Tooth disengagement protection structure and motor home vehicle lock

Abstract

The utility model relates to the technical field of motor home vehicle locks, in particular to a gear disengagement protection structure and a motor home vehicle lock, the gear disengagement protection structure comprises a gear box, an input main shaft, a first gear, a second gear and a pre-pressing spring; the first gear is provided with first end face teeth, the second gear is provided with second end face teeth, and the first end face teeth and the second end face teeth are meshed with each other to form transmission connection. One end of the pre-pressing spring abuts against the second gear, so that certain pre-pressing elastic force is applied to the second gear, and the first end face teeth and the second end face teeth are meshed with each other. The house lock further comprises a lock body base, a gear motor, a shifting rotary disc and a dead bolt assembly, the output end of the gear motor is in transmission connection with the input main shaft, the shifting rotary disc is in transmission connection with the second gear, and the dead bolt assembly is driven by the shifting rotary disc to conduct locking or unlocking operation. In conclusion, a disengagement protection structure with a disengagement design is provided, so that the motor home lock has higher tolerance and self-protection capability when facing external adverse effects.

Description

Technical Field

[0001] This utility model relates to the technical field of RV locks, and in particular to a tooth removal protection structure and an RV lock. Background Technology

[0002] Traditional RV lock structures may lack effective overload protection mechanisms. When encountering excessive resistance (e.g., jammed latch or forced entry), the motor is prone to overload or even burnout, and gears may break in extreme cases. Therefore, the tooth disengagement protection structure proposed in this patent implements an overload protection mechanism by introducing a separable gear mechanism (first gear and second gear) and a preload spring into the power transmission path. When the system encounters abnormal resistance, the gears automatically disengage, thereby protecting the motor and gear system from damage.

[0003] Traditional RV locks mostly use simple mechanical transmission systems, relying primarily on a geared motor and gear transmission structure. However, this structure often faces the following problems in practical applications:

[0004] Overload risk: During the locking or unlocking process of the RV lock, such as when the bolt encounters resistance, the geared motor may experience overload. This can lead to motor damage, gear wear, or even broken teeth, affecting the lifespan and security of the lock.

[0005] Lack of automatic protection mechanisms: Existing locks typically lack effective overload protection designs, relying mostly on the smooth operation of mechanical components to prevent malfunctions. In the event of an anomaly, such as motor failure, conventional designs cannot disconnect power transmission from the motor, rendering the mechanical lock cylinder or manual pivot unusable for locking or unlocking.

[0006] Poor user experience: In traditional gear transmission structures, users may not realize that the internal geared motor is damaged when applying force to unlock or lock. When the lock is stuck, users often continue to apply force, leading to damage to the device. Utility Model Content

[0007] To overcome the shortcomings mentioned above, this utility model aims to provide a technical solution that can solve the above problems.

[0008] This utility model provides a tooth removal protection structure, including:

[0009] The gearbox has a certain internal space and shaft holes at both ends;

[0010] The input spindle is rotatably connected to the shaft holes of the gearbox at both ends, with one end receiving rotational power from the outside.

[0011] The first gear is sleeved on the input spindle and forms a transmission connection with the input spindle;

[0012] The second gear is sleeved on the input spindle and forms a movable connection with the input spindle; and

[0013] A preload spring is fitted onto the end of the input spindle where the second gear is mounted.

[0014] The first gear has a first end face tooth, and the second gear has a second end face tooth. The first end face tooth and the second end face tooth mesh with each other to form a transmission connection. One end of the preload spring abuts against the second gear, thereby applying a certain preload spring force to the second gear, so that the first end face tooth and the second end face tooth mesh with each other.

[0015] As a further embodiment of this utility model: the part of the input spindle that connects to the first gear is set as a D-shaped shaft, and a D-shaped hole is provided at the central axis of the first gear, so that it is fitted onto the D-shaped shaft to form a transmission connection.

[0016] As a further embodiment of this utility model: a circular hole is provided at the central axis of the second gear, so that it can be fitted onto the input spindle to form a rotating connection.

[0017] As a further embodiment of this utility model: the end of the second gear away from the second end face teeth is provided with cylindrical straight teeth, which are used to mesh with the external gear and output rotational power to the outside.

[0018] As a further aspect of this utility model: the profile angle of the outer periphery of the first end face tooth and the second end face tooth is greater than the profile angle of the inner ring.

[0019] As a further aspect of this utility model: the angle between the outer periphery of the first end face tooth and the second end face tooth is greater than 90 degrees and less than 135 degrees.

[0020] As a further aspect of this utility model: the angle between the inner ring portion of the first end face tooth and the second end face tooth is greater than 60 degrees and less than 90 degrees.

[0021] This utility model also provides a RV lock, including the aforementioned tooth-removal protection structure, as well as a lock body base, a reduction motor, a rotary dial, and a latch assembly. The tooth-removal protection structure and the reduction motor are respectively installed on the lock body base, and the output end of the reduction motor is connected to the input main shaft of the tooth-removal protection structure. The rotary dial is rotatably connected to the lock body base and is connected to the second gear of the tooth-removal protection structure. The latch assembly is movably connected to the lock body base and performs locking or unlocking operations under the drive of the rotary dial.

[0022] As a further embodiment of this utility model: the actuating turntable is provided with a passive tooth, which meshes with the cylindrical spur teeth of the second gear to form a transmission connection.

[0023] As a further embodiment of this utility model: the actuating turntable is provided with actuating teeth, the latch assembly is provided with latching teeth, and the actuating teeth and latching teeth mesh with each other to form a transmission connection.

[0024] Compared with the prior art, the beneficial effects of this utility model are:

[0025] 1. A tooth-detachment protection structure is implemented: a first gear, a second gear, and a preload spring connected to them are introduced. Under normal operating conditions, the first gear transmits power to the second gear through meshing. However, when the second gear encounters resistance and cannot rotate smoothly, the first end face teeth and the second end face teeth will slide relative to each other, releasing the direct power transmission and preventing gear breakage or damage.

[0026] 2. Recoverable transmission connection: After the obstruction is removed, the preload spring pushes the second gear back to the meshing position, restoring power transmission. This design not only protects the mechanical components but also ensures stability and reliability after normal operation.

[0027] 3. Simplified Maintenance and Enhanced Security: The automatic tooth removal mechanism reduces malfunctions caused by improper use, enhancing the security and lifespan of the lock. Simultaneously, the simplicity of this design lowers maintenance costs and provides a more user-friendly experience.

[0028] In summary, through the above improvements, the technical solution of this patent effectively solves the shortcomings of traditional RV locks in terms of security and reliability, and provides a detachable tooth protection structure, which makes RV locks more resistant and self-protective when facing adverse external influences.

[0029] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0030] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0031] Figure 1 This is a schematic diagram of the gearbox and input spindle of this utility model;

[0032] Figure 2 This is a cross-sectional structural diagram of the first gear and the second gear of this utility model;

[0033] Figure 3 This is a schematic diagram of the structure of the first gear and the second gear of this utility model being separated;

[0034] Figure 4 This is a structural schematic diagram of the lock body base of this utility model;

[0035] Figure 5 This is a schematic diagram of the input spindle and preload spring of this utility model;

[0036] Figure 6 This is a structural schematic diagram of the first end face tooth and the second end face tooth of this utility model in a state of being disengaged from each other.

[0037] The reference numerals and names in the figure are as follows:

[0038] 10 Gearbox; 11 Shaft hole; 12 Input spindle; 13 D-shaped shaft; 14 Preload spring; 15 Clearance cylinder; 20 First gear; 21 First end face tooth; 22 D-shaped hole; 30 Second gear; 31 Second end face tooth; 32 Round hole; 33 Cylindrical spur tooth; 34 Step position; 35 Extension end; 40 Lock body base; 41 Mechanical lock cylinder; 42 Gear motor; 43 Manual rotating shaft; 44 Lock tongue assembly; 50 Actuating turntable; 51 Driven tooth; 52 Actuating tooth; 60 Lock tongue assembly; 61 Lock tongue locking tooth. Detailed Implementation

[0039] The technical solutions in the embodiments of this utility model will be clearly and completely described below. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0040] Please see Figures 1 to 6In this embodiment of the present invention, a tooth removal protection structure includes: a gearbox 10 with a certain internal space and shaft holes 11 at both ends; an input spindle 12 rotatably connected at both ends to the shaft holes 11 of the gearbox 10, with one end receiving rotational power from the outside; a first gear 20 sleeved on the input spindle 12 and forming a transmission connection with the input spindle 12, thereby rotating synchronously with the input spindle 12; a second gear 30 sleeved on the input spindle 12 and forming a movable connection with the input spindle 12; and a preload spring 14 sleeved on the input spindle 12. Shaft 12 is mounted on one end of the second gear 30; wherein, the end of the first gear 20 facing the second gear 30 is provided with a first end face tooth 21, and the end of the second gear 30 facing the first gear 20 is provided with a second end face tooth 31, the first end face tooth 21 and the second end face tooth 31 mesh with each other to form a transmission connection; one end of the preload spring 14 abuts against the inner wall of the gearbox 10, and the other end abuts against the second gear 30, thereby applying a certain preload spring force to the second gear 30, so that the first end face tooth 21 and the second end face tooth 31 abut against each other to transmit rotational power.

[0041] Specifically, under normal operating conditions, the input spindle 12 transmits the externally supplied rotational power to the first gear 20. The first gear 20, through the transmission connection between the first end face teeth 21 and the second end face teeth 31, transmits the power to the second gear 30. The second gear 30 then transmits the rotational power to the externally rotating disk 50. When the second gear 30 encounters resistance while transmitting power externally, preventing smooth rotation, the tooth surfaces of the first end face teeth 21 and the second end face teeth 31 interact, generating a certain pushing force along the axial direction of the input spindle 12. This causes the second gear 30 to move a certain distance away from the first gear 20, thereby disengaging the first end face teeth 21 and the second end face teeth 31, forming a disengaged state, and cutting off the transmission torque between the first gear 20 and the second gear 30. This configuration protects the gear system and prevents the extreme situation of broken teeth.

[0042] Secondly, when using the mechanical lock cylinder 41 to unlock or lock the RV lock, turning the lock cylinder can drive the actuating disc 50 to move the latch, enabling it to perform the unlocking or locking operation. At this time, the actuating disc 50 will also drive the second gear 30 to rotate synchronously. Since the first gear 20 remains stationary, the second gear 30 can also disengage from the first end face tooth 21 under the drive of the actuating disc 50, allowing the second gear 30 to rotate normally.

[0043] In addition, when the second gear 30 moves a certain distance away from the first gear 20, it will compress the preload spring 14 and cause it to deform. When the first gear 20 or the turntable 50 stops rotating, the preload spring 14 returns to its original position and pushes the second gear 30 toward the first gear 20, so that the first end face tooth 21 and the second end face tooth 31 come into contact with each other and re-mesh to form a transmission connection.

[0044] like Figure 1 , Figure 2 , Figure 3 and Figure 6 As shown, preferably, the portion of the input spindle 12 that connects to the first gear 20 is configured as a D-shaped shaft 13. The central axis of the first gear 20 has a D-shaped hole 22, which is fitted onto the D-shaped shaft 13 to form a transmission connection. The central axis of the second gear 30 has a circular hole 32, which is fitted onto the input spindle 12 to form a rotational connection.

[0045] Specifically, to enable the input spindle 12 to form a transmission connection with the first gear 20, a key connection, as used in the prior art, can be used to connect the first gear 20 to the input spindle 12. Alternatively, to simplify the connection structure, a D-shaped hole 22 can be directly provided to mate with a D-shaped shaft 13, allowing them to transmit rotational torque. Conversely, to prevent the second gear 30 from directly forming a transmission connection with the input spindle 12, the through hole of the second gear 30 can be set as a circular hole 32, with the diameter of the circular hole 32 slightly larger than the diameter of the D-shaped shaft, thus allowing the second gear 30 to rotate around the input spindle 12.

[0046] Secondly, since a preload spring 14 needs to be installed, a countersunk hole can be provided at the end of the second gear 30 away from the first gear 20, so that the diameter of the countersunk hole is larger than the diameter of the round hole 32, thereby forming a certain step position 34, which facilitates the installation of the preload spring 14, so that one end of the preload spring 14 can abut against the step position 34 to perform a preload operation on the second gear 30.

[0047] Furthermore, in order to optimize the meshing connection between the first gear 20 and the second gear 30, a certain protrusion can be provided at the central axis of the first end face tooth 21, and a corresponding countersunk hole can be provided at the central axis of the second end face tooth 31, so that the protrusion and the countersunk hole cooperate with each other to assist the meshing connection and disengagement process of the two.

[0048] like Figure 1 , Figure 2 and Figure 3 As shown, preferably, the end of the second gear 30 away from the second end face tooth 31 is provided with a cylindrical spur tooth 33, which is used to mesh with the external gear and output rotational power to the outside.

[0049] Specifically, the cylindrical spur tooth 33 can be a tooth of a common gear in the prior art, which facilitates meshing with the driven tooth 51 on the external rotary dial 50 to transmit the corresponding rotational torque. In order to install the input spindle 12 and the preload spring 14, a clearance cylinder 15 can also be provided at the position of the cylindrical spur tooth 33 of the second gear 30 in the gearbox 10. The clearance cylinder 15 has one open end fixed to the gearbox 10, and its other end has a bottom wall with a shaft hole 11 at the central axis of the bottom wall, so that the input spindle 12 can be movably connected to the shaft hole 11.

[0050] Secondly, the clearance cylinder 15 extends a certain length outward from the gearbox 10, thereby forming a certain cylindrical space, i.e., a clearance space, so that one end of the preload spring 14 can be installed in the cylindrical space and its other end abuts against the bottom wall of the clearance cylinder 15. At the same time, during the disengagement process, the end of the second gear 30 that is away from the first gear 20 can also move a certain distance into the clearance space of the clearance cylinder 15, so that it can correctly perform the disengagement operation.

[0051] In addition, to optimize the rotation and disengagement of the second gear 30, an extension end 35 can be provided at the end of the second gear 30 away from the second end face tooth 31. This extension end 35 can be inserted into the opening of the clearance cylinder 15, allowing it to move a certain distance into the clearance space of the clearance cylinder 15 during disengagement. Understandably, a certain clearance space should also be provided between the end of the cylindrical spur tooth 33 of the second gear 30 and the inner wall of the gearbox 10, so that the second gear 30 will not collide with the inner wall of the gearbox 10 during disengagement.

[0052] like Figure 3 As shown, preferably, the profile angle of the outer periphery of the first end face tooth 21 and the second end face tooth 31 is greater than the profile angle of the inner ring portion. The angle of the profile angle of the outer periphery of the first end face tooth 21 and the second end face tooth 31 is greater than 90 degrees and less than 135 degrees. The angle of the profile angle of the inner ring portion of the first end face tooth 21 and the second end face tooth 31 is greater than 60 degrees and less than 90 degrees.

[0053] Specifically, the angle of the profile angle of the outer periphery of the first end face tooth 21 and the second end face tooth 31 is set to γ1. Preferably, the angle of the profile angle of the inner ring of the first end face tooth 21 and the second end face tooth 31 is set to γ2. Preferably, after such a setting, the first end face tooth 21 and the second end face tooth 31 can form a meshing connection to transmit power, and when needed, the tooth surfaces of the two end face teeth can interact with each other to generate a certain pushing force, so that they can disengage from each other and form a disengaged state, cutting off the transmission torque between the first gear 20 and the second gear 30.

[0054] Secondly, preferably, the profile angles γ1 and γ2 of the first end face tooth 21 and the second end face tooth 31 are set to different values ​​(e.g., γ1=110°, γ2=75°). Experimental comparisons show that this setting, through optimized profile angle design, achieves the best tooth removal protection effect. By changing the profile angle, the contact area and contact pressure of the gear are altered, thereby affecting the tooth removal torque and reliability, thus verifying the influence of different profile angles on the tooth removal force.

[0055] like Figures 4 to 6 As shown, a preferred RV lock includes the aforementioned tooth-removal protection structure, as well as a lock body base 40, a reduction motor 42, a rotary dial 50, and a latch assembly 60. The tooth-removal protection structure and the reduction motor 42 are respectively installed on the lock body base 40, and the output end of the reduction motor 42 is connected to the input spindle 12 of the tooth-removal protection structure. The rotary dial 50 is rotatably connected to the lock body base 40 and is connected to the second gear 30 of the tooth-removal protection structure. The latch assembly 60 is movably connected to the lock body base 40 and performs locking or unlocking operations under the drive of the rotary dial 50.

[0056] Specifically, the aforementioned tooth-detaching protection structure can be installed in all locks that require a latch assembly 60, especially in locks that have both a mechanical lock cylinder 41 and an electric lock cylinder. Preferably, it is installed in a motorhome lock, allowing the motor's power to be transmitted to the rotary dial 50 after the electric lock cylinder's reduction motor 42 starts operating, causing it to actuate the latch assembly 60 to unlock or lock. Furthermore, after the unlocking or locking operation is completed and the rotary dial 50 stops rotating, the tooth-detaching structure between the first gear 20 and the second gear 30 can cut off the motor's power output, preventing gear breakage.

[0057] Secondly, even when the motor is not running, the turntable 50 can be rotated via the mechanical lock cylinder 41 or the manual rotating shaft 43 to allow it to lock or unlock the latch assembly 60 normally. This avoids the awkward situation of being unable to open or close the door when the motor malfunctions.

[0058] In addition, the RV lock also features a bolt assembly 44, a common feature in existing technology, to create a simple door lock system. Since the bolt assembly 44 lacks a deadbolt mechanism, it can be opened simply by pulling the handle wider. Therefore, a deadbolt assembly 60 is typically also required, which necessitates electronic or mechanical key authorization before unlocking.

[0059] like Figure 5 and Figure 6As shown, preferably, the actuating turntable 50 is provided with a driven tooth 51, which meshes with the cylindrical spur tooth 33 of the second gear 30 to form a transmission connection. The actuating turntable 50 is provided with an actuating tooth 52, and the latch assembly 60 is provided with a latching tooth 61, which meshes with the actuating tooth 52 and the latching tooth 61 to form a transmission connection.

[0060] Specifically, the second gear 30 rotates under the drive of the first gear 20, and through the cylindrical spur teeth 33 on it, it can transmit the rotational torque to the driven teeth 51 of the dial 50, thereby driving the dial 50 to rotate synchronously.

[0061] Secondly, the actuating tooth 52 can move the latching tooth 61 under the drive of the actuating turntable 50, so that the latching assembly 60 slides inside the lock body base 40, thereby popping out inside the lock body base 40 to form a locked state, or resetting and returning to the lock body base 40 to form an unlocked state.

[0062] The working principle of this utility model is as follows: The geared motor 42 drives the D-shaped shaft 13 to rotate, which in turn drives the first gear 20. The first gear 20 transmits power by meshing with the second end face teeth 31 of the second gear 30 through the first end face teeth 21. The cylindrical spur teeth 33 of the second gear 30 mesh with the driven teeth 51 of the actuating turntable 50, driving the actuating turntable 50. The actuating teeth 52 of the actuating turntable 50 mesh with the latching teeth 61 of the latch assembly 60, realizing the opening and closing of the latch assembly 60. When the second gear 30 encounters resistance, the first end face teeth 21 and the second end face teeth 31 move relative to each other axially, disengaging from the mesh. The preload spring 14 then pushes the second gear 30 back to the meshing position after the resistance is eliminated. The clearance cylinder 15 provides clearance space for the axial movement of the second gear 30.

[0063] Example 1: Basic structure of a motorhome lock

[0064] Structural components:

[0065] Gearbox 10: It has an internal housing structure containing two shaft holes 11 to support the rotation of the input spindle 12.

[0066] Input spindle 12: One end is connected to an external power device, and the other end is rotatably connected to the gearbox 10 through the shaft hole 11.

[0067] First gear 20: It is sleeved on the input spindle 12, and one end is connected to the input spindle 12 for transmission.

[0068] The second gear 30 is sleeved on the input spindle 12 and forms a detachable transmission connection with the first gear 20, which can protect against tooth loss when subjected to resistance.

[0069] Preload spring 14: Sleeve on input spindle 12, connected to second gear 30, applying a certain preload force to make the first end face tooth 21 and the second end face tooth 31 in close contact.

[0070] Operating procedure: Under normal operating conditions, the input spindle 12 drives the first gear 20 to rotate, and the power is transmitted to the second gear 31 through the first end face tooth 21. The second gear 30 then rotates and transmits energy outward. If the second gear 30 cannot rotate due to resistance, the first end face tooth 21 and the second end face tooth 31 will disengage, cutting off the power transmission and protecting other components from damage.

[0071] Example 2: Locking Mechanism of RV Lock

[0072] Structural components:

[0073] Linking the actuating turntable 50 and the latch assembly 60: The actuating turntable 50 and the second gear 30 are connected by a drive gear 51 and a cylindrical spur gear 33.

[0074] Locking tongue assembly 60: integrates locking tongue teeth 61, which can achieve locking or unlocking operations by rotating the dial 50.

[0075] Operation process: The user rotates the mechanical lock cylinder 41, causing the actuating turntable 50 to rotate, and the actuating teeth 52 push the latch assembly 60 to pop out or retract the latch. At this time, with the first gear 20 remaining stationary, the second gear 30 is equivalent to encountering excessive resistance during this process. Therefore, the second gear 30 will disengage from the first gear 20 to prevent any component from being damaged due to overload.

[0076] Example 3: RV lock using a new type of pre-compression spring 14

[0077] Structural components:

[0078] The preload spring 14 is configured such that a countersunk hole is opened at the end of the second gear 30 away from the first gear 20, and one end of the preload spring 14 abuts against the step position 34 of the countersunk hole.

[0079] Operation process: During operation, when the turntable 50 drives the second gear 30 to rotate synchronously to a certain angle, if resistance is encountered, the second gear 30 moves away from the first gear 20 to achieve tooth disengagement protection, causing the preload spring 14 to be compressed and deformed. After the resistance disappears, the preload spring 14 returns to its shape, pushing the second gear 30 to reset, so that the first end face tooth 21 and the second end face tooth 31 re-mesh, restoring power transmission.

[0080] Example 4: RV lock structure with clearance cylinder 15

[0081] Structural components:

[0082] A clearance cylinder 15 is provided to form a cylindrical space, which facilitates the installation of the preload spring 14, with one end of it abutting against the bottom wall of the cylinder. There is a certain space between the inner wall of the gearbox 10 and the second gear 30, allowing the second gear 30 to move a certain distance towards the clearance cylinder 15 when disengaging.

[0083] Operation process: During operation, when the user turns the lock cylinder and encounters resistance, the second gear 30 will move into the cylindrical space of the clearance cylinder 15, thus successfully disengaging and ensuring that the first gear 20 is not damaged. This design optimizes space utilization, ensures that the disengagement phenomenon is handled quietly and without damage, and improves flexibility and durability.

[0084] The above embodiments effectively demonstrate the technical design and application of this patented solution. These structural components and operational processes fully reflect the innovations in reliability and security of the proposed tooth-removal protection structure compared to traditional RV locks, and can effectively address potential problems encountered in practical use.

[0085] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention.

Claims

1. A tooth dislodgement protection structure, characterized by, The gear box (10) comprises a certain accommodating space inside and shaft holes (11) at both ends; The input main shaft (12) is rotatably connected to the shaft holes (11) of the gear box (10) at both ends, and one end is connected to the rotating power from the outside; The first gear (20) is sleeved on the input main shaft (12) and is in transmission connection with the input main shaft (12); The second gear (30) is sleeved on the input main shaft (12) and is in transmission connection with the input main shaft (12); and The pre-pressing spring (14) is sleeved on one end of the input main shaft (12) where the second gear (30) is installed; The first end face tooth (21) and the second end face tooth (31) are in meshing with each other to form transmission connection; one end of the pre-pressing spring (14) abuts against the second gear (30), so that a certain pre-pressing spring force is applied to the second gear (30), and the first end face tooth (21) and the second end face tooth (31) are in meshing with each other. The part where the input main shaft (12) is connected to the first gear (20) is provided with a D-shaped shaft (13), and the first gear (20) is provided with a D-shaped hole (22) at the central axis, so as to be sleeved on the D-shaped shaft (13) to form transmission connection.

2. A tooth disengagement protection structure according to claim 1, characterized in that The second gear (30) is provided with a circular hole (32) at the central axis, so as to be sleeved on the input main shaft (12) to form transmission connection.

3. The tooth disengagement protection structure according to claim 1, wherein The second gear (30) is provided with a cylindrical straight tooth (33) at one end away from the second end face tooth (31), which is used to mesh with the external gear to output rotating power.

4. The tooth disengagement protection structure according to claim 1, wherein The profile angle of the outer peripheral part of the first end face tooth (21) and the second end face tooth (31) is greater than the profile angle of the inner ring part.

5. The tooth disengagement protection structure according to claim 1, wherein The profile angle of the outer peripheral part of the first end face tooth (21) and the second end face tooth (31) is greater than 90 degrees and less than 135 degrees.

6. A ratchet guard according to claim 5, wherein 7. The tooth disengagement protection structure according to claim 5, wherein the profile angle of the inner ring part of the first end face tooth (21) and the second end face tooth (31) is greater than 60 degrees and less than 90 degrees. The tooth disengagement protection structure according to any one of claims 1-7 further comprises a lock body base (40), a speed reduction motor (42), a dialing turntable (50) and a dead bolt assembly (60), the tooth disengagement protection structure and the speed reduction motor (42) are respectively installed on the lock body base (40), and the output end of the speed reduction motor (42) is in transmission connection with the input main shaft (12) of the tooth disengagement protection structure, the dialing turntable (50) is rotatably connected to the lock body base (40) and is in transmission connection with the second gear (30) of the tooth disengagement protection structure, and the dead bolt assembly (60) is movably connected to the lock body base (40) and is driven by the dialing turntable (50) to perform locking or unlocking operation.

8. A recreational vehicle lock characterized by, The dialing turntable (50) is provided with a passive tooth (51), and the passive tooth (51) and the cylindrical straight tooth (33) of the second gear (30) are in meshing with each other to form transmission connection.

9. A recreational vehicle lock according to claim 8, wherein, ​ 10. The RV lock of claim 8, wherein: The dialing rotary disc (50) is provided with dialing teeth (52), the tongue assembly (60) is provided with tongue clamping teeth (61), the dialing teeth (52) and the tongue clamping teeth (61) are engaged with each other, thereby forming a transmission connection.

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