JP2010507086A - A watch movement that transmits power between a power source and a mechanical oscillator at a constant torque. - Google Patents

Abstract

The movement has a barrel with an output torque variable based on its charging state. A compensation device transmits a constant torque to a mechanical oscillator irrespective of the state of the barrel, and has a cam (12) with a radius variable based on the variations of the output torque. The device has an intermediate connection mechanism to assure sliding-less kinematic connection between a periphery of the cam and the gear-train. The mechanism has a lever (13) to carry a mobile wheel (10) with a permanent kinematic connection with a wheel (9).

Description

  The present invention relates to a movement of a timepiece provided with a power source attached to a frame and whose output torque changes according to the degree of winding.

  The power source is designed to maintain the oscillating operation of the mechanical oscillating device through the speed-regulating train wheel provided with the compensating device. The compensator has an input member connected to the power source so as to be able to transmit power directly or via at least one assembled vehicle, and an output member connected to be able to transmit power to the mechanical oscillation device. Thus, a substantially constant torque is transmitted to the mechanical oscillation device regardless of the degree of winding of the power source.

  This type of movement is used in particular in the field of table clocks, with the aim of using a mainspring that can store power over a long period of time while smoothing the inevitable fluctuations of the power that the mainspring gives to the train wheel of the movement. Has long been known. This variation is caused by a change in the degree of winding of the mainspring while the table clock is moving. More precisely, it will usually be understood that the more torque that the mainspring is wound, the greater the torque that the mainspring will transmit to the governing wheel train.

  A number of mechanisms have been proposed that use a second mainspring, commonly referred to as a constant force escapement or Lemontoire mechanism, which is periodically wound by the power of the main spring. The winding period must be short enough so that the force applied to the movement by the second mainspring is considered constant between when the degree of winding is minimum and maximum.

  Other types of mechanisms, particularly those of the type referred to as the chain fuser mechanism, operate more accurately in contact with the barrel on the upstream side of the power transmission compared to the second mainspring mechanism.

  These movements include a fusie which is a conical member with a spiral groove around which a chain connected to a barrel is wound. When the timepiece is being rolled up, the chain wraps itself around the fuzzy and the barrel mainspring is stressed. A car with a fixed diameter is fixed to the fusies coaxially with the fusies, so that the power of the mainspring of the barrel is transmitted from the fusies to the train wheel of the movement. In this way, the power of the mainspring of the barrel is transmitted from the train wheel to the movement with a constant torque.

  In fact, when the barrel spring is at its maximum degree of winding and exerting its maximum force, the chain is pulling the circumferential portion where the diameter of the fusian helix is minimum. On the other hand, as the degree of winding of the barrel mainspring decreases, the chain draws the circumferential portion of the portion where the diameter of the spiral of the fusies is larger.

  Such a mechanism has been known since the 16th century, but when implementing this mechanism it is still complex and expensive to implement a chain that contains a particularly large number of parts. For the task of mounting this mechanism on a wristwatch, the complexity of the manufacturing becomes a very big problem, and such a watch is only for the class of people specifically selected.

  The primary object of the present invention is to provide an alternative to the mechanism known from the prior art by proposing a timepiece movement that includes a device that compensates for variations in torque released by the power source. The structure is not overly complex and is affordable, and can save space while ensuring high operational reliability.

  To this end, more particularly, the present invention relates to a timepiece movement of the above type, wherein the compensator comprises a cam having a peripheral portion that changes in radius and substantially extends in a plane. In addition, the change in the radius of the cam corresponds to the output torque of the power source. This cam also has a plurality of teeth on the periphery. The compensator is also arranged so as to engage with the plurality of teeth of the cam and to connect between the peripheral portion of the cam and the speed-regulating train wheel so that power can be transmitted with little or no slippage. The intermediate connection mechanism is also included.

  It is expedient if the compensation mechanism has exclusively hard parts when viewed individually.

  Because of these features, the movement of the present invention is less bulky than prior art mechanisms, and is less complex than prior art, and therefore requires less manufacturing costs. Furthermore, the compensator provides great flexibility in its manufacture, especially in mounting the cam on the movement.

  According to a first preferred aspect of the present invention, the intermediate connecting mechanism is a lever that pivots about a mandrel fixed to a frame, and can freely rotate about the fixed mandrel. And a lever that supports a pinion that is attached and permanently connected to a vehicle that is mounted to be permanently engaged with at least one assembled vehicle in the speed train. . The pinion is arranged to engage the plurality of teeth of the cam with little or no slip.

  Due to these features, the configuration of the peripheral edge of this cam has great flexibility and can be adjusted precisely as a function of the power source behavior with respect to the output torque transmitted depending on the degree of winding. . On the other hand, power can be transmitted from the power source to the mechanical oscillation device with high reliability.

  According to a preferred modification of the aspect in which the peripheral edge of the cam is connected to the input member of the compensator, the pinion is disposed so as to engage with the wheel of the reduction gear train, so that the teeth of the cam Depending on the size and number of the power source, it is possible to determine the nature of the power source, particularly if the power source is a mainspring, the magnitude of deformation of the mainspring.

  In a second preferred aspect of the present invention, the intermediate connecting mechanism has another cam whose radius changes, and the peripheral portion of the second cam can transmit power to the first cam. The size is determined such that the sum of the lengths of the radii of both cams on a line segment connected to the peripheral edge of the cams and connecting the centers of the two cams is constant. The second cam is fixed to a driving vehicle connected to the power source so as to be capable of transmitting power so as to rotate together with the driving vehicle.

  Because of these characteristics, the power transmission connection between the two cams is very strong, so that the torque output as the output from the compensator is constant regardless of the degree of power source winding. Partially compensates for variations in the output torque of the power source.

  In general, it is preferable that the compensating device has a differential gear, the cam forms an input member of the operating gear, and an output member of the operating gear is connected to a mechanical oscillation device so as to transmit power. . In this case, it is advisable that the differential gear includes an additional input member capable of realizing the winding of the power source.

  Other features and advantages of the present invention will become more apparent upon reading the detailed description of the preferred embodiment, made below with reference to the accompanying drawings, given as non-limiting examples of the present invention. I will.

FIG. 3 is a simplified top view of a portion of a timepiece movement having a compensation device according to the first aspect of the present invention. FIG. 1b is a simplified top view of the first detail of the movement shown in FIG. 1a. FIG. 1b is a simplified cross-sectional side view of the movement shown in FIG. 1a. 2b is a simplified top view of the second detail of the portion of the movement visible in FIG. 2a. FIG. FIG. 2b is a simplified top view of the third detail of the portion of the movement visible in FIG. 2a. FIG. 6 is a simplified top view of a portion of a timepiece movement having a compensation device according to the second aspect of the present invention.

  For clarity, in all drawings, only elements useful for understanding the present invention are shown.

  FIG. 1a shows a simplified top view of a portion of the movement of a mainspring watch having a compensation device according to the first aspect of the invention. More precisely, in the power transmission chain that transmits power from the power source to the mechanical oscillation device in which oscillation is maintained by this power, only the elements of the movement that play the role of power transmission are shown.

  For reference, the power source takes the form of a barrel 1 that houses a barrel mainspring (shown in FIG. 2a), and the barrel mainspring, in particular, includes a speed-regulating wheel train, and only the car 3 and the pinion 4 are in a line. It is designed to maintain the oscillation of Tianfu 2 through the escapement shown.

  The barrel mainspring is of a conventional type, the torque transmitted by the barrel mainspring and the torque output to the governing wheel train changes in a known manner depending on the degree of winding. May harm the accuracy. Thus, according to the present invention, the speed-regulating train wheel includes the compensation device 5 that makes it possible to maintain the Tianfu oscillation with a constant force, thereby improving the accuracy of its operation.

  A toothed output wheel 6 is attached to the barrel so that it rotates together with the barrel, and the output wheel 6 is arranged to engage with the first assembly wheel 7 of the reduction gear train of the compensator. ing. This compensator is supported by a movement frame (visible in FIG. 2a). The first wheel train pinion 8 meshes with the first wheel 9 of this train wheel, and the first wheel 9 meshes with the second wheel 10 of the same train wheel.

  The second wheel 10 is arranged to engage with the peripheral edge of the cam 12 with teeth. The cam 12 preferably has a shape that substantially follows the Archimedes curve. More precisely, this cam is provided with a plurality of teeth provided on a peripheral surface thereof on a plane on which the cam exists.

  A lever that pivots about the rotation center axis 14 of the first wheel 9 with respect to the movement frame in order to reliably maintain the connection for transmitting power between the second wheel 10 and the peripheral edge of the cam 12 At 13, attach the first car. In this way, regardless of the length of the radius of the cam 12 in contact with the second vehicle 10, the second vehicle 10 continuously transmits the movement of the first vehicle 9 to the cam.

  This mechanical connection is more clearly visible in FIG. In FIG. 1b, this connection is shown extracted from the other parts of the movement when the barrel mainspring is wound to a considerable extent. In fact, when the movement is operated from a state in which the barrel is highly wound, the radius of the cam in contact with the second wheel 10 is reduced in order to minimize the high output torque value of the barrel. While the mainspring of the barrel is unwound, the barrel moves the power transmission chain described above and rotates the cam 12 clockwise in the figure. As the barrel mainspring is unwound, its output torque decreases, and the radius of the cam in contact with the second wheel 12 increases to compensate for the decrease in the barrel output torque.

  Returning to FIG. 1a, the output wheel 15 of the compensator is mounted coaxially with the cam 12 and gives a constant torque to the speed-regulating train located downstream of the power transmission, ie in the direction of the mechanical oscillator. . Here, the plate of the output wheel has five arms, but the number of arms is not limited to this. The structure of the mechanical connection between the cam 12 and the output wheel 15 will be described in detail below with reference to FIG. 2a.

  The output wheel 15 meshes with the first assembly wheel 16 of the speed reduction wheel train. This speed reduction wheel train is followed by the second assembly wheel 17, the large third wheel 18, and the third assembly. It includes a vehicle 19 and a second vehicle and pinion assembly 20 that meshes with the escapement pinion 4.

  Of course, the number of decelerating wheel trains described here is not limited to this. It should be noted that the mechanical properties of the barrel mainspring and the size and number of teeth of the cam influence the structure of the reduction gear train connecting them to each other. Similarly, the size of the cam and output wheel 15 of the compensation device and the nature and characteristics of the mechanical oscillation device to which power is supplied influence the structure of the reduction gear train.

  A person skilled in the art will not encounter any particular difficulty in adapting the reduction wheel train of the movement to his or her own needs without exceeding the scope of the present invention.

  FIG. 2a shows a simplified cross-sectional side view of the movement shown in FIG. 1a. In this figure, the barrel mainspring 22 is visible, and since the torque is transmitted from the barrel mainspring from the output wheel 6, it can be seen that the cylindrical housing of the barrel 1 has no teeth.

  It can also be seen from FIG. 2a that the compensator has a differential gear 23, the cam 12 serving as a first input member, and the output wheel 15 serving as an output member for outputting at a constant torque. Understood.

  The differential gear 23 is attached to the movement frame 24 by a central mandrel 25. The output wheel 15 is screwed to a core 26 that contacts the mandrel 25 and can freely rotate around it, and the core 26 has radial teeth 27.

  The differential receiver 30 is screwed to the cam 12, and both ends of the two satellite vehicles 31 are rotatably attached to the cam 12 and the differential receiver 30, respectively. Each of the satellite cars 31 has a pinion 32 and a car 33, and the pinion 32 is arranged so as to mesh with the teeth 27 of the core 26.

  The differential gear 23 has a second input member in the form of a wheel 35 which is mounted on the central mandrel 25 so as to rotate freely. The wheel 35 has a tooth portion 36 extending in the radial direction facing the central mandrel 25, and the tooth portion is arranged to be engaged with each wheel 33 of the satellite car 31. Yes.

  As better shown in FIG. 2b, the wheel 35 serves as the input member of the differential gear 23 and allows winding of the barrel complete. In this figure, a power transmission chain for connecting the external control member 40 to the vehicle 35 is shown by a diagram.

  The external control member is formed so as to be able to rotationally drive the chisel wheel 41 that meshes with the round hole wheel 42, and the round hole wheel is engaged with the crown 43. The crown is disposed so as to be engaged with the input wheel 35 of the differential gear 23. As will be described in detail below, the differential gear 23 is securely connected between the external control member 40 and the barrel 1 as described in detail below. It is connected to transmit power to. In order to prevent the car from rotating unexpectedly when the hoisting operation is not performed, a conventional type of saw blade (not shown) is also arranged in the hoisting wheel train.

  When the outer control member 40 is rotated to wind the barrel complete 22, the input wheel 35 is driven to rotate through the hoisting wheel train described immediately before. Considering that the output wheel 15 of the differential gear is fixed for most of the time, that is, while the escape wheel 3 is stopped, a first for explaining the operating principle of the differential gear. In approximation, it can be assumed that the core 26 of the differential gear does not move during this operation, so that the input wheel 35 rotates the two satellite wheels 31 in opposite directions via the teeth 36, FIG. And 1b, the cam 12 is rotated counterclockwise.

  The rotation of the cam 12 is transmitted to the car 10, then to the car 9, the assembly car 7, and finally the output car 6 of the barrel. As a result, the barrel 1 is driven to rotate counterclockwise in FIG. 1a and rewinds its mainspring 22 integrated with a barrel 50 which has an inner end fixed to the frame.

  When the hoisting wheel train is not receiving force from the external control member, it can be considered that the input wheel 35 of the differential gear is fixed.

  As previously described, the barrel mainspring 22 transmits its force to the cam 12 and attempts to rotate the cam clockwise in FIGS. 1a and 1b. However, this cam rotation is possible only when the escape wheel 3 is not stopped, that is, only when the output wheel 15 of the differential gear is not fixed. The two satellite cars 31 are integrated with a cam via the axis of the satellite car, and these satellite cars are driven by the same rotational movement as the cam. As a result, the vehicle 33 of the satellite car rotates because it meshes with the teeth 36 of the input car 35. These two satellite cars rotate and transmit torque to the core via the teeth 27 of the core 26, and therefore transmit torque to the output wheel 15.

  Because the differential input torque is kept constant by changing the radius of the cam 12, the output torque transmitted to the governing wheel train is independent of the degree of winding of the barrel mainspring 22. Regardless, the torque transmitted in the differential output by the output wheel 15 is also constant.

  As a result, the torque finally transmitted to the escape wheel 3 is constant, and the same force is applied to the Tianfu 2 for each impact, thereby guaranteeing excellent operation accuracy.

  As described below in the conventional method, the operation accuracy can be observed even at the time display level. The time display will shift slightly over time. The cylindrical pinion 60 designed to have a minute hand (not shown) is supported by the second wheel and the pinion 18 thereof, and the pipe pinion itself is a tube designed to have an hour hand (not shown). The car 61 is supported. The sun wheel train 62 ensures that the required rotational speed between these two members is reduced.

  A stepped cylindrical hook 60 is shown so that the corresponding timepiece can be set in a conventional manner without interrupting the operation of the mechanical oscillator. The setting wheel train not shown is conveniently arranged to connect the external operation member to the sun wheel train 62.

  As shown in FIG. 2c, which is an explanatory diagram that does not limit the present invention, it is preferable that there is an indexing mechanism at the corner position of the barrel 50.

  This indexing mechanism takes the form of a wheel 70 having a sawtooth, which rotates together with the barrel complete 50 and cooperates with the hose 71. This indexing mechanism allows the true angular position of the barrel to be adjusted in order to control the minimum value of the output torque associated with the maximum usable radius of the cam 12 provided by the barrel mainspring 22. This minimum value of the output torque is predetermined during the manufacture of the movement according to the mechanical characteristics of the barrel mainspring 22 used. This value generally defines the starting point of the range in which the torque transmitted by the barrel mainspring has regular operational variations, depending on the degree of winding, which is usually characterized by the number of revolutions of the barrel.

  In addition, in cooperation with the abutment surface 73 (shown by the line in FIG. 1b) supported by the cam 12 and fixed to the frame, a minimum output torque of the barrel is selected during manufacture. Also shown is a stop member 73 that stops rotation of the cam when reached.

  A similar stop member may be provided to limit hoisting when the cam radius is minimized, and this stop member is preferably associated with the maximum value of the output torque provided by the barrel mainspring 22. It is. As described above, the maximum value of the output torque indicates the end of the operating range of the mainspring of the barrel. A person skilled in the art could provide a conventionally used type of torque limiting mechanism in the hoisting train to avoid damaging the gear without exceeding the scope of the present invention.

  When a specific barrel mainspring is selected, the reduction gear train, that is, the cars 6, 9, and 10, and the assembly car 7, the total number of rotations of the barrel corresponding to the operating range of the barrel 1 is substantially It is optimal to choose to correspond to one revolution.

  FIG. 3 is a simplified top view of a portion of a timepiece movement including a compensator according to the second aspect of the present invention.

  The second aspect shows a connection mechanism that replaces the connection mechanism of the first aspect.

  The output wheel 6 of the barrel 1 meshes with the first assembly wheel 80 of the reduction gear train. Further, the first assembly vehicle is engaged with the second assembly vehicle 81. The second assembly vehicle drives the connection assembly vehicle via a vehicle 82 that is coaxial with the cam and is attached to the first cam 83 so as to rotate with the cam.

  The first cam 83 is disposed so that its peripheral portion is engaged with the second cam 84, preferably by using a tooth portion. Although the second cam is an example, the second cam can suitably function as an input member to a differential gear similar to the differential gear 23 described in relation to the first embodiment.

  The two cams 83 and 84 are sized so that their peripheral edges engage continuously. With this intent, the radius of the two cams is determined so that the sum of the radii of the two cams is constant when each radius is positioned on a line segment 85 connecting the centers of the two cams. Further, regardless of the degree of winding of the mainspring 1 of the barrel, and thus regardless of the output torque transmitted by the output wheel 6 from the barrel, the respective radii are set such that the torque provided by the second cam 84 is constant. The value of is adjusted.

  In this way, as the barrel mainspring releases its power, its output torque decreases and the radius of the first cam increases, substantially compensating for more torque than the torque received by the cam. To do. That is, the first cam transmits to the second cam 84 a torque whose value tends to increase only slightly. At the same time, the radius of the second cam 84 gradually decreases, and in order to give a constant torque as a whole to a mechanical oscillation device (not shown) arranged downstream of the power transmission, The increased amount of torque transmitted to itself by one cam 83 is accurately compensated.

  By connecting these two cams, variations in output torque from the barrel can be compensated with high accuracy while greatly reducing manufacturing and assembly efforts compared to prior art mechanisms. Further, the reliability of the power transmission realized between the two cams in this way is high, and is particularly excellent when realized by the gear which is a preferred mode.

  The foregoing description corresponds to preferred embodiments of the invention and is not intended to limit the invention. In particular, the forms illustrated and described as various component elements of the timepiece are exemplary forms only. Although this invention is not restrict | limited, Since the bulk is small, it can be said that this invention can be implemented suitably in a wristwatch-type timepiece.

  Numerous alternative embodiments can be provided without exceeding the scope of the present invention. In particular, with respect to the first described aspect, the peripheral edge of the cam can be connected to the output member of the compensator rather than the input member of the compensator. In this case, for example, an input vehicle connected to a power source so as to be able to transmit power is disposed, and an intermediate connection mechanism connected to a peripheral portion of the cam is connected to an output member of the compensation device, so that the cam is It can be driven by an input vehicle. In this case, it can be considered that the cam is directly attached to the barrel instead of the output wheel 6.

  In general, those skilled in the art will not encounter any particular difficulty in changing various gears, reduction gear trains or acceleration gear trains according to the needs of each person skilled in the art.

  Of course, the present invention is not limited by the nature of the power source described and illustrated herein. However, due to its function, it is noted that the present invention allows the use of so-called “low speed” barrel springs with low rotational speed. Due to the fact that the output torque is high and the torque variation between the ends of its operating range is very large, this type of mainspring is less common. However, such a low-speed mainspring has the effect that the risk of adhesion between the wound mainsprings, which is more commonly seen in “high-speed” mainsprings with a high number of rotations, is particularly small. Similarly, the present invention can also be used to handle very large torques transmitted to a speed governing train by a plurality of barrels mounted in parallel.

Claims (13)

A mechanical oscillation device (via a speed-regulating train) having a power source (1, 22) attached to the frame (24) and having an output torque that changes according to the degree of winding, and having a compensation device (5). 2, 3, 4), and the compensator is connected to the input member connected to transmit power from the power source and to the mechanical oscillator to transmit power. A watch movement arranged to transmit a substantially constant torque to the mechanical oscillation device regardless of the degree of winding of the power source,
The compensator--a cam (12, 84) having a peripheral portion of varying radius length, extending substantially in a substantially plane, wherein the variation of the radius of the cam is the power source And the cam has a plurality of teeth on the peripheral edge thereof, and the speed-regulating train is engaged with the plurality of teeth of the cam with little or no slippage. Intermediate connection member (9, 10, 13, 83) formed to make a connection to transmit power between the cam and the peripheral edge of the cam
The movement characterized by having.   2. Movement according to claim 1, characterized in that the intermediate connecting member (9, 10, 13, 83) contains only rigid parts.   The intermediate connecting member includes a lever (13) that pivots about a mandrel (14) fixed to the frame (24), so that the lever can freely rotate about the fixed mandrel. Supporting a movable vehicle (10) having a connection capable of permanently transmitting power with an attached vehicle (9), the vehicle being continuously engaged with at least one assembly vehicle (7) of the governing wheel train The movement according to claim 1 or 2, characterized in that the movable wheel meshes with a plurality of teeth of the cam (12) with little or no sliding.   A peripheral portion of the cam (12) is connected to the input member of the compensation device (5), and the cam is connected to the power source (1, 10, 13) via the intermediate connection mechanism (9, 10, 13). The movement according to any one of the preceding claims, wherein the movement is connected to 22) so as to be able to transmit power.   When the degree of winding of the power source is reduced, the cam (12) is arranged so that the radius of the cam is increased in the peripheral region of the cam that is connected to the power source so that power can be transmitted. The movement according to claim 4, wherein the movement is provided.   The intermediate connecting mechanism includes another cam (83) whose peripheral portion is connected to the peripheral portion of the cam (84) so that power can be transmitted and whose length of the radius is changed. The other cam (83) is sized so that the sum of the length of the radius of the cam and the length of the radius of the other cam on the line segment (85) connecting the centers is constant. The movement according to claim 1, wherein the movement is fixed to a driving vehicle connected to the power source so as to be capable of transmitting power together with the driving vehicle.   The compensator (5) has a differential gear (23), the cam (12) serves as an input member of the differential gear, and the differential gear is a hoisting mechanism (40, 41) of the power source. , 42, 43), another input member (35) connected to the mechanical oscillation device, and an output member (15) connected to the mechanical oscillation device so as to be capable of transmitting power, The movement according to any one of the items.   The cam (12) supports at least one satellite car (31) that pivots freely, including a pinion (32) and a car (33) that rotate together, and one of the pinion and car is the other Movement according to claim 7, characterized in that it is connected to one input member (35) and the other of the pinion and the vehicle is connected to the output member (15).   The power source has a mainspring (22) accommodated in a barrel (1), and the power source is arranged in consideration of a relative angle between the cam (12) and the barrel under a predetermined condition. Movement according to any one of the preceding claims, characterized in that it also comprises an indexing mechanism (70, 71) that is configured to enable.   When the degree of winding of the power source (1, 22) changes between its minimum and maximum values, the compensator (5) is arranged so that the cam (12) makes one maximum rotation. The movement according to claim 1, wherein the movement is provided.   11. The compensation device according to claim 10, characterized in that the compensator comprises first and second stop members (72) that respectively define a minimum value and a maximum value of the degree of winding of the power source. Movement.   The cam (12) has a stop member (72) designed to cooperate with an abutment surface (73) fixed to the frame, and defines a minimum winding degree of the power source. The movement according to claim 10.   A timepiece comprising the movement according to any one of the preceding claims.

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