CN111983913A - Differential adjusting mechanism and watch - Google Patents

Abstract

The present application is applicable to the technical field of clocks and watches, and provides a differential adjustment mechanism and a watch, including: a planetary carrier; a central shaft fixed on the planetary carrier, the central shaft being used to connect an indicating system; a first wheel set, rotatably sleeved on on the central axis, and drively connected to the first tourbillon; the second wheel set, which is rotatably sleeved on the central axis and distributed with the first wheel set, and the second wheel set is drivingly connected to the second tourbillon; the planetary wheel set , rotatably arranged on the planet carrier and meshed with the first wheel set and the second wheel set respectively. In this embodiment, the first tourbillon and the second tourbillon can average the rotational speed of the planet carrier, thereby reducing the travel time error of the central axis. In addition, the planetary gear set is meshed with the first wheel set and the second wheel set respectively, which facilitates the transmission of the rotational motion of the first wheel set and the second wheel set to the planet carrier, improves the stability of the speed transmission, and is conducive to reducing the travel time error, and The structure of the entire differential adjustment mechanism is very simple.

Description

Differential adjustment mechanism and watch

technical field

The present application belongs to the technical field of watches and clocks, and more specifically, relates to a differential adjustment mechanism and a watch.

Background technique

A clock is a timing device and a precision instrument for measuring and indicating time. The timepiece has an indication system that can be turned to indicate the time.

The indication system of the clock will have a certain travel time error when it rotates. At present, a differential adjustment mechanism is generally formed by combining two tourbillons with the differential gear train to average the travel time error of the indication system, thereby reducing the indication system. travel time error. However, at present, the differential gear train is generally formed by a combination of multiple center wheels and/or multiple planetary gears, and the transmission efficiency of the rotary motion is low and unstable, which is not conducive to meeting the requirement of reducing the travel time error, and the entire differential adjustment mechanism The structure is very complex.

SUMMARY OF THE INVENTION

One of the purposes of the embodiments of the present application is to provide a differential adjustment mechanism, which aims to solve the technical problems in the prior art that the transmission of the differential adjustment mechanism is not stable and the structure is complicated.

In order to solve the above-mentioned technical problems, the technical solutions adopted in the embodiments of the present application are:

A differential adjustment mechanism is provided that includes:

planet carrier;

a central shaft, fixed on the planet carrier, the central shaft is used to connect the indicating system;

a first wheel set, which is rotatably sleeved on the central shaft, and is connected to the first tourbillon by transmission;

a second wheel set, which is rotatably sleeved on the central shaft and is spaced apart from the first wheel set, and the second wheel set is drivingly connected to the second tourbillon;

The planetary gear set is rotatably arranged on the planet carrier and meshes with the first wheel set and the second wheel set respectively.

In one embodiment, the planetary gear set includes:

a first planetary wheel, which is rotatably arranged on the planet carrier and is engaged with the first wheel set;

The second planetary gear is rotatably arranged on the planetary carrier and is engaged with the second wheel set, and the first planetary gear is engaged with the second planetary gear.

In one embodiment, the first planetary gear includes a first planetary shaft, a first gear and a second gear, and the first gear and the second gear are respectively fixed to two ends of the first planetary shaft ; The first planetary shaft is rotatably arranged on the planet carrier, the first gear and/or the second gear is engaged with the second planetary gear, and the first gear is engaged with the first Round Group.

In one embodiment, the second planetary gear includes a second planetary shaft, a third gear and a fourth gear, and the third gear and the fourth gear are respectively fixed to both ends of the second planetary shaft ; The second planetary shaft is rotatably arranged on the planet carrier, the third gear and/or the fourth gear is engaged with the first planetary gear, and the third gear is engaged with the second Round Group.

In one embodiment, the first wheel set includes a first center wheel and a second center wheel that are simultaneously rotated and sleeved on the center shaft, the first center wheel is drivingly connected to the first tourbillon, The second center wheel is fixed to the first center wheel and meshes with the planetary gear set.

In one embodiment, the second wheel set includes a third center wheel and a fourth center wheel that are simultaneously rotated and sleeved on the center shaft, the third center wheel is drivingly connected to the second tourbillon, The fourth center wheel is fixed to the third center wheel and meshes with the planetary gear set.

In one embodiment, the differential adjustment mechanism further includes a first transmission assembly, the first transmission assembly includes a third planetary shaft, and a third planetary gear and a fourth planetary gear fixed on both ends of the third planetary shaft A planetary wheel, the third planetary wheel is engaged with the first wheel set, and the fourth planetary wheel is drivingly connected to the first tourbillon.

In one embodiment, the differential adjustment mechanism further includes a second transmission assembly, and the second transmission assembly includes a fourth planetary shaft and a fifth planetary gear and a sixth planetary gear fixed on both ends of the fourth planetary shaft A planetary wheel, the fifth planetary wheel is engaged with the second wheel set, and the sixth planetary wheel is drivingly connected to the second tourbillon.

In one embodiment, the differential adjustment mechanism further includes a power source, the power source includes a power gear, the planet carrier has external teeth, and the power gear is engaged with the planet carrier.

The embodiment of the present application also provides a wrist watch, including the above-mentioned differential adjustment mechanism.

The beneficial effects of the differential adjustment mechanism and the watch provided by the present application are: compared with the prior art, the present application is connected to the first wheel set through the first tourbillon drive, and the second tourbillon drive is connected to the second wheel set, The first wheel group and the second wheel group are arranged at intervals and can rotate around the central axis. The planetary wheel group is rotatably arranged on the planet carrier of the central axis and meshes with the first wheel group and the second wheel group respectively. In this way, the planet carrier passes through The planetary wheel sets are respectively connected with the first wheel set and the second wheel set, then the rotational motion of the first tourbillon and the second tourbillon are respectively transmitted to the first wheel set and the second wheel set, the first wheel set and The rotational motion of the second wheel group can be transmitted to the planet carrier through the planetary wheel group respectively, and the rotation speed of the planet carrier is half of the sum of the rotation speeds of the first wheel group and the second wheel group, that is, the first tourbillon and the second wheel group. The tourbillon averages the rotational speed of the planet carrier, thereby reducing the travel time error of the central axis. In addition, the first wheel set and the second wheel set are respectively rotatably sleeved on the central shaft, which improves the rotation flexibility of the first wheel set and the second wheel set. It can rotate on the planet carrier, and can revolve around the central axis as the pivot axis, and the planetary gear set is meshed with the first wheel set and the second wheel set respectively, which improves the flexibility of the planetary gear set and facilitates the realization of the first wheel set. The rotary motion of the first wheel group and the second wheel group is transmitted to the planet carrier, which improves the stability of the transmission and helps to reduce the travel time error, and the structure of the entire differential adjustment mechanism is very simple.

Description of drawings

In order to illustrate the technical solutions in the embodiments of the present application more clearly, the following briefly introduces the accompanying drawings that need to be used in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only for the present application. In some embodiments, for those of ordinary skill in the art, other drawings can also be obtained according to these drawings without any creative effort.

1 is a three-dimensional structural diagram of a differential adjustment mechanism provided by an embodiment of the present application;

2 is a cross-sectional view of a differential adjustment mechanism provided by an embodiment of the present application;

Fig. 3 is a partial enlarged view after rotation at A in Fig. 2;

FIG. 4 is a partial side view of the differential adjustment mechanism provided by the embodiment of the present application.

Among them, each reference sign in the figure:

1-planet carrier; 2-first wheel group; 21-first center wheel; 22-second center wheel; 3-second wheel group; 31-third center wheel; 32-fourth center wheel; 4-planet Wheel set; 41-first planetary gear; 411-first planetary shaft; 412-first gear; 413-second gear; 42-second planetary gear; 421-second planetary shaft; 422-third gear; 423 -4th gear; 5-first tourbillon; 51-seventh gear; 6-second tourbillon; 61-eighth gear; 7-first transmission assembly; 71-third planetary shaft; 72-third planet wheel; 73-fourth planetary gear; 74-first axle; 75-fifth gear; 8-second transmission assembly; 81-fourth planetary shaft; 82-fifth planetary gear; 83-sixth planetary gear; 84 - Second axle; 85 - sixth gear; 9 - power gear; 10 - center shaft.

Detailed ways

The following describes in detail the embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary, and are intended to be used to explain the present application, but should not be construed as a limitation to the present application.

In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "inner", "outer", etc. is based on the orientation or positional relationship shown in the accompanying drawings, only for the purpose of It is convenient to describe the application and to simplify the description, rather than indicating or implying that the device or element referred to must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the application.

In addition, the terms "first" and "second" are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature defined as "first", "second" may expressly or implicitly include one or more of that feature. In the description of the present application, "plurality" means two or more, unless otherwise expressly and specifically defined.

In this application, unless otherwise expressly specified and limited, the terms "installed", "connected", "connected", "fixed" and other terms should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection , or integrated; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the internal connection of the two elements or the interaction relationship between the two elements. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific situations.

In order to illustrate the technical solutions described in the present application, a detailed description is given below with reference to the specific drawings and embodiments.

Referring to FIG. 1 to FIG. 3 together, the differential adjustment mechanism provided by the embodiment of the present application will now be described. The differential adjustment mechanism provided by the embodiment of the present application is used to connect the indication system of the timepiece to average the travel time error of the indication system. The differential adjustment mechanism includes a planet carrier 1 , a central shaft 10 , a first wheel set 2 , a second wheel set 3 , a first tourbillon 5 , a second tourbillon 6 and a planetary wheel set 4 .

The central shaft 10 penetrates through the planetary carrier 1 and is fixed on the planetary carrier 1 , and the central shaft 10 is used for connecting the indicating system. The central shaft 10 or the planet carrier 1 is the power source, the central shaft 10 rotates synchronously with the planet carrier 1, and drives the indicating system to rotate for running time work. The central shaft 10 is arranged at the center of the planetary carrier 1 , and the planetary carrier 1 rotates with the central shaft 10 as the axis. The first wheel set 2 is rotatably sleeved on the central axis 10 and is spaced apart from the planet carrier 1. The first wheel set 2 forms a clearance fit with the central axis 10 and can rotate with the central axis 10 as the pivot axis, and the first tourbillon 5. A transmission is connected to the first wheel set 2 to transmit its rotational motion to the first wheel set 2. The second wheel set 3 is rotatably sleeved on the central shaft 10 and is spaced apart from the first wheel set 2 and the planetary carrier 1, respectively. The second wheel set 3 forms a clearance fit with the central shaft 10 and can use the central shaft 10 as a pivot axis. rotates, and the second tourbillon 6 is drivingly connected to the second wheel set 3 to transmit its rotational movement to the second wheel set 3 . The planetary gear set 4 forms a clearance fit with the planetary carrier 1, and is rotatably arranged on the planetary carrier 1, and the planetary gear set 4 is meshed with the first wheel set 2 and the second wheel set 3 respectively, so that the planetary carrier 1 and the first wheel set 3 are respectively engaged. The transmission connection between the wheel set 2 and the second wheel set 3, wherein the planetary wheel set 4 and the central shaft 10 are spaced apart to avoid affecting the transmission effect of the planetary wheel set 4 when the central shaft 10 rotates. It should be noted here that during the working process, when the central shaft 10 and the planetary carrier 1 rotate, the planetary gear set 4 rotates in the planetary carrier 1, and at the same time can revolve with the central shaft 10 as the pivot axis. 4 are meshed with the first wheel set 2 and the second wheel set 3 respectively, then the first wheel set 2 and the second wheel set 3 can rotate on the central shaft 10 respectively. When the rotation speed of the first tourbillon 5 is fast and the rotation speed of the second tourbillon 6 is slow, then under the transmission action of the first tourbillon 5 and the second tourbillon 6, the rotation speed of the first wheel group 2 increases, and the second wheel group The rotation speed of 3 decreases, and the first wheel set 2 and the second wheel set 3 are respectively meshed with the planetary wheel set 4, which can average the rotation speed of the planetary wheel set 4 revolving around the central axis 10, so as to achieve the average rotation speed of the planet carrier 1, and also That is, the rotational motions of the first wheel group 2 and the second wheel group 3 are respectively transmitted to the planet carrier 1, and the rotation speed of the planet carrier 1 is half of the sum of the rotation speed of the first wheel group 2 and the rotation speed of the second wheel group 3, so , the rotational speed of planet carrier 1 is:

Among them, n ₁ is the rotational speed of the planet carrier 1, that is, the rotational speed of the central shaft 10, n ₂ is the rotational speed of the first wheel set 2, and n ₃ is the rotational speed of the second wheel set 3, then the rotational speed of the central shaft 10 is the first Half the sum of the RPM of one wheel set 2 and the second wheel set 3.

It should also be noted here that if the planet carrier 1 is fixed to the central shaft 10, and the planet carrier 1 or the central shaft 10 is the driving source, the energy input end of the differential adjustment mechanism is the planet carrier 1, the first wheel set 2 and the The second wheel group 3 is respectively connected to the tourbillon by transmission, then the first wheel group 2 and the second wheel group 3 are both input ends, and the first wheel group 2 and the second wheel group 3 are respectively rotatably sleeved on the central shaft 10, The first wheel set 2 and the second wheel set 3 are both center wheels. In this way, in the embodiment of the present application, the energy input end is the planet carrier 1, and the output end is the two sun wheels, then n ₁ is the rotational speed of the planet carrier 1, and n ₂ and n ₃ are the rotational speeds of the sun wheels.

In the embodiment of the present application, the first tourbillon 5 is drivingly connected to the first wheel set 2, the second tourbillon 6 is drivingly connected to the second wheel set 3, and the first wheel set 2 and the second wheel set 3 are arranged at intervals and both Can rotate around the central axis 10, the planetary gear set 4 is rotatably arranged on the planetary carrier 1 of the central axis 10 and meshes with the first wheelset 2 and the second wheelset 3 respectively. In this way, the planetary carrier 1 is realized by the planetary gearset 4 respectively Connected with the transmission of the first wheel group 2 and the second wheel group 3, the rotational motions of the first tourbillon 5 and the second tourbillon 6 are respectively transmitted to the first wheel group 2 and the second wheel group 3. The first wheel group The rotational motions of 2 and the second wheel group 3 can be respectively transmitted to the planet carrier 1 through the planetary wheel group 4, then the rotational speed of the planet carrier 1 is half of the sum of the rotational speed of the first wheel group 2 and the rotational speed of the second wheel group 3, That is, the first tourbillon 5 and the second tourbillon 6 can average the rotational speed of the planet carrier 1 , thereby reducing the travel time error of the central axis 10 . In addition, the first wheel set 2 and the second wheel set 3 are respectively rotatably sleeved on the central shaft 10, which improves the rotation flexibility of the first wheel set 2 and the second wheel set 3, and the planetary wheel set 4 is rotatably arranged on the planet carrier 1, the planetary gear set 4 can rotate on the planet carrier 1, and can revolve around the central axis 10 as the pivot axis, and the planetary gear set 4 is meshed with the first wheel set 2 and the second wheel set 3 respectively. The flexibility of the planetary wheel set 4 is facilitated to realize the rotational motion transmission of the first wheel set 2 and the second wheel set 3 to the planet carrier 1, which improves the stability of the speed transmission, which is conducive to reducing the travel time error, and the entire differential adjustment mechanism. The structure is very simple.

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the planetary gear set 4 includes a first planetary gear 41 and a second planetary gear 42 , the first planetary gear 41 forms a clearance fit with the planet carrier 1 , and the first planetary gear 41 forms a clearance fit. The wheel 41 is rotatably arranged on the planetary carrier 1 and meshes with the first wheel set 2. The first planetary wheel 41 is spaced apart from the central shaft 10. When the central shaft 10 and the planetary carrier 1 rotate, the first planetary wheel 41 is on the planetary carrier 1. It rotates internally, and also revolves with the central axis 10 as the pivot axis. Correspondingly, the second planetary gear 42 forms a clearance fit with the planetary carrier 1, and the second planetary gear 42 is rotatably arranged on the planetary carrier 1 and meshes with the second wheel set 3. The second planetary gear 42 is spaced apart from the central shaft 10. Then, when the central shaft 10 and the planet carrier 1 rotate, the second planetary wheel 42 rotates in the planet carrier 1 and also revolves with the central shaft 10 as the pivot axis.

In a specific embodiment, the first planetary gear 41 is meshed with the first wheel set 2 , the second planetary wheel 42 is meshed with the second wheel set 3 , and the first planetary gear 41 is meshed with the second planetary gear 42 , then the first The wheel set 2 and the second wheel set 3 are connected by the first planetary wheel 41 and the second planetary wheel 42 in turn. Under the transmission action of the first tourbillon 5 and the second tourbillon 6, the first wheel set 2 and the The second wheel set 3 can average the rotational speed of the planetary gear set 4 revolving around the central axis 10 , that is, average the rotational speed of the planet carrier 1 through the first planetary gear 41 and the second planetary gear 42 . By meshing the first planetary gear 41 with the second planetary gear 42 , the flexibility of the planetary gear set 4 is improved, the rotation speed of the planetary carrier 1 is averaged, and the rotation error of the planetary carrier 1 is reduced.

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the first planetary gear 41 includes a first planetary shaft 411 , a first gear 412 and a second gear 413 , and the first gear 412 and the second gear 413 are respectively fixed at opposite ends of the first planetary shaft 411 . The first planetary shaft 411 is rotatably disposed on the planetary carrier 1 . Specifically, the planetary carrier 1 has first pivot holes spaced apart from the central axis 10 , the first planetary shaft 411 is penetrated in the first pivoting hole, and The first planetary shaft 411 can rotate in the first pivot hole, and can also revolve with the central axis 10 as the pivot axis, so as to drive the first gear 412 and the second gear 413 fixed on both ends of the first planetary shaft 411 to rotate on their own. and revolution. The first gear 412 and the second gear 413 are spaced apart from the central shaft 10 , the first gear 412 and/or the second gear 413 are engaged with the second planetary gear 42 , and the first gear 412 is engaged with the first wheel set 2 .

In a specific embodiment, as shown in FIGS. 3 and 4 , the first wheel set 2 and the second wheel set 3 are rotatably sleeved on the central shaft 10 , and the first wheel set 2 and the second wheel set 3 are distributed on the upper and lower sides of the planetary carrier 1 respectively, the first planetary shaft 411 penetrates the planetary carrier 1 , and the first gear 412 and the second gear 413 are distributed on the upper and lower sides of the planetary carrier 1 . The first gear 412 is engaged with the first wheel set 2 , and the first gear 412 and/or the second gear 413 is engaged with the second planetary gear 42 . Specifically: when the second planetary gear 42 is arranged on the upper side of the planet carrier 1 , the second planetary gear 42 is engaged with the first gear 412 ; when the second planetary gear 42 is arranged on the lower side of the planetary carrier 1 , the second planetary gear 42 is The wheel 42 meshes with the second gear 413; when the second planetary gear 42 penetrates the planet carrier 1, the second planetary gear 42 meshes with the first gear 412, or meshes with the second gear 413, or meshes with the first gear 412 and The second gear 413 .

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the second planetary gear 42 includes a second planetary shaft 421 , a third gear 422 and a fourth gear 423 , and the third gear 422 and the fourth gear 423 are respectively fixed At opposite ends of the second planetary shaft 421 , the second planetary shaft 421 is rotatably arranged on the planetary carrier 1 . Specifically, the planetary carrier 1 is provided with second pivots spaced apart from the central shaft 10 and the first pivoting holes, respectively. The second planetary shaft 421 passes through the second pivoting hole, and the second planetary shaft 421 can rotate in the second pivoting hole, and can also revolve with the central axis 10 as the pivoting axis, so as to drive the fixed The third gear 422 and the fourth gear 423 connected to both ends of the second planetary shaft 421 rotate and revolve. The third gear 422 and the fourth gear 423 are spaced apart from the central shaft 10 , the third gear 422 and/or the fourth gear 423 are engaged with the first planetary gear 41 , and the third gear 422 is engaged with the second wheel set 3 .

As shown in FIG. 3 and FIG. 4 , the first wheel set 2 and the second wheel set 3 are rotatably sleeved on the central shaft 10 , and the first wheel set 2 and the second wheel set 3 are respectively distributed on the planet carrier 1 On the upper and lower sides of the planetary carrier 1 , the second planetary shaft 421 penetrates the planetary carrier 1 , and the fourth gear 423 and the third gear 422 are respectively distributed on the upper and lower sides of the planetary carrier 1 . The third gear 422 meshes with the second wheel set 3 , and the third gear 422 and/or the fourth gear 423 meshes with the second planetary gear 42 . Specifically: when the first planetary gear 41 is arranged on the lower side of the planet carrier 1 , the first planetary gear 41 is engaged with the third gear 422 ; when the first planetary gear 41 is arranged on the upper side of the planetary carrier 1 , the first planetary gear 41 is The wheel 41 is engaged with the fourth gear 423; when the first planetary gear 41 penetrates the planet carrier 1, the first planetary gear 41 is engaged with the third gear 422, or with the fourth gear 423, or with the third gear 422 and Fourth gear 423 .

In a specific embodiment, as shown in FIGS. 3 and 4 , the first wheel set 2 and the second wheel set 3 are respectively distributed on the upper and lower sides of the planet carrier 1 , the first planet shaft 411 and the second planet The shafts 421 all pass through the planet carrier 1, the first gear 412 is arranged on the upper side of the planet carrier 1, the second gear 413 is arranged on the lower side of the planet carrier 1, the third gear 422 is arranged on the lower side of the planet carrier 1, and the fourth gear 423 is provided on the upper side of the planet carrier 1 . The first gear 412 meshes with the first wheel set 2 and the fourth gear 423 respectively, and the third gear 422 meshes with the second wheel set 3 and the second gear 413 respectively. In this way, the arrangement of the first gear 412 and the third gear 422 can be The meshing transmission of the first wheel set 2 and the second wheel set 3 on the upper and lower sides of the planet carrier 1 are respectively realized, and the first gear 412 is meshed with the fourth gear 423, and the second gear 413 is meshed with the third gear 422. The meshing of the first planetary wheel 41 and the second planetary wheel 42 improves the transmission stability of the first wheel set 2 and the second wheel set 3 and the planetary wheel set 4 respectively.

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the first wheel set 2 includes a first center wheel 21 and a second center wheel 22 , and the first center wheel 21 and the second center wheel 22 are fixedly connected and both Distributed at intervals from the planet carrier 1, the first center wheel 21 and the second center wheel 22 are rotated and sleeved on the center shaft 10 at the same time, that is, the first center wheel 21 and the second center wheel 22 can pivot on the center shaft 10 at the same time. The shaft rotates. The first center wheel 21 is drivingly connected to the first tourbillon 5 , and the second center wheel 22 is meshed with the planetary gear set 4 , specifically, the second center wheel 22 is meshed with the first gear 412 of the first planetary wheel 41 . Wherein, in this embodiment, n ₂ is the rotational speed of the first central wheel 21 or the second central wheel 22 , and the rotational speed of the first central wheel 21 and the rotational speed of the second central wheel 22 here are equal.

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the second wheel set 3 includes a third center wheel 31 and a fourth center wheel 32 , and the third center wheel 31 and the fourth center wheel 32 are fixedly connected and both Spaced from the planet carrier 1, the third center wheel 31 and the fourth center wheel 32 are rotated and sleeved on the center shaft 10 at the same time, that is, the third center wheel 31 and the fourth center wheel 32 can pivot on the center shaft 10 at the same time. The shaft rotates. The third center wheel 31 is drivingly connected to the second tourbillon 6 , and the fourth center wheel 32 is engaged with the planetary gear set 4 , specifically, the fourth center wheel 32 is engaged with the third gear 422 of the second planetary wheel 42 . Wherein, in this embodiment, n ₃ is the rotational speed of the third central wheel 31 or the fourth central wheel 32 , and the rotational speed of the third central wheel 31 and the rotational speed of the fourth central wheel 32 here are equal.

In this way, in this embodiment, the first center wheel 21 is drivingly connected to the first tourbillon 5 , and the third center wheel 31 is drivingly connected to the second tourbillon 6 . During operation, when the central shaft 10 and the planetary carrier 1 rotate, the first gear 412 , the second gear 413 , the third gear 422 and the fourth gear 423 rotate in the planetary carrier 1 , and can use the central shaft 10 as a pivot at the same time The shaft revolves. Since the first gear 412 is engaged with the second center wheel 22 and the third gear 422 is engaged with the fourth center wheel 32 , the first center wheel 21 , the second center wheel 22 , the third center wheel 31 and the fourth center wheel 32 are all They can be rotated on the central axis 10, respectively. When the rotation speed of the first tourbillon 5 is fast and the rotation speed of the second tourbillon 6 is slow, then under the transmission action of the first tourbillon 5 and the second tourbillon 6, the rotation speed of the first center wheel 21 increases, and the second center wheel The rotational speed of 22 also increases accordingly, the rotational speed of the third central wheel 31 decreases, and the rotational speed of the fourth central wheel 32 also decreases accordingly, then through the first gear 412, the second gear 413, the third gear 422 and the fourth gear 423, the rotational motion of the second sun wheel 22 and the fourth sun wheel 32 can be transmitted to the planet carrier 1, so that half of the sum of the rotational speeds of the first sun wheel 21 and the sum of the rotational speeds of the third sun wheel 31 is the planet carrier 1 The rotation speed is equivalent to reducing the rotation error of the planet carrier 1, that is, reducing the travel time error of the indicating system.

It should also be noted here that the first gear 412 , the second gear 413 , the third gear 422 , the fourth gear 423 , the second center wheel 22 and the fourth center wheel 32 may be set to have the same number of teeth, that is, the same number of teeth. The first center wheel 21 and the third center wheel 31 can be set to have the same number of teeth and are the same gear. In this way, in this embodiment, only two gear cutters of the differential adjustment mechanism can be provided. One gear cutter is the first gear 412, the second gear 413, the third gear 422, the fourth gear 423, the second center gear The wheel 22 and the fourth center wheel 32, the second type of gear cutters are the first center wheel 21 and the third center wheel 31, and the types of gear cutters used are very few, which facilitates the formation of the differential speed adjustment mechanism and reduces the manufacturing cost.

In a specific embodiment, the first center wheel 21 and the third center wheel 31 are both larger than the second center wheel 22 and the fourth center wheel 32 , and the sizes of the first center wheel 21 and the third center wheel 31 and the planets can be set here. The same as the carrier 1, it is convenient to realize that the rotational speed of the planet carrier 1 is averaged by the rotational speed of the first sun wheel 21 and the rotational speed of the third center, so that the rotational speed of the planet carrier 1 is the sum of the rotational speed of the first sun wheel 21 and the rotational speed of the third sun wheel 31. half.

In one embodiment, please refer to FIG. 3 and FIG. 4 together, the differential adjustment mechanism further includes a first transmission assembly 7, and the first transmission assembly 7 is respectively drivingly connected to the first wheel set 2 and the first tourbillon 5, The transmission connection between the first tourbillon 5 and the first wheel group 2 is realized. Specifically, the first transmission assembly 7 includes a third planetary shaft 71 , a third planetary gear 72 and a fourth planetary gear 73 fixed on both ends of the third planetary shaft 71 , and the third planetary gear 72 is engaged with the first wheel set 2 . The first central wheel 21 and the fourth planetary wheel 73 are drivingly connected to the first tourbillon 5 .

Referring to FIG. 1 , in a specific embodiment, the first transmission assembly 7 further includes a first axle 74 and a fifth gear 75 fixed thereon, and the fifth gear 75 is engaged with the fourth planetary gear 73 . The first tourbillon 5 is provided with a seventh gear 51 with external teeth, and the fifth gear 75 meshes with the seventh gear 51 . In this way, the first sun gear 21 meshes with the third planetary gear 72, the third planetary gear 72 is fixedly connected to the fourth planetary gear 73 through the third planetary shaft 71, the fourth planetary gear 73 meshes with the fifth gear 75, and the fifth gear 75 meshes with the seventh gear 51 on the first tourbillon 5 , thereby realizing the transmission connection between the first center wheel 21 and the first tourbillon 5 .

In one embodiment, the differential adjustment mechanism further includes a second transmission assembly 8, and the second transmission assembly 8 is drivingly connected to the second wheel set 3 and the second tourbillon 6, respectively, to realize the second tourbillon 6 and the second wheel. Group 3 drive connections. Specifically, the second transmission assembly 8 includes a fourth planetary shaft 81 , a fifth planetary gear 82 and a sixth planetary gear 83 fixed on both ends of the fourth planetary shaft 81 , and the fifth planetary gear 82 is engaged with the second wheel set 3 . The third center wheel 31 and the sixth planetary wheel 83 are drive-connected to the second tourbillon 6 .

Referring to FIG. 1 , in a specific embodiment, the second transmission assembly 8 further includes a second axle 84 and a sixth gear 85 fixed thereon. The sixth gear 85 is engaged with the sixth planetary gear 83 . The second tourbillon 6 is provided with an eighth gear 61 with external teeth, and the sixth gear 85 is engaged with the eighth gear 61 . In this way, the third sun gear 31 meshes with the fifth planetary gear 82 , the fifth planetary gear 82 is fixedly connected to the sixth planetary gear 83 through the fourth planetary shaft 81 , the sixth planetary gear 83 meshes with the sixth gear 85 , and the sixth gear 85 meshes with the eighth gear 61 on the second tourbillon 6 , thereby realizing the transmission connection between the third center wheel 31 and the second tourbillon 6 .

In one embodiment, please refer to FIG. 1 , the differential adjustment mechanism further includes a power source, the power source includes a power gear 9 , the planet carrier 1 and the power gear 9 both have external teeth, and the power gear 9 meshes with the planet carrier 1 . When the power gear 9 rotates, the planet carrier 1 meshes with the power gear 9 and rotates, so that the central shaft 10 and the planet carrier 1 rotate synchronously. At this time, the first tourbillon 5 and the second tourbillon 6 can pass the first wheel set 2 and the second tourbillon The second wheel set 3 realizes the average rotation speed of the planet carrier 1 and reduces the travel time error of the central shaft 10 .

The embodiment of the present application also provides a wristwatch, including an indicating system and a differential adjustment mechanism, wherein the indicating system is used for running time work, and the indicating system is connected to the central shaft 10 of the differential adjustment mechanism. The differential adjustment mechanism in this embodiment is the same as the differential adjustment mechanism in the previous embodiment. For details, please refer to the relevant description of the differential adjustment mechanism in the previous embodiment, which will not be repeated here.

In the watch provided by the embodiment of the present application, by adopting the setting of the differential adjustment mechanism, the planet carrier 1 is respectively connected with the first wheel group 2 and the second wheel group 3 through the planetary wheel group 4, and then the first tourbillon 5 and the rotational movement of the second tourbillon 6 are respectively transmitted to the first wheel set 2 and the second wheel set 3, and the rotational movement of the first wheel set 2 and the second wheel set 3 can be respectively transmitted to the planet carrier through the planetary wheel set 4 1, then the rotational speed of the planet carrier 1 is half of the sum of the rotational speed of the first wheel group 2 and the rotational speed of the second wheel group 3, that is, the first tourbillon 5 and the second tourbillon 6 can average the rotational speed of the planet carrier 1. , thereby reducing the travel time error of the indicating system connected to the central shaft 10 . In addition, the first wheel set 2 and the second wheel set 3 are respectively rotatably sleeved on the central shaft 10, which improves the rotation flexibility of the first wheel set 2 and the second wheel set 3, and the planetary wheel set 4 is rotatably arranged on the planet carrier 1, the planetary gear set 4 can rotate on the planet carrier 1, and can revolve around the central axis 10 as the pivot axis, and the planetary gear set 4 is meshed with the first wheel set 2 and the second wheel set 3 respectively. The flexibility of the planetary wheel set 4 is facilitated to realize the rotational motion transmission of the first wheel set 2 and the second wheel set 3 to the planet carrier 1, which improves the stability of the speed transmission, which is beneficial to reduce the travel time error of the indicating system, and the entire differential speed. The structure of the adjustment mechanism is very simple, which simplifies the structure of the watch.

The above descriptions are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection of the present application. within the range.

Claims (10)

1. a differential speed adjusting mechanism, is characterized in that, comprises: planet carrier; a central shaft, fixed on the planet carrier, the central shaft is used to connect the indicating system; a first wheel set, which is rotatably sleeved on the central shaft, and is connected to the first tourbillon by transmission; a second wheel set, which is rotatably sleeved on the central shaft and is spaced apart from the first wheel set, and the second wheel set is drivingly connected to the second tourbillon; The planetary gear set is rotatably arranged on the planet carrier and meshes with the first wheel set and the second wheel set respectively. 2. The differential adjustment mechanism of claim 1, wherein the planetary gear set comprises: a first planetary wheel, which is rotatably arranged on the planet carrier and is engaged with the first wheel set; The second planetary gear is rotatably arranged on the planetary carrier and is engaged with the second wheel set, and the first planetary gear is engaged with the second planetary gear. 3. The differential adjustment mechanism according to claim 2, wherein the first planetary gear comprises a first planetary shaft, a first gear and a second gear, the first gear and the second gear are respectively fixed on both ends of the first planetary shaft; the first planetary shaft is rotatably arranged on the planet carrier, and the first gear and/or the second gear are engaged with the second planetary gear , and the first gear meshes with the first wheel set. 4. The differential adjustment mechanism according to claim 2, wherein the second planetary gear comprises a second planetary shaft, a third gear and a fourth gear, the third gear and the fourth gear respectively fixed on both ends of the second planetary shaft; the second planetary shaft is rotatably arranged on the planet carrier, and the third gear and/or the fourth gear are engaged with the first planetary gear , and the third gear meshes with the second wheel set. 5 . The differential adjustment mechanism according to claim 1 , wherein the first wheel set comprises a first center wheel and a second center wheel that are sleeved on the center shaft simultaneously, and the first wheel set is rotatable. A center wheel is drivingly connected to the first tourbillon, and the second center wheel is fixed to the first center wheel and meshes with the planetary gear set. 6 . The differential adjustment mechanism according to claim 1 , wherein the second wheel set comprises a third center wheel and a fourth center wheel that are sleeved on the central shaft simultaneously, and the The three center wheels are drivingly connected to the second tourbillon, and the fourth center wheel is fixed to the third center wheel and meshes with the planetary gear set. 7. The differential adjustment mechanism according to any one of claims 1 to 6, wherein the differential adjustment mechanism further comprises a first transmission assembly comprising a third planetary shaft and a third planetary gear and a fourth planetary gear fixed on both ends of the third planetary shaft, the third planetary gear is engaged with the first wheel set, and the fourth planetary gear is drivingly connected to the first rotor flywheel. 8. The differential adjustment mechanism according to any one of claims 1 to 6, wherein the differential adjustment mechanism further comprises a second transmission assembly comprising a fourth planetary shaft and A fifth planetary gear and a sixth planetary gear fixed on both ends of the fourth planetary shaft, the fifth planetary gear is engaged with the second wheel set, and the sixth planetary gear is drivingly connected to the second rotor flywheel. 9 . The differential adjustment mechanism according to claim 1 , wherein the differential adjustment mechanism further comprises a power source, the power source comprises a power gear, and the planet carrier has an outer teeth, the power gear meshes with the planet carrier. 10. A wristwatch, characterized by comprising the differential adjustment mechanism according to any one of claims 1-9.

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