration of a comparison example 2, the resistance (torque) which is applied to the balance by the exit of the leaf spring is generated after the balance passes through the neutral position.
(6) Results of tests of an extended model
[0088] Compared to the detent escapement of the present invention, an enlarged model of the escapement part, which is configured to be of an enlarged size compared to a size of a general watch, has been prepared, and the comparison test was performed.
(6-1) Size of the enlarged model
The sizes of the main components in the extended model are as follows.Diameter of a mobile exhaust: 41 mm;Moment of inertia of the balance: 5.329 * 10 <–> <5> kg · m <2>;Diameter of a path of one end of a clearance pallet: 7.19 mm;Diameter of a path of one end of an impulse vane: 27.39 mm;Central distance between a center of rotation of a mobile escapement and a center of rotation of a balance: 33.2 mm;Central distance between a center of rotation of a balance and a center of rotation of a blade: 56.32 mm;Length of a straight line part of a spring part of a leaf spring: 32.15 mm;Angle of impact: 34 °;Distance from a position of the pendulum to a center of rotation in which a release paddle receives resistance from a leaf of a leaf spring: 7.07 mm.
(6-2) Graph showing test results
[0090] With reference to FIG. 16, fig. 16 is a graph showing test results of the enlarged model of the exhaust. In fig. 16, under the above conditions, the neutral position of the balance is changed to three parameters of 0 ° (previous corresponding position), + 20 ° (position corresponding to an example corrected in the embodiment of the present invention) , and –20 ° (comparison example which is set in the direction opposite to an example corrected in the embodiment of the present invention), in each of the neutral positions, the pulse torque which receives from the mobile d The escapement and the change of period of the balance wheel are shown when the impulse torque receiving from the exhaust mobile is changed at eight points from 0.403 [mN · m], 0.3628 [mN · m], 0.3225 [mN · m] , 0.282 [mN · m], 0.2419 [mN · m], 0.202 [mN · m], 0.1613 [mN · m], and 0.1209 [mN · m]. In fig. 16, the horizontal axis shows the torque [mN · m] of the escapement rotor, and the vertical axis shows the average period (seconds) of the balance.
(6-3) Extended model test evaluation reference
In the test of the extended model, when the correction of the neutral position with respect to the period of oscillation of a free damping of the balance is carried out in each of the values of the impulse torques that the balance receives from the mobile escapement, it is confirmed whether or not the change in the period of oscillation of the balance wheel can be eliminated to become smaller.
(6-4) Test evaluation results of an extended model
As a result of the test of the enlarged model, it was confirmed that the change in the period of oscillation of the balance could be suppressed to be smaller compared to the period of oscillation of the free damping of the balance by correcting the neutral position of the balance at + 20 °. In addition, it was confirmed that there was an effect suppressing the change of the balance period of oscillation according to the change of torque by correcting the neutral position of the balance to + 20 °.
On the other hand, if the neutral position of the balance is set to –20 °, the change in the period of oscillation of the balance with respect to the period of oscillation of the free damping of the balance becomes larger, and it was confirmed that the change of the period of oscillation of the balance wheel according to the change of torque also becomes larger.
(7) Results of a simulation
[0094] With respect to the detent escapement of the present invention, a simulation model was designed and a comparison and review thereof was carried out.
(7-1) Equation of motion
[0095] An equation of motion showing a free oscillation of a friction system and a viscosity system of one degree of freedom is indicated by the following equation 1.
[0096] [Equation 1]
θ: angle of rotation of a balance (rad); I: moment of inertia of a balance (kg · mm <2>); F: viscosity coefficient (kg m <2> / s); K: spring constant of a balance-spring (kg m <2> / s <2>); R: solid frictional resistance (kg m <2> / s <2>); T: total sum of an impulse torque from an escapement mobile, an extended blade which is received by a balance, and a resistance torque at the exit moment of a leaf spring which are applied to the balance during a period (kg m <2> / s <2>).
A simulation model in which the setting to which T is given as a function of 8 and (resistance / pulse components before and after neutral) are generated while a period was changed, was prepared, and the simulation of the operation of the exhaust was carried out.
(7-2) Size of a simulation model
[0098] The size of each component is adjusted to approximately match the size of the component of the general watch.Number of teeth of an escapement unit: 15;Resistance torque which is received by a balance when the blade comes out: 0.252 * 10 <–> <6> N · m;Resistance torque which is received by a balance at the time of the exit of a leaf spring: 0.044 * 10 <–> <6> N · m.
(7-3) Graph showing results of a simulation
[0099] FIG. 17 is a graph showing the results of a simulation of the exhaust simulation model. In fig. 17, under the conditions described above, the corrected neutral positions of the balance wheel are changed to three parameters of + 10 °, + 30 °, and + 50 °, and the results in which the values of the diurnal rate of the timepiece (number of seconds in which the timepiece is delayed or advanced during a day: second / day) when the angle of oscillation of the balance wheel is 200 ° or more are simulated with a value of 50 seconds / day are represented. In fig. 17, the horizontal axis shows the angle of oscillation (in degrees) of the balance and the vertical axis shows the diurnal rate (in seconds / day) of the timepiece.
(7-4) Reference of an evaluation of a simulation
[0100] In the simulation, it is confirmed whether or not the daytime running of the timepiece (number of seconds in which the timepiece is delayed or advanced during a day: second / day) is 50 seconds / day when the swing angle of the balance is 200 ° or more.
(7-5) Results of an evaluation of a simulation
[0101] As a result of a simulation, by correcting the neutral position of the balance to be set between + 10 ° and + 50 °, it was confirmed that the daytime running of the timepiece could be 50 seconds / day when the swing angle of the balance wheel was 200 ° or more.
(7-6) Conclusion of test results and simulation results
[0102] From the test results and the simulation results, it was confirmed that the corrected amount of the neutral position of the balance wheel could be set from + 10 ° to + 50 ° as a range which satisfies general daytime running. and practical (the daytime running of the timepiece is 50 seconds / day when the angle of oscillation of the balance is 200 ° or more). In addition, from the test results and simulation results, it was confirmed that the correction range + 20 ° to + 30 ° was an appropriate range as the amount of correction of the general neutral position of the balance wheel. Further, also from the results in which the same simulation was performed in values other than the value described above of the resistance torque received by the balance wheel, it is confirmed that + 20 ° to + 30 ° is an appropriate range. as a quantity corrected for the neutral position of the balance.
(8) Mechanical timepiece including a detent escapement of the present invention
[0103] In addition, in the present invention, the mechanical timepiece is arranged to include the mainspring which is a source of driving the mechanical timepiece, the front gear which is driven by a torque of rotation when the mainspring is charged, and the exhaust to control the rotation of the front gear, in which the exhaust is arranged as the detent escapement. According to this configuration, an error due to the escapement is significantly small, and the mechanical timepiece having improved transmission efficiency of the escapement force can be realized. Further, in the mechanical timepiece of the present invention, the mainspring can be smaller, or a durable mechanical timepiece can be made using a barrel drum of the same size.
[0104] With reference to FIGS. 7 and 7A, the movement 300 includes the plate 170 which forms the support of the movement 300. A winding rod 310 is disposed in the "three o'clock direction" of the movement 300. The winding rod 110 is movably incorporated in a plate winding rod indicating hole 170. The detent escapement which includes the balance 120, the escapement mobile 110, and the blade 130 and the front gear which includes a second mobile 327, a third mobile 326 , a center movable 325, and a movement barrel 320 are disposed on the "front side" of the movement 100. A switching mechanism (not shown) which includes an adjustment lever, a rocker, and a rocker support is provided. on the "back side" of movement 300. Additionally, a barrel bridge (not shown) which movably supports the upper part of the axis of movement barrel 320, a cog bridge (not shown) which supports movably the upper part of the axis of the three th mobile 326, the upper part of the axis of the second mobile 327, and the upper part of the axis of the escape wheel 110, a blade bridge (not shown) which movably supports the upper part of the The axis of the blade 130, and a balance bridge 180 which movably supports the upper part of the balance 120 are disposed on the "front side" of the movement 300.
[0105] The center mobile 325 is arranged to be rotated by the rotation of the movement barrel 320. The center mobile 325 includes a center wheel and a center pinion. A barrel drum wheel is arranged to be engaged with the center pinion. The third mobile 326 is arranged to be rotated by the rotation of the center mobile 325. The third mobile 326 includes a third wheel and a third pinion. The second mobile 327 is arranged to rotate once per minute as a result of the rotation of the third mobile 326. The second mobile 327 includes a second wheel and a second pinion. The third wheel is arranged to be engaged with the second pinion. According to the rotation of the second mobile 327, the escape wheel 110 is arranged to rotate while being controlled by the blade 130. The escape wheel 110 includes an escape wheel and an escape pin. The second wheel is arranged to be engaged with the escapement pin. A minute wheel 329 is arranged to rotate according to the rotation of the movement barrel 320. The movement barrel 320, the center mobile 325, the third mobile 326, the second mobile 327, and the minute wheel 329 form the front gear .
[0106] A minute wheel 340 is arranged to be rotated based on the rotation of a carriageway 329 which is mounted on the center mobile 325. An hour wheel (not shown) is arranged to be rotated based on the rotation of the minute wheel 340. According to the rotation of the center mobile 325, the third mobile 326 is arranged to be rotated. According to the rotation of the third mobile 326, the second mobile 327 is arranged to rotate once per minute. The hour wheel is arranged to rotate once every twelve hours. A sliding mechanism is provided between the center mobile 325 and the roadway 329. The center mobile 325 is arranged to rotate once per hour.
Industrial applicability
[0107] The detent escapement of the present invention can be configured so that the error due to the exhaust is significantly reduced. In addition, the mechanical timepiece of the present invention is not easily subjected to the influence of a disturbance. Therefore, the detent escapement of the present invention can be widely applied to a mechanical watch, a maritime chronometer, a mechanical clock, a mechanical wall timepiece, a large street mechanical timepiece, a tourbillon which uses the detent escapement of the present invention, a watch having the detent escapement of the present invention, or the like.

权利要求:
Claims (6)
[1]
1. Timepiece detent escapement (100), which includes:an escape wheel (110) having teeth (112) forming a toothing,a beam (120) having a pulse pallet (122) arranged to cooperate with each tooth (112) of the toothing and a release pallet (124), anda trigger formed by a blade (130) and having a rest pallet (132) arranged to cooperate with each tooth (112) of the toothing, and a leaf spring (140) provided on the blade (130), and arranged to cooperate with the release pallet (124),wherein a resistance before the dead point is that one end of the leaf spring is in contact with the balance release pallet and applies resistance to the balance before the balance passes through a neutral position,wherein a pulse before the dead point is the fact that the tooth of the escapement mobile is in contact with the pendulum pulse pallet and applies a force relative to a direction of advance of the balance before the balance passes through the dead point,in which an impulse after the dead point is the fact that the tooth of the escape wheel pushes the pendulum pulse pallet and applies a force relative to a direction of advance of the pendulum after the pendulum has passed through the point deathin which a resistance after the neutral position is that the end of the leaf spring is in contact with the balance clearing pallet and applies resistance to the balance after the balance has passed through the neutral position, and the fact that the end of the leaf spring is in contact with the armature release pallet and applies resistance to the pendulum after the balance has passed through the neutral position, then returned to the neutral position, then returned to neutral,wherein a rotation reference line (120D) is a straight line which passes through a center of rotation (130A) of the blade (130) and a center of rotation (120C) of the beam (120), andwherein, in a state where the rocker (120) is in neutral position, the release pallet (124) is offset in the opposite direction to the escapement wheel (110) from the rotational reference line (120D). ) so that the sum total of the influences that advance the diurnal walk of the timepiece, including the sum of the influence on the rotary movement of the balance that is generated by a pulse before the dead point and the influence on the rotary movement of the balance which is generated by a resistance after the neutral point, and the sum total of the influences which delay the diurnal march of the timepiece, including the sum of the influence on the rotary movement of the pendulum which is generated by a resistance before the neutral point and the influence on the rotary movement of the balance which is generated by a pulse after the neutral point, balance each other.
[2]
A detent escapement according to claim 1, wherein the release pallet (124) is attached to a position in which, in a state where the rocker (120) is in neutral, the release pallet is rotated by 10 degrees. ° at 50 ° to the rotation reference line (120D) in the opposite direction to the escapement (110).
[3]
An expansion escapement according to claim 1, wherein the release pallet (124) is attached to a position in which, in a state where the rocker (120) is in neutral position, the release pallet is rotated 20 At 30 ° with respect to the rotational reference line (120D) in the opposite direction to the escape wheel (110).
[4]
4. Mechanical timepiece, including a mainspring which forms a driving source of the mechanical timepiece, a gear train which is driven by a torque when the mainspring is armed, and an escapement for check the rotation of the gear train, wherein the exhaust is according to claim 1.
[5]
The mechanical timepiece of claim 4, wherein the balance (120) includes a hairspring (118), an outer end of the hairspring (118) is attached to a pin (175) which is arranged to be rotatable relative to a pendulum bridge, the mechanical timepiece being arranged to change the position of the release pallet (124) and the position of the impulse pallet (122) relative to the rotational reference line ( 120D) by turning the peak (175) relative to the balance bridge.
[6]
The mechanical timepiece of claim 5, further comprising: rotating range indicating means for indicating a range on which the pin can be rotated.

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同族专利:

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公开号 | 公开日

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CN102870049B|2014-03-05|

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WO2011111250A1|2011-09-15|

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JP2011185849A|2011-09-22|

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US20130070571A1|2013-03-21|

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US8807827B2|2014-08-19|

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CN102870049A|2013-01-09|

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JP5441168B2|2014-03-12|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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JP2010053313A|JP5441168B2|2010-03-10|2010-03-10|Detent escapement and mechanical watch|

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PCT/JP2010/064819|WO2011111250A1|2010-03-10|2010-08-31|Detent escapement and mechanical clock|

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