Innovative trailer arm and vehicle enabling fast hitching

Abstract

The utility model relates to the technical field of automobile parts, especially to an innovative trailer arm and vehicle capable of realizing quick traction connection, which mainly comprises two components of a self-latching trailer tenon and a ball mount socket. The self-latching trailer tenon and the ball mount socket are connected and disassembled quickly through the reverse-docking square sleeve. The reverse-docking square sleeves are distributed on the ball mount socket at a certain interval. Different heights of reverse-docking square sleeves are selected to meet the application requirements of ball heads of different heights. Meanwhile, the self-latching trailer tenon and the trailer interface are connected and disassembled quickly through the anti-dropping bolt, and the gap between the self-latching trailer tenon and the trailer interface is eliminated through the locking wedge. Various ball head configurations are provided on the ball mount socket for selection. Through rotation selection, the appropriate ball head structure is used for traction.

Description

Technical Field

[0001] This utility model relates to the field of automotive parts technology, specifically to an innovative trailer arm that enables rapid traction connection. Background Technology

[0002] In the European and American markets, pickup trucks, SUVs, and passenger cars are generally equipped with trailer hitch receivers (compliant with SAE J684 standards) for connecting towing ball mounts to tow caravans, boats, or other vehicles.

[0003] Due to the diverse usage scenarios, trailer heights, towing capacities, and trailer interface specifications vary, necessitating the replacement and adaptation of trailer hitches. The mainstream market solution uses a sliding sleeve-type adjustment structure combined with a multi-stage hole adjustment device with pin positioning to achieve adjustable functionality. However, the sliding sleeve-type adjustment structure typically has a clearance exceeding 1.00mm between the sleeve and the main beam, causing 3-5Hz resonance and shaking when the vehicle is traveling on unpaved roads. Furthermore, with the multi-stage hole adjustment device with pin positioning, human error leading to pin detachment accounts for 37% of towing device failure cases (NHTSA 2024 Annual Report), exposing the safety hazards of traditional mechanical locking mechanisms. In addition, the adaptability deficiencies of adjustable trailer hitches have evolved from simple height adjustment to multi-dimensional expansion requirements.

[0004] Existing typical multi-functional trailer hitch products feature a grooved structure, shaped like a figure "7". The grooved structure is usually vertically arranged for connection with the ball joint, allowing for easy vertical adjustment of the ball joint. Connecting holes are distributed regularly on the horizontal and vertical arms. The horizontal holes connect to the trailer interface, while the vertical holes secure the ball joint in the vertical direction. By engaging different holes on the vertical arm, the ball joint achieves varying heights, accommodating trailers of different heights.

[0005] Existing typical multi-functional trailer hitch products use a pin-type connection method, which has the following drawbacks:

[0006] a) It has many auxiliary parts and relies on manual installation, which can easily lead to problems such as forgetting to install or incorrectly installing them, causing the risk of drag failure.

[0007] b) The clearance between the sliding groove structure and the ball head seat generally exceeds 1.00mm, which causes looseness and shaking and abnormal noise during dragging;

[0008] c) Its use is limited and it lacks scalability. Utility Model Content

[0009] The purpose of this invention is to provide an innovative trailer arm that enables rapid traction connection, in order to solve the problems mentioned in the background art.

[0010] To achieve the above objectives, this utility model provides the following technical solution:

[0011] An innovative trailer boom enabling rapid towing connection includes:

[0012] Self-locking drag bolts and extended ball joints;

[0013] The self-locking tow bolt includes an anti-detachment pin, a locking wedge, a square tube structure, a tow bolt head, and a drive component. The drive device is installed inside the square tube structure. The square tube structure is used for insertion connection with the trailer interface, and the tow bolt head is used for locking connection with the extension ball seat. The square tube structure and the tow bolt head are connected as a whole by welding.

[0014] The drive device includes a gear swing arm mechanism, an anti-detachment pin telescopic mechanism, a gap elimination mechanism, a square sleeve locking mechanism, and a support structure.

[0015] There is a linkage between the anti-detachment pin telescopic mechanism and the gap elimination mechanism. When the self-locking tow bolt is connected to the trailer interface, the drive component drives the gear swing arm mechanism to rotate clockwise, pushing the anti-detachment pin telescopic mechanism to push the anti-detachment pin out of the square tube structure and insert it into the pin holes on both sides of the trailer interface. This locks the self-locking tow bolt in the trailer interface to prevent it from coming out. When the anti-detachment pin is fully pushed out, the vertical plate structure of the push plate in the anti-detachment pin telescopic mechanism triggers the gap elimination mechanism to push the locking wedge out of the square tube structure so that the locking wedge presses against the inner wall of the trailer interface. This eliminates the gap between the trailer hook and the trailer interface. When the extension ball seat is connected to the self-locking tow bolt, the square sleeve locking mechanism is triggered to extend the pin shaft, achieving a quick, firm, and reliable locking connection between the self-locking tow bolt and the extension ball seat.

[0016] Furthermore, the support structure consists of an upper rear support structure, a middle rear support structure, a lower rear support structure, and a front support structure. The middle rear support structure is fixedly installed on the lower rear support structure and is installed close to the front support structure to form a lower support structure. The upper rear support structure is installed on the middle rear support structure and the front support structure and is located on one side of the middle rear support structure and the front support structure. The upper rear support structure, the middle rear support structure, the lower rear support structure, and the front support structure are connected together to form a solid whole, which is installed inside the square tube structure to restrict and support the moving parts.

[0017] Furthermore, the gear swing arm mechanism mainly consists of a force transmission square shaft, a rotating shaft, a grooved gear one, a grooved gear two, a swing arm wheel, and a swing arm;

[0018] Among them, grooved gear one, grooved gear two and swing arm wheel are mounted on the rotating shaft. There are three shaft positions distributed on the rotating shaft, namely shaft position one, shaft position two and shaft position three. The cross-sections of shaft position one and shaft position three are circular, and the cross-section of shaft position two is square.

[0019] Grooved gear one and grooved gear two are respectively installed on shaft one and shaft three through their respective circular holes, and can rotate freely around the shaft;

[0020] The swing arm wheel is installed on the second axle through a square hole, and the swing arm wheel rotates together with the rotating shaft;

[0021] The grooved gear has a C-shaped groove on the side near the swing arm wheel, and the swing arm wheel has a boss on the corresponding radius on the side near the grooved gear. The boss is embedded in the C-shaped groove.

[0022] The grooved gear 2 has C-shaped grooves 2 distributed on the side near the swing arm wheel, and the swing arm wheel has a boss 2 arranged on the corresponding radius on the side near the grooved gear 2, and the boss 2 is embedded in the C-shaped groove 2.

[0023] When the swing arm wheel rotates, when the boss is within the distribution range of the C-shaped groove, the slotted gear is stationary relative to the swing arm wheel.

[0024] When the movement range of the boss one exceeds the distribution range of the C-shaped groove one, the swing arm wheel will drive the grooved gear one to rotate together;

[0025] When the swing arm wheel rotates, when the second boss is within the distribution range of the second C-shaped groove, the second grooved gear is stationary relative to the swing arm wheel;

[0026] When the movement range of the second boss exceeds the distribution range of the second C-shaped groove, the swing arm wheel will drive the second grooved gear to rotate together.

[0027] Furthermore, the anti-detachment pin telescopic mechanism mainly consists of a push plate and an anti-detachment pin;

[0028] The anti-detachment pin is connected to the push plate by a pin. The inclined surface on the anti-detachment pin matches the outer inclined surface on the push plate. The pin is inserted into the hole of the anti-detachment pin and matches the inner inclined surface of the push plate. By moving the push plate back and forth, the two anti-detachment pins arranged on the left and right move axially.

[0029] When the push plate moves forward and the anti-detachment pin reaches its maximum extension, the straight section of the push plate cooperates with the straight section of the anti-detachment pin to effectively suppress the retraction of the anti-detachment pin.

[0030] The push plate is equipped with grooves for guiding purposes and functional grooves that engage with cylindrical pins fixed on the anti-loosening rack shaft. When the anti-loosening rack shaft extends, the functional grooves restrict the retraction of the push plate and also restrict the retraction of the anti-loosening pin. When the anti-loosening rack shaft retracts, the functional grooves drive the push plate to retract together and simultaneously drive the anti-loosening pin to retract. The vertical plate structure on the push plate is used to trigger the action of the gap elimination mechanism.

[0031] Furthermore, the swing arm is connected to the swing arm wheel by a pin. When the swing arm wheel is on the push plate, the swing arm contacts the groove of the push plate through the arm end.

[0032] When the swing arm wheel rotates in the direction of the push plate, it completes the action of pushing the push plate to move away from the swing arm wheel;

[0033] When the swing arm wheel is under the push plate, the swing arm tilts upward under the constraint of the limiting structure in the rear support structure, and the arm end leaves the groove of the push plate.

[0034] Furthermore, the gap elimination mechanism mainly consists of an anti-loosening rack shaft, a spring, a locking wedge, a cylindrical pin, a round-headed pin, a rack shaft retaining pin, and a retaining spring.

[0035] The anti-loosening rack shaft has an inclined surface that mates with the locking wedge, a rack structure for movement, a guiding cylindrical surface, and a hole for accommodating the rack shaft retaining pin.

[0036] The cylindrical pin is tightly integrated with the anti-loosening rack shaft and fits into the groove on the push plate. When the anti-loosening rack shaft moves, it drives the push plate to move.

[0037] The locking wedge engages with the inclined surface of the anti-loosening rack shaft via an inclined surface, transforming the axial movement of the anti-loosening rack shaft into a locking action where the locking wedge moves radially along the anti-loosening rack shaft. A spring provides a continuous thrust to the locking wedge, maintaining its clamping position and securely locking the square tube structure within the trailer interface. The output force of spring one is not less than 210N.

[0038] The hole on the anti-loosening rack shaft is used to accommodate the locking spring and the rack shaft locking pin, and together with the round head pin installed on the front support structure, they form the triggering structure of the anti-loosening rack shaft. When the vertical plate structure of the push plate in the anti-disengagement pin telescopic mechanism moves and presses the round head pin, the trigger gap elimination mechanism is activated.

[0039] Furthermore, when the anti-loosening rack shaft compresses the spring and reaches the locking position, under the action of the locking spring, the rack shaft locking pin pops out, exposing its end face to the outer cylindrical surface of the anti-loosening rack shaft, and inserts into the hole of the front support structure, pressing the round-headed pin against it so that its head is exposed. When the drive component is rotated clockwise, the push plate moves towards the locking wedge under the action of the swing arm wheel and the swing arm. The round-headed pin installed on the front support structure is pressed by the vertical plate, which drives the compression of the rack shaft locking pin. When the end face of the rack shaft locking pin is flush with the cylindrical surface of the anti-loosening rack shaft, the anti-loosening rack shaft loses the locking of the locking pin and is pushed by the spring to move axially towards the locking wedge.

[0040] Furthermore, the square sleeve locking mechanism mainly consists of an eccentric rack shaft, two springs, a pin shaft, two round-headed pins, two rack shaft locking pins, and two locking springs;

[0041] The inclined surface of the eccentric rack shaft engages with the inclined surface of the pin shaft, converting the horizontal forward and backward movement of the eccentric rack shaft into the vertical up and down movement of the pin shaft. This amplifies the force applied by the horizontal spring two on the eccentric rack shaft and outputs it onto the pin shaft, thus achieving clamping and locking of the extended ball seat. Spring two provides a continuous thrust to the eccentric rack shaft and acts on the pin shaft, maintaining the pin shaft in a continuous clamping state and preventing loosening of the lock on the extended ball seat. The output force of spring two is not less than 200N.

[0042] The copper sleeve and round pin 2 installed on the towing bolt head, as well as the locking spring 2 embedded in the eccentric rack shaft and the rack shaft locking pin 2, constitute the action triggering component of the eccentric rack shaft.

[0043] The hole on the eccentric rack shaft is used to accommodate the second locking spring and the second rack shaft locking pin, while the second round-headed pin is retained in the hole of the drag bolt head. The copper sleeve positions the second round-headed pin and seals it in the drag bolt head.

[0044] Furthermore, when the eccentric rack shaft compresses the second spring and reaches the locking position, under the action of the second retaining spring, the second retaining pin of the rack shaft pops out so that its end face is exposed on the outer cylindrical surface of the eccentric rack shaft, and is inserted into the hole of the drag bolt head, pressing the second round-head pin, so that the ball head surface of the second round-head pin is exposed on the lower surface of the drag bolt head.

[0045] Furthermore, the planes on the left and right sides of the drag bolt head cooperate with the inner walls on the left and right sides of the inner cavity of the inverted square sleeve, restricting the left and right movement of the inverted square sleeve on the drag bolt head.

[0046] The inclined surface of the upper plane of the drag bolt head matches the inner inclined surface of the upper plane near the front end of the inverted square sleeve. The trapezoidal bosses protruding from both sides of the drag bolt head match the trapezoidal grooves on the left and right sides of the inverted square sleeve, together completing the forward movement and swing of the inverted square sleeve.

[0047] The inclined boss at the rear end of the lower plane of the drag bolt head cooperates with the inner inclined surface at the rear end of the lower plane inside the inverted square sleeve, and the inclined surface of the protruding pin shaft cooperates with the inner inclined surface at the rear end of the upper plane inside the inverted square sleeve, together completing the backward movement and swing of the inverted square sleeve.

[0048] Furthermore, the extended ball seat mainly consists of an inverted square sleeve, a ball head seat, a multi-functional ball head component, and a reinforcing plate structure;

[0049] The number of inverted square sleeves is determined by the adjustment height that the extended ball seat needs to achieve. At least one inverted square sleeve is required. Multiple inverted square sleeves are welded or cast into a whole by vertical stacking, and the two sides are reinforced by welding or casting reinforcing plates. The ball seat is welded or cast to the lowest inverted square sleeve.

[0050] The multi-functional ball joint component mainly consists of a base, a connecting shaft, a ball head, a load-bearing ring groove, and a positioning hole. The connecting shaft fits into the seat hole of the ball head base, allowing the multi-functional ball joint component to rotate freely around the ball head base.

[0051] The structural pin is embedded in the hole of the ball head seat and extends into the load-bearing ring groove of the multi-functional ball head component to prevent the multi-functional ball head component from falling out of the ball head seat;

[0052] The positioning pin mainly consists of a pin seat, a positioning pin, and a pin spring, and is fixed in the hole of the ball head seat. The positioning pin is inserted into the positioning hole of the multi-functional ball head component to prevent the multi-functional ball head component from rotating during use.

[0053] Furthermore, the driving component includes, but is not limited to, a handle or a motor.

[0054] To achieve the above objectives, this utility model provides the following technical solution:

[0055] A vehicle comprising the innovative trailer arm as described above.

[0056] Compared with the prior art, the beneficial effects of this utility model are:

[0057] 1. By integrating the anti-detachment pin and locking wedge into the square tube structure of the trailer hook, the product's integration is improved, eliminating the need for additional accessories and providing a better user experience.

[0058] 2. By introducing a handle, the locking and unlocking of the trailer hook product can be achieved by varying the direction and angle of the handle's rotation, eliminating the reliance on tools during the installation process.

[0059] 3. Through the structural design of the push plate parts, a linkage bridge is established between the anti-detachment pin and the locking wedge. By operating the handle, the actions between the anti-detachment pin and the locking wedge are linked, realizing the simultaneous realization of the locking function and the gap elimination function when the trailer hook product is installed.

[0060] 4. The design of the C-shaped groove on the grooved gear and the boss on the swing arm wheel solves both the need for independent rotation between the swing arm wheel and the grooved gear, and the need for transmission of the swing arm wheel to drive the grooved gear to rotate, which is innovative in terms of function.

[0061] 5. By using spring one, when the anti-loosening rack shaft extends forward and presses against the locking wedge, spring one can continuously apply pressure to the anti-loosening rack shaft. Through the cooperation between the cylindrical pin fixed on the anti-loosening rack shaft and the functional groove on the push plate, the retraction of the push plate is restricted, thereby eliminating the risk of the anti-loosening pin retraction and realizing the safety redundancy design of anti-loosening.

[0062] 6. By using spring one, when the anti-loosening rack extends forward and presses against the locking wedge, spring one can continuously apply pressure to the anti-loosening rack shaft, ensuring that the locking wedge is always in a clamped state, realizing the dynamic and continuous action of the gap elimination function. No new gap will be formed during vehicle operation, realizing the redundant design of gap elimination.

[0063] 7. By introducing a retractable pin shaft and cooperating with various positioning bevels, the inverted square tube seat is quickly locked on the drag bolt head, meeting the need for quick assembly and disassembly of the inverted square tube seat and creating a brand-new connection method. This connection method does not rely on additional pins and safety pins, avoiding the risk of drag failure due to human negligence.

[0064] 8. By applying force to the eccentric rack shaft through the two springs, the force is continuously applied to the ejected pin shaft, so that the various positioning buckles and trapezoidal notches arranged on the inverted square tube seat and the various positioning inclined surfaces and trapezoidal positioning blocks on the drag bolt head are always in a state of pressure contact, and no gap will be formed to cause the connection between the inverted square tube seat and the drag bolt head to fail, thus realizing the redundant design of drag safety.

[0065] 9. By applying force to the eccentric rack shafts through the two springs, the force is continuously applied to the ejected pin shaft, so that the various positioning buckles and trapezoidal notches arranged on the inverted square tube seat and the various positioning inclined surfaces and trapezoidal positioning blocks on the drag bolt head are always in a state of pressure contact. All gaps between the contact surfaces are eliminated, so that the self-locking drag bolt and the various extended applications of the welded or cast inverted square tube seat form a gapless connection, eliminating the root cause of noise and swaying.

[0066] 10. By fixing the self-locking tow hook to a standard trailer interface conforming to SAE-J684, and designing the tow hook head and the inverted square tube seat as a standard structural form, the tow hook head forms a new standard interface. Through the combination of the inverted square tube seat and other expansion components, various application forms can be formed; for example, by stacking multiple inverted square tube seats and combining them with other expansion components, various height-adjustable trailer hook structures with different functions can be formed, etc. These all expand the application range of this connection method and have broad commercial prospects. Attached Figure Description

[0067] Figure 1 This is a three-dimensional schematic diagram of an existing trailer boom structure with basic functions.

[0068] Figure 2 This is a three-dimensional schematic diagram of an existing trailer boom structure with height adjustable function.

[0069] Figure 3 This is a three-dimensional schematic diagram of the overall structure and assembly relationship of this utility model.

[0070] Figure 4 This is a three-dimensional schematic diagram of the category expansion and connection relationship of this utility model.

[0071] Figure 5 This is a cross-sectional perspective view of the present invention in its assembled state.

[0072] Figure 6 This is a cross-sectional perspective view of the assembled state of this utility model from another angle.

[0073] Figure 7 This is an exploded view of the gear swing arm mechanism of this utility model.

[0074] Figure 8 This is an exploded view of the anti-detachment pin telescopic mechanism of this utility model.

[0075] Figure 9 This is a schematic diagram showing three positional states of the swing arm wheel and swing arm in the gear swing arm mechanism of this utility model.

[0076] Figure 10 This is a three-dimensional schematic diagram illustrating the relationship between the gear swing arm mechanism, the anti-detachment pin telescopic mechanism, and the gap elimination mechanism of this utility model.

[0077] Figure 11 This is a three-dimensional schematic diagram illustrating the relationship between the gear swing arm mechanism, the square sleeve locking mechanism, and the extended ball seat of this utility model.

[0078] Figure 12This is a three-dimensional schematic diagram illustrating the ball head assembly form of the multifunctional ball head component of this utility model and its connection relationship with the extended ball seat.

[0079] In the diagram: 1-Self-locking drag bolt, 1.1-Square tube structure, 1.2-Drag bolt head, 1.2.1-Beveled surface, 1.2.2-Beveled boss, 1.2.3-Flat surface, 1.2.4-Trapezoidal boss, 1.2.5-Hole, 2-Extended ball seat, 2.1-Inverted square sleeve, 2.1.1-Inner beveled surface, 2.1.2-Inner beveled surface, 2.1.3-Inner sidewall, 2.1.4-Inner beveled surface, 2.1.5-Lower plane, 2.1.6-Trapezoidal groove, 2.2-Ball head seat, 2.2.1-Seat hole, 2.2.2-Hole, 2.2.3-Hole, 2.3-Reinforcing plate structure, 3-Multifunctional ball head component, 3.1-Seat body, 3.2-Connecting shaft, 3.3-Ball head, 3.4 - Load-bearing ring groove, 3.5 - Positioning hole, 4 - Anti-detachment pin, 4.1 - Inclined surface, 4.2 - Straight section, 4.3 - Hole, 5 - Locking wedge, 5.1 - Inclined surface, 6 - Handle, 7 - Pin shaft, 7.1 - Upper inclined surface, 7.2 - Lower inclined surface, 8 - Structural pin, 9 - Rear support structure - Upper, 10 - Rear support structure - Middle, 10.1 - Limiting structure, 11 - Rear support structure - Lower, 12 - Front support structure, 13 - Force transmission square shaft, 14 - Rotating shaft, 14.1 - Shaft position one, 14.2 - Shaft position two, 14.3 - Shaft position three, 15 - Grooved gear one, 15.1 - Hole, 15.2 - C-shaped groove one, 16 - Grooved gear two, 16.1 - Hole, 16.2 - C-shaped groove two, 17 - Swing arm wheel, 17.1-Square hole, 17.2-Boss 1, 17.3-Pin hole, 17.4-Boss 2, 18-Swing arm, 18.1-Arm end, 18.2-Swing arm end hole, 19-Anti-loosening rack shaft, 19.1-Rack structure, 19.2-Beveled surface, 19.3-Cylindrical surface, 19.4-Hole, 20-Cylindrical pin, 21-Spring 1, 22-Push plate, 22.1-Groove, 22.2-Groove, 22.3-Groove, 22.4-Vertical plate, 22.5-Inner beveled surface, 22.6-Outer beveled surface, 22.7-Straight section, 23-Reset spring, 24-Eccentric rack shaft, 24.1-Beveled surface, 24.3-Hole, 25-Spring 2, 26-Rack shaft retaining pin 2, 27-Round 28-Cap, 29-Clamping Spring II, 30-Rack Shaft Clamping Pin I, 30.1-End Face, 32-Round Head Pin I, 33-Pin Seat, 34-Pin Spring, 35-Positioning Pin, 36-Pin, 37-Washer, 38-Snap Ring, 39-Pin, 40-Clamping Spring I, 41-Copper Sleeve, A-Trailer Interface, A.1-Trailer Interface Inner Wall, A.2-Pin Hole, B.1-Gap Elimination Partition I, B.2-Gap Elimination Partition II, CL-Shaped Trailer Arm, C.1-Connecting Hole I, C.2-Connecting Hole II, D-Pin, D.1-Hole, E-Locking Screw, F-Elastic Pin, G-Ball Head Slide, H-Ball Head, J-Trailer Arm, J.1-Connecting Hole III, J.2-Hole. Detailed Implementation

[0080] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0081] In the description of this utility model, it should be noted that the terms "upper end," "lower end," "inner," "outer," "front end," "rear end," "both ends," "one end," and "the other end," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0082] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," "sleeved with," "connected," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0083] Please see Figures 1 to 12 This utility model provides a technical solution:

[0084] The purpose of this invention is to provide a trailer hitch product with a novel connection method. The trailer hitch product consists of two components: a self-locking trailer tenon and a ball mount socket. The self-locking trailer tenon and the ball mount socket are connected and disassembled quickly via inverted square sleeves. These inverted square sleeves are distributed on the ball mount socket in a certain number and at certain intervals. Selecting inverted square sleeves of different heights to combine with the self-locking trailer tenon allows for the application of ball heads of varying heights. Simultaneously, the self-locking trailer tenon and the trailer interface can also be quickly locked together via an anti-detachment pin, and a locking wedge eliminates any gap between the self-locking trailer tenon and the trailer interface. The ball mount socket offers a variety of ball head configurations to choose from; by rotating, a suitable ball head structure can be selected for towing.

[0085] The innovative connection between the self-locking tow bolt and the extension ball joint provides a wide range of combination options for trailer hitch products, as well as extensive expansion applications. The connection between the self-locking tow bolt and the extension ball joint is stable and reliable, easy to install and remove, and convenient to expand, making it suitable for a wide range of towing and mounting needs.

[0086] A trailer hitch product with a completely new connection method consists of two main components: a self-locking trailer tenon that connects to the trailer interface, and a ball-mount stocket that allows for quick connection to the self-locking trailer tenon.

[0087] The two parts are functionally divided as follows: The self-locking tow bolt serves as both a connecting component for fixed connection to the towing vehicle and a supporting component for the installation and connection of the extension ball joint. It is securely connected to the trailer interface of the towing vehicle via an anti-detachment pin and a locking wedge, with the exposed end used for connection to the extension ball joint. The extension ball joint is a multi-functional ball joint component. Through an inverted square sleeve structure, it can be quickly and securely fixed to the self-locking tow bolt. The inverted square sleeves are distributed on the extension ball joint in a certain number and spacing. Selecting inverted square sleeves of different heights to connect with the self-locking tow bolt can meet the application needs of ball joints of different heights. Multiple ball joint configurations can be combined, and by rotating the selection tool, a suitable ball joint structure can be quickly and conveniently selected for towing.

[0088] The self-locking tow bolt is a completely new connection device that extends from the trailer interface of the towing vehicle. The extended ball joint, as a combination component with a standard, proprietary connection structure, can be used in combination with various ball head structures to meet different usage requirements through the use of inverted square sleeves.

[0089] The self-locking tow bolt consists of a square tube structure, a tow bolt head, a handle, and a drive mechanism housed within the square tube structure. The square tube structure and the tow bolt head are welded together as a single unit. The handle, through different steering and angle adjustments, manipulates the drive mechanism within the square tube structure to achieve different actions, thus completing the locking connection with the trailer interface and extension ball joint of the towing vehicle. The drive mechanism comprises three parts: an anti-detachment pin telescopic mechanism, a gap elimination mechanism, and a square sleeve locking mechanism. The anti-detachment pin telescopic mechanism and the gap elimination mechanism are linked, working together to lock the self-locking tow bolt within the trailer interface of the towing vehicle. The square sleeve locking mechanism then locks the extension ball joint to the tow bolt head.

[0090] The extended ball joint consists of an inverted square sleeve, a ball head seat, a multi-functional ball head component, and a reinforcing plate structure. When constructing the extended ball joint, depending on the application, either a single inverted square sleeve can be used as a component connecting to the self-locking towing bolt, or multiple inverted square sleeves can be welded or cast vertically into a single unit to expand the height adjustment range of the extended ball joint. The ball head seat is welded or cast to the lowest inverted square sleeve in the vertical direction to form a single unit, with reinforcing plates on both sides of the inverted square sleeve for added strength. The multi-functional ball head component consists of two or more ball heads. Depending on functional requirements, other components such as hooks can be welded in to further expand the application range of the extended ball joint. The multi-functional ball head component is inserted into the ball head seat and connected using structural pins. This ensures the connection strength between the multi-functional ball head component and the ball head seat while allowing the multi-functional ball head component to rotate freely within the ball head seat. A locating pin locks the multi-functional ball head component in place, allowing for the selection of different ball heads.

[0091] Insert the self-locking tow hook into the trailer hitch. Turn the handle clockwise to rotate the gear swing arm mechanism inside the square tube structure. The swing arm pushes the anti-loosening pin push plate mechanism, pushing the anti-loosening pin out along the inclined surface of the push plate and inserting it into the corresponding hole on the side wall of the trailer hitch, locking the self-locking tow hook in the trailer hitch. When the anti-loosening pin is fully extended, the trigger of the anti-loosening rack shaft of the gap elimination mechanism is activated. This releases the anti-loosening rack shaft driven by the compressed spring, causing it to extend axially towards the locking wedge. The inclined surface on the anti-loosening rack shaft pushes out the locking wedge, which presses against the inner wall of the trailer hitch, occupying the gap between the self-locking tow hook and the trailer hitch, thus preventing the trailer hook from loosening. Release the handle; the handle returns to its original position, and the self-locking tow hook is in the locked state.

[0092] If the handle is rotated clockwise, the boss on the swing arm wheel drives the grooved gear to retract the anti-loosening rack shaft. The anti-loosening rack shaft compresses the spring and resets the trigger, locking the anti-loosening rack shaft in the compressed position. During the retraction of the anti-loosening rack shaft, the locking wedge returns to its original position under the action of the return spring, releasing the anti-loosening state of the self-locking tow bolt and restoring the clearance with the trailer interface. At the same time, the fixing pin on the anti-loosening rack shaft drives the anti-detachment pin push plate to retract, and the anti-detachment pin retracts under the action of the slide groove, releasing the self-locking tow bolt from its locked state in the trailer interface.

[0093] When the extended ball seat is combined with the self-locking drag bolt, the inverted square sleeve of the extended ball seat is inserted into the drag bolt head. During the insertion process, the trigger of the eccentric rack shaft at the bottom of the drag bolt head is pressed and triggered by the lower plane inside the inverted square sleeve. The trigger of the eccentric rack shaft is released by the eccentric rack shaft driven by the compression spring and extends towards the pin shaft. Relying on the inclined surface on the eccentric rack shaft, the pin shaft is pushed out of the upper surface of the drag bolt head and pressed against the inner inclined surface of the inverted square sleeve. Together with the inclined surface structure at the upper and lower ends of the drag bolt head and the V-shaped positioning structure on both sides of the drag bolt head, the extended ball seat is tightly and firmly locked onto the self-locking drag bolt.

[0094] When the extended ball seat is disconnected from the self-locking towing bolt, the handle is rotated counterclockwise to drive the gear swing arm mechanism inside the square tube structure to rotate. The boss on the swing arm wheel drives the grooved gear to retract the eccentric rack shaft. The eccentric rack shaft compresses the spring and resets the trigger of the eccentric rack shaft. The eccentric rack shaft is locked in the spring compression position. The pin shaft loses the support of the inclined surface of the eccentric rack shaft and retracts into the towing bolt head, releasing the locking connection to the extended ball seat.

[0095] The grooved gear one and the grooved gear two are provided with C-shaped grooves to avoid the boss on the swing arm wheel, so as to realize different operating actions of the handle in different directions.

[0096] The following is a detailed introduction:

[0097] A trailer hitch product with a brand-new connection method includes two independent components: a self-locking tow bolt 1 and an extension ball seat 2. The self-locking tow bolt 1 and the extension ball seat 2 are connected quickly, firmly, and reliably using a brand-new connection method, and the connection can also be quickly released.

[0098] The self-locking tow bolt 1 consists of a square tube structure 1.1, a tow bolt head 1.2, an anti-detachment pin 4, a locking wedge 5, a handle 6, a pin shaft 7, a cover 28, and a drive device installed inside the square tube structure 1.1. The square tube structure 1.1 and the tow bolt head 1.2 are welded together to form a whole. The handle 6 transmits the driving force to the drive device through the force-transmitting square shaft 13. The drive device consists of a gear swing arm mechanism, an anti-detachment pin telescopic mechanism, a gap elimination mechanism, a square sleeve locking mechanism, and a support structure. The gear swing arm mechanism is the external driving force distribution unit. Through the coordination of the rotation direction and rotation angle of the swing arm wheel 17, the anti-detachment pin telescopic mechanism, the gap elimination mechanism, and the square sleeve locking mechanism are controlled separately. The combined action of the anti-detachment pin telescopic mechanism and the gap elimination mechanism enables a quick, secure, and reliable locking connection of the self-locking tow bolt 1 in the trailer interface A; the square sleeve locking mechanism enables a quick, secure, and reliable locking connection between the self-locking tow bolt 1 and the extended ball seat 2.

[0099] The support structure consists of a front support structure 12, a rear support structure - upper 9, a rear support structure - middle 10, and a rear support structure - lower 11.

[0100] like Figure 7 The pin hole 17.3 on the swing arm wheel 17 is used to connect the swing arm 18 to the swing arm wheel 17 by inserting a pin 36 into the pin hole 17.3 and the swing arm end hole 18.2, thereby achieving a hinge connection between the swing arm 18 and the swing arm wheel 17. This allows the swing arm 18 to swing relative to the swing arm wheel 17, realizing the reciprocating motion of the arm end 18.1. Figure 3 and Figure 7 As shown, starting from the handle 6 side, the rotating shaft 14 is sequentially equipped with a grooved gear 15, a rocker arm wheel 17, a grooved gear 16, a washer 37, and a retaining ring 38. The retaining ring 38 is used to lock the sequentially installed parts on the rotating shaft 14, preventing axial movement and ensuring accurate positioning. The washer 37 is used to increase the blocking area of ​​the retaining ring 38.

[0101] like Figure 7 The gear-arm mechanism consists of a force-transmitting square shaft 13, a rotating shaft 14, a grooved gear 15, a grooved gear 16, an arm wheel 17, and an arm 18. The grooved gear 15, grooved gear 16, and arm wheel 17 are mounted on the rotating shaft 14. The rotating shaft 14 has three shaft positions: shaft positions 14.1 and 14.3 have circular cross-sections, while shaft position 14.2 has a square cross-section. The grooved gears 15 and 16 are mounted on shaft positions 14.1 and 14.3 respectively through circular holes 15.1 and 16.1, allowing them to rotate freely around the rotating shaft 14. The arm wheel 17 is mounted on shaft position 14.2 through a square hole 17.1 and rotates together with the rotating shaft 14. The grooved gear 15 has C-shaped grooves 15.2 distributed on the side near the rocker arm wheel 17. The rocker arm wheel 17 has a boss 17.2 arranged on the corresponding radius on the side near the grooved gear 15. The boss 17.2 is embedded in the C-shaped groove 15.2. When the rocker arm wheel 17 rotates, when the boss 17.2 is within the distribution range of the C-shaped groove 15.2, the grooved gear 15 is stationary relative to the rocker arm wheel 17. When the movement range of the boss 17.2 exceeds the distribution range of the C-shaped groove 15.2, the rocker arm wheel 17 will drive the grooved gear 15 to rotate together. Similarly, the grooved gear 16 has C-shaped grooves 16.2 distributed on the side near the swing arm wheel 17, and the swing arm wheel 17 has bosses 17.4 arranged on the corresponding radius on the side near the grooved gear 16. The bosses 17.4 are embedded in the C-shaped grooves 16.2. When the swing arm wheel 17 rotates, the grooved gear 16 is stationary relative to the swing arm wheel 17 when the bosses 17.4 are within the distribution range of the C-shaped grooves 16.2. When the movement range of the bosses 17.4 exceeds the distribution range of the C-shaped grooves 16.2, the swing arm wheel 17 will drive the grooved gear 16 to rotate together.

[0102] like Figure 8 The anti-detachment pin telescopic mechanism consists of a push plate 22 and an anti-detachment pin 4. The anti-detachment pin 4 is connected to the push plate 22 via a pin 39. The inclined surface 4.1 on the anti-detachment pin 4 engages with the outer inclined surface 22.6 on the push plate 22. The pin 39 is inserted into the hole 4.3 of the anti-detachment pin 4 and engages with the inner inclined surface 22.5 of the push plate 22. By moving the push plate 22 back and forth, the two anti-detachment pins 4 arranged on the left and right move axially. When the push plate 22 moves forward and the anti-detachment pin 4 reaches its maximum extension, the straight section 22.7 of the push plate 22 engages with the straight section 4.2 of the anti-detachment pin 4, effectively suppressing the retraction of the anti-detachment pin 4. The groove 22.3 on the push plate 22 is used for guidance. The groove 22.1 on the push plate 22 engages with the cylindrical pin 20 fixed on the anti-loosening rack shaft 19. When the anti-loosening rack shaft 19 extends, it restricts the retraction of the push plate 22 and also restricts the retraction of the anti-detachment pin 4. When the anti-loosening rack shaft 19 retracts, it drives the push plate 22 to retract as well, and at the same time drives the anti-detachment pin 4 to retract.

[0103] like Figure 9 The forward movement of the push plate 22 is achieved by the swing arm 18, which is connected to the swing arm wheel 17 via a pin 36. When the swing arm wheel 17 is above the push plate 22, the swing arm 18 contacts the groove 22.2 of the push plate 22 through its arm end 18.1. When the swing arm wheel 17 rotates towards the push plate 22, it pushes the push plate 22 away from the swing arm wheel 17. When the swing arm wheel 17 is below the push plate 22, the swing arm 18, restricted by the limiting structure 10.1 of the rear support structure 10, tilts upward, and the arm end 18.1 leaves the groove 22.2 of the push plate 22.

[0104] like Figure 10The gap elimination mechanism consists of an anti-loosening rack shaft 19, a spring 21, a locking wedge 5, a cylindrical pin 20, a round-headed pin 32, a rack shaft retaining pin 30, and a retaining spring 40. The anti-loosening rack shaft 19 has an inclined surface 19.2 that mates with the locking wedge 5, a rack structure 19.1 for movement, a guiding cylindrical surface 19.3, and a hole 19.4 for accommodating the rack shaft retaining pin 30. The cylindrical pin 20 is tightly integrated with the anti-loosening rack shaft 19 and mates with a groove 22.1 on the push plate 22, driving the push plate 22 to move when the anti-loosening rack shaft 19 moves. The locking wedge 5, through its inclined surface 5.1 mates with the inclined surface 19.2 of the anti-loosening rack shaft 19, converts the axial movement of the anti-loosening rack shaft 19 into a locking action where the locking wedge 5 moves radially along the anti-loosening rack shaft 19. The hole 19.4 on the anti-loosening rack shaft 19 is used to accommodate the locking spring 40 and the rack shaft locking pin 30, and together with the round-headed pin 32 installed on the front support structure 12, they form the triggering structure of the anti-loosening rack shaft 19. When the anti-loosening rack shaft 19 is locked on the front support structure 12 by the rack shaft locking pin 30, the push plate 22 moves towards the locking wedge block 5 under the action of the swing arm wheel 17 and the swing arm 18. The upright plate 22.4 presses the round-headed pin 32 installed on the front support structure 12, which drives the compression of the rack shaft locking pin 30. When the end face 30.1 of the rack shaft locking pin 30 is flush with the cylindrical surface 19.3 of the anti-loosening rack shaft 19, the anti-loosening rack shaft 19 is pushed by the spring 21 and moves axially towards the locking wedge block 5 quickly.

[0105] like Figure 11 The square sleeve locking mechanism consists of an eccentric rack shaft 24, a second spring 25, a pin shaft 7, a second round-headed pin 27, a rack shaft retaining pin 26, and a retaining spring 29. The inclined surface 24.1 of the eccentric rack shaft 24 engages with the lower inclined surface 7.2 of the pin shaft 7, converting the horizontal forward-backward movement of the eccentric rack shaft 24 into the vertical up-and-down movement of the pin shaft 7. It also amplifies the force applied by the horizontal spring 25 on the eccentric rack shaft 24, outputting it on the pin shaft 7 to achieve clamping and locking of the extended ball seat 2. The copper sleeve 41 and the second round-headed pin 27 mounted on the towing bolt head 1.2, along with the retaining spring 29 and the rack shaft retaining pin 26 embedded in the eccentric rack shaft 24, constitute the triggering assembly of the eccentric rack shaft 24. The hole 24.3 on the eccentric rack shaft 24 is used to accommodate the second locking spring 29 and the second rack shaft locking pin 26. The second round-headed pin 27 is retained in the hole 1.2.5 of the drag bolt head 1.2. The copper sleeve 41 positions the second round-headed pin 27 and seals it in the drag bolt head 1.2. When the eccentric rack shaft 24 compresses the second spring 25 and reaches the locked position, under the action of the second locking spring 29, the second rack shaft locking pin 26 pops out, so that its end face protrudes from the outer cylindrical surface of the eccentric rack shaft 24, and is inserted into the hole 1.2.5 of the drag bolt head 1.2, pressing the second round-headed pin 27 and making the ball head surface of the second round-headed pin 27 protrude from the lower surface of the drag bolt head 1.2.

[0106] The connection between the self-locking drag bolt 1 and the extended ball seat 2 is achieved through the combination of the drag bolt head 1.2 and the inverted square sleeve 2.1. The planes 1.2.3 on the left and right sides of the drag bolt head 1.2 cooperate with the inner sidewalls 2.1.3 on the left and right sides of the inner cavity of the inverted square sleeve 2.1, restricting the left and right movement of the inverted square sleeve 2.1 on the drag bolt head 1.2. The inclined surface 1.2.1 on the upper plane of the drag bolt head 1.2 cooperates with the inner inclined surface 2.1.1 near the front end of the upper plane of the inverted square sleeve 2.1. The trapezoidal protrusions on both sides of the drag bolt head 1.2 The boss 1.2.4 engages with the trapezoidal grooves 2.1.6 on the left and right sides of the inverted square sleeve 2.1 to restrict the forward movement and swing of the inverted square sleeve 2.1. The inclined boss 1.2.2 on the lower plane of the drag bolt head 1.2 near the rear end engages with the inner inclined surface 2.1.4 on the lower inner plane of the inverted square sleeve 2.1. The upper inclined surface 7.1 of the protruding pin shaft 7 engages with the inner inclined surface 2.1.2 on the upper inner plane of the inverted square sleeve 2.1 near the rear end to restrict the backward movement and swing of the inverted square sleeve 2.1. By fitting the inverted square sleeve 2.1 onto the drag bolt head 1.2 and restricting it in the left, right, up, down, and forward and backward directions, a firm and reliable locking connection between the extended ball seat 2 and the self-locking drag bolt 1 is ensured.

[0107] The extended ball joint 2 consists of an inverted square sleeve 2.1, a ball head seat 2.2, a multi-functional ball head component 3, and a reinforcing plate structure 2.3. The number of inverted square sleeves 2.1 is determined by the required adjustment height of the extended ball joint 2; at least one inverted square sleeve 2.1 is required. Multiple inverted square sleeves 2.1 are vertically stacked and welded or cast into a single unit. The two sides are reinforced by welded or cast reinforcing plate structures 2.3. The ball head seat 2.2 is welded or cast to the lowest inverted square sleeve 2.1. The multi-functional ball head component 3 typically consists of a seat body 3.1, a connecting shaft 3.2, a ball head 3.3, a load-bearing ring groove 3.4, and a positioning hole 3.5. The connecting shaft 3.2 mates with the seat hole 2.2.1 of the ball head seat 2.2, allowing the multi-functional ball head component 3 to rotate freely around the ball head seat 2.2. The structural pin 8 is embedded in the hole 2.2.3 of the ball joint 2.2 and extends into the load-bearing ring groove 3.4 of the multi-functional ball joint component 3, preventing the multi-functional ball joint component 3 from falling out of the ball joint 2.2. The positioning pin consists of a pin seat 33, a positioning pin 35, and a pin spring 34, and is fixed in the hole 2.2.2 of the ball joint 2.2. The positioning pin 35 is inserted into the positioning hole 3.5 of the multi-functional ball joint component 3 to prevent the multi-functional ball joint component 3 from rotating during use.

[0108] When using the trailer hitch, first ensure that the anti-loosening rack shaft 19 is locked on the front support structure 12 by the rack shaft retaining pin 1 30, and that the eccentric rack shaft 24 is locked on the towing head 1.2 by the rack shaft retaining pin 2 26. Insert the self-locking tow bolt 1 into the trailer interface A. Turn the handle 6 clockwise facing it to trigger the anti-detachment pin extension mechanism and the gap elimination mechanism, securely and reliably locking the self-locking tow bolt 1 into the trailer interface A. Then, slightly tilt the extension ball seat 2 and insert the inverted square sleeve 2.1 into the tow bolt head 1.2 of the self-locking tow bolt 1. After insertion, the trapezoidal bosses 1.2.4 on both sides of the tow bolt head 1.2 position the extension ball seat 2. Move the extension ball seat 2 upwards to activate the trigger assembly of the eccentric rack shaft 24 at the lower end of the tow bolt head 1.2, extending the pin shaft 7 and achieving a secure and reliable locking connection between the extension ball seat 2 and the self-locking tow bolt 1. Detailed operation is as follows:

[0109] Insert the square tube structure 1.1 of the self-locking tow bolt 1 into the trailer interface A, and align the anti-detachment pin 4 with the pin hole A.2 of the trailer interface A. Rotate the handle 6 clockwise from its starting position. The handle 6 transmits external power to the gear swing arm mechanism through the force transmission square shaft 13, which in turn drives the swing arm wheel 17 to rotate clockwise through the rotating shaft 14. At this time, the boss 17.2 on the swing arm wheel 17 is located in the C-shaped groove 15.2 of the grooved gear 15, and the boss 17.2 is at a certain distance from both ends of the C-shaped groove 15.2; the boss 17.4 on the swing arm wheel 17 is located in the C-shaped groove 16.2 of the grooved gear 16, and the boss 17.4 is at a certain distance from both ends of the C-shaped groove 16.2; the swing arm wheel 17 is above the plane of the push plate 22 in its starting position, and the arm end 18.1 of the swing arm 18 contacts the groove 22.2 of the push plate 22. The clockwise rotation of the swing arm wheel 17 drives the swing arm 18 to push the push plate 22 away from the swing arm wheel 17. Under the action of the outer inclined surface 22.6 of the push plate 22, the two anti-detachment pins 4 are inserted into the pin holes A.2 of the trailer interface A, preventing the self-locking tow bolt 1 from coming out of the trailer interface A, thus locking the self-locking tow bolt 1 in the trailer interface A. As described above, the boss 17.2 maintains a certain distance from both ends of the C-shaped groove 15.2 of the slotted gear 15, and the boss 17.4 maintains a certain distance from both ends of the C-shaped groove 16.2 of the slotted gear 16. During the clockwise rotation of the swing arm wheel 17, the boss 17.2 and the boss 17.4 do not contact the ends of the C-shaped groove 15.2 and the C-shaped groove 16.2. The swing arm wheel 17 maintains independent movement, completing the pushing action of the push plate 22.

[0110] After the anti-detachment pin 4 is fully extended, the swing arm wheel 17 continues to push the push plate 22 to the maximum position through the swing arm 18. At this time, the vertical plate 22.4 of the push plate 22 presses the round head pin 32, forcing the rack shaft retaining pin 30 to retract the cylindrical surface 19.3 of the anti-loosening rack shaft 19, releasing the restriction of the anti-loosening rack shaft 19. The anti-loosening rack shaft 19 is pushed by the compressed spring 21 to move towards the locking wedge 5. The locking wedge 5 is pushed out of the square tube structure 1.1 through the inclined surface 19.2. The locking wedge 5 presses against the inner wall A.1 of the trailer interface A, occupying the gap between the square tube structure 1.1 and the trailer interface A, so that the self-locking towing bolt 1 is tightly connected with the trailer interface A. During the process of the anti-loosening rack shaft 19 pushing the locking wedge 5 through the inclined plane 19.2 to tightly connect the square tube structure 1.1 with the trailer interface A, the spring 21 always exerts a strong force on the anti-loosening rack shaft 19, preventing the locking wedge 5 from loosening due to external factors such as vibration. This ensures a reliable connection between the self-locking tow bolt 1 and the trailer interface A. During the movement of the anti-loosening rack shaft 19 toward the locking wedge block 5, the cylindrical pin 20, which is tightly connected to the anti-loosening rack shaft 19, moves forward relative to the groove 22.1 of the push plate 22. At the same time, the anti-detachment pin 4, in its fully extended state, has its straight section 4.2 engaging with the straight section 22.7 of the push plate 22. The cylindrical pin 22 occupies the front end position of the groove 22.1, hindering the space for the push plate 22 to retract. The anti-detachment pin 4 cannot reach the outer inclined section 22.6 from the straight section 22.7 of the push plate 22, eliminating the risk of the anti-detachment pin 4 retracting and ensuring reliable locking of the self-locking tow bolt 1 and the trailer interface A.

[0111] As mentioned earlier, after the boss 17.2 on the swing arm wheel 17 rotates clockwise, it still maintains a certain distance from both ends of the C-shaped groove 15.2. During the movement of the anti-loosening rack shaft 19 towards the locking wedge block 5, the rack structure 19.1 of the anti-loosening rack shaft 19 will drive the grooved gear 15 to rotate counterclockwise, causing the lower end of the C-shaped groove 15.2 to approach the boss 17.2 without contacting it. During this process, since the boss 17.2 and the C-shaped groove 15.2 still do not contact each other, the swing arm wheel 17 will maintain the state of pushing the push plate 22 to its furthest point, and the handle 6 will not be affected by the counter-clockwise rotation of the grooved gear 15.

[0112] If it is necessary to unlock and remove the self-locking tow bolt 1 from the trailer interface A, the handle 6 needs to be rotated clockwise. At this time, the swing arm wheel 17 is driven by the force transmission square shaft 13 to rotate clockwise. The swing arm wheel 17 will rotate to the lower plane of the push plate 22. The boss 17.2 of the swing arm wheel 17 contacts the lower end of the C-shaped groove 15.2 of the grooved gear 15. The swing arm wheel 17 drives the grooved gear 15 to rotate clockwise together. The grooved gear 15 drives the anti-loosening rack shaft 19 to move away from the locking wedge block 5 through the rack structure 19.1. The cylindrical pin 20 fixed on the anti-loosening rack shaft 19 will move along the groove 22.1 of the push plate 22 and drive the push plate 22 to move together towards the swing arm wheel 17. Under the constraint of the limiting structure 10.1 of the rear support structure - middle 10, the swing arm 18 raises the arm end 18.1 above the groove 22.2 of the push plate 22, making room for the push plate 22 to retract. The retraction of the push plate 22 is caused by the inner inclined surface 22.5 driving the anti-detachment pin 4 to retract through the pin 39, releasing the self-locking tow bolt 1 from the trailer interface A. At the same time, the retraction of the anti-loosening rack shaft 19 removes the locking force on the locking wedge 5. Under the action of the return spring 23, the locking wedge 5 retracts into the square tube structure 1.1, completing the release of the self-locking tow bolt 1 from the trailer interface A.

[0113] During the process of releasing the self-locking drag bolt 1, the anti-loosening rack shaft 19 moves away from the locking wedge block 5, compressing the spring 21. When the rack shaft retaining pin 30 on the anti-loosening rack shaft 19 aligns with the round head pin 32, under the action of the retaining spring 40, the rack shaft retaining pin 30 extends out of the cylindrical surface 19.3 of the anti-loosening rack shaft 19 and locks onto the front support structure 12. The round head pin 32 is also exposed by the push of the rack shaft retaining pin 30.

[0114] During the process of unlocking the self-locking tow bolt 1 from the trailer interface A, the swing arm wheel 17 continues to rotate clockwise driven by the handle 6. At this time, the C-shaped groove 16.2 on the grooved gear 16 still retains a groove to accommodate the clearance space for the boss 17.4 to continue to move clockwise with the swing arm wheel 17, so that the grooved gear 16 maintains its independent and unaffected characteristics during the entire clockwise rotation of the swing arm wheel 17.

[0115] During the connection between the extended ball seat 2 and the self-locking drag bolt 1, the extended ball seat 2 is tilted slightly so that the inverted square sleeve 2.1 is fitted onto the drag bolt head 1.2 of the self-locking drag bolt 1. The planes 1.2.3 on the left and right sides of the drag bolt head 1.2 cooperate with the inner side walls 2.1.3 of the inverted square sleeve 2.1 to restrict the extended ball seat 2 in the left and right directions. When the trapezoidal bosses 1.2.4 on both sides of the drag bolt head 1.2 engage with the trapezoidal grooves 2.1.6 on both sides of the inverted square sleeve 2.1, gently lift the expansion ball seat 2 upwards so that the lower inner plane 2.1.5 of the inverted square sleeve 2.1 presses against the round-headed pin 27 extending from the lower plane of the drag bolt head 1.2, causing the rack shaft retaining pin 26 to retract into the eccentric rack shaft 24, releasing the restriction of the eccentric rack shaft 24. Under the action of the compressed spring 25, it moves rapidly towards the pin shaft 7, and the inclined surface 24.1 of the eccentric rack shaft 24 engages with the pin shaft 7. The lower inclined surface 7.2 pushes the pin shaft 7 to extend towards the upper end of the drag bolt head 1.2. The upper inclined surface 7.1 of the pin shaft 7 engages with the inner inclined surface 2.1.2 near the rear end of the upper end of the inverted square sleeve 2.1, causing the inclined boss 1.2.2 on the lower plane of the drag bolt head 1.2 to contact with the inner inclined surface 2.1.4 near the rear end of the lower end of the inverted square sleeve 2.1, and the inclined surface 1.2.1 on the upper plane of the drag bolt head 1.2 to contact with the inner inclined surface 2.1.1 near the front end of the upper end of the inverted square sleeve 2.1. Through the engagement of the upper and lower inverted inclined surfaces, the two side planes, and the boss, the extended ball seat 2 is securely and reliably locked onto the self-locking drag bolt 1. After the extension ball seat 2 is locked in place, the spring 25 always applies force to the eccentric rack shaft 24, so that the upper inclined surface 7.1 of the pin shaft 7 always applies force to the inner inclined surface 2.1.2 of the inverted square sleeve 2.1 of the extension ball seat 2, preventing the extension ball seat 2 from loosening and ensuring a reliable connection between the extension ball seat 2 and the self-locking drag bolt 1.

[0116] During the movement of the eccentric rack shaft 24 toward the pin shaft 7, the rack structure 24.2 of the eccentric rack shaft 24 drives the grooved gear 16 to rotate clockwise. As mentioned earlier, the boss 17.4 on the swing arm wheel 17 is a certain distance away from both ends of the C-shaped groove 16.2 of the grooved gear 16. When the grooved gear 16 rotates clockwise, the upper end of the C-shaped groove 16.2 is close to the boss 17.4 but does not contact it, so that the state of the swing arm wheel 17 is not affected.

[0117] When the extended ball seat 2 is released from the self-locking drag bolt 1, the handle 6 is rotated counterclockwise. During the counterclockwise rotation of the swing arm wheel 17, the boss 17.4 contacts the upper end of the C-shaped groove 16.2 of the grooved gear 16, and drives the grooved gear 16 to rotate counterclockwise. The grooved gear 16, through the rack structure 24.2, moves the eccentric rack shaft 24 away from the pin shaft 7. The pin shaft 7 loses its force, and the reliable contact between the upper inclined surface 7.1 and the inner inclined surface 2.1.2 of the inverted square sleeve 2.1 is released. The extended ball seat 2 can then be easily removed from the self-locking drag bolt 1.

[0118] During the process of releasing the locking of the extended ball seat 2, the eccentric rack shaft 24 moves away from the pin shaft 7, compressing the second spring 25. When the rack shaft retaining pin 26 on the eccentric rack shaft 24 is aligned with the round head pin 27, under the action of the retaining spring 29, the rack shaft retaining pin 26 extends out of the eccentric rack shaft 24 and exposes its outer cylindrical surface, locking onto the drag bolt head 1.2. The round head pin 27 is also exposed by the push of the rack shaft retaining pin 26.

[0119] During the process of unlocking the extended ball seat 2 from the self-locking drag bolt 1, the swing arm wheel 17 is driven by the handle 6 to rotate counterclockwise. At this time, the C-shaped groove 15.2 on the grooved gear 15 has a groove to accommodate the clearance space for the boss 17.2 to rotate counterclockwise with the swing arm wheel 17, so that the grooved gear 15 remains independent and unaffected during the counterclockwise rotation of the swing arm wheel 17 to retract the eccentric rack shaft 24.

[0120] This utility model:

[0121] 1. In the anti-detachment pin extension mechanism and the gap elimination mechanism, the linkage between the extension of the anti-detachment pin and the locking wedge block is realized through the cooperation between the groove on the push plate and the cylindrical pin on the rack shaft, as well as the cooperation between the vertical plate on the push plate and the round head pin and the tenon pin, thus realizing the synchronous completion of the locking and gap elimination actions of the trailer arm product.

[0122] ① The anti-detachment pin extension mechanism extends the anti-detachment pin and triggers the gap elimination mechanism.

[0123] ② By eliminating the gap in the system, the gap between the trailer hook and the interface is restored, and the anti-detachment pin is retracted.

[0124] 2. In the design of the anti-detachment pin telescopic mechanism, the cylindrical pin fixed on the rack shaft and the slot of a limited length on the push plate cooperate to achieve the following: after the push plate drives the anti-detachment pin to extend, the cylindrical pin fixedly installed on the rack shaft after extension occupies the space for the push plate to retract, preventing the push plate from retracting and causing the anti-detachment pin to retract, thus realizing the self-locking and anti-retraction function.

[0125] By continuously applying force to the gap elimination mechanism through the spring, and through the connection between the gap elimination system and the push plate, a safety redundancy design is achieved for the anti-retraction pin function.

[0126] 3. In the gap elimination mechanism, the spring tension continuously presses the anti-loosening rack shaft in the locked state, continuously squeezing the locking wedge block, thus realizing the dynamic and continuous action of the gap elimination function. No new gap will be formed during vehicle operation, realizing the redundancy design of the gap elimination function.

[0127] 4. In the design of the anti-detachment pin telescopic mechanism and the gap elimination mechanism, during the locking process, the action of the anti-detachment pin takes precedence over the action of the locking wedge block. This ensures that the anti-detachment pin extends before triggering the gap elimination action logic, avoiding a situation where the gap elimination mechanism has reached its position but the anti-detachment pin has not, thus ensuring absolute safety.

[0128] 5. By cooperating with the various positioning undercuts and trapezoidal notches arranged on the undercut square tube seat and the various positioning inclined surfaces and trapezoidal positioning blocks arranged on the drag bolt head, and by ensuring that the arrangement direction of the inclined surfaces is conducive to the fixed connection of the undercut square tube seat on the drag bolt head, reliable positioning of the undercut square tube seat on the drag bolt head is achieved; by using the retractable pin shaft, in conjunction with the positioning undercuts between the pin shaft and the undercut square tube seat, reliable locking and firm connection of the undercut square tube seat on the drag bolt head is achieved.

[0129] ① The multiple positioning bevels on the upper and lower planes of the drag bolt head, the trapezoidal positioning blocks on both sides, and the positioning bevels on the retractable pin shaft are in a corresponding and matching relationship with the positioning undercuts and trapezoidal notches on the upper and lower surfaces of the undercut square tube seat.

[0130] ② The towing bolt head requires at least four positioning surfaces to achieve the towing function, including an upper positioning slope, a lower positioning slope, a positioning slope on the retractable pin shaft, and positioning blocks on both sides, corresponding to four or more positioning buckles and positioning notches. Among them, two or more sets of positioning surfaces, such as the front positioning slope on the upper surface of the towing bolt head shown in the example of this utility model and the positioning blocks on both sides, are used to fix the buckled square tube seat and bear the forward force; the other two or more sets of positioning surfaces, such as the rear positioning slope on the lower surface of the towing bolt head shown in the example of this utility model and the positioning slope of the pin shaft extending from the upper surface, are used to fix the buckled square tube seat and bear the backward force.

[0131] ③ Of the at least four positioning surfaces required for the towing head to achieve the towing function, at least one of the positioning surfaces is engaged through a retractable movable part with a positioning bevel. In the example of this utility model, the movable part is a pin that can extend out of the upper plane. When the pin extends out of the upper plane of the towing head, the positioning bevel on the pin, in conjunction with the other positioning surfaces, achieves a stable, firm, and tight connection between the self-locking towing head and the inverted square tube seat. When the pin retracts to the upper plane of the towing head, it releases the lock on the inverted square tube seat, allowing the inverted square tube seat to be easily removed from the self-locking towing head.

[0132] 6. In the locked state, the continuous pressure of the spring on the eccentric rack shaft keeps the eccentric rack shaft pressed against the retractable pin shaft through the inclined plane, eliminating the possibility of loosening of the mating surface. By setting the angle of the inclined plane, the output force of the spring is amplified, realizing reliable contact between each positioning inclined plane and trapezoidal positioning surface, ensuring a firm connection between the inverted square tube seat and the self-locking drag bolt, avoiding the possibility of loosening and dragging failure, and realizing high reliability of connection and dragging safety redundancy design.

[0133] 7. The inverted square tube seat is a standard independent structure that works with the self-locking tow bolt. It includes all the connection structures required for connecting with the self-locking tow bolt, and has a regular outer contour, making it easy to assemble and connect. Together with the self-locking tow bolt, it forms a brand-new towing connection device. By matching one or more inverted square tube seats with each other and combining them with extension parts, it can be installed on the self-locking tow bolt to form different trailer hook forms, which have a wide range of flexible extended applications.

[0134] This embodiment also provides a vehicle including the innovative trailer arm that enables rapid towing connection as described above. The specific structure of this innovative trailer arm is the same as described in the above embodiments. Since this vehicle adopts all the technical solutions of all the above embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be elaborated upon here.

[0135] The parts of this utility model not described are existing technology, or may be the same as existing technology, or may be known technology, or may be implemented using existing technology, and will not be described in detail here.

[0136] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. An innovative trailer arm capable of rapid traction connection, characterized in that, include: Self-locking drag bolt (1) and extended ball seat (2); The self-locking towing bolt (1) includes an anti-detachment pin (4), a locking wedge (5), a square tube structure (1.1), a towing bolt head (1.2), and a drive unit. The drive unit is installed inside the square tube structure (1.1). The square tube structure (1.1) is used for insertion connection with the trailer interface (A), and the towing bolt head (1.2) is used for locking connection with the extension ball seat (2). The square tube structure (1.1) and the towing bolt head (1.2) are connected as a whole by welding. The drive device is placed inside the square tube structure (1.1), with a cross-sectional dimension not exceeding 40mm×40mm, and includes a gear swing arm mechanism, an anti-detachment pin telescopic mechanism, a gap elimination mechanism, a square sleeve locking mechanism, and a support structure. There is a linkage between the anti-detachment pin telescopic mechanism and the gap elimination mechanism. When the self-locking tow bolt (1) is connected to the trailer interface (A), the drive component drives the gear swing arm mechanism to rotate clockwise, pushing the anti-detachment pin telescopic mechanism to move. This pushes the anti-detachment pin (4) out of the square tube structure (1.1) and inserts it into the pin holes (A.2) on both sides of the trailer interface (A), locking the self-locking tow bolt (1) in the trailer interface (A) to prevent it from coming out. When the anti-detachment pin (4) is fully pushed out, the anti-detachment mechanism... The push plate (22.4) of the push plate (22) in the release pin telescopic mechanism triggers the gap elimination mechanism to push the locking wedge (5) out from the square tube structure (1.1) so that the locking wedge (5) presses against the inner wall of the trailer interface (A) to eliminate the gap between the trailer hook and the trailer interface (A). When the extension ball seat (2) is connected to the self-locking towing bolt (1), the square sleeve locking mechanism is triggered to extend the pin shaft (7) to realize the locking connection between the self-locking towing bolt (1) and the extension ball seat (2).

2. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The support structure consists of a rear support structure-upper (9), a rear support structure-middle (10), a rear support structure-lower (11), and a front support structure (12). The rear support structure-middle (10) is fixedly installed on the rear support structure-lower (11) and is installed close to the front support structure (12) to form a lower support structure. The rear support structure-upper (9) is installed on the rear support structure-middle (10) and the front support structure (12) and is located on one side of the rear support structure-middle (10) and the front support structure (12). The rear support structure-upper (9), the rear support structure-middle (10), the rear support structure-lower (11), and the front support structure (12) are connected together to form a solid whole and installed inside the square tube structure (1.1) to restrict and support the moving parts.

3. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The gear swing arm mechanism is mainly composed of a force transmission square shaft (13), a rotating shaft (14), a grooved gear one (15), a grooved gear two (16), a swing arm wheel (17), and a swing arm (18); Among them, grooved gear one (15), grooved gear two (16) and swing arm wheel (17) are installed on the rotating shaft (14). There are three shaft positions distributed on the rotating shaft (14), namely shaft position one (14.1), shaft position two (14.2) and shaft position three (14.3). Among them, the cross-section of shaft position one (14.1) and shaft position three (14.3) is circular, and the cross-section of shaft position two (14.2) is square. Grooved gear one (15) and grooved gear two (16) are installed on shaft one (14.1) and shaft three (14.3) respectively through circular holes (15.1) and (16.1), and can rotate freely around the rotating shaft (14); The swing arm wheel (17) is installed on the shaft position two (14.2) through the square hole (17.1), and the swing arm wheel (17) rotates together with the rotating shaft (14); The grooved gear 1 (15) has a C-shaped groove 1 (15.2) distributed on the side near the swing arm wheel (17). The swing arm wheel (17) has a boss 1 (17.2) arranged on the corresponding radius on the side near the grooved gear 1 (15). The boss 1 (17.2) is embedded in the C-shaped groove 1 (15.2). The grooved gear 2 (16) has C-shaped grooves 2 (16.2) distributed on the side near the swing arm wheel (17). The swing arm wheel (17) has a boss 2 (17.4) arranged on the corresponding radius on the side near the grooved gear 2 (16). The boss 2 (17.4) is embedded in the C-shaped groove 2 (16.2).

4. The innovative trailer boom capable of rapid traction connection as described in claim 3, characterized in that, When the swing arm wheel (17) rotates, when the boss (17.2) is within the distribution range of the C-shaped groove (15.2), the slotted gear (15) is stationary relative to the swing arm wheel (17). When the movement range of the boss (17.2) exceeds the distribution range of the C-shaped groove (15.2), the swing arm wheel (17) will drive the grooved gear (15) to rotate together; When the swing arm wheel (17) rotates, when the boss two (17.4) is within the distribution range of the C-shaped groove two (16.2), the grooved gear two (16) is stationary relative to the swing arm wheel (17); When the movement range of the second boss (17.4) exceeds the distribution range of the second C-shaped groove (16.2), the swing arm wheel (17) will drive the second grooved gear (16) to rotate together.

5. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The anti-detachment pin telescopic mechanism is mainly composed of a push plate (22) and an anti-detachment pin (4); The anti-detachment pin (4) is connected to the push plate (22) by the pin (39). The inclined surface (4.1) on the anti-detachment pin (4) cooperates with the outer inclined surface (22.6) on the push plate (22). The pin (39) is inserted into the hole (4.3) of the anti-detachment pin (4) and cooperates with the inner inclined surface (22.5) of the push plate (22). By moving the push plate (22) back and forth, the two anti-detachment pins (4) arranged on the left and right are driven to move axially. When the push plate (22) moves forward and the anti-detachment pin (4) reaches its maximum extension, the straight section (22.7) of the push plate (22) cooperates with the straight section (4.2) of the anti-detachment pin (4) to effectively suppress the retraction of the anti-detachment pin (4). The groove (22.3) on the push plate (22) is used for guiding. The groove (22.1) on the push plate (22) cooperates with the cylindrical pin (20) fixed on the anti-loosening rack shaft (19). When the anti-loosening rack shaft (19) extends, it restricts the retraction of the push plate (22) and also restricts the retraction of the anti-detachment pin (4). When the anti-loosening rack shaft (19) retracts, it drives the push plate (22) to retract together and drives the anti-detachment pin (4) to retract. The vertical plate (22.4) on the push plate (22) is used to trigger the action of the gap elimination mechanism.

6. The innovative trailer boom capable of rapid traction connection as described in claim 3, characterized in that, The swing arm (18) is connected to the swing arm wheel (17) via a pin (36). When the swing arm wheel (17) is on the push plate (22), the swing arm (18) contacts the groove (22.2) of the push plate (22) through the arm end (18.1). When the swing arm wheel (17) rotates in the direction of the push plate (22), it completes the action of pushing the push plate (22) to move away from the swing arm wheel (17); When the swing arm wheel (17) is below the push plate (22), the swing arm (18) is tilted upward under the restriction of the limiting structure (10.1) of the rear support structure-middle (10), and the arm end (18.1) leaves the groove (22.2) of the push plate (22).

7. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The gap elimination mechanism is mainly composed of an anti-loosening rack shaft (19), a spring (21), a locking wedge (5), a cylindrical pin (20), a round-headed pin (32), a rack shaft retaining pin (30), and a retaining spring (40); The anti-loosening rack shaft (19) has an inclined surface (19.2) that mates with the locking wedge (5), a rack structure (19.1) for movement, a guiding cylindrical surface (19.3) and a hole (19.4) for receiving the rack shaft retaining pin (30); The cylindrical pin (20) is tightly integrated with the anti-loosening rack shaft (19) and cooperates with the groove (22.1) on the push plate (22). When the anti-loosening rack shaft (19) moves, it drives the push plate (22) to move. The locking wedge (5) engages with the inclined surface (19.2) of the anti-loosening rack shaft (19) via the inclined surface (5.1), transforming the axial movement of the anti-loosening rack shaft (19) into a locking action where the locking wedge (5) moves radially along the anti-loosening rack shaft (19); the spring (21) provides a continuous thrust to the anti-loosening rack shaft (19) on the locking wedge (5), keeping the locking wedge (5) in a continuous clamping state, and firmly locking the square tube structure (1.1) in the trailer interface (A); the output force of the spring (21) is not less than 210N; The hole (19.4) on the anti-loosening rack shaft (19) is used to accommodate the locking spring (40) and the rack shaft locking pin (30), and together with the round head pin (32) installed on the front support structure (12), it forms the triggering structure of the anti-loosening rack shaft (19). When the vertical plate (22.4) of the push plate (22) in the anti-disengagement pin telescopic mechanism moves and presses the round head pin (32), the trigger gap elimination mechanism is activated.

8. An innovative trailer boom capable of rapid traction connection as described in claim 7, characterized in that, When the anti-loosening rack shaft (19) compresses the spring (21) and reaches the locking position, under the action of the latch spring (40), the rack shaft latch pin (30) pops out so that its end face is exposed on the outer cylindrical surface of the anti-loosening rack shaft (19) and inserted into the hole (12.1) of the front support structure (12), pressing the round head pin (32) so that the head of the round head pin (32) is exposed. When the drive unit is rotated clockwise, the push plate (22) moves toward the locking wedge (5) under the action of the swing arm wheel (17) and the swing arm (18). The upright plate (22.4) presses the round head pin (32) installed on the front support structure (12), which drives the compression of the rack shaft tenon pin (30). When the end face (30.1) of the rack shaft tenon pin (30) is flush with the cylindrical surface (19.3) of the anti-loosening rack shaft (19), the anti-loosening rack shaft (19) loses the locking of the rack shaft tenon pin (30) and is pushed by the spring (21) to move axially toward the locking wedge (5).

9. An innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The square sleeve locking mechanism is mainly composed of an eccentric rack shaft (24), a second spring (25), a pin shaft (7), a second round-headed pin (27), a rack shaft retaining pin (26), and a retaining spring (29); The inclined surface (24.1) of the eccentric rack shaft (24) cooperates with the lower inclined surface (7.2) of the pin shaft (7) to convert the horizontal back-and-forth movement of the eccentric rack shaft (24) into the vertical up-and-down movement of the pin shaft (7), and amplifies the force applied by the horizontal spring 2 (25) on the eccentric rack shaft (24), which is output from the upper inclined surface (7.1) of the pin shaft (7) to achieve clamping and locking of the extended ball seat (2); the spring 2 (25) provides a continuous thrust to the eccentric rack shaft (24) on the pin shaft (7), so that the pin shaft (7) maintains a continuous clamping state and prevents the locking of the extended ball seat (2) from loosening; the output force of the spring 2 (25) is not less than 200N; The copper sleeve (41) and round pin two (27) installed on the towing bolt head (1.2), as well as the locking spring two (29) and the rack shaft locking pin two (26) embedded in the eccentric rack shaft (24), constitute the action triggering component of the eccentric rack shaft (24); The hole (24.3) on the eccentric rack shaft (24) is used to accommodate the second retaining spring (29) and the second rack shaft retaining pin (26), while the second round-headed pin (27) is retained in the hole (1.2.5) of the drag bolt head (1.2). The copper sleeve (41) positions the second round-headed pin (27) and seals the second round-headed pin (27) in the drag bolt head (1.2).

10. An innovative trailer boom capable of rapid traction connection as described in claim 9, characterized in that, When the eccentric rack shaft (24) compresses the second spring (25) and reaches the locking position, under the action of the second latch spring (29), the rack shaft latch pin (26) pops out so that its end face is exposed on the outer cylindrical surface of the eccentric rack shaft (24) and inserted into the hole (1.2.5) of the drag bolt head (1.2), pressing the round head pin (27) against it, so that the ball head surface of the round head pin (27) is exposed on the lower surface of the drag bolt head (1.2).

11. An innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The planes (1.2.3) on the left and right sides of the drag bolt head (1.2) cooperate with the inner walls (2.1.3) on the left and right sides of the inner cavity of the inverted square sleeve (2.1) to restrict the left and right movement of the inverted square sleeve (2.1) on the drag bolt head (1.2); The inclined surface (1.2.1) on the upper plane of the drag bolt head (1.2) cooperates with the inner inclined surface (2.1.1) near the front end of the upper plane of the inverted square sleeve (2.1). The trapezoidal bosses (1.2.4) protruding from both sides of the drag bolt head (1.2) cooperate with the trapezoidal grooves (2.1.6) on the left and right sides of the inverted square sleeve (2.1), together to restrict the forward movement and swing of the inverted square sleeve (2.1). The inclined boss (1.2.2) on the lower plane of the drag bolt head (1.2) at the rear end cooperates with the inner inclined surface (2.1.4) on the lower plane of the inverted square sleeve (2.1) at the rear end. The upper inclined surface (7.1) of the protruding pin shaft (7) cooperates with the inner inclined surface (2.1.2) on the upper plane of the inverted square sleeve (2.1) at the rear end, together to restrict the backward movement and swing of the inverted square sleeve (2.1).

12. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The extended ball seat (2) is mainly composed of one or more inverted square sleeves (2.1), a ball head seat (2.2), a multi-functional ball head component (3), and a reinforcing plate structure (2.3); The number of inverted square sleeves (2.1) is determined by the adjustment height that the extended ball seat (2) needs to achieve. At least one inverted square sleeve (2.1) is required. Multiple inverted square sleeves (2.1) are welded or cast into a whole by vertical stacking, and the two sides are reinforced by welding or casting reinforcing plate structure (2.3). The ball seat (2.2) is welded or cast to the lowest inverted square sleeve (2.1). The multi-functional ball joint component (3) is mainly composed of a seat (3.1), a connecting shaft (3.2), a ball head (3.3), a bearing ring groove (3.4), and a positioning hole (3.5). The connecting shaft (3.2) is fitted with the seat hole (2.2.1) of the ball head seat (2.2), so that the multi-functional ball joint component (3) can rotate freely around the ball head seat (2.2). The structural pin (8) is embedded in the hole (2.2.3) of the ball head seat (2.2) and extends into the load-bearing ring groove (3.4) of the multifunctional ball head component (3) to prevent the multifunctional ball head component (3) from falling out of the ball head seat (2.2); The positioning pin is mainly composed of a pin seat (33), a positioning pin (35) and a pin spring (34), and is fixed in the hole (2.2.2) of the ball head seat (2.2). The positioning pin (35) is inserted into the positioning hole (3.5) of the multi-functional ball head component (3) to prevent the multi-functional ball head component (3) from rotating during use.

13. The innovative trailer boom capable of rapid traction connection as described in claim 1, characterized in that, The driving components include, but are not limited to, a handle (6) or a motor.

14. A vehicle, characterized in that, Including the innovative trailer arm as described in any one of claims 1 to 13.

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