CN219492957U

CN219492957U - Electronic lock

Info

Publication number: CN219492957U
Application number: CN202223548187.8U
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: 2023-08-08
Anticipated expiration: 2032-12-28

Abstract

Disclosed herein is an electronic lock including: a driving device including an output shaft outputting torque; the speed increasing device comprises an annular fixed gear ring, a gear is arranged on the inner periphery of the fixed gear ring, a multistage planetary gear assembly meshed with the gear, 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 planet carrier of the primary planetary gear assembly; an output gear is connected with a sun gear of the final planetary gear assembly; the lock rod is provided with a rack; the output gear is meshed with the rack to drive the lock rod to reciprocate. The speed-raising device formed by the planetary gear assemblies of the electronic lock has the advantages of 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. And, its gear drive mainly adopts the transmission of fixed axis train, and the structure is complicated, and part quantity is too much, and the assembly step is complicated, and the installation accuracy requires highly, and whole assembly process inefficiency, current electronic lock are the speed reduction lock generally simultaneously, can't satisfy the demand of speed increasing lock, and ejection force is little. Accordingly, there is a need to provide a new solution to the above-mentioned problems with electronic locks.

Disclosure of Invention

An object of the present utility model is to provide an electronic lock capable of being assembled in a small space while having a stable structure and a speed increase.

An electronic lock, comprising:

a driving device including an output shaft outputting torque;

the speed increasing device 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 planet carrier of the primary planetary gear assembly;

an output gear connected with a sun gear of the final planetary gear assembly;

the locking rod is provided with a rack at least partially;

the driving device drives the output gear to rotate through the speed increasing device, and the output gear is meshed with the rack to drive the lock rod to reciprocate.

Therefore, the multistage planetary gear assembly is arranged to realize multistage speed increasing, and the multistage planetary gear assembly has the advantages of small transmission structure size, compact structure, stable motion, larger transmission bearing capacity and high transmission efficiency.

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

Therefore, through the meshing of the gear and the rack, the axial telecontrol direction along the output shaft is changed into the direction perpendicular to the axial line, and meanwhile, the loss of torque is avoided.

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

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

Thus, the transmission mode of the step-up transmission of the multistage planetary gear assembly is determined.

Preferably, the planet carrier of each of the remaining stages of the planetary gear assemblies, except for the primary planetary gear assembly, is connected to the sun gear of the planetary gear assembly of the immediately preceding stage, 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 step-by-step speed increasing effect is realized.

Preferably, the planet carrier comprises a carrier body, a plurality of fixing shafts arranged on one side of the carrier body and a transmission shaft arranged on the other side of the carrier body, wherein the plurality of fixing shafts are correspondingly connected with the plurality of planet gears, and the transmission shaft is connected with the sun gear of the planetary gear assembly on the adjacent upper stage.

Therefore, by setting the specific structure of the planet carrier, the planet carrier is connected with the adjacent upper-stage sun gear to serve as an input body of the current-stage planetary gear assembly, so that the multistage planetary gear assembly is connected in series.

Preferably, the axis of the transmission shaft coincides with the geometrical axis of the wheel carrier body.

Therefore, the geometric axis of the wheel carrier body is designed to be coincident with the axis of the transmission shaft, and the loss of output force is avoided.

Preferably, the axes of a plurality of said fixed axles are offset in parallel with respect to the geometric axis of said wheel carriage body.

Therefore, the axes of the fixed shafts are arranged parallel to the geometric axis of the wheel carrier body, so that the planetary gears are uniformly stressed.

Preferably, a plurality of the planetary gears and the sun gear are helical gears.

Therefore, the bearing capacity of the gear can be improved due to the increase of the contact ratio of the bevel gears, and the service life of the gear is prolonged, so that the bevel gears with good meshing performance are arranged between the planet gears and the sun gear for transmission.

Preferably, the number of teeth of the planetary gear is equal to the number of teeth of the sun gear.

Therefore, the number of teeth of the planetary gears is designed to be equal to the number of teeth of the sun gear, and the transmission of each planetary gear and the sun gear in the ratio of 1 is realized.

Preferably, the output gear is a herringbone gear.

Therefore, the herringbone gear has the advantages of high bearing capacity, stable transmission, small axial load and the like, and realizes stable reciprocating motion of the lock rod and high ejection force.

Preferably, the rack is a herringbone rack.

Therefore, the herringbone rack is meshed with the herringbone gear, so that high ejection force of the lock rod is achieved.

Preferably, the output power of the driving device is 0.5W to 40W.

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 output gear is 1/42-1/3.

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 planetary carrier is arranged to be in active transmission, and the plurality of planetary gears meshed with the planetary carrier are arranged around the sun wheel, so that the speed increasing effect 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 disclosed by the utility model has the advantages that the output gear rack is designed into the herringbone gear rack, the advantages of high bearing capacity, stable transmission, small axial load and the like of the herringbone gear are utilized, and the gear rack is meshed to output higher ejection force.

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

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

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 view of the structure of the planet carrier of the electronic lock of the present utility model;

FIG. 4 is a schematic diagram of the herringbone gear structure of the electronic lock of the present utility model;

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

The figures are marked as follows:

1-drive, 2-upshift, 21-stationary ring gear, 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-planet carrier, 222-sun gear, 223-planet gear, 224-carrier body, 225-fixed shaft, 226-transmission shaft, 3-output gear, 4-lock lever, 41-rod body, 42-additional body, 43-rack.

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. 1-3, an electronic lock includes:

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

the speed increasing device 2 comprises an annular fixed gear ring 21, a gear 23 arranged on the inner periphery of the fixed gear ring 21 and a multistage planetary gear assembly 22 meshed with the gear 23;

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 221; the output shaft is coaxially connected with the carrier 221 of the primary planetary gear assembly 22 a;

an output gear 3, said output gear 3 being connected to a sun gear 222 of said final planetary gear assembly 22 c;

a lock lever 4, at least part of the lock lever 4 being provided with a rack 41;

the driving device 1 drives the output gear 3 to rotate through the speed increasing device 2, and the output gear 3 is meshed with the rack 43 to drive the lock rod 4 to reciprocate.

The speed increasing device 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 output gear 3 is defined as a final planetary gear assembly 22c, the planetary gear assembly intermediate 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. Thus, at least 3 steps up can be achieved.

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

The speed increasing principle of the speed increasing device 2 is as follows: the annular gear ring 21 is fixedly arranged, the planet carrier 221 is active, and the sun gear 222 is passive, so that an output shaft of the driving device 1 is connected with the planet carrier 221 of the primary planetary gear assembly 22a, the output gear 3 is connected with the sun gear 222 of the final planetary gear assembly 22c, and the driving device 1 drives the output gear 3 to rotate through the speed increasing device 2, and the output gear 3 is meshed with the rack 43 to drive the lock rod 4 to reciprocate.

Thus, by setting the planet carrier 221 as active transmission, the plurality of planet gears 223 are respectively meshed with the sun gear 222 and the gear 23, so that the planet gears 223 can rotate and revolve, and the planetary gear assembly 22 of the planet gears can achieve the function of accelerating; 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 changed to a linear movement by the engagement of the output gear 3 with the rack 43 of the lock lever 4 via the output gear 3 connected to the speed raising means 2, and the direction of the linear movement may be any direction.

In this embodiment, to ensure an optimal output force, the lock lever 4 is arranged perpendicular to the output shaft. Meanwhile, in order to strengthen the strength of the lock rod 4, an additional body 42 is provided on the lock rod body 41, the additional body 42 protrudes radially from the rod body 41, and a herringbone rack is provided on the additional body 42, so that deformation or breakage of the lock rod 4 due to large ejection force is avoided, and larger ejection force can be output.

The additional body 41 may take various shapes, and may be one of a cylinder, a circular truncated cone, a cone, an elliptic cylinder, an elliptic truncated cone, an elliptic cone, a polygonal column, a polygonal table and a polygonal pyramid, and a lock lever may be determined according to actual conditions.

Preferably, a plurality of the planetary gears 223 are engaged with the gear 23, the sun gear 222 is engaged with a plurality of the planetary gears 223, and the carrier 221 is connected to 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 planetary gears 223 is 3.

Preferably, the driving device 1 drives the planet carrier 221 of the primary planetary gear assembly 22a to rotate and drives the sun gear 222 to rotate through the plurality of planet gears 223, and the sun gear 222 of the primary planetary gear assembly 22a is coaxially connected with the planet carrier 221 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 sun gear 222 of the intermediate planetary gear assembly 22 b.

In the present embodiment, the transmission sequence of the speed increasing device 2 is: the output shaft of the driving device 1 is connected with a planet carrier 221 of the primary planetary gear assembly 22a to drive the planet carrier 221 to rotate, the planet carrier 221 is connected with a plurality of planet gears 223 to drive the planet gears 223 to rotate, and the planet gears 223 are meshed with a sun gear 222 and a gear 23 to realize the rotation and revolution of the planet gears 223, so that the sun gear 222 is driven to rotate to realize the rotation of the primary planetary gear assembly 22 a; the sun gear of the primary planetary gear assembly 22a is connected to the planet carrier 221 of the intermediate planetary gear assembly 22b such that the planet carrier 221 serves as the input of the present stage, effecting rotation of the intermediate planetary gear assembly 22b, and the sun gear 222 of the intermediate planetary gear assembly 22b is connected to the planet carrier 221 of the final planetary gear assembly 22c effecting rotation of the final planetary gear assembly 22 c. Thus, the manner of transmission of the multi-stage planetary gear assembly is determined.

Preferably, the planet carriers 221 of the planetary gear assemblies of each stage, except for the primary planetary gear assembly 22a, are respectively connected to the sun gear 222 of the planetary gear assembly of the immediately preceding stage.

In this embodiment, the speed raising device 2 is composed of a 3-stage planetary gear assembly, and the 3-stage planetary gear assembly is a 3-stage speed raising realized by connecting in series, the carrier 221 of the primary planetary gear assembly 22a is connected to the output shaft, the carrier 221 of the intermediate planetary gear assembly 22b is connected to the sun gear 222 of the primary planetary gear assembly, and the carrier 221 of the final planetary gear assembly 22c is connected to the sun gear 222 of the intermediate planetary gear assembly 22b, so the carrier 221 is the input body of the present-stage planetary gear assembly.

Preferably, 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, 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 previous stage.

Preferably, the axis of the drive shaft 226 coincides with the geometric axis of the wheel carrier body 224.

Preferably, the axes of the plurality of fixed shafts 225 are offset in parallel with respect to the geometric axis of the wheel carrier body 224.

Specifically, the planet carrier 221 serves as an input body of the present-stage planetary gear assembly, so a plurality of fixed shafts 225 and a transmission shaft 226 are provided to be arranged on both sides of the carrier body 224, and the plurality of fixed shafts 225 are correspondingly connected to a plurality of planetary gears 223, and the transmission shaft 226 is connected to the sun gear 222 of the next-stage planetary gear assembly.

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.

By setting the specific configuration of the carrier 221, the carrier 221 serves as an input body of the present-stage planetary gear assembly, thereby realizing the series connection of the multistage planetary gear assemblies.

Preferably, a plurality of the planetary gears 223 and the sun gear 222 are helical gears.

Specifically, the planetary gear 223 and the sun gear 222 may be one of cylindrical gears, and in this embodiment, the planetary gear 223 and the sun gear 222 are designed as helical gears.

Preferably, the number of teeth of the planetary gear 223 is equal to the number of teeth of the sun gear 222.

Specifically, the planet gear 223 and the sun gear 222 need to have the same modulus for engagement, but different numbers of teeth can be selected, and the speed increasing effect can be achieved through different transmission ratios.

In the present embodiment, the number of teeth of the planetary gear 223 is designed to be equal to the number of teeth of the sun gear 222.

As shown in fig. 4, the output gear 3 is a herringbone gear.

In some embodiments, the output gear 3 is a cylindrical gear.

In the present embodiment, the output gear 3 is set as the herringbone gear by utilizing the characteristics of high bearing capacity, stable transmission, small axial load, and the like of the herringbone gear.

As shown in fig. 5, the rack 43 is a herringbone rack.

In the present embodiment, the rack 43 is provided as a herringbone rack that meshes with a herringbone gear.

Preferably, the output power of the driving device 1 is 0.5W to 40W.

Specifically, the output power of the driving device 1 is 0.5W to 40W. 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

Power (W)	0.4	0.5	1	5	8	10	15	20	25	30	35	40	45
														Number of completions	39	40	45	52	57	62	68	75	79	85	94	95	95
Whether or not to make abnormal sound	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Whether or not	Is that

As shown in table 1, when the output power of the driving apparatus 1 is less than 0.5W, the number of times of switching the electronic lock is completed in 1 minute is less than 40, and the speed is too slow to be acceptable, so the inventors selected the minimum power of the driving apparatus 1 to be 0.5W. When the output power of the driving device 1 is greater than 40W, the electronic lock is influenced by the overall design, the speed enters the bottleneck period without obvious improvement, and abnormal sound can occur at the same time, so that the output power of the driving device 1 selected by the inventor is 0.5W-40W. Specifically, it may be 0.5W, 1W, 5W, 8W, 10W, 15W, 20W, 25W, 30W, 35W, 40W, etc.

Preferably, the transmission ratio of the driving device 1 and the output gear 3 is 1/42-1/3.

Specifically, the transmission ratio of the driving device 1 to the output gear 3 is 1/42-1/3, the transmission ratio=the driving wheel rotation speed/the driven wheel rotation speed, and it can be seen from the formula that the transmission ratio is inversely proportional to the driven wheel rotation speed, i.e. the smaller the transmission ratio, the larger the rotation speed of the driven wheel, the abnormal sound can easily occur due to inaccurate control. Therefore, the inventors selected different gear ratios of the driving device 1 and the output gear 3 for testing, 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 occurred, and the results are shown in table 2.

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

Ratio of transmission

1/2

1/3

1/5

1/6

1/9

1/12

1/18

1/24

1/30

1/36

1/42

1/45

Number of completions

38

41

47

53

61

70

78

84

89

92

95

98

Whether or not to make abnormal sound

Whether or not

Is that

As can be seen from table 2, if the transmission ratio of the driving device 1 to the output gear 3 is greater than 1/3, the electronic lock is failed because the locking or unlocking operation completed within 1 minute is less than 40 times; meanwhile, after the transmission ratio of the driving device 1 to the output gear 3 is smaller than 1/42, abnormal sound can occur in the electronic lock and the electronic lock is disqualified, so that the inventor selects the transmission ratio of the driving device 1 to the output gear 3 to be 1/42-1/3.

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 planet carrier 221 of the primary planet gear assembly 22a to rotate, the planet carrier 221 is driven to rotate a plurality of planet gears 223, the planet gears 223 realize rotation and revolution by being meshed with the sun gear 222 and the gear 23, the rotation is transmitted to the sun gear 222 meshed with the planet gears 223, the transmission shaft 226 of the planet carrier 221 of the middle planet gear assembly 22b is connected with the sun gear 222 of the primary planet gear assembly 22a and drives the planet gears 223 of the middle planet gear assembly 22b to rotate, the planet gears 223 realize self-assembly and revolution by being meshed with the sun gear 222 and the gear 23, the sun gear 222 of the middle planet gear assembly 22b is connected with the planet carrier 221 of the final planet gear assembly 22c and drives the planet gears 223 to rotate, the planet gears 223 realize rotation and revolution by being meshed with the sun gear 222 and the gear 23, the rotation is transmitted to the sun gear 222 meshed with the sun gear, the sun gear 222 is connected with the output gear 3 and drives the output gear 3 to rotate, the output gear 3 is meshed with the rack 43 of the lock lever 4, the rotation is converted into linear motion, and locking or unlocking of the lock lever 4 is 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;

an output gear connected with a sun gear of the final planetary gear assembly;

the locking rod is provided with a rack at least partially;

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 each stage of the plurality of planet gears is in mesh with the gear wheel, the sun gear is in mesh with the plurality of planet gears, and the planet carrier is coupled to the plurality of planet gears.

4. An electronic lock according to claim 3, wherein the driving device drives the planet carrier of the primary planetary gear assembly to rotate and drives the sun gear to rotate through a plurality of planet gears, the sun gear of the primary planetary gear assembly is coaxially connected with the planet carrier 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 sun gear of the intermediate planetary gear assembly.

5. The electronic lock of claim 4, wherein the planet carrier of each of the remaining stages of the planetary gear assembly, except the primary planetary gear assembly, is respectively connected to the sun gear of an adjacent previous stage of the planetary gear assembly.

6. The electronic lock of claim 5, wherein the planet carrier comprises a carrier body, a plurality of fixed shafts arranged on one side of the carrier body, and a transmission shaft arranged on the other side of the carrier body, the plurality of fixed shafts are correspondingly connected with the plurality of planet gears, and the transmission shaft is connected with the sun gear of the planetary gear assembly on the adjacent upper stage.

7. The electronic lock of claim 6, wherein an axis of the drive shaft coincides with a geometric axis of the wheel carrier body.

8. The electronic lock of claim 7, wherein the axes of the plurality of stationary shafts are offset in parallel with respect to the geometric axis of the wheel carriage body.

9. The electronic lock of claim 1, wherein a plurality of the planet gears and the sun gear are helical gears.

10. The electronic lock of claim 9, wherein the number of teeth of the planet gears is equal to the number of teeth of the sun gear.

11. The electronic lock of claim 1, wherein the output gear is a herringbone gear.

12. The electronic lock of claim 1, wherein the rack is a herringbone rack.

13. The electronic lock of claim 1, wherein the output power of the driving means is 0.5W to 40W.

14. The electronic lock of claim 1, wherein a ratio of the drive means to the output gear is 1/42-1/3.