CN105404130B - Constant force mechanisms, machine core and clock and watch - Google Patents
Constant force mechanisms, machine core and clock and watch Download PDFInfo
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- CN105404130B CN105404130B CN201510551824.2A CN201510551824A CN105404130B CN 105404130 B CN105404130 B CN 105404130B CN 201510551824 A CN201510551824 A CN 201510551824A CN 105404130 B CN105404130 B CN 105404130B
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- G—PHYSICS
- G04—HOROLOGY
- G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
- G04B1/00—Driving mechanisms
- G04B1/10—Driving mechanisms with mainspring
- G04B1/22—Compensation of changes in the motive power of the mainspring
- G04B1/225—Compensation of changes in the motive power of the mainspring with the aid of an interposed power-accumulator (secondary spring) which is always tensioned
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Abstract
The present invention provides constant force mechanisms, machine core and clock and watch, can fully ensure the deflection of torque adjustment spring, it can be ensured that good accuracy of timekeeping.Constant force mechanisms have: powershift portion (11) are assembled into from the train (70) that the barrel as power source takes turns to release catch (60)；Oscillating rod (20), powershift portion (11), which are supported to, to be rotated around first axle (C1)；And period control mechanism (30), stopping wheel (31) are included, can be rotated and being passed power (movement torque) from driving wheel on barrel；Spring (40) are used in torque adjustment, drive release catch (60) using flexible generation active force；And engaging portion (39), it is acted by torque adjustment with spring (40) and locking with stopping wheel (31), the period control mechanism (30) rotates oscillating rod (20) intermittently.
Description
Technical field
The present invention relates to constant force mechanisms, machine core and clock and watch.
Background technique
In mechanical clock, when being transferred to the torque of release catch from the driving wheel on barrel as power source according to the hair of driving wheel on barrel
The loose winding (volume I solution け) of item and when changing, the pivot angle of hair-spring balance changes and daily rate degree changes.Therefore,
In order to inhibit the variation for the torque for being transferred to release catch, proposes one kind and adjusted between driving wheel on barrel and release catch configured with torque
With the constant force mechanisms of spring.
For example, constant force mechanisms described in patent document 1 have: fast pulley；Frame arm (Carriage arm), with fixation
It is rotated centered on the axle center of wheel；And torque adjustment spring, link via link mechanism and frame arm.1 institute of patent document
The constant force mechanisms stated are using the leaf spring of strip as torque adjustment spring.
But release catch is passed by the torque of the active force generation of torque adjustment spring and is driven.Therefore, because turning round
Rate of torque ripple caused by the variation of the active force of square adjustment spring produces bigger effect accuracy of timekeeping.
Patent document 1: No. 6948845 specifications of U.S. Patent No.
But since in the prior art, torque adjustment is formed with spring by leaf spring, therefore, it is impossible to ensure enough scratch
The change in torque of Qu Liang, per unit deflection become larger.Accordingly, there exist following worries: in constant force mechanisms movement, because torque adjusts
Rate of torque ripple caused by variation with the active force of spring becomes larger, and accuracy of timekeeping reduces.
Summary of the invention
Therefore, the present invention is to complete in view of the above problems, and project is, torsion can be fully ensured by providing one kind
The deflection of spring is used in square adjustment, and can ensure the constant force mechanisms, machine core and clock and watch of good accuracy of timekeeping.
In order to solve above-mentioned problem, constant force mechanisms of the invention are characterized in that having: powershift portion, by group
In the train from power source to release catch；Oscillating rod, the powershift portion, which is supported to, to be rotated around first axle；
And period control mechanism, stopping wheel is included, power is passed from the power source and can rotate；Torque adjustment is used
Spring drives the release catch using flexible generation active force；And engaging portion, by the torque adjustment spring
It is acted and locking with the stopping wheel, the period control mechanism rotates the oscillating rod intermittently.
According to this structure, due to having using the flexible torque adjustment spring for generating active force, with the prior art
It compares, can fully ensure the deflection of torque adjustment spring.Thereby, it is possible to inhibit torque adjustment spring because of effect
Therefore rate of torque ripple caused by the variation of power can be stably driven with release catch.Therefore, be capable of forming can ensure that it is good
The constant force mechanisms of accuracy of timekeeping.
In addition, being characterized in that, the period control mechanism has the upper arm member, and the upper arm member and the oscillating rod link,
And the engaging portion is supported to and can be rotated around the second axis, the torque adjustment spring and the upper arm member link, and
Apply active force around second axis.
According to this structure, since period control mechanism has the upper arm member with oscillating rod connection, by appropriately designed
The linking portion of oscillating rod and the upper arm member can arbitrarily set the rotational angle of oscillating rod, the rotational angle of the upper arm member, constant force
The period etc. of mechanism.In particular, only passing through the setting number of teeth in the case where oscillating rod and the upper arm member are interlinked by teeth portion
Than, oscillating rod and length of the upper arm member etc., it will be able to easily set the rotational angle of oscillating rod, the rotational angle of the upper arm member,
The period etc. of constant force mechanisms.In addition, linked due to torque adjustment spring and the upper arm member and apply active force around the second axis, because
This, can by make in the axial direction in first axle torque adjustment with spring it is not Chong Die with oscillating rod in a manner of come configure torque adjustment use
Spring.Thereby, it is possible to inhibit the thickness of constant force mechanisms, miniaturization is realized.Therefore, it is capable of forming the excellent constant force of design freedom
Mechanism.
In addition, being characterized in that, there is spring adjustment mechanism, the spring adjustment mechanism adjusts the torque adjustment and uses spring
Deflection.
According to this structure, the deflection of torque adjustment spring can be adjusted after assembling period control mechanism.That is,
Without assembling cycle control mechanism in the state of bending torque adjustment with spring, it is accordingly possible to ensure good assemblability.
In addition, after period control mechanism is assembled and is assembled in machine core, can with the manufacture deviation of machine core correspondingly
Adjust the deflection that spring is used in torque adjustment.Therefore, the excellent constant force mechanisms of assemblability are capable of forming.
In addition, machine core of the invention is characterized in that the constant force mechanisms for having above-mentioned.
In addition, clock and watch of the invention are characterized in that the machine core for having above-mentioned.
According to this structure, high-precision clock and watch and machine core are capable of forming.
Invention effect
According to the present invention, due to having the torque adjustment spring for generating active force using stretching, with existing skill
Art compares, and can fully ensure the deflection of torque adjustment spring.Thereby, it is possible to inhibit torque adjustment spring because making
Therefore rate of torque ripple caused by variation firmly can be stably driven with release catch.Therefore, being capable of forming can ensure that well
Accuracy of timekeeping constant force mechanisms.
Detailed description of the invention
Fig. 1 is the top view of mechanical clock.
Fig. 2 is the perspective view of machine core.
Fig. 3 is the cross-sectional view of the line A-A along Fig. 2.
Fig. 4 is the cross-sectional view of the line B-B along Fig. 2.
Curve graph when Fig. 5 is the amount of storage of the movement torque using horizontal axis as the time, by torque adjustment spring of the longitudinal axis.
Fig. 6 is the block diagram for having the machine core of constant force mechanisms.
Fig. 7 is the action specification figure of constant force mechanisms.
Fig. 8 is the action specification figure of constant force mechanisms.
Fig. 9 is the action specification figure of constant force mechanisms.
Figure 10 is the curve for indicating the reduction rate of active force and movement torque of torque adjustment spring in the prior art
Figure.
Figure 11 is the curve for indicating the reduction rate of active force and movement torque of the torque adjustment spring of present embodiment
Figure.
Label declaration
1: clock and watch；5: machine core；10: constant force mechanisms；11: powershift portion；12: planetary gear (powershift portion) 20: swinging
Bar；30: period control mechanism；31: stopping wheel；35: the upper arm member；39: engaging portion；40: spring is used in torque adjustment；50: spring tune
Save mechanism；60: release catch；65: driving wheel on barrel (power source)；70: train；C1: first axle；C2: the second axis.
Specific embodiment
In the following, the embodiments of the present invention will be described with reference to the drawings.
In general, the mechanical body of the drive part including clock and watch is referred to as " machine core ".After dial plate, needle being installed on the machine core
The state for being put into clock and watch shell and becoming finished goods is referred to as " finished product (complete) " of clock and watch.The substrate of clock and watch will be constituted
The side that there are the side of the glass of clock and watch shell, i.e. there is dial plate in the two sides of bottom plate is referred to as " back side " of machine core.Separately
Outside, by the two sides of bottom plate there are the side of the shell body rear cover of clock and watch shell, sides i.e. opposite with dial plate to be referred to as machine core
" face side ".
Fig. 1 is the top view of clock and watch 1.
As shown in Figure 1, clock and watch 1 have the dial plate 2 comprising scale 3 etc., scale 3 indicates the information about hour.Clock and watch 1 have
Standby needle 4, the needle 4 include: the hour hands 4a for indicating hour；Indicate the minute hand 4b of minute；And the second hand 4c of expression second.In addition,
Clock and watch 1 have winding arbor 6.Winding arbor 6 is for example in the amendment on date or to expression (expression of hour and minute) constantly
The timepiece used when being modified.The crown 7 positioned at the side of clock and watch shell is installed in the one end of winding arbor 6.
Fig. 2 is the perspective view of machine core 5.
Fig. 3 is the cross-sectional view of the line A-A along Fig. 2.
Fig. 4 is the cross-sectional view of the line B-B along Fig. 2.
Also, in Fig. 2 into Fig. 4, for the ease of observing attached drawing, suitably it is omitted in the timepiece for constituting machine core 5
The diagram of a part.
As shown in Fig. 2, the machine core 5 of embodiment has: as power source driving wheel on barrel 65 (it is in Fig. 2 not shown, referring to figure
6), release catch 60, train 70 and constant force mechanisms 10.Hereinafter, each component parts to machine core 5 is illustrated.
There is mainspring barrel (not shown) in the inside of driving wheel on barrel 65 (referring to Fig. 6).By making winding arbor 6 (referring to Fig.1)
Rotate and roll tightly the mainspring barrel of driving wheel on barrel 65.Be configured to, rotary force when driving wheel on barrel 65 is by mainspring barrel loose winding and rotate.
As shown in Fig. 2, release catch 60 mainly has escape wheel 61 and escapement lever (not shown).
As shown in figure 3, be supported to by bottom plate 90 and the first train supporting member 91 can be by bearing and around rule for escape wheel 61
Fixed rotary shaft rotation, the first train supporting member 91 are located at than bottom plate 90 by the position of the face side of machine core 5.Escape wheel 61
Have escapement teeth portion 62 and escapement pinion gear 63.Escapement teeth portion 62 is formed in the periphery of the main part of escape wheel 61.
Escapement lever is supported on bottom plate 90 in a manner of it can rotate around defined rotary shaft and escapement lever (not shown) supports
Between part, escapement lever has a pair of of fork watt.A pair of fork Valley is alternately opposite with the defined period with governor (not shown)
Engaged and released in the escapement teeth portion 62 of escape wheel 61.Escape wheel 61 can carry out escapement with the defined period as a result,.
As shown in Fig. 2, train 70 is made of driving wheel on barrel side wheel system 70A and release catch side wheel system 70B.
As shown in figure 3, driving wheel on barrel side wheel system 70A has: the driving wheel on barrel (not shown) engaged with driving wheel on barrel 65 (Fig. 6 reference)
The wheel of side two；The wheel 73 of driving wheel on barrel side three with the pinion gear 73a engaged with the wheel of driving wheel on barrel side two；And have and barrel
Take turns the wheel 74 of driving wheel on barrel side four of the pinion gear 74a of 73 engagement of the wheel of side three.The wheel of driving wheel on barrel side two, the wheel 73 of driving wheel on barrel side three
And each gear of the wheel of driving wheel on barrel side four 74 respectively by bottom plate 90 and the first train supporting member 91 be supported to can by bearing and
It is rotated around defined rotary shaft.Driving wheel on barrel side wheel system 70A by the power of the mainspring barrel of driving wheel on barrel 65, (hereinafter referred to as " turn round by movement
Square ".) it is transferred to constant force mechanisms 10.
Release catch side wheel system 70B has: breast wheel 76 is engaged with the escapement pinion gear 63 of escape wheel 61；And release catch
The wheel 77 of side four, is engaged with the pinion gear 76a of breast wheel 76.Breast wheel 76 is by the first train supporting member 91 and the second train branch
Bearing member 92, which is supported to, to be rotated by bearing and around defined rotary shaft, and the second train supporting member 92 is set to the first round
It is between supporting member 91 and bottom plate 90.In addition, the wheel 77 of release catch side four is supported by the first train supporting member 91 and the second train
Part 92, which is supported to, to be rotated by bearing around first axle C1.Release catch side wheel system 70B will further be passed from constant force mechanisms 10
It passs the movement torque come and is transferred to release catch 60.In addition, the wheel 77 of release catch side four is corresponding with the second hand 4c of Fig. 1.
(constant force mechanisms)
Constant force mechanisms 10 are to inhibit to be transferred to the dynamic of release catch 60 from the driving wheel on barrel 65 (referring to Fig. 6) as power source
Make the variation of torque and be arranged, is made of powershift portion 11, oscillating rod 20 and period control mechanism 30.Hereinafter, to constant force
Each component parts of mechanism 10 is illustrated.
Powershift portion 11 is assembled in from the driving wheel on barrel 65 as power source into the train 70 of release catch 60.This embodiment party
The powershift portion 11 of formula is the escapement with No. four 74 and release catch side wheel system 70B of wheel in driving wheel on barrel side of driving wheel on barrel side wheel system 70A
The planetary gear 12 of 77 engagement of the wheel of device side four.Powershift portion 11 is dynamic to the first power transfer path P1 (referring to Fig. 6) and second
Power transmission path P2 (referring to Fig. 6) is switched over, and the first power transfer path P1 is will to be stored in torque adjustment spring
Movement torque in 40 is transferred to the path of release catch 60, and the second power transfer path P2 is will be from (the ginseng of driving wheel on barrel 65
According to Fig. 6) movement torque be transferred to the path of aftermentioned torque adjustment spring 40.
Oscillating rod 20 is supported to by the first train supporting member 91 and third train supporting member 93 can be by bearing and around
One axis C1 rotation, the third train supporting member 93 are set to than the first train supporting member 91 by the position of the face side of machine core 5.
Oscillating rod 20 is upwardly extended in the side vertical with first axle C1, also, has planetary gear supporting part 21, the planetary gear
Planetary gear 12 is supported to and can be rotated by bearing by supporting part 21.Planetary gear supporting part 21 along with the rotation of oscillating rod 20 and
Planetary gear 12 is supported to and carries out rotation while around first axle C1 revolution.
As shown in Fig. 2, oscillating rod 20 has a balanced support portion 23 in the following manner, the balanced support portion 23 is towards clipping the
Side one axis C1 opposite with planetary gear supporting part 21 extends.In balanced support portion 23, with the center of gravity and first axle of oscillating rod 20
The consistent mode of C1 is equipped with counterweight 24.By being arranged counterweight 24, oscillating rod 20 can with the postures of clock and watch 1 (referring to Fig.1) without
Ground is closed steadily to rotate.
In addition, oscillating rod 20 has oscillating rod gear 25 in the following manner, the oscillating rod gear 25 is towards clipping first axle
Side C1 opposite with release catch 60 extends.Oscillating rod gear 25 is formed as the fan centered on first axle C1 in plan view
Shape.Multiple oscillating rod teeth portion 25a are formed on the outer peripheral surface of oscillating rod gear 25.
(period control mechanism)
Period control mechanism 30 mainly has: stopping wheel 31, the upper arm member 35, engaging portion 39, torque adjustment spring 40, with
And spring adjustment mechanism 50.
As shown in figure 4, be supported to by bottom plate 90 and third train supporting member 93 can be by bearing and around rule for stopping wheel 31
Fixed rotary shaft rotation.There is stop teeth portion 32 on the outer peripheral surface of stopping wheel 31.In addition, stopping wheel 31 has and driving wheel on barrel side
The stop pinion gear 33 of No. four 74 engagements of wheel.Movement torque from driving wheel on barrel 65 (referring to Fig. 6) is via driving wheel on barrel side wheel system 70A
It is transferred to stopping wheel 31, so that stopping wheel 31 can rotate.
It is true that the upper arm member 35 includes arm arbor (ア ー system) 38, extend along the second axis C2, second axis C2 clips first
Axis C1 is located at the side opposite with release catch 60；With the upper arm member main part 36, it is installed on arm arbor 38.The both ends of arm arbor 38
Portion is supported by bearing and by bottom plate 90 and third train supporting member 93 respectively, so that the upper arm member 35 can turn around the second axis C2
It is dynamic.It is equipped with around the upper arm member main part 36 for the rotational angle of the upper arm member main part 36 to be limited to not scheming for specified value
The banking pin shown.
The upper arm member main part 36 is formed as extending along the direction vertical with the second axis C2, and has towards oscillating rod 20 and extend
Arm gear 37 and towards stopping wheel 31 extend engaging portion 39.
Arm gear 37 is formed as the fan-shaped centered on the second axis C2 in plan view.On the outer peripheral surface of arm gear 37
It is formed with multiple arm teeth portion 37a.Arm gear 37 is engaged with oscillating rod gear 25, and thus the upper arm member 35 and oscillating rod 20 link.
Engaging portion 39 has stop fork watt 39a.Stop fork watt 39a, which is for example fixed on by binder etc., is formed in engaging portion
In 39 slot.The upper arm member 35 rotates, so that stop teeth portion 32 engagings/disengaging of watt 39a relative to stopping wheel 31 is pitched in stop.
Torque adjustment spring 40 is can be using the flexible spring for generating active force, for example, by using balance spring 41.Balance spring 41
Be formed as in plan view along the archimedes curve centered on the second axis C2.The inner end 41a of balance spring 41 for example through
It is fixed in the upper arm member 35 by fixed cylinder 43, fixed cylinder 43, which is externally embedded to, to be fixed on arm arbor 38.In addition, the outer end of balance spring 41
Portion 41b is for example fixed on bottom plate 90 via the fixed part 46 for the aftermentioned spring regulating wheel 45 being fixed on bottom plate 90.
About balance spring 41, rotated by the upper arm member 35, thus in the state that outer end 41b is fixed, balance spring 41 it is interior
End 41a is rotated around the second axis C2, and enlarged outside diameter/diminution (flexible) of balance spring 41.Balance spring 41 is fixed with following states
In the upper arm member 35 and bottom plate 90: the balance spring 41 is rolled tightly and active force is made to act on the side that engaging portion 39 leaves stopping wheel 31
To on (clockwise direction centered on the second axis C2 in Fig. 2).
Spring adjustment mechanism 50 is mainly made of spring regulating wheel 45, holding member 47.
Spring regulating wheel 45 is formed as tubular, and has spring regulating wheel teeth portion 45a on outer peripheral surface.Spring adjusts the gear teeth
Portion 45a can be engaged with tool gear (not shown).Spring regulating wheel 45 is for example outer embedded in being coaxially formed with the second axis C2
The cylindrical portion 90a of bottom plate 90.
Holding member 47 has a pair of of the clamping part 47a being arranged in a manner of extending parallel to.Holding member 47 is to utilize
The state of a pair of of clamping part 47a clamp springs regulating wheel 45 is fixed on bottom plate 90.Holding member 47 using clamping part 47a and
The frictional force of spring regulating wheel 45 and spring regulating wheel 45 is kept into and cannot be rotated around the second axis C2.
Spring regulating wheel 45 for example rotates predetermined angular by tool gear when manufacturing machine core 5.Balance spring 41 is rolled up as a result,
Tight specified amount is adjusted to desired deflection.In this way, spring adjustment mechanism 50 according to the present embodiment, only by making bullet
Spring regulating wheel 45 rotates, it will be able to easily adjust the deflection of balance spring 41.
(effect)
Fig. 5 is the movement amount of storage of torque using horizontal axis as the time, by torque adjustment spring 40 of the longitudinal axis and schematic
Curve graph shown in ground.
Fig. 6 is the block diagram of constant force mechanisms 10, is the explanatory diagram for schematically showing the transmitting of movement torque.
The action specification figure of constant force mechanisms 10 when Fig. 7 to Fig. 9 is from the face side of machine core 5 respectively.
Next, being illustrated to the effect of constant force mechanisms 10 configured as described.In addition, in the following description,
Following actions in the movement of clock and watch 1 are illustrated, which is the storage in the movement torque of torque adjustment spring 40
It measures (hereinafter referred to as " amount of storage W ".) become maximum after, be stored in torque adjustment and be passed with the movement torque in spring 40
To release catch 60, amount of storage W becomes minimum, the movement until amount of storage W becomes maximum again.In addition, in following the description
In, the clockwise direction when face side of slave machine core 5 of the Fig. 7 into Fig. 9 is observed is referred to as the direction CW, and counter clockwise direction is claimed
Make the direction CCW.In addition, in the following description, about the label of each component, please as needed together referring to Figure 2 to Figure 4.
As shown in figure 5, in time t1, constant force mechanisms 10 become using the movement torque of driving wheel on barrel 65 (referring to Fig. 6) and by
The maximum state of amount of storage W (hereinafter referred to as " state S1 " of the movement torque of the torque adjustment spring 40 rolled tightly.).At this point,
As shown in fig. 7, constant force mechanisms 10 become the state that engaging portion 39 engages with stopping wheel 31.In addition, stopping wheel 31 and driving wheel on barrel side
Each gear of train 70A becomes the state that rotation stops.
Then, with time going by, torque adjustment is stored in gradually to be discharged with the movement torque in spring 40.At this point,
Torque adjustment is played a role with the active force of spring 40, so that the upper arm member 35 is rotated centered on the second axis C2 along the direction CW.
When the upper arm member 35 is rotated along the direction CW, the oscillating rod 20 linked with the upper arm member 35 edge centered on first axle C1
The rotation of the direction CCW.
Here, the wheel 74 of driving wheel on barrel side four becomes halted state.Therefore, the planetary gear 12 supported by oscillating rod 20 with item
In the state of 74 engagement of the wheel of box wheel side four, revolve around first axle C1 along the direction CCW, while along the rotation of the direction CW.In addition, with row
The wheel of release catch side four 77 that star-wheel 12 engages due to planetary gear 12 from then be passed movement torque, thus along the direction CCW
Rotation.Then, the movement torque for being passed to No. four wheels 77 in release catch side is passed to catching for release catch 60 via breast wheel 76
Vertical wheel 61.That is, the movement torque from driving wheel on barrel 65 is in quilt as shown in the first power transfer path P1 in Fig. 6
After storing torque adjustment spring 40, release catch 60 is passed to change less state.
Then, as shown in figure 5, the movement torque of the torque adjustment of constant force mechanisms 10 spring 40 is released, in time t2,
The smallest state of amount of storage (hereinafter referred to as " state S2 " of movement torque as torque adjustment spring 40.).At this point, such as
Shown in Fig. 8, constant force mechanisms 10 become the state that engaging of the engaging portion 39 with stopping wheel 31 is released from.
Then, as shown in figure 5, constant force mechanisms 10 after the time t 2, become stored into torque adjustment spring 40 it is dynamic
Make the state (hereinafter referred to as " state S3 " of torque.).
At this point, as shown in figure 9, each gear and stopping wheel 31 of driving wheel on barrel side wheel system 70A are using from 65 (reference of driving wheel on barrel
Movement torque Fig. 6) and rotate.Specifically, the wheel 74 of driving wheel on barrel side four is rotated along the direction CCW.In addition, with driving wheel on barrel side four
Number wheel 74 engagement stopping wheel 31 rotated along the direction CW.In addition, at this point, escape wheel 61 and the release catch side wheel system of release catch 60
Each gear of 70B becomes the state that rotation stops.
When wheel 74 is rotated along the direction CCW when driving wheel on barrel side four, 74 12 edges of planetary gear engaged are taken turns for No. four with driving wheel on barrel side
The rotation of the direction CW.
Here, the wheel 77 of release catch side four becomes halted state.Therefore, in the wheel 77 of release catch side four and driving wheel on barrel side four
In the state of number 74 engagement of wheel, the planetary gear 12 engage with the wheel of release catch side four 77 around first axle C1 along the revolution of the direction CW, together
When along the rotation of the direction CW.In addition, the oscillating rod 20 of supporting planetary wheel 12 is with first axle C1 along with the revolution of planetary gear 12
Center is rotated along the direction CW.
When oscillating rod 20 is rotated along the direction CW, the upper arm member 35 linked with oscillating rod 20 overcomes torque adjustment spring 40
The direction CW active force and centered on the second axis C2 along the direction CCW rotate.Torque adjustment is utilized with spring 40 from item as a result,
Box wheel 65 (referring to Fig. 6) is transferred to the movement torque of the upper arm member 35 and is rolled tightly.That is, such as the second power transfer path in Fig. 6
Shown in P2 like that, the movement torque from driving wheel on barrel 65 is passed in torque adjustment spring 40 and is stored.Then,
As shown in figure 5, the amount of storage W that constant force mechanisms 10 become the movement torque of torque adjustment spring 40 again is maximum in time t3
State S1.In addition, at this point, as shown in fig. 7, constant force mechanisms 10 become the state that engaging portion 39 engages with stopping wheel 31.
Hereafter, by repeating above-mentioned movement, the repressed state of variation for the movement torque that release catch 60 comes in transmitting
It is lower to be driven.
Figure 10 is the curve for indicating the reduction rate of active force and movement torque of torque adjustment spring in the prior art
Figure, Figure 11 are the curve graphs for indicating the reduction rate of active force and movement torque of the torque adjustment spring 40 of present embodiment.
Also, in Figure 10 and Figure 11, horizontal axis is expressed as to the deflection of time and torque adjustment spring 40, the longitudinal axis is expressed as base
In the movement torque of the mainspring barrel of the active force and driving wheel on barrel 65 (referring to Fig. 6) of torque adjustment spring.In addition, chain-dotted line indicates
The relationship of the movement torque and time of the mainspring barrel of driving wheel on barrel 65 (referring to Fig. 6), solid line are indicated based on torque adjustment spring
The relationship of the movement torque and time of active force.
In addition, torque adjustment spring 40 is transferred to the upper arm member 35 using from driving wheel on barrel 65 when constant force mechanisms 10 act
Movement torque and be rolled tightly, thus store movement torque.It is based at this point, the movement torque needs from driving wheel on barrel 65 overcome
The movement torque of the active force of torque adjustment spring 40.But generally, based on the dynamic of the active force of torque adjustment spring 40
Make torque to have differences in release and when rolling tightly.
As shown in Figure 10 and Figure 11, the flexure burst size of torque adjustment spring 40 is being set as Tc, by corresponding torque
The maximum actuation torque of adjustment spring 40 is set as TrMAX, minimum movements torque is set as TrMIN, by torque adjustment spring 40
Spring constant (movement torque/deflection) when being set as k, relational expression below is set up.
TrMIN=TrMAX-k × Tc ... (1)
About torque adjustment spring 40, spring constant k is bigger, is more difficult to happen flexible deformation, and deflection becomes smaller；Spring
Constant k is smaller, is more easy to happen flexible deformation, and deflection becomes larger.
In addition, importing the value of bending coefficient n and defining following formula.
K=TrMAX/ (n × Tc) ... (2)
N is indicated: torque adjustment has the flexure of several times of degree of the actuating quantity of flexure with spring 40.According to formula (1) and formula
(2) relationship can obtain following formula.
TrMIN=TrMAX × (n-1)/n ... (3)
In addition, the difference of maximum actuation torque T rMAX and minimum movements torque T rMIN (hereinafter referred to as " is acted torque
Difference ".) when being set as △ Tr, be represented by the following formula.
△ Tr=TrMAX-TrMIN=TrMAX/n ... (4)
According to formula (4), it may be said that in the biggish situation of n, that is, torque adjustment obtains more flexures with spring 40
Amount, the variation for acting torque are smaller.
In addition, by from driving wheel on barrel 65 movement torque and maximum actuation torque T rMAX and minimum movements torque T rMIN it
Between the state that mutually balances of movement torque be defined as unstable state.The constant force mechanisms 10 to play pendulum movement and
It is irregularly repeated between stopping.Therefore, the movement torque for being transferred to release catch 60 changes, and accuracy of timekeeping is also unstable
Change.
The relationship that monotone decreasing is in by the time of the movement torque and machine core 5 of driving wheel on barrel 65.Therefore, torque is acted
Poor △ Tr is smaller, and the movement torque range that the driving wheel on barrel 65 (i.e. mainspring barrel) of unstable state occurs reduces, with being connected with this,
Time as unstable state also reduces.
Here, in the prior art, become bending coefficient n=3 or so when the duration of machine core 5 is set as Tm, this
When unstable state time T1 become machine core 5 duration T m 1/5 or so (referring to Fig.1 0).
In contrast, in torque adjustment in the present embodiment for using balance spring 41 in spring 40, such as by making to scratch
Bowed pastern number n=20, so as to which the time T2 of unstable state to be contracted to 1/20 or so (ginseng of 5 Chi continued time Tm of machine core
According to Figure 11).Also, the case where bending coefficient n=20 is an example, such as can also make 20 or more bending coefficient n.This
Sample compared with prior art, can substantially shorten the time of unstable region, therefore, can obtain in the present embodiment
Accuracy of timekeeping excellent machine core 5 and clock and watch 1.
According to the present embodiment, due to the torque adjustment spring with balance spring 41 as the flexible generation active force of utilization
40, therefore, compared with prior art, it can fully ensure the deflection of torque adjustment spring.Thereby, it is possible to inhibit to turn round
Square adjustment with spring 40 because active force variation caused by rate of torque ripple therefore can be stably driven with release catch 60.Cause
This, is capable of forming the constant force mechanisms 10 that can ensure that good accuracy of timekeeping.
In addition, since period control mechanism 30 has the upper arm member 35 linked with oscillating rod 20, by appropriately designed
The linking portion of oscillating rod 20 and the upper arm member 35 can arbitrarily set the rotation of the rotational angle, the upper arm member 35 of oscillating rod 20
Angle, period of constant force mechanisms 10 etc..In particular, in the case where oscillating rod 20 and the upper arm member 35 are interlinked by teeth portion,
Only pass through setting gear ratio, oscillating rod 20 and length of the upper arm member 35 etc., it will be able to easily set the angle of rotation of oscillating rod 20
Degree, the rotational angle of the upper arm member, period of constant force mechanisms etc..In addition, since torque adjustment spring 40 and the upper arm member 35 link
And around the second axis C2 apply active force, therefore, can with make in the axial direction of first axle C1 torque adjustment spring 40 not with pendulum
The mode that lever 20 is overlapped configures torque adjustment spring 40.Thereby, it is possible to inhibit the thickness of constant force mechanisms 10, realize small-sized
Change.Therefore, the excellent constant force mechanisms 10 of design freedom are capable of forming.
In addition, due to spring adjustment mechanism 50, the adjustable torque after assembling cycle control mechanism 30
The adjustment deflection of spring 40.That is, due to without assembling cycle control in the state of bending torque adjustment spring 40
Mechanism 30, it is accordingly possible to ensure good assemblability.In addition, being assembled to period control mechanism 30 and being assembled to machine core 5
After interior, the deflection of torque adjustment spring 40 can be correspondingly adjusted with the manufacture deviation of machine core 5.It therefore, being capable of shape
At the constant force mechanisms 10 that assemblability is excellent.
In addition, being capable of forming high-precision machine core 5 and clock and watch 1 by having above-mentioned constant force mechanisms 10.
In addition, the above-mentioned embodiment that the present invention is not limited to be illustrated referring to attached drawing, in its technology scope
It is contemplated that various modifications example.
In embodiments, although being used as torque adjustment spring 40 using balance spring 41, it is not limited to balance spring, as long as
Being can be using the flexible elastomeric element for generating active force.Thus, for example work can also be generated using that can utilize to stretch
Helical spring firmly is as torque adjustment spring 40.
In embodiments, the rotation center of No. four wheels 77 of the center of rotation of oscillating rod 20 and release catch side is respectively first
Axis C1, although be it is coaxial, however, you can also not be coaxial.
The spring adjustment mechanism 50 of embodiment is configured to, when by means of sandwiching spring regulating wheel 45 using holding member 47
Frictional force and kept in the state that balance spring 41 is rolled tightly specified amount.In contrast, spring adjustment mechanism 50 can also be with
It is configured to, such as spring regulating wheel 45 is fixed on by specified position by using stop jumper (jumper), thus will swimming
Silk 41 is kept in the state of rolling tightly specified amount.
In embodiments, although being used as powershift portion 11 using planetary gear 12, it is not limited to planetary gear 12, only
If allowing hand over the structure of the direction of transfer of movement torque.Therefore, powershift portion 11 is for example also possible to have difference
The differential attachment of dynamic pinion gear, the differential pinion have in rotation on the direction that the rotation axis with oscillating rod 20 is intersected
The heart.
Furthermore it is possible to without departing from the scope of spirit of the present invention suitably by the structural element in above embodiment
Replace with well known structural element.
Claims (4)
1. a kind of constant force mechanisms, which is characterized in that
The constant force mechanisms have:
Powershift portion is assembled into the train from power source to release catch；
Oscillating rod, the powershift portion, which is supported to, to be rotated around first axle；And
Period control mechanism, includes stopping wheel, is passed power from the power source and can rotate；Torque adjustment is used
Spring drives the release catch using flexible generation active force；And engaging portion, by the torque adjustment spring
It being acted and locking with the stopping wheel, the period control mechanism rotates the oscillating rod intermittently,
The period control mechanism has the upper arm member, and the upper arm member and the oscillating rod link, and the engaging portion is supported
At can be rotated around the second axis,
The torque adjustment spring and the upper arm member link, also, apply active force around second axis by flexible.
2. constant force mechanisms according to claim 1, which is characterized in that
The period control mechanism has spring adjustment mechanism, and the spring adjustment mechanism adjusts the torque adjustment spring
Deflection.
3. a kind of machine core, which is characterized in that
The machine core has constant force mechanisms of any of claims 1 or 2.
4. a kind of clock and watch, which is characterized in that
The clock and watch have machine core as claimed in claim 3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014182261A JP6388333B2 (en) | 2014-09-08 | 2014-09-08 | Constant force mechanism, movement and watch |
| JP2014-182261 | 2014-09-08 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105404130A CN105404130A (en) | 2016-03-16 |
| CN105404130B true CN105404130B (en) | 2019-04-09 |
Family
ID=55456449
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510551824.2A Active CN105404130B (en) | 2014-09-08 | 2015-09-01 | Constant force mechanisms, machine core and clock and watch |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6388333B2 (en) |
| CN (1) | CN105404130B (en) |
| CH (1) | CH710108B1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6566432B1 (en) * | 2018-06-07 | 2019-08-28 | セイコーインスツル株式会社 | Constant torque mechanism, watch movement and watch |
| EP3599515B1 (en) * | 2018-07-24 | 2022-07-06 | Harry Winston SA | Timepiece driving mechanism |
| EP3599517B1 (en) * | 2018-07-24 | 2021-03-10 | Harry Winston SA | Timepiece retrograde tourbillon or karussel |
| JP7103041B2 (en) * | 2018-08-03 | 2022-07-20 | セイコーエプソン株式会社 | Ankles, movements, watches |
| JP7260446B2 (en) * | 2019-09-12 | 2023-04-18 | セイコーウオッチ株式会社 | Transmission wheel, self-winding mechanism, watch movement and watch |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6948845B2 (en) * | 2003-10-28 | 2005-09-27 | Journe Francois-Paul | Mechanical timepiece |
| CN102160003A (en) * | 2008-09-18 | 2011-08-17 | 阿根豪尔股份公司 | Clock movement including a constant force device |
| WO2011113757A1 (en) * | 2010-03-17 | 2011-09-22 | Complitime Sa | Movement for a timepiece with equalizing winding mechanism |
| CN102467070A (en) * | 2010-11-17 | 2012-05-23 | 精工电子有限公司 | Anchor escapement, speed controlling escapement mechanism and mechanical watch having the same |
| CN103777510A (en) * | 2012-10-18 | 2014-05-07 | 精工电子有限公司 | Constant-torque mechanism for clock, movement having the mechanism, and mechanical clock |
-
2014
- 2014-09-08 JP JP2014182261A patent/JP6388333B2/en active Active
-
2015
- 2015-09-01 CN CN201510551824.2A patent/CN105404130B/en active Active
- 2015-09-08 CH CH01290/15A patent/CH710108B1/en unknown
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6948845B2 (en) * | 2003-10-28 | 2005-09-27 | Journe Francois-Paul | Mechanical timepiece |
| CN102160003A (en) * | 2008-09-18 | 2011-08-17 | 阿根豪尔股份公司 | Clock movement including a constant force device |
| WO2011113757A1 (en) * | 2010-03-17 | 2011-09-22 | Complitime Sa | Movement for a timepiece with equalizing winding mechanism |
| CN102467070A (en) * | 2010-11-17 | 2012-05-23 | 精工电子有限公司 | Anchor escapement, speed controlling escapement mechanism and mechanical watch having the same |
| CN103777510A (en) * | 2012-10-18 | 2014-05-07 | 精工电子有限公司 | Constant-torque mechanism for clock, movement having the mechanism, and mechanical clock |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6388333B2 (en) | 2018-09-12 |
| CH710108A2 (en) | 2016-03-15 |
| JP2016057111A (en) | 2016-04-21 |
| CN105404130A (en) | 2016-03-16 |
| CH710108B1 (en) | 2020-03-31 |
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