Differential adjustment mechanism and watch

Abstract

This application is applicable to the field of clock technology, and provides a differential adjustment mechanism and a watch, including: a planet carrier; a central shaft fixed to the planet carrier, and the central shaft is used to connect an indication system; a first wheel set rotatably sleeved on the central shaft and drivingly connected to a first tourbillon; a second wheel set rotatably sleeved on the central shaft and spaced from the first wheel set, and the second wheel set is drivingly connected to a second tourbillon; a planet gear set rotatably arranged on the planet carrier and meshing with the first wheel set and the second wheel set respectively. In this embodiment, the first tourbillon and the second tourbillon can average the rotation speed of the planet carrier, thereby reducing the timekeeping error of the central shaft. In addition, the planet gear set meshes with the first wheel set and the second wheel set respectively, which is convenient for transmitting the rotational motion of the first wheel set and the second wheel set to the planet carrier, improving the stability of the rotational speed transmission, facilitating the reduction of the timekeeping error, and the structure of the entire differential adjustment mechanism is very simple.

Description

Technical Field

[0001] This application belongs to the technical field of clocks and watches. More specifically, it relates to a differential adjustment mechanism and a watch. Background Art

[0002] A clock and watch is a timekeeping device and a precision instrument for measuring and indicating time. A clock and watch has an indicating system that can rotate to indicate time.

[0003] When the indicating system of a clock and watch rotates, there will always be a certain timekeeping error. Currently, generally, two tourbillons cooperate with a differential gear train to form a differential adjustment mechanism to average the timekeeping error of the indicating system, thereby reducing the timekeeping error of the indicating system. However, currently, the differential gear train is generally formed by combining multiple central gears and / or multiple planetary gears, and the transmission efficiency of the rotational motion is low and unstable, which is not conducive to meeting the requirement of reducing the timekeeping error, and the structure of the entire differential adjustment mechanism is very complex. Summary of the Invention

[0004] One of the purposes of the embodiments of this application is to provide a differential adjustment mechanism, aiming to solve the technical problems of unstable transmission and complex structure of the differential adjustment mechanism in the prior art.

[0005] To solve the above technical problems, the technical solution adopted in the embodiments of this application is:

[0006] A differential adjustment mechanism is provided, including:

[0007] A planet carrier;

[0008] A central shaft, fixed on the planet carrier, and the central shaft is used to connect the indicating system;

[0009] A first gear set, rotatably sleeved on the central shaft and drivingly connected to the first tourbillon;

[0010] A second gear set, rotatably sleeved on the central shaft and spaced apart from the first gear set, and the second gear set is drivingly connected to the second tourbillon;

[0011] A planetary gear set, rotatably arranged on the planet carrier and meshing with the first gear set and the second gear set respectively.

[0012] In one embodiment, the planetary gear set includes:

[0013] A first planetary gear, rotatably arranged on the planet carrier and meshing with the first gear set;

[0014] A second planetary gear, rotatably arranged on the planet carrier and meshing with the second gear set, and the first planetary gear meshes with the second planetary gear.

[0015] 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 planetary carrier, the first gear and / or the second gear are meshed with the second planetary gear, and the first gear is meshed with the first wheel set.

[0016] 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 two ends of the second planetary shaft; the second planetary shaft is rotatably arranged on the planetary carrier, the third gear and / or the fourth gear are meshed with the first planetary gear, and the third gear is meshed with the second wheel set.

[0017] In one embodiment, the first wheel set includes a first center wheel and a second center wheel which are simultaneously rotatably mounted on the center shaft, the first center wheel is transmission-connected to the first tourbillon, and the second center wheel is fixedly connected to the first center wheel and meshed with the planetary wheel set.

[0018] In one embodiment, the second wheel set includes a third center wheel and a fourth center wheel which are simultaneously rotatably mounted on the center shaft, the third center wheel is transmission-connected to the second tourbillon, and the fourth center wheel is fixedly connected to the third center wheel and meshed with the planetary wheel set.

[0019] In one embodiment, the differential adjustment mechanism also includes a first transmission assembly, which includes a third planetary shaft and a third planetary gear and a fourth planetary gear fixed to both ends of the third planetary shaft, the third planetary gear is meshed with the first wheel set, and the fourth planetary gear is transmission-connected to the first tourbillon.

[0020] In one embodiment, the differential adjustment mechanism also includes a second transmission assembly, the second transmission assembly includes a fourth planetary shaft and a fifth planetary gear and a sixth planetary gear fixed to both ends of the fourth planetary shaft, the fifth planetary gear is meshed with the second wheel set, and the sixth planetary gear is transmission-connected to the second tourbillon.

[0021] 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 meshed with the planet carrier.

[0022] An embodiment of the present application also provides a watch, comprising the above-mentioned differential adjustment mechanism.

[0023] The beneficial effects of the differential adjustment mechanism and the watch provided by this application are as follows: Compared with the prior art, in this application, the first tourbillon is drivingly connected to the first wheel set, the second tourbillon is drivingly connected to the second wheel set, the first wheel set and the second wheel set are arranged at intervals and can both rotate around the central axis, the planetary gear set is rotatably arranged on the planet carrier of the central axis and meshes with the first wheel set and the second wheel set respectively. Thus, the planet carrier realizes the driving connection with the first wheel set and the second wheel set respectively through the planetary gear set, so the rotational movements of the first tourbillon and the second tourbillon are respectively transmitted to the first wheel set and the second wheel set, and the rotational movements of the first wheel set and the second wheel set can be respectively transmitted to the planet carrier through the planetary gear set. Then, the rotational speed of the planet carrier is half of the sum of the rotational speeds of the first wheel set and the second wheel set, that is, the first tourbillon and the second tourbillon can average the rotational speed of the planet carrier, thereby reducing the timekeeping error of the central axis. In addition, the first wheel set and the second wheel set are respectively rotatably sleeved on the central axis, which improves the rotational flexibility of the first wheel set and the second wheel set. The planetary gear set is rotatably arranged on the planet carrier, so the planetary gear set can rotate on its own on the planet carrier and can revolve around the central axis as the pivot axis, and the planetary gear set meshes with the first wheel set and the second wheel set respectively, which improves the flexibility of the planetary gear set, facilitates the transmission of the rotational movements of the first wheel set and the second wheel set to the planet carrier, improves the transmission stability, is conducive to reducing the timekeeping error, and the structure of the entire differential adjustment mechanism is very simple. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the embodiments of this application, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the following drawings are only some embodiments of this application. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0025] Figure 1 Stereoscopic structure diagram of the differential adjustment mechanism provided by the embodiment of this application;

[0026] Figure 2 Cross-sectional view of the differential adjustment mechanism provided by the embodiment of this application;

[0027] Figure 3 is Figure 2 Partially enlarged view after rotation at A in

[0028] Figure 4 Partial side view of the differential adjustment mechanism provided by the embodiment of this application.

[0029] Among them, the reference numerals in the drawings are as follows:

[0030] 1 - Planet carrier; 2 - First gear set; 21 - First sun gear; 22 - Second sun gear; 3 - Second gear set; 31 - Third sun gear; 32 - Fourth sun gear; 4 - Planet gear set; 41 - First planet gear; 411 - First planet shaft; 412 - First gear; 413 - Second gear; 42 - Second planet gear; 421 - Second planet shaft; 422 - Third gear; 423 - Fourth gear; 5 - First tourbillon; 51 - Seventh gear; 6 - Second tourbillon; 61 - Eighth gear; 7 - First transmission assembly; 71 - Third planet shaft; 72 - Third planet gear; 73 - Fourth planet gear; 74 - First gear shaft; 75 - Fifth gear; 8 - Second transmission assembly; 81 - Fourth planet shaft; 82 - Fifth planet gear; 83 - Sixth planet gear; 84 - Second gear shaft; 85 - Sixth gear; 9 - Power gear; 10 - Central shaft. Detailed implementation manners

[0031] The embodiments of the present application will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the accompanying drawings are exemplary and are intended to explain the present application and should not be construed as a limitation to the present application.

[0032] 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, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present application.

[0033] 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 implicitly indicating the number of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, "a plurality" means two or more, unless otherwise specifically defined.

[0034] In the present application, unless otherwise clearly defined and limited, the terms "mounted", "connected", "connected to", "fixed", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0035] In order to illustrate the technical solution described in this application, a detailed description is given below in conjunction with specific drawings and embodiments.

[0036] Please also read Figures 1 to 3 The differential adjustment mechanism provided in the embodiment of the present application is now described. The differential adjustment mechanism provided in the embodiment of the present application is used to connect the indication system of the clock to average the travel time error of the indication system. The differential adjustment mechanism includes a planetary frame 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.

[0037] The central shaft 10 passes through the planetary frame 1 and is fixed on the planetary frame 1. The central shaft 10 is used to connect the indication system. The central shaft 10 or the planetary frame 1 is a power source. The central shaft 10 rotates synchronously with the planetary frame 1 to drive the indication system to rotate to perform the timekeeping work. Among them, the central shaft 10 is arranged at the center position of the planetary frame 1, and the planetary frame 1 rotates with the central shaft 10 as the axis. The first wheel set 2 is rotatably sleeved on the central shaft 10 and is spaced apart from the planetary frame 1. The first wheel set 2 forms a clearance fit with the central shaft 10 and can rotate with the central shaft 10 as the pivot axis, and the first tourbillon 5 is transmission-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 frame 1 respectively. The second wheel set 3 forms a clearance fit with the central shaft 10 and can rotate with the central shaft 10 as the pivot axis, and the second tourbillon 6 is transmission-connected to the second wheel set 3 to transmit its rotational motion 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 respectively meshed with the first wheel set 2 and the second wheel set 3, so as to realize the transmission connection between the planetary carrier 1 and the first wheel set 2 and the second wheel set 3, respectively, wherein the planetary gear set 4 is spaced apart from the central shaft 10 to avoid affecting the transmission effect of the planetary gear 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 around the central shaft 10 as the pivot axis, and since the planetary gear set 4 is respectively meshed with the first wheel set 2 and the second wheel set 3, the first wheel set 2 and the second wheel set 3 can respectively rotate on the central shaft 10. When the first tourbillon 5 rotates at a fast speed and the second tourbillon 6 rotates at a slow speed, the speed of the first wheel set 2 increases and the speed of the second wheel set 3 decreases under the transmission action of the first tourbillon 5 and the second tourbillon 6. The first wheel set 2 and the second wheel set 3 are respectively engaged with the planetary wheel set 4, so that the speed of the planetary wheel set 4 revolving around the central axis 10 can be averaged, thereby realizing the average speed of the planetary carrier 1, that is, the rotational motion of the first wheel set 2 and the second wheel set 3 are respectively transmitted to the planetary carrier 1, and the speed of the planetary carrier 1 is half of the sum of the speeds of the first wheel set 2 and the second wheel set 3. In this way, the speed of the planetary carrier 1 is:

[0038]

[0039] Among them, n 1 is the speed of the planet carrier 1, that is, the speed of the central shaft 10, n 2 is the speed of the first wheel group 2, n 3 is the rotation speed of the second wheel set 3 , then the rotation speed of the central shaft 10 is half of the sum of the rotation speeds of the first wheel set 2 and the second wheel set 3 .

[0040] It should also be noted that the planet carrier 1 is fixedly connected to the central shaft 10, and the planet carrier 1 or the central shaft 10 is the power source, so the energy input end of the differential adjustment mechanism is the planet carrier 1, and the first wheel set 2 and the second wheel set 3 are respectively connected to the tourbillon in a transmission manner, so the first wheel set 2 and the second wheel set 3 are both input ends, and the first wheel set 2 and the second wheel set 3 are respectively rotatably sleeved on the central shaft 10, and 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 center wheels, then n 1 is the speed of planet carrier 1, n 2 and n 3 are the rotation speeds of the center wheel.

[0041] In the embodiment of the present application, the first tourbillon 5 is connected to the first wheel set 2 through transmission, and the second tourbillon 6 is connected to the second wheel set 3 through transmission. The first wheel set 2 and the second wheel set 3 are arranged at intervals and can rotate around the central axis 10. The planetary wheel set 4 is rotatably arranged on the planetary carrier 1 of the central axis 10 and is respectively engaged with the first wheel set 2 and the second wheel set 3. In this way, the planetary carrier 1 is respectively connected to the first wheel set 2 and the second wheel set 3 through the planetary wheel set 4. The rotational motion of the first tourbillon 5 and the second tourbillon 6 is respectively transmitted to the first wheel set 2 and the second wheel set 3. The rotational motion of the first wheel set 2 and the second wheel set 3 can be respectively transmitted to the planetary carrier 1 through the planetary wheel set 4. The rotational speed of the planetary carrier 1 is half of the sum of the rotational speeds of the first wheel set 2 and the second wheel set 3. That is, the first tourbillon 5 and the second tourbillon 6 can average the rotational speed of the planetary 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 axis 10, which improves the rotational flexibility of the first wheel set 2 and the second wheel set 3. The planetary wheel set 4 is rotatably arranged on the planetary carrier 1, so that the planetary wheel set 4 can rotate on the planetary carrier 1 and can revolve around the central axis 10 as the pivot axis. The planetary wheel set 4 is respectively meshed with the first wheel set 2 and the second wheel set 3, which improves the flexibility of the planetary wheel set 4, facilitates the transmission of the rotational motion of the first wheel set 2 and the second wheel set 3 to the planetary carrier 1, improves the stability of the speed transmission, and is beneficial to reduce the travel time error. In addition, the structure of the entire differential adjustment mechanism is very simple.

[0042] In one embodiment, please refer to Figure 3 and Figure 4The 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 planetary carrier 1, and the first planetary gear 41 is rotatably arranged on the planetary carrier 1 and meshed with the first wheel set 2. The first planetary gear 41 is spaced apart from the central axis 10. When the central axis 10 and the planetary carrier 1 rotate, the first planetary gear 41 rotates in the planetary carrier 1 and also revolves around the central axis 10 as a 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 meshed with the second wheel set 3. The second planetary gear 42 is spaced apart from the central axis 10. When the central axis 10 and the planetary carrier 1 rotate, the second planetary gear 42 rotates in the planetary carrier 1 and also revolves around the central axis 10 as a pivot axis.

[0043] In a specific embodiment, the first planetary gear 41 is meshed with the first wheel set 2, the second planetary gear 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 wheel set 2 and the second wheel set 3 are sequentially connected through the first planetary gear 41 and the second planetary gear 42, and under the transmission action of the first tourbillon 5 and the second tourbillon 6, the first wheel set 2 and the second wheel set 3 can average the speed of the planetary gear set 4 revolving around the central axis 10, that is, the speed of the planet carrier 1 is averaged through the first planetary gear 41 and the second planetary gear 42. The meshing of the first planetary gear 41 and the second planetary gear 42 improves the flexibility of the planetary gear set 4, facilitates the average speed of the planet carrier 1, and reduces the rotation error of the planet carrier 1.

[0044] In one embodiment, please refer to Figure 3 and Figure 4 The first planetary gear 41 includes a first planetary shaft 411, a first gear 412 and a second gear 413. The first gear 412 and the second gear 413 are respectively fixed to opposite ends of the first planetary shaft 411. The first planetary shaft 411 is rotatably arranged on the planetary carrier 1. Specifically, the planetary carrier 1 has a first pivot hole spaced apart from the central axis 10. The first planetary shaft 411 is inserted into the first pivot hole. The first planetary shaft 411 can rotate in the first pivot hole and can also revolve around the central axis 10 as the pivot axis, thereby driving the first gear 412 and the second gear 413 fixed to the two ends of the first planetary shaft 411 to rotate and revolve. The first gear 412 and the second gear 413 are both spaced apart from the central axis 10. The first gear 412 and / or the second gear 413 are meshed with the second planetary gear 42, and the first gear 412 is meshed with the first wheel set 2.

[0045] In a specific embodiment, Figure 3 and Figure 4In the perspective shown, 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 upper and lower sides of the planet carrier 1. The first planet shaft 411 penetrates through the planet carrier 1, and the first gear 412 and the second gear 413 are distributed on the upper and lower sides of the planet carrier 1. The first gear 412 meshes with the first wheel set 2, and the first gear 412 and / or the second gear 413 mesh with the second planet gear 42. Specifically: when the second planet gear 42 is arranged on the upper side of the planet carrier 1, the second planet gear 42 meshes with the first gear 412; when the second planet gear 42 is arranged on the lower side of the planet carrier 1, the second planet gear 42 meshes with the second gear 413; when the second planet gear 42 penetrates through the planet carrier 1, the second planet 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 respectively.

[0046] In one embodiment, please refer to Figure 3 and Figure 4 as well. The second planet gear 42 includes a second planet shaft 421, a third gear 422, and a fourth gear 423. The third gear 422 and the fourth gear 423 are respectively fixed to opposite ends of the second planet shaft 421. The second planet shaft 421 is rotatably arranged on the planet carrier 1. Specifically, the planet carrier 1 is provided with second pivot holes that are spaced apart from the central shaft 10 and the first pivot hole respectively. The second planet shaft 421 passes through the second pivot hole, and the second planet shaft 421 can rotate on its own axis within the second pivot hole and can also revolve around the central shaft 10 as a pivot axis, so as to drive the third gear 422 and the fourth gear 423 fixed to both ends of the second planet shaft 421 to rotate and revolve. Both 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 mesh with the first planet gear 41, and the third gear 422 meshes with the second wheel set 3.

[0047] As Figure 3 and Figure 4 shown in the perspective, 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 upper and lower sides of the planet carrier 1. The second planet shaft 421 penetrates through the planet carrier 1, and the fourth gear 423 and the third gear 422 are respectively distributed on the upper and lower sides of the planet carrier 1. The third gear 422 meshes with the second wheel set 3, and the third gear 422 and / or the fourth gear 423 mesh with the second planet gear 42. Specifically: when the first planet gear 41 is arranged on the lower side of the planet carrier 1, the first planet gear 41 meshes with the third gear 422; when the first planet gear 41 is arranged on the upper side of the planet carrier 1, the first planet gear 41 meshes with the fourth gear 423; when the first planet gear 41 penetrates through the planet carrier 1, the first planet gear 41 meshes with the third gear 422, or meshes with the fourth gear 423, or meshes with the third gear 422 and the fourth gear 423 respectively.

[0048] In a specific embodiment, Figure 3 and Figure 4 From the perspective shown in , 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 planetary shaft 411 and the second planetary shaft 421 both penetrate the planetary carrier 1, the first gear 412 is arranged on the upper side of the planetary carrier 1, the second gear 413 is arranged on the lower side of the planetary carrier 1, the third gear 422 is arranged on the lower side of the planetary carrier 1, and the fourth gear 423 is arranged on the upper side of the planetary carrier 1. The first gear 412 is respectively meshed with the first wheel set 2 and the fourth gear 423, and the third gear 422 is respectively meshed with the second wheel set 3 and the second gear 413. In this way, the arrangement of the first gear 412 and the third gear 422 can respectively realize the meshing transmission of the first wheel set 2 and the second wheel set 3 on the upper and lower sides of the planetary carrier 1, and the first gear 412 is meshed with the fourth gear 423, and the second gear 413 is meshed with the third gear 422, so as to strengthen the meshing of the first planetary gear 41 and the second planetary gear 42, and improve the transmission stability of the first wheel set 2 and the second wheel set 3 and the planetary gear set 4.

[0049] In one embodiment, please refer to Figure 3 and Figure 4 The first wheel set 2 includes a first center wheel 21 and a second center wheel 22, which are fixedly connected and spaced apart from the planet carrier 1. The first center wheel 21 and the second center wheel 22 are simultaneously rotatably sleeved on the center shaft 10, that is, the first center wheel 21 and the second center wheel 22 can simultaneously rotate with the center shaft 10 as the pivot axis. The first center wheel 21 is connected to the first tourbillon 5 by transmission, and the second center wheel 22 is meshed with the planetary wheel set 4, specifically, the second center wheel 22 is meshed with the first gear 412 of the first planetary wheel 41. In this embodiment, n 2 is the rotation speed of the first center wheel 21 or the second center wheel 22. Here, the rotation speed of the first center wheel 21 is equal to the rotation speed of the second center wheel 22.

[0050] In one embodiment, please refer to Figure 3 and Figure 4 The second wheel set 3 includes a third center wheel 31 and a fourth center wheel 32, which are fixedly connected and spaced apart from the planet carrier 1. The third center wheel 31 and the fourth center wheel 32 are simultaneously rotatably sleeved on the center shaft 10, that is, the third center wheel 31 and the fourth center wheel 32 can simultaneously rotate with the center shaft 10 as the pivot axis. The third center wheel 31 is transmission-connected to the second tourbillon 6, and the fourth center wheel 32 is meshed with the planetary wheel set 4, specifically, the fourth center wheel 32 is meshed with the third gear 422 of the second planetary wheel 42. In this embodiment, n 3is the rotational speed of the third central gear 31 or the fourth central gear 32, where the rotational speeds of the third central gear 31 and the fourth central gear 32 are equal.

[0051] Thus, in this embodiment, the first central gear 21 is drivingly connected to the first tourbillon 5, and the third central gear 31 is drivingly connected to the second tourbillon 6. During operation, when the central shaft 10 and the planet carrier 1 rotate, the first gear 412, the second gear 413, the third gear 422, and the fourth gear 423 rotate within the planet carrier 1 and can simultaneously revolve about the central shaft 10 as a pivot axis. Since the first gear 412 meshes with the second central gear 22 and the third gear 422 meshes with the fourth central gear 32, the first central gear 21, the second central gear 22, the third central gear 31, and the fourth central gear 32 can all rotate on the central shaft 10 respectively. When the rotational speed of the first tourbillon 5 is fast and the rotational speed of the second tourbillon 6 is slow, under the driving action of the first tourbillon 5 and the second tourbillon 6, the rotational speed of the first central gear 21 increases, and the rotational speed of the second central gear 22 also increases accordingly. The rotational speed of the third central gear 31 decreases, and the rotational speed of the fourth central gear 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 central gear 22 and the fourth central gear 32 can be transmitted to the planet carrier 1, so that half of the sum of the rotational speeds of the first central gear 21 and the third central gear 31 is the rotational speed of the planet carrier 1, which is equivalent to reducing the rotational error of the planet carrier 1, that is, reducing the timekeeping error of the indicating system.

[0052] 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 central gear 22, and the fourth central gear 32 can be set to have equal numbers of teeth, that is, they are the same gears; the first central gear 21 and the third central gear 31 can be set to have equal numbers of teeth and are the same gears. Thus, in this embodiment, only two types of gear cutters for the differential adjustment mechanism can be provided. One type of gear cutter is the first gear 412, the second gear 413, the third gear 422, the fourth gear 423, the second central gear 22, and the fourth central gear 32, and the second type of gear cutter is the first central gear 21 and the third central gear 31. The types of gear cutters used are very few, which is convenient for the formation of the differential adjustment mechanism and reduces the manufacturing cost.

[0053] In a specific embodiment, both the first central gear 21 and the third central gear 31 are larger than the second central gear 22 and the fourth central gear 32. Here, the sizes of the first central gear 21 and the third central gear 31 can be set to be the same as that of the planet carrier 1, which is convenient for averaging the rotational speed of the planet carrier 1 by the rotational speeds of the first central gear 21 and the third central gear, and realizing that the rotational speed of the planet carrier 1 is half of the sum of the rotational speeds of the first central gear 21 and the third central gear 31.

[0054] In one embodiment, please refer to Figure 3 and Figure 4 The differential adjustment mechanism further includes a first transmission assembly 7, which is respectively connected to the first wheel set 2 and the first tourbillon 5 to achieve transmission connection between the first tourbillon 5 and the first wheel set 2. Specifically, the first transmission assembly 7 includes a third planetary shaft 71 and a third planetary gear 72 and a fourth planetary gear 73 fixed to both ends of the third planetary shaft 71. The third planetary gear 72 is meshed with the first center wheel 21 of the first wheel set 2, and the fourth planetary gear 73 is connected to the first tourbillon 5.

[0055] See also Figure 1 In a specific embodiment, the first transmission assembly 7 further includes a first wheel shaft 74 and a fifth gear 75 fixed thereto, and the fifth gear 75 is meshed with the fourth planetary gear 73. The first tourbillon 5 is provided with a seventh gear 51 having external teeth, and the fifth gear 75 is meshed with the seventh gear 51. In this way, the first center wheel 21 is meshed with the third planetary gear 72, the third planetary gear 72 is fixed to the fourth planetary gear 73 through the third planetary shaft 71, the fourth planetary gear 73 is meshed with the fifth gear 75, and the fifth gear 75 is meshed 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.

[0056] In one embodiment, the differential adjustment mechanism further includes a second transmission assembly 8, which is respectively connected to the second wheel set 3 and the second tourbillon 6 to achieve transmission connection between the second tourbillon 6 and the second wheel set 3. Specifically, the second transmission assembly 8 includes a fourth planetary shaft 81 and a fifth planetary wheel 82 and a sixth planetary wheel 83 fixed to both ends of the fourth planetary shaft 81, the fifth planetary wheel 82 is meshed with the third center wheel 31 of the second wheel set 3, and the sixth planetary wheel 83 is connected to the second tourbillon 6.

[0057] See also Figure 1 In a specific embodiment, the second transmission assembly 8 further includes a second wheel shaft 84 and a sixth gear 85 fixed thereto, and the sixth gear 85 is meshed with the sixth planetary gear 83. The second tourbillon 6 is provided with an eighth gear 61 having external teeth, and the sixth gear 85 is meshed with the eighth gear 61. In this way, the third center wheel 31 is meshed with the fifth planetary gear 82, the fifth planetary gear 82 is fixed to the sixth planetary gear 83 through the fourth planetary shaft 81, the sixth planetary gear 83 is meshed with the sixth gear 85, and the sixth gear 85 is meshed 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.

[0058] In one embodiment, see Figure 1The differential adjustment mechanism also includes a power source, which includes a power gear 9. Both the planet carrier 1 and the power gear 9 have external teeth, and the power gear 9 is meshed with the planet carrier 1. When the power gear 9 rotates, the planet carrier 1 meshes with the power gear 9 and rotates, thereby realizing the synchronous rotation of the central shaft 10 and the planet carrier 1. At this time, the first tourbillon 5 and the second tourbillon 6 can realize the average rotation speed of the planet carrier 1 through the first wheel set 2 and the second wheel set 3, thereby reducing the travel time error of the central shaft 10.

[0059] The embodiment of the present application also provides a watch, including an indication system and a differential adjustment mechanism, wherein the indication system is used for timekeeping, and the indication system is connected to the central axis 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, and please refer to the relevant description of the differential adjustment mechanism in the previous embodiment for details, which will not be repeated here.

[0060] The watch provided in the embodiment of the present application adopts the setting of the differential adjustment mechanism, and the planetary carrier 1 is respectively connected to the first wheel group 2 and the second wheel group 3 through the planetary wheel group 4. The rotational motion of the first tourbillon 5 and the second tourbillon 6 is respectively transmitted to the first wheel group 2 and the second wheel group 3, and the rotational motion of the first wheel group 2 and the second wheel group 3 can be respectively transmitted to the planetary carrier 1 through the planetary wheel group 4. Then, the rotational speed of the planetary 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 planetary carrier 1, thereby reducing the travel time error of the indicating system connected to the central axis 10. In addition, the first wheel set 2 and the second wheel set 3 are respectively rotatably mounted on the central axis 10, thereby improving the rotational flexibility of the first wheel set 2 and the second wheel set 3. The planetary wheel set 4 is rotatably mounted on the planetary frame 1, so that the planetary wheel set 4 can rotate on the planetary frame 1 and can revolve around the central axis 10 as the pivot axis. The planetary wheel set 4 is respectively meshed with the first wheel set 2 and the second wheel set 3, thereby improving the flexibility of the planetary wheel set 4, facilitating the transmission of the rotational motion of the first wheel set 2 and the second wheel set 3 to the planetary frame 1, improving the stability of the speed transmission, and facilitating reducing the travel time error of the indicating system. In addition, the structure of the entire differential adjustment mechanism is very simple, thereby simplifying the structure of the watch.

[0061] The above description is only a preferred embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present application should be included in the protection scope of the present application.

Claims

1. A differential adjustment mechanism, characterized in that, it includes: a planet carrier; a central shaft fixed to the planet carrier, and the central shaft is used to connect an indicating system; a first wheel set rotatably sleeved on the central shaft and drivingly connected to a first tourbillon; a second wheel set rotatably sleeved on the central shaft and spaced from the first wheel set, and the second wheel set is drivingly connected to a second tourbillon; a planet gear set rotatably arranged on the planet carrier and meshing with the first wheel set and the second wheel set respectively; The planet gear set includes: a first planet gear rotatably arranged on the planet carrier and meshing with the first wheel set; a second planet gear rotatably arranged on the planet carrier and meshing with the second wheel set, and the first planet gear meshes with the second planet gear; The first wheel set includes a first central gear and a second central gear that are simultaneously rotatably sleeved on the central shaft, the first central gear is drivingly connected to the first tourbillon, and the second central gear is fixedly connected to the first central gear and meshes with the planet gear set.

2. The differential adjustment mechanism according to claim 1, characterized in that, the first planet gear includes a first planet shaft, a first gear and a second gear, and the first gear and the second gear are respectively fixedly connected to both ends of the first planet shaft; the first planet shaft is rotatably arranged on the planet carrier, the first gear and / or the second gear meshes with the second planet gear, and the first gear meshes with the first wheel set.

3. The differential adjustment mechanism according to claim 1, characterized in that, the second planet gear includes a second planet shaft, a third gear and a fourth gear, and the third gear and the fourth gear are respectively fixedly connected to both ends of the second planet shaft; the second planet shaft is rotatably arranged on the planet carrier, the third gear and / or the fourth gear meshes with the first planet gear, and the third gear meshes with the second wheel set.

4. The differential adjustment mechanism according to claim 1, characterized in that, the second wheel set includes a third central gear and a fourth central gear that are simultaneously rotatably sleeved on the central shaft, the third central gear is drivingly connected to the second tourbillon, and the fourth central gear is fixedly connected to the third central gear and meshes with the planet gear set.

5. The differential adjustment mechanism according to any one of claims 1-4, characterized in that, the differential adjustment mechanism further includes a first transmission assembly, the first transmission assembly includes a third planet shaft and a third planet gear and a fourth planet gear fixedly connected to both ends of the third planet shaft, the third planet gear meshes with the first wheel set, and the fourth planet gear is drivingly connected to the first tourbillon.

6. The differential adjustment mechanism according to any one of claims 1-4, characterized in that, the differential adjustment mechanism further includes a second transmission assembly, the second transmission assembly includes a fourth planet shaft and a fifth planet gear and a sixth planet gear fixedly connected to both ends of the fourth planet shaft, the fifth planet gear meshes with the second wheel set, and the sixth planet gear is drivingly connected to the second tourbillon.

7. The differential adjustment mechanism according to any one of claims 1-4, characterized in that, 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 meshes with the planet carrier.

8. A watch, characterized in that it includes the differential adjustment mechanism according to any one of claims 1-7.

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