CN219159448U

CN219159448U - Electronic lock

Info

Publication number: CN219159448U
Application number: CN202223508525.5U
Authority: CN
Inventors: 王超
Original assignee: Changchun Jetty Automotive Parts Co Ltd
Current assignee: Changchun Jetty Automotive Parts Co Ltd
Priority date: 2022-12-28
Filing date: 2022-12-28
Publication date: 2023-06-09
Anticipated expiration: 2032-12-28

Abstract

The utility model discloses an electronic lock, comprising: a driving device including an output shaft outputting torque; the speed reduction device comprises an annular fixed gear ring, a gear is arranged on the inner periphery of the fixed gear ring, the gear is meshed with a multistage planetary gear assembly, and the multistage planetary gear assembly comprises a primary planetary gear assembly, a final planetary gear assembly and at least one middle planetary gear assembly; each stage of the planetary gear assembly comprises a planet carrier, a sun gear and a plurality of planet gears; the output shaft is coaxially connected with a sun gear of the primary planetary gear assembly; a cam portion coupled to a planet carrier of the final planetary gear assembly; the lock rod is provided with an abutting groove; the cam part is abutted with the abutting groove so as to drive the lock rod to reciprocate. The speed reducer composed of the planetary gear components of the electronic lock has small transmission structure size, compact structure, stable motion, larger transmission bearing capacity and high transmission efficiency.

Description

Electronic lock

Technical Field

The utility model relates to the technical field of automobile charging, in particular to an electronic lock.

Background

The charging interface of the new energy automobile is usually provided with a locking device to play a role in fixing the charging gun in the charging process. However, the driving device in the traditional electronic lock greatly consumes electric energy and motor moment due to mutual transmission among transmission mechanisms and friction force generated by changing circular motion into linear motion, which not only leads to too short service life of the electronic lock and easy noise generation, but also easily causes abrasion of a motor gear set and unstable driving device of the electronic lock. In addition, the gear transmission mechanism mainly adopts a common-axis gear train for transmission, has the advantages of complex structure, excessive parts, complex assembly steps, high requirement on installation precision, low efficiency of the whole assembly process and single motion of the existing electronic lock rod, so that a new scheme of the electronic lock is needed to solve the problems.

Disclosure of Invention

An object of the present utility model is to provide an electronic lock which can be assembled in a small space, and which is simple in structure and convenient to maintain.

An electronic lock, comprising:

a driving device including an output shaft outputting torque;

the speed reducer comprises an annular fixed gear ring, a gear is arranged on the inner periphery of the fixed gear ring, and a multistage planetary gear assembly meshed with the gear;

the multi-stage planetary gear assembly includes a primary planetary gear assembly, a final planetary gear assembly, and at least one intermediate planetary gear assembly connected to the primary planetary gear assembly and the final planetary gear assembly, respectively;

each stage of the planetary gear assembly comprises a planet carrier, a sun gear and a plurality of planet gears, wherein the sun gear and the planet gears are arranged on the planet carrier; the output shaft is coaxially connected with a sun gear of the primary planetary gear assembly;

a cam portion connected to a planet carrier of the final planetary gear assembly;

the lock rod is provided with an abutting groove;

the driving device drives the cam part to rotate through the speed reducing device, and the cam part is abutted with the abutting groove so as to drive the lock rod to reciprocate.

Therefore, the multistage planetary gear assembly is arranged to realize multistage deceleration, and the multistage planetary gear assembly has the advantages of small transmission structure size, compact structure, stable motion, large transmission capacity and high transmission efficiency. Meanwhile, the lock rod can obtain any preset motion rule through the cam mechanism with simple and compact structure.

Preferably, the direction of the reciprocating motion is perpendicular to the axial direction of the output shaft.

Thus, the cam is arranged perpendicular to the output axis, the direction of the axial movement along the output axis is changed to the direction perpendicular to the axis, and the loss of torque is avoided.

Preferably, the cam part comprises a driving end and an abutting end, the driving end is connected with the planet carrier of the planetary gear assembly, and the abutting end abuts against the abutting groove to drive the lock rod to reciprocate.

Therefore, the requirements of meeting the motion trail of the lock rod are met by determining the positions of the transmission end and the abutting end.

Preferably, the axis of the driving end coincides with the axis of the output shaft, and the axis of the abutting end is deviated from the axis of the driving end.

Therefore, the axis of the transmission end and the axis of the output shaft are designed to be coincident, the loss of output force is avoided, and meanwhile, the axis of the abutting end is deviated from the axis of the transmission end, so that the lock rod reaches the preset moving distance according to the preset track.

Preferably, the drive end and the abutment end each consist of curved sections of different radii of curvature.

Thus, by means of different radii of curvature, any desired movement is achieved.

Preferably, the radius of curvature of the driving end is larger than the radius of curvature of the abutting end.

Therefore, the curvature radius of the transmission end is designed to be larger than that of the abutting end, the strength of the cam is ensured, and the movement track of the cam is realized.

Preferably, the cam further comprises a first transition section and a second transition section, wherein the first transition section is connected with the abutting end and one end of the driving end, and the second transition section is connected with the abutting end and the other end of the driving end.

Therefore, the abutting end and the transmission end are connected through the first transition section and the second transition section, the swing radius of the cam is met, and the preset moving distance of the lock rod is realized.

Preferably, the first transition section and the second transition section are straight sections.

Thus, the first transition section and the second transition section may be the simplest straight sections, facilitating processing.

Preferably, the first transition section and the second transition section are curved sections.

Therefore, the first transition section and the second transition section can be curved sections, and different movement tracks of the lock rod can be met.

Preferably, a plurality of the planetary gears of the planetary gear assembly of each stage are respectively meshed with the gears, the sun gear is respectively meshed with the plurality of the planetary gears, and the planet carrier is connected with the plurality of the planetary gears.

Therefore, a plurality of planetary gears meshed with the planetary gears are arranged around the sun gear, and the planetary gears revolve through self-rotation, so that the planetary gear assembly achieves the effect of reducing speed.

Preferably, the driving device drives the sun gear of the primary planetary gear assembly to rotate and drives the planet carrier to rotate through a plurality of planet gears, the planet carrier of the primary planetary gear assembly is coaxially connected with the sun gear of the intermediate planetary gear assembly, and drives the intermediate planetary gear assembly to rotate and drives the final planetary gear assembly to rotate through the planet carrier of the intermediate planetary gear assembly.

Thus, the manner of transmission of the multi-stage planetary gear assembly is determined.

Preferably, the sun gear of each of the remaining stages of the planetary gear assemblies, except for the primary planetary gear assembly, is connected to the planet carrier of the adjacent previous stage of the planetary gear assembly, respectively.

Therefore, the multistage planetary gear assembly is connected in series, so that the transmission of the multistage planetary gear assembly is met, and the effect of step-by-step speed reduction is realized.

Preferably, the output power of the driving device is 1W to 60W.

Thus, by calculating the output power, a sufficient output torque can be ensured in this section.

Preferably, the transmission ratio of the driving device and the cam is 3/1-60/1.

Thus, the transmission ratio can meet the output speed requirement in this section by calculation.

The utility model has the following beneficial effects:

1. according to the electronic lock, the multistage planetary gear assembly is arranged, the sun gear is arranged to be in active transmission, and the plurality of planetary gears meshed with the sun gear are arranged around the sun gear, so that the effect of reducing speed is achieved; the transmission structure has small volume, compact structure, stable motion, larger transmission ratio, large bearing capacity and high transmission efficiency.

2. The electronic lock can enable the lock rod to obtain any preset motion rule through the cam mechanism with simple and compact structure.

3. According to the electronic lock, the sun gear is set to be in active transmission, and the plurality of planetary gears meshed with the sun gear are arranged around the sun gear, so that the effect of reducing speed is achieved.

4. The electronic lock of the utility model enables the planet carrier to be used as an output body of the planetary gear assembly of the present stage and as an input body of the planetary gear assembly of the next stage by setting the specific structure of the planet carrier, and realizes the serial connection of the multi-stage planetary gear assemblies.

Other features of the present utility model and its advantages will become apparent from the following detailed description of exemplary embodiments of the utility model, which proceeds with reference to the accompanying drawings.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description, serve to explain the principles of the utility model.

FIG. 1 is a schematic cross-sectional view of an electronic lock according to the present utility model;

FIG. 2 is a schematic diagram of the operation of the planetary gear assembly of the electronic lock of the present utility model;

FIG. 3 is a schematic diagram of the assembly of the planet carrier and cam of the electronic lock of the present utility model;

FIG. 4 is a schematic view of the cam of the electronic lock of the present utility model;

FIG. 5 is a schematic view of the structure of the electronic lock lever of the present utility model;

the figures are marked as follows:

1-driving device, 2-speed reducer, 21-fixed gear ring, 22-planetary gear assembly,

22 a-primary planetary gear assembly, 22 b-primary planetary gear assembly,

22 c-primary planetary gear assembly, 23-gear, 221-carrier, 222-sun gear,

223-planet wheel, 224-wheel carrier body, 225-fixed shaft, 226-transmission shaft, 3-cam portion,

31-a driving end, 32-a abutting end,

33-first transition section, 34-second transition section, 4-lock lever, 41-abutment slot.

Detailed Description

Various exemplary embodiments of the present utility model will now be described in detail with reference to the accompanying drawings. It should be noted that: the relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise.

The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses.

Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate.

In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of exemplary embodiments may have different values.

As shown in fig. 1 and 2, an electronic lock includes:

a drive device 1, the drive device 1 including an output shaft outputting torque;

a reduction gear 2 including a ring-shaped fixed ring gear 21 having a gear 23 provided at an inner periphery thereof, and a multistage planetary gear assembly 22 meshed with the gear;

the multi-stage planetary gear assembly 22 includes a primary planetary gear assembly 22a, a final planetary gear assembly 22c, and at least one intermediate planetary gear assembly 22b connected to the primary and final planetary gear assemblies, respectively;

each stage of the planetary gear assembly comprises a planet carrier 221, a sun gear 222 and a plurality of planet gears 223 arranged on the planet carrier; the output shaft is coaxially coupled to the sun gear 222 of the primary planetary gear assembly 22 a;

a cam portion 3, the cam portion 3 being connected to a carrier 221 of the final stage planetary gear assembly 22 c;

a lock lever 4, the lock lever 4 being provided with an abutment groove 41;

the driving device 1 drives the cam part 3 to rotate through the speed reducing device 2, and the cam part 3 is abutted with the abutting groove 41 so as to drive the lock rod 4 to reciprocate.

The reduction gear 2 includes a fixed ring gear 21, a gear 23 is provided inside the fixed ring gear 21, and a multistage planetary gear assembly 22 is provided inside the fixed ring gear 21.

The planetary gear assembly connected to the output shaft of the multi-stage planetary gear assembly 22 is defined as a primary planetary gear assembly 22a, the planetary gear assembly connected to the cam portion 3 is defined as a final planetary gear assembly 22c, the planetary gear assembly intermediate between the primary planetary gear assembly 22a and the final planetary gear assembly 22c is an intermediate planetary gear assembly 22b, and the number of intermediate planetary gear assemblies 22b is at least 1.

In the present embodiment, the multi-stage planetary gear assembly 22 is a 3-stage planetary gear assembly, i.e., the number of intermediate planetary gear assemblies 22b is 1. Thereby, at least 3-stage deceleration is possible.

Specifically, each stage of planetary gear assembly includes a planet carrier 221, a sun gear 222, and a plurality of planet gears 223.

The principle of deceleration of the deceleration device 2 is: the ring gear 21 is fixedly arranged, the sun gear 222 is active, and the planet carrier 221 is passive, so that the output shaft of the driving device 1 is connected with the sun gear 222 of the primary planetary gear assembly 22a, the cam part 3 is connected with the planet carrier 221 of the final planetary gear assembly 22c, the driving device 1 drives the cam part 3 to rotate through the speed reducing device 2, and the cam part 3 is abutted with the abutting groove 41 of the lock rod 4 so as to drive the lock rod 4 to reciprocate.

Thus, by setting the sun gear 222 as active transmission, the plurality of planet gears 223 are respectively meshed with the sun gear 222 and the gears 23, so that the planet gears 223 rotate and revolve, and the planetary gear assembly 22 of the planet gears achieves the function of reducing speed; the transmission structure has small volume, compact structure, stable motion, large transmission ratio, large bearing capacity and high transmission efficiency.

In the present embodiment, the driving device 1 is a motor.

In another embodiment, the drive device 1 is a hydraulic motor.

It will be appreciated that the rotational movement of the output shaft is output through the cam 3 connected to the reduction gear 2, and the abutment end 32 of the cam 3 abuts against the abutment end 41 of the lock lever 4 to change the rotational movement to a linear movement.

In this embodiment, the direction of the reciprocating motion is perpendicular to the axis direction of the output shaft, avoiding output force loss.

As shown in fig. 4, the cam portion 3 includes a driving end 31 and an abutment end 32, the driving end 31 is connected to the planet carrier 223 of the planetary gear assembly 22, and the abutment end 32 abuts against the abutment groove 41 to drive the lock lever 4 to reciprocate.

Preferably, the axis of the driving end 31 coincides with the axis of the output shaft, and the axis of the abutment end 32 is offset from the axis of the driving end.

Specifically, the cam 3 is mainly divided into two parts, one part is a driving end 31 connected with the planetary gear assembly 22 and driven to rotate by the planetary gear assembly 22, the other part is an abutting end 32 which drives power through the driving end 31 and abuts against an abutting groove 41 of the lock rod 4 to drive the lock rod 4 to reciprocate, in order to avoid the loss of output force, the axis of the driving end 31 is designed to coincide with the axis of the output shaft, and in order to meet the requirement that the lock rod 4 can reach a preset moving distance, the axis of the abutting end 32 is deviated from the axis of the driving end 31.

Preferably, the driving end 31 and the abutment end 32 each consist of curved sections of different radii of curvature.

Preferably, the radius of curvature of the driving end 31 is larger than the radius of curvature of the abutting end 32.

In some embodiments, the driving end 31 and the abutting end 32 are composed of a plurality of different radii of curvature in order to satisfy a predetermined movement trajectory.

In the present embodiment, the driving end 31 and the abutting end 32 are each composed of a single radius of curvature, and the radius of curvature of the driving end 31 is designed to be larger than that of the abutting end 32.

Thus, the radius of curvature of the driving end 31 is designed to be larger than the radius of curvature of the abutting end 32, the strength of the cam 3 is ensured, and the movement track of the cam 3 is realized.

Preferably, the cam 3 further comprises a first transition section 33 and a second transition section 34, wherein the first transition section 33 connects the abutting end 32 and one end of the driving end 31, and the second transition section 34 connects the abutting end 32 and the other end of the driving end 31.

Specifically, in order to ensure that the driving end 31 and the abutting end 32 can smoothly transition and simultaneously ensure that the preset moving distance of the lock rod 4 can be met, the driving end 31 and the abutting end 32 are smoothly connected through the first transition section 33 and the second transition section 34 respectively.

Preferably, the first transition section 33 and the second transition section 34 are straight sections.

In this embodiment, the first transition section 33 and the second transition section 34 are designed as straight line sections, which not only meets the requirement of the moving distance of the lock lever 4, but also is convenient for processing.

Preferably, the first transition section 33 and the second transition section 34 are curved sections.

In some embodiments, different movement trajectories of the locking lever 4 can be achieved, the first transition section 33 and the second transition section 34 being designed as curved sections.

Preferably, a plurality of the planetary gears 223 of the planetary gear assembly of each stage are respectively meshed with the gears 23, the sun gear 222 is respectively meshed with a plurality of the planetary gears 223, and the planet carrier 221 is connected with a plurality of the planetary gears 223.

Specifically, the plurality of planetary gears 223 are disposed between the sun gear 222 and the gear 23, and the plurality of planetary gears 223 are respectively meshed with the sun gear 222 and the gear 23, the sun gear 222 is a driving member to drive the plurality of planetary gears 223 to rotate, rotation and revolution of the plurality of planetary gears 223 are realized, the planetary carrier 221 is a driven member, the planetary carrier 223 is connected with the plurality of planetary gears 223, and the planetary carrier 221 is driven to rotate by the plurality of planetary gears 223.

In the present embodiment, the number of the plurality of planetary gears 223 is 3.

As shown in fig. 1-3, the driving device 1 drives the sun gear 222 of the primary planetary gear assembly 22a to rotate and drives the planet carrier 221 to rotate through a plurality of planet gears, the planet carrier 221 of the primary planetary gear assembly 22a is coaxially connected with the sun gear 222 of the intermediate planetary gear assembly 22b, and drives the intermediate planetary gear assembly 22b to rotate and drives the final planetary gear assembly 22c to rotate through the planet carrier 221 of the intermediate planetary gear assembly 22 b.

In the present embodiment, the transmission sequence of the reduction gear 2 is: the output shaft of the driving device 1 is connected with the sun gear 222 of the primary planetary gear assembly 22a to drive the sun gear 222 to rotate, and the plurality of planet gears 223 are meshed with the sun gear 222 and the gears 23 to realize the rotation and revolution of the plurality of planet gears 223, so that the planet carrier 221 is driven to rotate to realize the rotation of the primary planetary gear assembly 22 a; the planet carrier 221 of the primary planetary gear assembly 22a serves as the output end of the present stage and the input end of the intermediate planetary gear assembly 22b which is the next adjacent planetary gear assembly, so that the planet carrier 221 of the primary planetary gear assembly 22a serves as the power source to rotate the intermediate planetary gear assembly 22b with the sun gear 222 of the intermediate planetary gear assembly 22b, and the planet carrier 221 of the intermediate planetary gear assembly 22b is connected to the sun gear 222 of the final planetary gear assembly 22c to rotate the final planetary gear assembly 22 c.

Preferably, the sun gear 222 of each of the remaining planetary gear assemblies except for the primary planetary gear assembly 22a is connected to the planet carrier 221 of the adjacent, previous planetary gear assembly.

In this embodiment, the reduction gear 2 is composed of a 3-stage planetary gear assembly, and the 3-stage planetary gear assembly is a 3-stage reduction realized by serial connection, the sun gear 222 of the primary planetary gear assembly 22a is connected with the output shaft, the sun gear of the intermediate planetary gear assembly 22b is connected with the transmission shaft 226 of the planet carrier 221 of the primary planetary gear assembly, and the sun gear 222 of the final planetary gear assembly 22c is connected with the transmission shaft 226 of the planet carrier 221 of the intermediate planetary gear assembly 22b, so that the planet carrier 221 is the output body of the planetary gear assembly at the present stage and the input body of the planetary gear assembly at the next adjacent stage.

Specifically, the planet carrier 221 includes a carrier body 224, a plurality of fixed shafts 225 disposed on one side of the carrier body 224, and a transmission shaft 226 disposed on the other side of the carrier body 224, wherein the plurality of fixed shafts 225 are correspondingly connected to the plurality of planet gears 223, and the transmission shaft 226 is connected to the sun gear 222 of the planetary gear assembly adjacent to the next stage.

The planet carrier 221 serves as an output body of the present stage planetary gear assembly and an input body of an adjacent lower stage planetary gear assembly, and realizes series connection of the multi-stage planetary gear assemblies. A plurality of fixed shafts 225 and a driving shaft 226 are provided to be disposed at both sides of the carrier body 224, and the plurality of fixed shafts 225 are correspondingly connected to the plurality of planetary gears 223, and the driving shaft 226 is connected to the sun gear 222 of the planetary gear assembly of the next stage.

In this embodiment, the planet carrier body 224 is a triangular plate, the transmission shaft 226 is disposed at the center of the triangular plate, and the axis coincides with the rotation axis of the sun gear 222. At each corner of the triangular plate, 3 fixed shafts 225 are provided, and the axis of the fixed shaft 224 is parallel to the rotation axis of the sun gear.

Preferably, the output power of the driving device is 1W to 60W.

Specifically, the output power of the driving device 1 is 1W to 60W. The output power of the driving device 1 determines the working speed of the electronic lock, the higher the power is, the faster the electronic lock completes the work, the lower the power is, the slower the electronic lock completes the work, and even the locking work of the lock rod 4 cannot be completed. In order to test the influence of output power on the operation of the electronic lock, the inventor performs relevant tests, the test method is to select driving devices 1 with different output powers, other structures of the electronic lock are the same, each driving device 1 continuously works for 1 minute, the number of times of completing the operation of the electronic lock is recorded, the number of times is more than or equal to 40 and is qualified, and the number of times is less than 40 and is not qualified. If abnormal sound occurs during the operation of the electronic lock, the electronic lock is regarded as unqualified. The results are shown in Table 1.

Table 1: influence of different output power on electronic lock speed and abnormal sound

As shown in table 1, when the output power of the driving device 1 is less than 1W, the number of times of switching the electronic lock is completed within 1 minute is less than 40, and the speed is too slow to be unqualified, so the inventor selects the minimum power of the driving device 1 to be 1W, when the output power of the driving device 1 is greater than 60W, the electronic lock is affected by the overall design, the speed enters the bottleneck period without obvious improvement, and abnormal noise occurs, so the output power of the driving device 1 selected by the inventor is 1W to 60W. Specifically, it may be 1W, 2W, 5W, 10W, 20W, 30W, 40W, 45W, 50W, 55W, 60W, etc.

Preferably, the transmission ratio of the driving device 1 and the cam 3 is 3/1-60/1.

Specifically, the transmission ratio of the driving device 1 to the cam 3 is 3/1-84/1. The ratio=driving wheel rotation speed/driven wheel rotation speed, and it can be seen from the formula that the ratio is inversely proportional to the driven wheel rotation speed, i.e. the smaller the ratio is, the larger the rotation speed of the driven wheel is, the abnormal sound is likely to occur due to inaccurate control. Therefore, the inventors selected different gear ratios of the driving device 1 and the cam 3 to test, observed that the number of times of completion of the locking or unlocking operation of the lock lever 4 within 1 minute was less than 40 times, and failed, and the abnormal sound was also occurred, and the results are shown in table 2.

Table 2: influence of the transmission ratio of the drive 1 and the cam 3 on the speed of the electronic lock

Ratio of transmission

2/1

3/1

9/1

15/1

24/1

30/1

36/1

42/1

48/1

54/1

60/1

63/1

Number of completions

98

96

91

88

83

78

70

61

53

47

40

38

Whether or not to make abnormal sound

Is that

Whether or not

As can be seen from table 2, if the transmission ratio of the driving device 1 to the cam 3 is less than 3/1, the electronic lock will generate abnormal sound, so it is not qualified; meanwhile, when the transmission ratio of the driving device 1 to the output gear 3 is larger than 60/1, the locking or opening actions of the electronic lock completed within 1 minute are less than 40 times, and the response speed is too slow and is not qualified; therefore, the inventor selects the transmission ratio of the driving device 1 and the eccentric assembly to be 3/1-60/1.

The working principle of the electronic lock is described in detail below with reference to the accompanying drawings: the motor 1 is started, the output shaft rotates to drive the sun gear 222 of the primary planetary gear assembly 22a to rotate, 3 planetary gears 223 are meshed with the sun gear 222 and the gear 23 to realize self-assembly and revolution, rotation is transmitted to the planetary carrier 221 connected with the planetary gears 223, the transmission shaft 226 of the planetary carrier 221 of the primary planetary gear assembly 22a is connected with the sun gear 222 of the middle planetary gear assembly 22b and drives the sun gear 222 to rotate, 3 planetary gears 223 of the middle planetary gear assembly 22b are meshed with the sun gear 222 and the gear 23 to realize self-assembly and revolution, rotation is transmitted to the planetary carrier 221 connected with the planetary gears 223, the planetary carrier 221 of the middle planetary gear assembly 22b is meshed with the sun gear 222 and the gear 23 to realize self-rotation and revolution, rotation is transmitted to the planetary carrier 221 connected with the planetary gears 223, the planetary carrier 221 drives the transmission end 31 of the cam 3 to rotate, and the abutting end 32 abuts against the abutting groove 41 to drive the locking rod 4 to reciprocate, and locking and unlocking are realized.

While certain specific embodiments of the utility model have been described in detail by way of example, it will be appreciated by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the utility model. It will be appreciated by those skilled in the art that modifications may be made to the above embodiments without departing from the scope and spirit of the utility model. The scope of the utility model is defined by the appended claims.

Claims

1. An electronic lock, comprising:

a driving device including an output shaft outputting torque;

the lock rod is provided with an abutting groove;

2. The electronic lock of claim 1, wherein the direction of the reciprocation is perpendicular to the axial direction of the output shaft.

3. The electronic lock of claim 1, wherein the cam portion includes a driving end and an abutment end, the driving end being connected to the planet carrier of the planetary gear assembly, the abutment end being in abutment with the abutment groove to reciprocate the lock rod.

4. An electronic lock according to claim 3, wherein the axis of the drive end coincides with the axis of the output shaft, and the axis of the abutment end is offset from the axis of the drive end.

5. The electronic lock of claim 4, wherein the driving end and the abutment end each consist of curved sections of different radii of curvature.

6. The electronic lock of claim 5, wherein the radius of curvature of the driving end is greater than the radius of curvature of the abutment end.

7. The electronic lock of claim 6, wherein the cam further comprises a first transition section and a second transition section, the first transition section connecting the abutment end and one end of the drive end, the second transition section connecting the abutment end and the other end of the drive end.

8. The electronic lock of claim 7, wherein the first transition section and the second transition section are straight sections.

9. The electronic lock of claim 7, wherein the first transition section and the second transition section are curvilinear sections.

10. The electronic lock of claim 1, wherein a plurality of said planets of each stage of said planetary gear assembly are respectively engaged with said gear, said sun gear is respectively engaged with a plurality of said planets, and said planet carrier is connected with a plurality of said planets.

11. The electronic lock of claim 10, wherein the driving device drives the sun gear of the primary planetary gear assembly to rotate and drives the planet carrier to rotate through a plurality of planet gears, the planet carrier of the primary planetary gear assembly is coaxially connected with the sun gear of the intermediate planetary gear assembly and drives the intermediate planetary gear assembly to rotate and drives the final planetary gear assembly to rotate through the planet carrier of the intermediate planetary gear assembly.

12. The electronic lock of claim 11, wherein the sun gear of each stage of the planetary gear assembly, except the primary planetary gear assembly, is respectively connected with the planet carrier of an adjacent, previous stage of the planetary gear assembly.

13. The electronic lock of claim 1, wherein the output power of the driving means is 1W to 60W.

14. The electronic lock of claim 1, wherein a transmission ratio of the driving means to the cam is 3/1 to 60/1.