A driving mechanism for a fastener driving machine

Abstract

The present invention discloses a driving mechanism for a fastener driving machine, which comprises: a rotatable crank; a driving frame assembly rotatably mounted on the crank, which comprises an engaging element, a supporting element and a driving frame; and at least one fixed guiding element, wherein the supporting element and / or the engaging element can move along a trajectory set thereon. The present invention has a simple structure, few parts, and stable operation. When the crank rotates, the motion trajectory of the engaging element is a straight line or close to 0°, so as to minimize the load motion friction and avoid problems such as wear. At the same time, it ensures that the thrust direction of the later impact unit during the compression energy storage process is constant and the eccentric load is small, thereby realizing the rapid release of the driving mechanism, ensuring the stability and smoothness of the operation of the impact unit, and improving the work quality.

Description

Technical field:

[0001] The invention relates to the technical field of mechanical tool products, in particular to a driving mechanism for a fastener driving machine. Background technology:

[0002] In a fast fastening machine (also known as a nail gun or a fastener driving machine), it is usually necessary to store energy by compressing an energy storage medium (such as gas, spring, rubber, vacuum, etc.), and then quickly release it to achieve external work.

[0003] In addition, the common driving mechanism converts rotational motion into reciprocating motion, and its structure is a crank-connecting rod structure. However, this structure will have a large force deviation angle during the movement process, that is, the connecting rod swings at a large angle. When the deviation angle is too large, the friction of the load (impact unit) movement will increase, and the mechanism will wear and other problems, resulting in the product service life cannot be guaranteed.

[0004] How to make the drive mechanism quickly release the energy storage medium after compressing it becomes a difficult point in the design process of such mechanical equipment.

[0005] In view of this, the inventor proposes the following technical solution. Summary of the invention:

[0006] The object of the present invention is to overcome the deficiencies of the prior art and provide a driving mechanism for a fastener driving machine.

[0007] In order to solve the above technical problems, the present invention adopts the following technical solution: the driving mechanism for the fastener driving machine includes: a crank that can rotate; a driving frame assembly rotatably mounted on the crank, which includes an engaging element, a supporting element and a driving frame; at least one fixed guide element, and the supporting element and / or the engaging element can move along the trajectory set thereon.

[0008] Furthermore, in the above technical solution, the driving frame is rotatably mounted on the crank, and the engaging element and the supporting element are both arranged on the driving frame; the guiding element is provided with at least one guiding groove serving as a track, and the supporting element and / or the engaging element are slidably arranged in the guiding groove.

[0009] Furthermore, in the above technical solution, the number of the guide grooves is two, which are respectively a first guide groove and a second guide groove, and the engaging element and the supporting element are respectively slidably arranged in the first guide groove and the second guide groove.

[0010] Furthermore, in the above technical solution, the meshing elements and the supporting elements are distributed on the driving frame along the circumference with respect to the rotation axis of the driving frame as the center. When the circumferential radius of the meshing elements is equal to the distance between the rotation axis of the crank and the rotation axis of the driving frame, when the crank drives the driving frame to rotate, the motion trajectory of the meshing elements is a straight line; when the circumferential radius of the supporting elements is equal to the distance between the rotation axis of the crank and the rotation axis of the driving frame, when the crank drives the driving frame to rotate, the motion trajectory of the supporting elements is a straight line.

[0011] Furthermore, in the above technical solution, the first guide groove and the second guide groove are cross-arranged.

[0012] Furthermore, in the above technical solution, the engaging element and the supporting element are both cylindrical pins; a shaft body is formed at the lower end of the driving frame, and the shaft body is rotatably mounted on the crank.

[0013] Furthermore, in the above technical solution, the locking mechanism is rotatably mounted on the upper end of the engaging element.

[0014] Furthermore, in the above technical solution, the locking mechanism includes a rocker arm and a reset element located beside the rocker arm, one end of the rocker arm is formed with an axial hole, and the other end is provided with a locking shaft for engaging and positioning with a striker in the impact unit.

[0015] Furthermore, in the above technical solution, the striker is slidably mounted in the guide rail; the guide rail is mounted on the base, and the reset element is arranged on the guide rail; the guide rail is also provided with a release mechanism for driving the striker to disengage from the rocker arm.

[0016] Furthermore, in the above technical solution, the release mechanism includes a release seat arranged on the side of the guide rail, and the release seat is provided with a disengagement guide surface for guiding the rocker arm to disengage from the striker.

[0017] After adopting the above technical scheme, the present invention has the following beneficial effects compared with the prior art: the present invention has a simple structure, few parts, and stable operation. When the crank rotates, the drive frame can be driven to revolve around the rotating axis of the crank, and the drive frame also rotates, and the meshing element and the supporting element on the drive frame slide in the first guide groove and the second guide groove respectively, so that the movement trajectory of the meshing element is a straight line or close to 0°, and its deflection angle is 0° or close to 0°, so as to minimize the load movement friction and avoid problems such as wear. At the same time, it is ensured that the thrust direction of the later impact unit in the compression energy storage process is constant and the eccentric load is small, so as to achieve the rapid release of the driving mechanism, ensure the stability and smoothness of the operation of the impact unit, improve the work quality, and make the present invention have a strong market competitiveness. In addition, in the state of the nail, the present invention can still achieve normal meshing with the impact unit, ensure normal operation, and be extremely convenient to use. Description of the drawings:

[0018] Figure 1 It is an assembly diagram of the present invention, the locking mechanism and the impact unit;

[0019] Figure 2 is an assembly diagram of the present invention, the locking mechanism and the impact unit from another perspective;

[0020] Figure 3 yes Figure 1 Exploded diagram of

[0021] Figure 4 is a three-dimensional diagram of the driving frame of the present invention;

[0022] Figure 5 is a stereogram of the present invention;

[0023] Figure 6 It is a working principle diagram of the present invention;

[0024] Figure 7 is a front view of a fastener driving machine including the present invention;

[0025] Figure 8 is a perspective view of a fastener driving machine incorporating the present invention;

[0026] Fig. 9 is a cross-sectional view of a fastener driving machine incorporating the present invention;

[0027] Fig.10 is a schematic diagram of a second structure of the present invention;

[0028] Fig.11 is a schematic diagram of a third structure of the present invention;

[0029] Fig.12 It is the operating state diagram of the present invention.

[0030] Fig.13 It is an operating status diagram of another structure of the present invention.

[0031] Fig.14 1 is an operating state diagram of a fastener driving machine according to the present invention.

[0032] Fig.15 The invention discloses a mechanism operating state diagram of the fastener driving machine in a staple-stitching state. Specific implementation method:

[0033] The present invention is further described below in conjunction with specific embodiments and drawings.

[0034] See Figure 1-15 As shown, a driving mechanism for a fastener driving machine is shown, and the driving mechanism 1 comprises:

[0035] A crank 11 that can rotate; a drive frame assembly 12 that is rotatably mounted on the crank 11, which includes an engagement element 122, a support element 123 and a drive frame 121, and at least one fixed guide element 13, wherein the support element 123 and / or the engagement element 122 can move along the track set thereon. The present invention has a simple structure, few parts, and stable operation. When the crank 11 rotates, the drive frame 121 can be driven to revolve around the rotation axis of the crank 11, and the drive frame 121 also rotates, and the engagement element 122 and the support element 123 move along the track respectively, so that the motion track of the engagement element 122 is a straight line or close to 0°, and its deflection angle is 0° or close to 0°, so as to minimize the load motion friction, avoid problems such as wear, and at the same time ensure that the thrust direction of the later impact unit in the compression energy storage process is constant and the eccentric load is small, so as to achieve the rapid release of the driving mechanism, ensure the stability and smoothness of the operation of the impact unit, improve the work quality, and make the present invention have strong market competitiveness.

[0036] Further, the driving frame 121 is rotatably mounted on the crank 11, and the engaging element 122 and the supporting element 123 are both arranged on the driving frame 121; the guiding element 13 is provided with at least one guiding groove as a track, and the supporting element 123 and / or the engaging element 122 are slidably arranged in the guiding groove. More specifically, the guiding element 13 is provided with a first guiding groove 131 and a second guiding groove 132 as a track, and the engaging element 122 and the supporting element 123 are slidably arranged in the first guiding groove 131 and the second guiding groove 132, respectively. When the crank 11 rotates, the driving frame 121 can be driven to revolve around the rotation axis of the crank 11. At the same time, the driving frame 121 also rotates, and the engaging element 122 and the supporting element 123 on the driving frame 121 slide in the first guide groove 131 and the second guide groove 132 respectively, so that the movement trajectory of the engaging element 122 is a straight line or close to 0°, and its deflection angle is 0° or close to 0°.

[0037] The engaging element 122 and the supporting element 123 are both distributed on the driving frame 121 along a circle with the rotation axis of the driving frame 121 as the center. When the radius of the circle on which the engaging element 122 is distributed is equal to the distance between the rotation axis of the crank 11 and the rotation axis of the driving frame 121, when the crank 11 drives the driving frame 121 to rotate, the movement trajectory of the engaging element 122 is a straight line; when the radius of the circle on which the supporting element 123 is distributed is equal to the distance between the rotation axis of the crank 11 and the rotation axis of the driving frame 121, when the crank 11 drives the driving frame 121 to rotate, the movement trajectory of the supporting element 123 is a straight line.

[0038] In other words, the rotation axis of the crank 11 is A, the position center of the meshing element is B, the position center of the supporting element is C, and the rotation center of the driving frame is O. When OA=OB, the motion trajectory of the meshing element 122 is a straight line, and the corresponding first guide groove 131 is in the shape of a straight bar; when OA≠OB, the motion trajectory of the meshing element 122 is an ellipse, and the corresponding first guide groove 131 is in the shape of an ellipse. When OA=OC, the motion trajectory of the supporting element is a straight line, and the corresponding second guide groove 132 is in the shape of a straight bar; when OA≠OC, the motion trajectory of the supporting element is an ellipse, and the corresponding second guide groove 132 is in the shape of an ellipse. When OA=OB=OC, if the first guide groove 131 and the second guide groove 132 are both in the shape of a straight bar, assuming that the angle between the two guide grooves is a, and the angle between OB and OC is θ, then θ=2a.

[0039] The first guide groove 131 and the second guide groove 132 are arranged crosswise and located in the same plane, and the intersections thereof are connected. In addition, the first guide groove 131 and the second guide groove 132 may not be arranged crosswise, and may not be on the same plane.

[0040] The engaging element 122 and the supporting element 123 are both cylindrical pins, and the structure is simpler. A shaft body 101 is formed at the lower end of the driving frame 121, and the shaft body 101 is rotatably mounted on the crank 11.

[0041] The upper end of the engagement element 122 passes through the first guide groove 131 and protrudes outside the upper end surface of the guide element 13; the locking mechanism 2 is rotatably mounted on the upper end of the engagement element 122. Specifically, the locking mechanism 2 can move linearly or approximately linearly with the linear or approximately linear movement of the driving mechanism 1. When the impact unit moves along the first direction, the locking mechanism engages with the impact unit, driving it to move along the first direction so that the energy storage unit stores energy.

[0042] The locking mechanism 2 includes a rocker rod 21 and a reset element 22 located next to the rocker rod 21. An axial hole 211 is formed at one end of the rocker rod 21, and a locking shaft 212 for engaging and positioning with a striker 31 in the impact unit 3 is provided at the other end, wherein the striker 31 has a sawtooth 311 engaged and positioned with the locking shaft 212, and the sawtooth 311 has an inclined guiding surface so that the locking shaft 212 can slide along the inclined guiding surface to pass over the sawtooth 311 and lock with the sawtooth 311 later.

[0043] The reset element 22 is an elastic element, which includes a spring or elastic rubber. In this embodiment, the reset element 22 is a rubber strip, which is arranged parallel to the striker 31 and is located beside the lock shaft 212. The rubber strip can ensure that the lock shaft 212 is always close to the striker 31.

[0044] The striker 31 is slidably mounted in the guide rail 4 to ensure the smoothness of the sliding of the striker 31 and the direction of operation; the guide rail 4 is mounted on the base 5, and the reset element 22 is arranged on the guide rail 4; the guide rail 4 is also provided with a release mechanism 6 for driving the striker 31 to disengage from the swing rod 21. Specifically, the release mechanism 6 includes a release seat 61 arranged on the side of the guide rail 4, and the release seat 61 is provided with a disengagement guide surface 611 for guiding the swing rod 21 to disengage from the striker 31. When the locking mechanism 2 pushes the impact unit 3 to move a certain distance in the first direction, the locking mechanism will engage with the disengagement guide surface 611. Due to the limitation of the inclined surface, the lock shaft 212 at the end of the swing rod 21 is subjected to a force perpendicular to the first direction while moving in the first direction. At this time, the swing rod 21 can rotate around the engagement element 122, thereby pushing the locking mechanism to disengage from the impact unit. After disengagement, the impact unit moves in the second direction under the action of the energy storage unit force, thereby realizing the fastener driving function. When the locking mechanism is not engaged with the disengagement guide surface 611 , the elastic force of the rubber strip resets the rocker rod 21 so that it re-engages with the striker 31 .

[0045] The guide element 13 is fixed on the base 5. The base 5 is provided with an energy storage unit 7 that realizes energy storage through displacement change. The impact unit 3 is connected to the energy storage unit 7. The base 5 is also provided with a power mechanism 8. The crank 11 is installed on the power mechanism 8 and driven by the power mechanism 8 to rotate. The power mechanism 8 includes a gear transmission mechanism 81 installed at the lower end of the base 5 and a motor 82 installed in matching with the gear transmission mechanism 81. The motor 82 provides torque and speed. The gear transmission mechanism is usually a reduction box, which is used to reduce the speed and increase the torque. The crank 11 is installed on the gear transmission mechanism 81.

[0046] The energy storage unit 7 is a medium that can store energy through displacement changes, such as an air spring, a mechanical spring, a rubber element, a vacuum, etc. This embodiment takes an air spring as an example, wherein the cylinder and the piston form a closed space containing gas, thereby forming an air spring.

[0047] The impact unit 3 moves in the first direction to store energy in the energy storage unit, and the impact unit 3 moves in the second direction to drive the fastener into the workpiece. The first direction refers to the direction of the impact unit 3 toward the energy storage unit 7, and the second direction refers to the direction of the energy storage unit 7 toward the impact unit 3.

[0048] The impact unit 3 includes a piston 32 disposed in the energy storage unit 7 and a striker 31 mounted on the piston 32 .

[0049] The base 5 is also provided with a buffer pad 50 for colliding with the piston 32 in the impact unit 3, so as to achieve shock absorption and prevent excessive impact from damaging the mechanism.

[0050] The base 5 is also equipped with a nail guide plate 51 and a nail clamp 52 disposed at the lower end of the nail guide plate 51 and used to convey fasteners to the nail guide plate 51. The nail guide plate 51 has a channel for the striker 31 in the impact unit 3 to pass through. The nail clamp 52 is a fastener loading device that can convey fasteners (such as nails) to the nail guide plate. The nail guide plate 51 receives fasteners from the nail clamp. When the fasteners fall into the channel of the nail guide plate 51, the striker 31 in the impact unit releases energy in the energy storage unit 7 to impact, and the striker 31 passes through the channel and drives the fasteners (such as nails) in the channel into the workpiece (usually wood, metal plate or cement, etc.).

[0051] Combination Figure 5-6As shown, when the crank 11 rotates, if OA=OB, the meshing element is in linear motion. If OA and OB are not equal, the motion trajectory of the meshing element 122 is an ellipse. When the difference between OA and OB is small, the minor axis of the ellipse is small, and the motion trajectory of the meshing element 122 can be regarded as an approximate linear motion. It is preferred to select OA and OB to be equal, so that the meshing element is in linear motion, so that the impact unit has a small load when moving along the first direction. Similarly, if OA=OC, the support element 123 is in linear motion. If OA and OC are not equal, the motion trajectory of the support element is an ellipse. When the difference between OA and OC is small, the minor axis of the ellipse is small, and the motion trajectory of the support element can be regarded as an approximate linear motion. Because the meshing element 122 and the support element 123 do not necessarily move linearly at the same time, OB and OC are not necessarily equal. However, in order to simplify the design, it is preferred to make OA=OB=OC, so that the shapes of the first guide groove 131 and the second guide groove 132 can be made simpler, and the meshing element and the support element both move linearly. At this time, the included angle α between the two guide grooves is half of the included angle θ between OB and OC.

[0052] Combination Figure 5-6 As shown, when the engagement element 122 passes through point A and the vicinity, the second guide groove 132 cooperates with the support element 123 to provide support force for the drive frame 121, so that the drive frame 121 maintains the rotation in the opposite direction to the crank 11, thereby maintaining the movement of the engagement element along the direction of the first guide groove 131. Similarly, when the support element passes through point A and the vicinity, the first guide groove 131 cooperates with the engagement element 122 to support the drive frame, thereby maintaining the movement of the support element 123 along the direction of the second guide groove 132. When both the engagement element 122 and the support element 123 are not at point A and the vicinity, only one of the first guide groove 131 and the second guide groove 132 is required to play a supporting role.

[0053] Therefore, the lengths of the first guide groove 131 and the second guide groove 132 do not need to cover the entire travel of the engagement element 122 and the support element 123. Figure 10-11 Two incomplete guide groove forms are shown. Other forms are within the scope of protection of this patent as long as the working principles are the same. Fig.10 In the embodiment, the two guide grooves are of different lengths, and the first guide groove degenerates into two short straight grooves, which only play a supporting role when the supporting element passes through point A and the surrounding area. Fig.11 In the middle of the two guide grooves, the same length L is hollowed out. Figure 6 and Fig.11 As shown, let the angle between OC and OB be θ, θ varies between 0° and 180°, OA=OB=OC=R, then L=(2√2)*R*(√(1-cos(θ / 2))). Let θ=180°, then L=(2√2)*R, where √ is the square root.

[0054] Combination Figure 6 , 12 As shown, state ah shows a complete motion cycle of the driving mechanism under the condition of OA=OB=OC. The angle between OB and OC is 120°, and the angle α between the first guide groove 131 and the second guide groove 132 is 60°. State a is the initial state, and the meshing element is located at the lower dead center along the first direction. The crank rotates counterclockwise, the meshing element moves along the first direction, and the supporting element moves along the second guide groove 132. The crank rotates counterclockwise by 30°, as shown in state b, and the supporting element moves to point A, at which time the driving frame and the meshing element are supported by the first guide groove 131. The crank rotates counterclockwise by 90°, as shown in state c, and the meshing element moves to point A. The crank rotates counterclockwise by 120°, as shown in state d, and the supporting element moves to the upper dead center along the direction of the second guide groove 132. The crank continues to rotate, and the supporting element moves in the opposite direction along the second guide groove 132. The crank rotates counterclockwise by 180°, as shown in state e, and the meshing element moves to the upper dead center along the first direction. The crank continues to rotate, and the meshing element moves in the second direction. The crank rotates 210° counterclockwise, as shown in state f, and the supporting element moves to point A. At this time, the drive frame and the meshing element are supported by the first guide groove 131. The crank rotates 270° counterclockwise, as shown in state g, and the meshing element moves to point A in the second direction. The crank rotates 300° counterclockwise, as shown in state h, and the supporting element moves to the bottom dead center in the opposite direction of the second guide groove 132. The crank rotates 360° counterclockwise, and the drive mechanism returns to the initial state a.

[0055] Combination Figure 6 , 13 As shown, the angle between OB and OC is 180°, and the angle α between the first guide groove 131 and the second guide groove 132 is 90°. The motion cycle is similar to the case when the angle between OB and OC is 120°, but the crank rotation angles corresponding to the meshing unit and the support unit passing through point A are different. When the crank rotates 0° counterclockwise, as shown in state a; the crank rotates 180° counterclockwise, as shown in state e, the support element moves to point A, and the drive frame and the meshing element are supported by the first guide groove. When the crank rotates 90° counterclockwise, as shown in state c; the crank rotates 270° counterclockwise, as shown in state g, the meshing element moves to point A, and the drive frame and the support element are supported by the second guide groove.

[0056] Combination Figure 6 , 14As shown, state AJ corresponds to a working cycle under the condition that OA=OB=OC and the angle between OB and OC is 120°. As shown in state A, it is the initial state. At this time, the impact unit is located at the position where the fastener is driven in. The crank rotates counterclockwise, driving the meshing element to move in the first direction. The locking mechanism is installed on it and engages with the impact unit, thereby driving the impact unit to move in the first direction and compressing the air spring, as shown in states B, C, and D. The crank continues to rotate counterclockwise, the lock shaft engages with the disengagement guide surface 611 of the release mechanism 6, and pushes the rocker to rotate around the meshing element until the lock shaft disengages from the impact unit, as shown in state E. Under the action of the air spring, the impact unit moves at high speed in the second direction to drive the fastener into the workpiece, as shown in state F. The crank continues to rotate counterclockwise, as shown in states G and H, the meshing element moves in the second direction, and the locking mechanism rotates in the opposite direction under the action of the reset element until it abuts against the side of the striker. The crank continues to rotate counterclockwise, as shown in states I and J, the engaging element moves in the second direction, the locking mechanism passes over the serrations of the striker, and is reset under the action of the reset element, and finally re-engages with the impact unit and returns to the state shown in state A.

[0057] Combination Figure 6 , 15 The figure shows the operating state of the mechanism of the present invention in the state of nailing, and the analysis of the nailing state under the condition of OA=OB=OC, and the angle between OB and OC is 120°. When the nail is stuck for some reason, the fastener is stuck in the nail guide plate. At this time, the impact unit may stop at any position along the second direction, as shown in state K. Driven by the motor, the crank rotates counterclockwise, pushing the meshing element and the locking mechanism to move along the second direction to the same distance as the normal working cycle. The locking mechanism passes over the saw teeth of the striker and abuts against the side of the striker under the action of the reset element, as shown in states L and M. The crank continues to rotate counterclockwise, pushing the meshing element and the locking mechanism to move along the first direction until they re-engage with the striker, as shown in state N. After that, the striker also moves along the first direction to compress the air spring to store energy, as shown in state E, and then returns to the normal working cycle. That is to say, in the state of nailing, the present invention can still achieve normal engagement with the impact unit, ensuring normal operation, and is extremely convenient to use.

[0058] In summary, the present invention has a simple structure, few parts, and stable operation. When the crank 11 rotates, the drive frame 121 can be driven to revolve around the rotation axis of the crank 11, and the drive frame 121 also rotates, and the meshing element 122 and the support element 123 on the drive frame 121 slide in the first guide groove 131 and the second guide groove 132, so that the movement trajectory of the meshing element 122 is a straight line or close to 0°, and its deflection angle is 0° or close to 0°, so as to minimize the load movement friction, avoid problems such as wear, and at the same time ensure that the thrust direction of the later impact unit in the compression energy storage process is constant and the eccentric load is small, so as to achieve the rapid release of the driving mechanism, ensure the stability and smoothness of the operation of the impact unit, improve the work quality, and make the present invention have a strong market competitiveness. In addition, in the nail state, the present invention can still achieve normal meshing with the impact unit, ensure normal operation, and be extremely convenient to use.

[0059] Of course, the above description is only a specific embodiment of the present invention and is not intended to limit the scope of implementation of the present invention. All equivalent changes or modifications made according to the structure, characteristics and principles described in the patent application scope of the present invention should be included in the patent application scope of the present invention.

Claims

1. A driving mechanism for a fastener driving machine, characterized in that: The driving mechanism (1) comprises: A crank (11) capable of rotational movement; A drive frame assembly (12) rotatably mounted on the crank (11), comprising an engaging element (122), a supporting element (123) and a drive frame (121); At least one fixed guide element (13), the support element (123) and / or the engagement element (122) being movable along a trajectory along which the support element (123) and / or the engagement element (122) are arranged; The driving frame (121) is rotatably mounted on the crank (11), the guide element (13) is provided with at least one guide groove as a track, and the supporting element (123) and / or the engaging element (122) are slidably arranged in the guide groove; The engaging element (122) and the supporting element (123) are both arranged on the driving frame (121); The number of the guide grooves is two, namely a first guide groove (131) and a second guide groove (132); the engaging element (122) and the supporting element (123) are respectively slidably arranged in the first guide groove (131) and the second guide groove (132).

2. A driving mechanism for a fastener driving machine according to claim 1, characterized in that: The meshing element (122) and the supporting element (123) are both distributed on the driving frame (121) along a circle with the rotation axis of the driving frame (121) as the center. When the radius of the circle on which the meshing element (122) is distributed is equal to the distance between the rotation axis of the crank (11) and the rotation axis of the driving frame (121), when the crank (11) drives the driving frame (121) to rotate, the motion trajectory of the meshing element (122) is a straight line; when the radius of the circle on which the supporting element (123) is distributed is equal to the distance between the rotation axis of the crank (11) and the rotation axis of the driving frame (121), when the crank (11) drives the driving frame (121) to rotate, the motion trajectory of the supporting element (123) is a straight line.

3. A driving mechanism for a fastener driving machine according to claim 1, characterized in that: The first guide groove (131) and the second guide groove (132) are arranged crosswise.

4. A driving mechanism for a fastener driving machine according to claim 1, characterized in that: The engaging element (122) and the supporting element (123) are both cylindrical pins; a shaft body (101) is formed at the lower end of the driving frame (121), and the shaft body (101) is rotatably mounted on the crank (11).

5. A driving mechanism for a fastener driving machine according to any one of claims 1 to 4, characterized in that: A locking mechanism (2) is mounted on the upper end of the engaging element (122), wherein the locking mechanism (2) comprises a swing rod (21) rotatably mounted on the upper end of the engaging element (122) and a reset element (22) located beside the swing rod (21), wherein an axial hole (211) is formed at one end of the swing rod (21), and a locking shaft (212) is provided at the other end for engaging and positioning with a striker (31) in the impact unit (3).

6. A driving mechanism for a fastener driving machine according to claim 5, characterized in that: The striker (31) is slidably mounted in the guide rail (4); the guide rail (4) is mounted on a base (5), and the reset element (22) is disposed on the guide rail (4); the guide rail (4) is also provided with a release mechanism (6) for driving the striker (31) to disengage from the swing rod (21).

7. A driving mechanism for a fastener driving machine according to claim 6, characterized in that: The release mechanism (6) comprises a release seat (61) arranged on the side of the guide rail (4), and a disengagement guide surface (611) for guiding the swing rod (21) to disengage from the striker (31) is provided on the release seat (61).

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