Pneumatic nailing gun piston driving structure based on ratchet wheel clutch

Abstract

The utility model relates to the technical field of pneumatic tools, in particular to a pneumatic nailing gun piston driving structure based on ratchet clutch, which comprises an air cylinder, a piston, a firing pin and a piston driving component, a bulge is arranged on a firing pin shaft, and the piston driving component comprises a transmission shaft, a rotating disc, a connecting seat and a pawl. The rotating disc is provided with a ratchet wheel and a meshing element meshed with the protrusion of the firing pin, pawls which are centrosymmetric and vertically staggered at the tail ends are hinged to the connecting base, the head ends of the pawls are meshed with the ratchet wheel, the tail ends of the pawls are matched with the disengaging element, and the reset spring enables the head ends of the pawls to be tightly attached to the tooth face of the ratchet wheel. According to the driving structure, through the design of the double pawls, the meshing stability and durability are improved, abrasion and slipping are reduced, the overall structure is simple and efficient, and the maintenance cost is reduced.

Description

Technical Field

[0001] This utility model belongs to the field of pneumatic tool technology, and in particular relates to a piston drive structure for a pneumatic nail gun based on a ratchet clutch. Background Technology

[0002] In reciprocating pneumatic nail guns, the reliability of the piston drive mechanism directly determines the work efficiency. Existing pneumatic nail guns using a ratchet clutch structure typically have a single pawl on the drive shaft that engages with a rotating ratchet, controlling the piston's impact stroke through the pawl's unidirectional engagement.

[0003] However, this structure has the following technical problems in practical applications: when a single pawl is engaged, local stress concentration can easily cause wear on the ratchet tooth surface, resulting in insufficient engagement or even slippage after long-term use. Utility Model Content

[0004] The purpose of this invention is to address the aforementioned problems in existing technologies by proposing a pneumatic nail gun piston drive structure based on a ratchet clutch.

[0005] The objective of this utility model can be achieved through the following technical solution: A pneumatic nail gun piston drive structure based on a ratchet clutch includes a cylinder, a piston slidably disposed within the cylinder, a firing pin fixedly connected to the piston, and a piston drive assembly. Several protrusions are arranged in an array along the axial direction of the firing pin. The piston drive assembly includes a drive shaft and a rotating disk rotatably mounted on the drive shaft. Several meshing elements capable of engaging the protrusions are arranged circumferentially on the rotating disk. A ratchet is provided on the rotating disk. A connecting seat is fixedly connected to the drive shaft, and the two ends of the connecting seat are hinged. The device has pawls arranged in a centrally symmetrical manner. A disengagement element, corresponding to each pawl, is provided around the circumference of the connecting seat. Each pawl has a head end that engages with the ratchet teeth and a tail end that abuts against the disengagement element. The tail ends of the two pawls are staggered vertically so that they can only engage with their corresponding disengagement elements during rotation. The connecting seat is provided with a return spring that keeps the head end in close contact with the ratchet teeth. When the tail end abuts against the disengagement element, it can drive the head end to disengage from the ratchet.

[0006] Preferably, the ratchet and the rotating disk are integrally formed and coaxially arranged.

[0007] Preferably, the head end and tail end are symmetrically distributed in the circumferential direction of the pawl, and the length of the tail end is greater than the length of the head end.

[0008] Preferably, the detachment element is annular in shape, with its tail end forming an arc that gradually expands outward.

[0009] Preferably, the connecting seat is sleeved on the drive shaft and connected to it by threads.

[0010] Preferably, the return spring is a torsion spring, and a limiting hole is provided on the connecting seat. One end of the return spring abuts against the tail end, and the other end passes through the limiting hole.

[0011] Preferably, the piston drive assembly is provided with a mounting housing, and an end cover is detachably fixed to the mounting housing. Bearings are installed at both ends of the drive shaft, and the two bearings are respectively fixedly installed on the mounting housing and the end cover.

[0012] Preferably, the engaging element is a pin or a tooth.

[0013] Preferably, the pneumatic nail gun piston drive structure based on ratchet clutch further includes a power output component that provides power to the drive shaft. The power output component includes a motor and a reducer. The reducer is connected to the output end of the motor via a coupling, and the drive shaft is connected to the output end of the reducer.

[0014] Compared with the prior art, the present invention has the following advantages:

[0015] 1. By adopting two centrally symmetrically arranged pawls and a tail end design with staggered upper and lower positions, the uniform force between the pawls and the ratchet is ensured, avoiding ratchet tooth surface wear and slippage caused by local stress concentration, thus improving the reliability and durability of the ratchet clutch.

[0016] 2. A stable transmission and reset mechanism ensures the stability and reliability of the nailing process, and the rotating disk is subjected to uniform force, reducing the yaw vibration of the transmission shaft;

[0017] 3. The arc-shaped design of the detachment component and tail end makes the pawl disengage more smoothly during the disengagement process, reducing impact and noise. The return spring adopts a torsion spring design, ensuring that the pawl can quickly and reliably return to the initial position after disengagement, improving reset efficiency;

[0018] 4. No additional return mechanism is required, simplifying the structure and reducing costs. The threaded connection seat is easy to disassemble and replace, reducing maintenance costs.

[0019] 5. The ratchet and rotating disk are integrally formed and coaxially arranged, eliminating the eccentric torque caused by eccentric installation, improving transmission efficiency and smoothness. The installation of bearings reduces friction and wear, improving the operating efficiency of the entire piston drive assembly. Attached Figure Description

[0020] Figure 1 This is the overall isometric drawing of this utility model.

[0021] Figure 2 This is a schematic diagram showing the disassembled structure of this utility model.

[0022] Figure 3 This is a schematic diagram showing the disassembled structure of the piston drive assembly.

[0023] Figure 4 This is a schematic diagram of the cross-sectional structure of the firing pin and the rotating disk.

[0024] Figure 5 This is a schematic diagram of the cross-sectional structure of the ratchet, pawl, and disengagement element.

[0025] Figure 6 This is a cross-sectional elevation view of the piston drive assembly.

[0026] Figure 7 This is a schematic diagram of the structure of the firing pin and piston drive assembly.

[0027] In the diagram, 1 is the cylinder; 2 is the piston; 3 is the firing pin; 31 is the protrusion; 4 is the piston drive assembly; 41 is the drive shaft; 42 is the rotating disk; 421 is the meshing element; 422 is the ratchet; 43 is the bearing; 5 is the connecting seat; 51 is the limiting hole; 6 is the pawl; 61 is the head end; 62 is the tail end; 63 is the return spring; 7 is the disengagement element; 8 is the mounting housing; 81 is the end cover; 9 is the power output assembly; 91 is the motor; 92 is the reducer; and 93 is the coupling. Detailed Implementation

[0028] The following are specific embodiments of the present invention, which are described in conjunction with the accompanying drawings. However, the present invention is not limited to these embodiments.

[0029] like Figures 1-7As shown, this embodiment discloses a pneumatic nail gun piston drive structure based on a ratchet clutch, including a cylinder 1, a piston 2 slidably disposed within the cylinder 1, a firing pin 3 fixedly connected to the piston 2, and a piston drive assembly 4. Several protrusions 31 are arranged in an array along the axial direction of the firing pin 3. The piston drive assembly 4 includes a drive shaft 41 and a rotating disk 42 rotatably mounted on the drive shaft 41. Several meshing elements 421 capable of engaging the protrusions 31 are provided circumferentially on the rotating disk 42. A ratchet 422 is provided on the rotating disk 42. A connecting seat 5 is fixedly connected to the drive shaft 41, and the two ends of the connecting seat 5 are hinged to a centrally symmetrical... The pawl 6 is provided with a disengagement element 7 corresponding to each pawl 6 in the circumferential direction of the connecting seat 5. The pawl 6 has a head end 61 that can maintain engagement with the tooth surface of the ratchet 422 and a tail end 62 that can form an abutment engagement with the disengagement element 7. The tail ends 62 of the two pawls 6 are staggered so that they can only engage with their corresponding disengagement elements 7 during rotation. The connecting seat 5 is provided with a return spring 63 that keeps the head end 61 in close contact with the tooth surface of the ratchet 422. When the tail end 62 abuts with the disengagement element 7, it can drive the head end 61 to disengage from the ratchet 422.

[0030] Cylinder 1, as the main part of the entire drive structure, forms a sealed compression chamber inside to store and release compressed air to drive the movement of piston 2. Piston 2 is tightly and slidably mounted inside cylinder 1 to ensure smooth and efficient reciprocating movement under air pressure. The striker 3 is fixedly connected to piston 2 to ensure synchronous movement during the drive process, ultimately striking the nail to achieve the nail-driving function. Several protrusions 31 are arranged in an axial array on the striker 3. These protrusions 31 are used to engage with the meshing element 421 on the rotating disk 42 to achieve the compression and release of piston 2.

[0031] The piston drive assembly 4 is the core part of the entire drive structure, including a drive shaft 41 and a rotating disk 42 that can rotate freely around the drive shaft 41. Several meshing elements 421 are evenly arranged in the circumference of the rotating disk 42. The shape of each meshing element 421 matches the protrusion 31 on the striker 3, ensuring that the two can mesh tightly and effectively, thereby converting the rotational motion of the drive shaft 41 into the linear motion of the piston 2 and the striker 3.

[0032] To achieve unidirectional transmission, when the pawl 6 is engaged with the ratchet 422, the rotating disk 42 is allowed to drive the piston 2 to compress the cylinder 1 under the action of the transmission shaft 41. After the pawl 6 disengages from the ratchet 422, the piston 2 is allowed to return freely by air pressure. No additional return mechanism is required, which simplifies the structure and improves efficiency.

[0033] A connecting seat 5 is fixedly connected to the drive shaft 41. Two pawls 6 are hinged to the two sides of the connecting seat 5 in a centrally symmetrical manner. Each pawl 6 includes a head end 61 that can engage with the tooth surface of the ratchet 422, and a tail end 62 that can contact the disengagement element 7. To ensure that each pawl 6 can rotate 360° to fully compress the piston 2, and can correctly engage with the corresponding disengagement element 7 during rotation, the tail ends 62 of the two pawls 6 are designed to be staggered vertically. The head end 61 of each pawl 6 can simultaneously engage or disengage with the tooth surface of the ratchet 422. The engagement between the pawl 6 and the ratchet 422 is tight and stable, effectively avoiding wear on the tooth surface of the ratchet 422 due to local stress concentration, and preventing slippage due to insufficient engagement after long-term use. The rotating disk 42 is subjected to uniform force, which can effectively prevent accidental disengagement due to vibration or impact, reduce the yaw vibration of the drive shaft 41, improve the stability and reliability of the nailing process, and ensure nailing accuracy.

[0034] Two disengagement elements 7 are correspondingly provided on the circumferential direction of the connecting seat 5. The position and shape of each disengagement element 7 are matched with the tail end 62 of the corresponding pawl 6. When it is necessary to disengage the pawl 6 from the ratchet 422, the corresponding disengagement element 7 will contact the tail end 62 of the pawl 6, forcing the head end 61 of the pawl 6 to lift off the tooth surface of the ratchet 422, thereby disengaging the engagement state.

[0035] To ensure that the pawl 6 always fits tightly against the tooth surface of the ratchet 422 and can quickly reset even after being subjected to external force, this drive structure has a return spring 63 installed on the connecting seat 5. When the pawl 6 is not subjected to external force, the return spring 63 can restore its original shape, thereby forcing the pawl 6 back to the position of engaging with the ratchet 422.

[0036] The working process of this driving structure in practical applications is described in detail below:

[0037] In the initial state, piston 2 is in the initial position of cylinder 1, and the firing pin 3 is in the state of compressing piston 2. At this time, the return spring 63 forces the head end 61 of pawl 6 to maintain engagement with the tooth surface of ratchet 422.

[0038] During the power input phase, the power output component that provides power to the drive shaft 41 drives the drive shaft 41 to rotate in one direction, which in turn drives the pawl 6 to rotate synchronously through the connecting seat 5. Since the head end 61 of the pawl 6 engages with the ratchet 422, the rotating disk 42 rotates synchronously with the drive shaft 41, and the engaging element 421 pushes the protrusion 31 of the striker 3, which drives the piston 2 to compress the air in the cylinder 1;

[0039] During the disengagement triggering phase, when the rotating disk 42 rotates to 360°, the tail end 62 of the pawl 6 abuts against the corresponding disengagement element 7. Due to the vertical misalignment of the two pawls 6, they simultaneously trigger the disengagement action. The abutment force forces the pawl 6 to deflect around the hinge point, and the head end 61 disengages from the tooth surface of the ratchet 422, thus disengaging the linkage between the rotating disk 42 and the drive shaft 41.

[0040] During the nailing and resetting phases, the high-pressure gas inside cylinder 1 pushes piston 2 in the opposite direction, and the striking pin 3 quickly extends to complete the nailing action. When the striking pin 3 retracts, the protrusion 31 drives the rotating disk 42 to rotate freely in another direction through the meshing element 421 until piston 2 returns to its initial position. The return spring 63 restores its original shape through its own elasticity, forcing the head end 61 of the pawl 6 to re-engage with the ratchet 422, preparing for the next drive.

[0041] Furthermore, such as Figure 3 , Figure 7 As shown, the ratchet 422 and the rotating disk 42 are integrally formed and coaxially arranged. That is, the rotation center axes of the ratchet 422 and the rotating disk 42 coincide, improving transmission efficiency and stability. The coaxial structure eliminates the eccentric torque caused by eccentric installation, eliminates the need for a centering mechanism, reduces the number of parts and reduces assembly complexity. The coaxial design avoids the risk of jamming or free rotation caused by misalignment of the rotating disk 42 and the ratchet 422.

[0042] Furthermore, the head end 61 and tail end 62 are symmetrically distributed around the circumference of the pawl 6, and the length of the tail end 62 is greater than the length of the head end 61. This design takes into account the mechanical requirements of the pawl 6 when it contacts the disengagement element 7 and disengages from the ratchet 422. Since the disengagement element 7 is located on the outer periphery of the pawl 6 and far from the ratchet 422, increasing the length of the tail end 62 can provide a greater leverage effect, making it easier for the pawl 6 to disengage from the ratchet 422 when subjected to the action of the disengagement element 7, thereby improving the response speed and reliability of the ratchet clutch mechanism.

[0043] The disengagement element 7 is annular, with its tail end 62 gradually expanding outwards in an arc shape. This design allows the tail end 62 to disengage more smoothly from the ratchet 422 under the action of the disengagement element 7. The arc-shaped tail end 62 helps reduce impact and noise during disengagement, while also improving the durability of the pawl 6. The gradually expanding outward arc structure also provides a larger contact area for the tail end 62, forming a more stable contact relationship with the disengagement element 7, ensuring that the pawl 6 is not damaged due to uneven force during disengagement.

[0044] Furthermore, such as Figure 6As shown, the connecting seat 5 is sleeved on the drive shaft 41 and connected to it by threads. As the connecting component between the pawl 6 and the drive shaft 41, the threaded connection design of the connecting seat 5 provides a robust and reliable connection, allowing the connecting seat 5 to be tightly fixed on the drive shaft 41 and to withstand the force and torque transmitted by the pawl 6, ensuring the stability and reliability of the ratchet clutch mechanism. Furthermore, the threaded connection facilitates the disassembly and replacement of the connecting seat 5, reducing maintenance costs.

[0045] Furthermore, such as Figure 7 As shown, the return spring 63 is a torsion spring, with a limiting hole 51 provided on the connecting seat 5. One end of the return spring 63 abuts against the tail end 62, and the other end passes through the limiting hole 51. The torsion spring design allows the return spring 63 to provide a more effective return force to the pawl 6, ensuring that the pawl 6 can quickly and reliably return to its initial position after disengagement, thereby improving the return efficiency of the ratchet clutch mechanism.

[0046] Furthermore, such as Figure 2 , Figure 3 As shown, a mounting housing 8 is provided on the outside of the piston drive assembly 4. An end cap 81 is detachably fixed to the mounting housing 8. Bearings 43 are installed at both ends of the drive shaft 41, and the two bearings 43 are respectively fixedly installed on the mounting housing 8 and the end cap 81. The mounting housing 8 is designed to cover the outside of the piston drive assembly 4 to protect its internal precision components from interference and damage from the external environment. The end cap 81 is designed to be detachably fixed to one end of the mounting housing 8 to seal the internal space of the mounting housing 8 and prevent dust, moisture and other debris from entering. The main function of the bearings 43 is to support the drive shaft 41 and allow it to rotate within a certain range to reduce friction and wear and improve the operating efficiency of the entire piston drive assembly 4.

[0047] Furthermore, such as Figure 7 As shown, the engaging element 421 is a pin or a tooth. Both the pin and the tooth can ensure full engagement with the protrusion 31, improve the reliability of the engagement between the striker 3 and the rotating disk 42, prevent loosening or falling off during operation, and improve the connection reliability of the entire ratchet clutch mechanism.

[0048] Furthermore, such as Figure 2 , Figure 3As shown, this pneumatic nail gun piston drive structure based on a ratchet clutch also includes a power output assembly 9 that provides power to the drive shaft 41. The power output assembly 9 includes a motor 91 and a reducer 92. The reducer 92 is connected to the output end of the motor 91 via a coupling 93, and the drive shaft 41 is connected to the output end of the reducer 92. The power output assembly 9 provides the necessary power to the drive shaft 41, thereby driving the entire piston drive structure. The motor 91 serves as the power source, providing the initial rotational power, and its performance directly affects the power, speed, and efficiency of the nail gun. The reducer 92 is connected to the output end of the motor 91 to reduce the speed and increase the torque, which helps convert the high-speed rotation of the motor 91 into a low-speed, high-torque output suitable for the nail gun piston drive. The coupling 93 connects the output end of the motor 91 and the input end of the reducer 92, ensuring smooth and reliable power transmission between them.

[0049] The specific embodiments described herein are merely illustrative examples illustrating the spirit of this utility model. Those skilled in the art to which this utility model pertains may make various modifications or additions to the described specific embodiments or use similar methods to substitute them, without departing from the spirit of this utility model or exceeding the scope defined by the appended claims.

Claims

1. A pneumatic nail gun piston drive structure based on a ratchet clutch, comprising a cylinder (1), a piston (2) slidably disposed within the cylinder (1), a firing pin (3) fixedly connected to the piston (2), and a piston drive assembly (4), wherein a plurality of protrusions (31) are arranged in an array along the axial direction of the firing pin (3), and the piston drive assembly (4) comprises a drive shaft (41) and a rotating disk (42) rotatably mounted on the drive shaft (41), wherein the rotating disk (42) is provided with a plurality of engagement elements (421) circumferentially disposed thereon that can engage with the protrusions (31), characterized in that, The rotating disk (42) is provided with a ratchet (422), and the drive shaft (41) is fixedly connected with a connecting seat (5). The two ends of the connecting seat (5) are hinged with pawls (6) arranged in a centrally symmetrical manner. The connecting seat (5) is provided with a disengagement element (7) corresponding to the pawl (6) in the circumferential direction. The pawl (6) has a head end (61) that can maintain engagement with the tooth surface of the ratchet (422) and a tail end (62) that can form an abutment engagement with the disengagement element (7). The tail ends (62) on the two pawls (6) are staggered so that they can only engage with their corresponding disengagement element (7) during rotation. The connecting seat (5) is provided with a return spring (63) that can keep the head end (61) in close contact with the tooth surface of the ratchet (422). When the tail end (62) abuts with the disengagement element (7), it can drive the head end (61) to disengage from the ratchet (422).

2. The ratchet clutch based pneumatic nail gun piston drive structure according to claim 1, wherein, The ratchet (422) and the rotating disk (42) are integrally formed and coaxially arranged.

3. The piston driving structure of the pneumatic nail gun based on the ratchet clutch according to claim 1 or 2, characterized in that, The head end (61) and tail end (62) are symmetrically distributed in the circumferential direction of the pawl (6), and the length of the tail end (62) is greater than the length of the head end (61).

4. The ratchet clutch based pneumatic nail gun piston drive structure according to claim 3, wherein, The detachment element (7) is annular, and its tail end (62) is an arc shape that gradually expands outward.

5. The ratchet clutch based pneumatic nailer piston drive structure of claim 1 or 2, wherein, The connecting seat (5) is sleeved on the transmission shaft (41) and connected to it by threads.

6. The ratchet clutch based pneumatic nail gun piston drive structure according to claim 1, wherein, The reset spring (63) is a torsion spring, and a limiting hole (51) is provided on the connecting seat (5). One end of the reset spring (63) abuts against the tail end (62), and the other end passes through the limiting hole (51).

7. The ratchet clutch based pneumatic nail gun piston drive structure according to claim 1, wherein, An mounting housing (8) is provided on the outer cover of the piston drive assembly (4). An end cover (81) is detachably fixed to the mounting housing (8). Bearings (43) are installed at both ends of the drive shaft (41), and the two bearings (43) are respectively fixedly installed on the mounting housing (8) and the end cover (81).

8. The ratchet clutch based pneumatic nail gun piston drive structure according to claim 1, wherein, The engaging element (421) is a pin or a tooth.

9. A ratchet clutch based pneumatic nailer piston drive structure according to any of claims 1 or 2 or 4 or 6 or 7 or 8, wherein, The pneumatic nail gun piston drive structure based on ratchet clutch also includes a power output assembly (9) that provides power to the drive shaft (41). The power output assembly (9) includes a motor (91) and a reducer (92). The reducer (92) is connected to the output end of the motor (91) via a coupling (93). The drive shaft (41) is connected to the output end of the reducer (92).

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