CN212351876U

CN212351876U - Driving mechanism for fastener driving machine

Info

Publication number: CN212351876U
Application number: CN202020532897.3U
Authority: CN
Inventors: 徐瀛
Original assignee: Dongguan Gaote Design Consulting Co Ltd
Current assignee: Jiuwei Technology (Suzhou) Co.,Ltd.
Priority date: 2020-04-13
Filing date: 2020-04-13
Publication date: 2021-01-15
Anticipated expiration: 2030-04-13

Abstract

The utility model discloses a actuating mechanism for fastener is squeezed into machine, it includes: a crank which can rotate; a drive frame assembly rotatably mounted on the crank and including an engagement member, a support member and a drive frame; at least one stationary guide element, along which the support element and/or the engagement element can be displaced. The utility model discloses simple structure, the part is few, and the operation is stable, and when the crank rotated, this meshing element's movement track was sharp or is close O to the maximum reduction carries dynamic friction, avoids appearing wearing and tearing scheduling problem, guarantees simultaneously that later stage impact unit is invariable and the unbalance loading is little in the thrust direction that compression energy storage in-process received, has realized actuating mechanism's quick release, guarantees impact unit operation's stability and smooth and easy nature, improves operating mass with rated load.

Description

Driving mechanism for fastener driving machine

The technical field is as follows:

the utility model relates to a mechanical tool product technical field refers in particular to a actuating mechanism that is used for fastener to squeeze into machine.

Background art:

in a quick fastening machine (also known as a nailer or fastener driver), energy is typically stored by compressing an energy storage medium (e.g., gas, spring, rubber, vacuum, etc.) and then quickly released to perform work externally.

In addition, a common driving mechanism converts rotary motion into reciprocating motion, and the structure of the common driving mechanism is a crank-connecting rod structure, but a large stress deflection angle can occur in the motion process of the structure, namely, the swinging angle of a connecting rod is large, when the deflection angle is too large, the motion friction force of a load (an impact unit) is increased, the mechanism is abraded, and the like, so that the service life of a product cannot be guaranteed.

How to make the driving mechanism realize quick release after compressing the energy storage medium becomes a difficulty in the design process of the mechanical equipment.

In view of the above, the present inventors propose the following.

The utility model has the following contents:

an object of the utility model is to overcome prior art's not enough, provide a actuating mechanism that is used for the fastener to squeeze into machine.

In order to solve the technical problem, the utility model discloses a following technical scheme: the drive mechanism for a fastener driving machine includes: a crank which can rotate; a drive frame assembly rotatably mounted on the crank and including an engagement member, a support member and a drive frame; at least one stationary guide element, along which the support element and/or the engagement element can be displaced.

Further, in the above technical solution, the driving frame is rotatably mounted on the crank, and the engaging element and the supporting element are both disposed on the driving frame; the guide element is provided with at least one guide groove as a track, in which the support element and/or the engagement element is slidably arranged.

Further, 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 disposed in the first guide groove and the second guide groove.

Furthermore, in the above technical solution, the engaging element and the supporting element are both circumferentially distributed on the driving frame with respect to the rotation axis of the driving frame as a center of circle, and when the circumferential radius of the distribution of the engaging element is equal to the distance between the rotation axis of the crank and the rotation axis of the driving frame, the crank drives the driving frame to rotate, and the motion trajectory of the engaging element is a straight line; when the supporting elements are distributed with a circle radius equal to the distance between the rotation axis of the crank and the rotation axis of the driving frame, the crank drives the driving frame to rotate, and the motion trail of the supporting elements is a straight line.

Further, in the above technical solution, the first guide groove and the second guide groove are arranged to intersect with each other.

Further, in the above technical solution, the engaging element and the supporting element are both cylindrical pins; the lower end of the driving frame is formed with a shaft body which is rotatably arranged on the crank.

Further, in the above technical solution, the locking mechanism is rotatably mounted at the upper end of the engaging element.

Furthermore, in the above technical solution, the latch mechanism includes a swing link and a reset element located beside the swing link, one end of the swing link is formed with a shaft hole, and the other end is provided with a lock shaft for engaging and positioning with a striker in the impact unit.

Further, in the above-described aspect, the striker is slidably mounted to the guide rail; the guide rail is arranged 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 be separated from the swing rod.

Further, in the above technical solution, the release mechanism includes a release seat provided on a side surface of the guide rail, and the release seat is provided with a release guide surface for guiding the swing link to release from the striker.

After the technical scheme is adopted, compared with the prior art, the utility model has following beneficial effect: the utility model discloses simple structure, the part is few, and the operation is stable, when the crank rotates, can order about the carriage around the articulate rotation axis revolution, the carriage is the rotation still simultaneously, and meshing element and support component on this carriage slide in well first guide way and second guide way, make this meshing element's movement track be sharp or be close to O, its declination is 0 or be close to 0, so that the biggest reduction load carries dynamic friction, avoid appearing wearing and tearing scheduling problem, guarantee simultaneously that later stage impact unit is invariable and the unbalance loading is little at the thrust direction that compression energy storage in-process received, realized actuating mechanism's quick release, guarantee impact unit moving stability and smooth and easy nature, improve operating mass, the order the utility model discloses extremely strong market competition has. In addition, under the bail state, the utility model discloses still can realize and strike the normal meshing of unit, guarantee to work normally, it is very convenient to use.

Description of the drawings:

FIG. 1 is an assembly view of the present invention with a latch mechanism and an impact unit;

fig. 2 is an assembly view of the present invention from another perspective with respect to the latch mechanism and the striking unit;

FIG. 3 is an exploded view of FIG. 1;

fig. 4 is a perspective view of the driving frame of the present invention;

fig. 5 is a perspective view of the present invention;

FIG. 6 is a schematic diagram of the present invention;

figure 7 is a front view of a fastener driver incorporating the present invention;

figure 8 is a perspective view of a fastener driver incorporating the present invention;

figure 9 is a cross-sectional view of a fastener driver incorporating the present invention;

FIG. 10 is a schematic view of a second configuration of the present invention;

FIG. 11 is a schematic view of a third configuration of the present invention;

fig. 12 is an operation state diagram of the present invention.

Fig. 13 is an operational state diagram of another configuration of the present invention.

Figure 14 is an operational state diagram of a fastener driver incorporating the present invention.

Fig. 15 is a mechanism operation state diagram including the fastener driver of the present invention in the staple state.

The specific implementation mode is as follows:

the present invention will be further described with reference to the following specific embodiments and accompanying drawings.

Referring to figures 1 to 15, there is shown a drive mechanism for a fastener driving machine, the drive mechanism 1 comprising:

a crank 11 which is rotationally movable; a drive frame assembly 12 rotatably mounted on the crank 11 and comprising an engagement member 122, a support member 123 and a drive frame 121, at least one stationary guide member 13, said support member 123 and/or engagement member 122 being movable along a trajectory along which it is arranged. The utility model discloses simple structure, the part is few, and the operation is stable, when crank 11 rotates, can order about the rotation axis revolution of bogie 121 around crank 11, while bogie 121 still rotation, and this meshing element 122 and support element 123 remove along the orbit respectively, make this meshing element 122's movement track be sharp or be close O, its declination is 0 or be close 0, so that the at utmost reduces the burden and carries the dynamic friction power, avoid appearing wearing and tearing scheduling problem, guarantee simultaneously that the thrust direction that later stage impact unit received is invariable and the unbalance loading is little at compression energy storage in-process, realized actuating mechanism's quick release, guarantee the stability and the smooth and easy nature of impact unit operation, improve work quality, the order the utility model discloses extremely strong market competition has.

Further, the driving frame 121 is rotatably mounted on the crank 11, and the engaging element 122 and the supporting element 123 are both disposed on the driving frame 121; the guide member 13 is provided with at least one guide groove as a track, in which the support member 123 and/or the engagement member 122 is slidably provided. More specifically, the guide member 13 is provided with a first guide groove 131 and a second guide groove 132 as a track, and the engaging member 122 and the supporting member 123 are slidably provided in the first guide groove 131 and the second guide groove 132, respectively. When the crank 11 rotates, the driving rack 121 can be driven to revolve around the rotation axis of the crank 11, and simultaneously, the driving rack 121 also rotates, and the engaging element 122 and the supporting element 123 on the driving rack 121 slide in the first guide groove 131 and the second guide groove 132 respectively, so that the motion track of the engaging element 122 is a straight line or close to O °, and the deflection angle is 0 ° or close to 0 °.

The engaging element 122 and the supporting element 123 are both circumferentially distributed on the driving frame 121 with respect to the rotation axis of the driving frame 121 as a circle center, and when the circumferential radius of the distribution of the engaging element 122 is equal to the distance between the rotation axis of the crank 11 and the rotation axis of the driving frame 121, the crank 11 drives the driving frame 121 to rotate, and the motion track of the engaging element 122 is a straight line; when the supporting elements 123 are distributed with a circumferential radius equal to the distance between the rotation axis of the crank 11 and the rotation axis of the driving frame 121, the crank 11 drives the driving frame 121 to rotate, and the motion track of the supporting elements 123 is a straight line.

In other words, the rotation axis of the crank 11 is a, the position center of the engaging element is B, the position center of the supporting element is C, the rotation center of the driving frame is O, when OA is OB, the motion track of the engaging element 122 is a straight line, and the corresponding first guide groove 131 is in a straight strip shape; when OA ≠ OB, the movement locus of the engaging element 122 is elliptical, and the corresponding first guide groove 131 is elliptical. When OA is equal to OC, the motion trajectory of the supporting element is a straight line, and the corresponding second guiding groove 132 is a straight strip; when OA ≠ OC, the motion trajectory of the supporting member is elliptical, and the corresponding second guiding groove 132 is elliptical. When OA is equal to OB, if the first guide groove 131 and the second guide groove 132 are both straight, and an included angle between the two guide grooves is a, and an included angle between OB and OC is θ, θ is equal to 2 a.

The first guide groove 131 and the second guide groove 132 are arranged in an intersecting manner, are located on the same plane, and the intersection of the first guide groove and the second guide groove is communicated. The first guide groove 131 and the second guide groove 132 may not intersect with each other, or may not be on the same plane.

The engaging member 122 and the supporting member 123 are cylindrical pins, which are simpler in structure. 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.

The upper end of the engaging element 122 protrudes out of the upper end surface of the guiding element 13 through the first guiding groove 131; the latch mechanism 2 is rotatably mounted to the upper end of the engagement member 122. In particular, the latching mechanism 2 can move linearly or approximately linearly with the linear or approximately linear movement of the drive mechanism 1. When the impact unit moves along the first direction, the locking mechanism is meshed with the impact unit to drive the impact unit to move along the first direction, so that the energy storage unit stores energy.

The latch mechanism 2 includes a swing link 21 and a returning member 22 located at a side of the swing link 21, the swing link 21 is formed with a shaft hole 211 at one end and a locking shaft 212 at the other end for being engaged with the striker 31 in the striking unit 3, wherein the striker 31 has a saw tooth 311 engaged with the locking shaft 212 and the saw tooth 311 has an inclined guide surface so that the locking shaft 212 slides along the inclined guide surface to pass over the saw tooth 311 and is locked with the saw tooth 311 at a later stage.

The restoring element 22 is an elastic element which includes a spring or an elastic rubber. In the present embodiment, the reset element 22 is a rubber strip, which is disposed parallel to the striker 31 and beside the lock shaft 212, and the rubber strip can ensure that the lock shaft 212 is always abutted against the striker 31.

The striker 31 is slidably mounted in the guide rail 4 so as to ensure the smoothness of the sliding of the striker 31 and ensure the direction of travel; the guide rail 4 is arranged on the base 5, and the resetting element 22 is arranged on the guide rail 4; the guide 4 is also provided with a release mechanism 6 for actuating the striker 31 out of engagement with the rocker 21. Specifically, the release mechanism 6 includes a release seat 61 provided on a side surface of the guide rail 4, and the release seat 61 is provided with a release guide surface 611 for guiding the swing lever 21 to release from the striker 31. When the latch mechanism 2 pushes the impact unit 3 to move a certain distance along the first direction, the latch mechanism will engage with the release guide surface 611, and due to the restriction of the inclined surface, the lock shaft 212 at the end of the swing link 21 receives a force perpendicular to the first direction while moving along the first direction, and at this time, the swing link 21 can rotate around the engaging element 122, thereby pushing the latch mechanism to release from the impact unit. After the energy storage unit is separated from the fastener driving unit, the impact unit moves along the second direction under the action of the energy storage unit force, and therefore the fastener driving function is achieved. When the locker mechanism is not engaged with the release guide surface 611, the elastic force of the rubber strip resets the swing lever 21 to be re-engaged with the striker 31.

The guide element 13 is fixed on the base 5, the base 5 is provided with an energy storage unit 7 for storing energy through displacement change, the impact unit 3 is connected with the energy storage unit 7, and the base 5 is also provided with a power mechanism 8; the crank 11 is mounted on the power mechanism 8 and is driven to rotate by the power mechanism 8. The power mechanism 8 includes a gear 81 mounted at the lower end of the base 5 and a motor 82 mounted in a matching manner with the gear 81, the motor 82 provides torque and rotation speed, and the gear is usually a reduction box for reducing the rotation speed and increasing the torque. The crank 11 is mounted on the gear transmission 81.

The energy storage unit 7 is a medium capable of storing energy through displacement change, such as an air spring, a mechanical spring, a rubber element, vacuum, and the like. The present embodiment takes an air spring as an example, wherein a cylinder and a piston form a closed space, and gas is contained therein, thereby forming an air spring.

The impact unit 3 moves along the first direction to enable the energy storage unit to store energy, and the impact unit 3 moves along the second direction to achieve the function of driving the fastener into the workpiece. The first direction is the direction of the percussion unit 3 towards the energy storage unit 7 and the second direction is the direction of the energy storage unit 7 towards the percussion unit 3.

The striking unit 3 includes a piston 32 provided in the energy storage unit 7 and a striker 31 attached to the piston 32.

The base 5 is also provided with a cushion 50 for collision with the piston 32 in the impact unit 3 to achieve shock absorption and also to prevent excessive impact from damaging the mechanism.

The base 5 is further provided with a nail guide plate 51 and a nail clamp 52 provided at a lower end of the nail guide plate 51 for feeding a fastener to the nail guide plate 51, the nail guide plate 51 having a passage through which the striker 31 in the striking unit 3 passes. The staple holder 52 is a fastener loading device that can deliver fasteners (e.g., staples) to a guide. The guide plate 51 receives fasteners from the nail holder, and when the striker 31 in the impact unit releases energy at the energy storage unit 7 for impact after the fasteners fall into the channel of the guide plate 51, the striker 31 passes through the channel and drives the fasteners (e.g., nails) in the channel into a workpiece (typically wood, sheet metal, cement, or the like).

As shown in fig. 5 to 6, when the crank 11 rotates, if OA is equal to OB, the engaging element moves linearly, if OA is not equal to OB, the motion trajectory of the engaging element 122 is an ellipse, and when OA and OB differ by a small amount, the minor axis of the ellipse is small, and the motion trajectory of the engaging element 122 can be regarded as an approximately linear motion. OA and OB are preferably chosen to be equal so that the engagement element is moved linearly to provide a low offset load when the striking unit is moved in the first direction. Similarly, if OA is equal to OC, the supporting element 123 moves linearly, and if OA is not equal to OC, the movement locus of the supporting element is an ellipse, and when OA and OC are different from each other, the minor axis of the ellipse is smaller, and the movement locus of the supporting element can be regarded as an approximately linear movement. OB and OC are not necessarily equal because the engaging member 122 and the supporting member 123 do not necessarily move linearly at the same time. However, for simplicity of design, OA and OC are preferably set so that the shape of the first guide groove 131 and the second guide groove 132 can be made simpler, and both the engaging element and the supporting element 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.

As shown in fig. 5-6, when the engaging member 122 passes through point a and the vicinity thereof, the second guide groove 132 cooperates with the supporting member 123 to provide a supporting force to the driving frame 121, so that the driving frame 121 maintains the rotation in the opposite direction to the crank 11, thereby maintaining the movement of the engaging member in the direction of the first guide groove 131. Similarly, the first guide groove 131 cooperates with the engagement member 122 to support the driving frame when the support member passes the point a and the vicinity thereof, thereby maintaining the movement of the support member 123 in the direction of the second guide groove 132. When neither the engaging member 122 nor the supporting member 123 is located at and near the point a, either one of the first guide groove 131 and the second guide groove 132 is required to be supported.

Therefore, the lengths of the first guide groove 131 and the second guide groove 132 need not cover the entire stroke of the engaging member 122 and the supporting member 123. In connection with fig. 10-11, two incomplete forms of guide grooves are shown, and other forms are within the scope of protection of the present patent as long as the working principle is the same. In fig. 10, the two guide grooves are not of the same length, and the first guide groove is degenerated into two short linear grooves, which only serve as a support when the support element passes through point a and the vicinity thereof. In fig. 11, the two guide grooves are hollowed out in the middle by the same length L. Referring to fig. 6 and 11, when the angle between OC and OB is θ, θ varies from 0 ° to 180 °, and OA ═ OC ═ R, L ═ 2 √ R (√ 1-cos (θ/2))). Let θ be 180 °, L be (2 √ 2) × R, which is a root.

As shown in fig. 6 and 12, states a to h show a complete cycle of movement of the drive mechanism under OA-OB-OC conditions. 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 °. The state a is an initial state, and the engaging element is located at the bottom dead center along the first direction. The crank is rotated counterclockwise and the engagement member moves in the first direction and the support member moves along the second guide groove 132. The crank is rotated 30 counter clockwise as shown in state b and the support element is moved to point a, where the drive carriage and the engagement element are supported by means of the first guide slot 131. The crank is rotated 90 counterclockwise as shown in state c and the engagement element moves to point a. The crank is rotated 120 counterclockwise as shown in state d, and the support member is moved to the top dead center in the direction of the second guide groove 132. The crank continues to rotate and the support member moves in the opposite direction along the second guide groove 132. The crank is rotated 180 deg. counter clockwise as shown in state e and the engagement element is moved to top dead centre in the first direction. The crank continues to rotate and the engagement member moves in the second direction. The crank is rotated 210 counter clockwise as shown in state f and the support element is moved to point a, where the drive carriage and the engagement element are supported by means of the first guide slot 131. The crank is rotated 270 counterclockwise as shown in state g and the engagement member is moved in the second direction to point a. The crank is rotated counterclockwise by 300 deg., as shown in state h, and the support member moves to the bottom dead center in the opposite direction of the second guide groove 132. The crank rotates 360 deg. counterclockwise and the drive mechanism returns to the initial state a.

As shown in fig. 6 and 13, 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 movement cycle is similar to the case when the angle between OB and OC is 120 deg., but the crank rotation angle of the engagement unit and the support unit passing through the point A is different. When the crank rotates counterclockwise by 0 degrees, as shown in state a; the crank is rotated 180 counter clockwise as shown in state e and the support member is moved to point a, at which time the drive carriage and the engagement member are supported against the first guide slot. The crank is rotated 90 ° counterclockwise, as shown in state c; the crank is rotated 270 counter clockwise as shown in state g and the engagement member is moved to point a, at which time the drive frame and the support member are supported by means of the second guide slot.

As shown in fig. 6 and 14, the states a to J correspond to one duty cycle under the condition that OA is equal to OB, and OC is included at 120 °. And state a, an initial state in which the impact unit is in a position to complete the driving of the fastener, the crank is rotated counterclockwise to move the engaging element in the first direction, and the latch mechanism is mounted thereon to engage with the impact unit, thereby moving the impact unit in the first direction to compress the air spring, as shown in state B, C, D. The crank continues to rotate anticlockwise and the lock shaft engages the release guide surface 611 of the release mechanism 6, pushing the rocker to rotate about the engagement element until the lock shaft disengages from the impact unit, as shown in state E. The impact unit moves at a high speed in a second direction under the action of the air spring to drive the fastener into the workpiece, as shown in state F. Continued counterclockwise rotation of the crank moves the engagement element in the second direction as shown at state G, H and the latch mechanism is rotated in the opposite direction against the side of the striker by the reset element. The crank continues to rotate counterclockwise as shown at state I, J, and the engagement element moves in the second direction and the latch mechanism clears the serrations of the striker and is reset by the reset element, eventually reengaging the striking unit and returning to the state shown at state a.

Referring to fig. 6 and 15, in order to analyze the mechanism operating state in the staple state of the present invention, the staple state is analyzed under the condition that OA ═ OB ═ OC and the included angle between OB and OC is 120 °. When for some reason the staple is jammed and the fastener is stuck in the staple guide, the striking unit may stop at any position in the second direction, as shown in state K, and the crank is rotated counterclockwise by the motor to push the engaging element and the latch mechanism to move in the second direction to the same distance as the normal operation cycle, and the latch 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 state L, M. The crank continues anticlockwise rotation, promotes engaging element and latched device and moves along first direction until reengages with the firing pin, as state N shows, later the firing pin also along first direction removal compression air spring along with it stores energy, as state E shows, and then gets back to normal duty cycle again, that is to say, under the bail state, the utility model discloses still can realize with the normal meshing of impact unit, guarantee can normally work, it is very convenient to use.

To sum up, the utility model discloses simple structure, the part is few, and the operation is stable, when crank 11 rotates, can order about the rotation axis revolution of driving frame 121 around crank 11, driving frame 121 still rotates simultaneously, and meshing element 122 and the support element 123 branch on this driving frame 121 slide in first guide way 131 and second guide way 132, make this meshing element 122's movement track be sharp or be close O, its declination is 0 or be close 0, so that the at utmost reduces the burden and carry dynamic friction, avoid appearing wearing and tearing scheduling problem, guarantee that the thrust direction that later stage impact unit received is invariable and the unbalance loading is little at compression energy storage in-process simultaneously, realized actuating mechanism's quick release, guarantee impact unit operation's stability and smooth and easy nature, improve work quality, the order the utility model discloses extremely strong market competition has. In addition, under the bail state, the utility model discloses still can realize and strike the normal meshing of unit, guarantee to work normally, it is very convenient to use.

Of course, the above description is only an exemplary embodiment of the present invention, and not intended to limit the scope of the present invention, and all equivalent changes and modifications made by the constructions, features, and principles of the present invention in accordance with the claims of the present invention are intended to be included in the scope of the present invention.

Claims

1. A drive mechanism for a fastener driving machine, characterized by: the drive mechanism (1) comprises:

a crank (11) which can rotate;

a drive frame assembly (12) rotatably mounted on the crank (11) and including an engagement member (122), a support member (123) and a drive frame (121);

at least one stationary guide element (13), along which the support element (123) and/or the engagement element (122) can be displaced.

2. A drive mechanism for a fastener driving machine according to claim 1, wherein: the drive frame (121) is rotatably mounted on the crank (11), and the engagement element (122) and the support element (123) are both disposed on the drive frame (121).

3. A drive mechanism for a fastener driving machine according to claim 1, wherein: the guide element (13) is provided with at least one guide groove as a track, in which the support element (123) and/or the engagement element (122) is slidably arranged.

4. A drive mechanism for a fastener driving machine according to claim 3, wherein: the number of the guide grooves is two, which are a first guide groove (131) and a second guide groove (132), respectively, and the engaging member (122) and the supporting member (123) are slidably disposed in the first guide groove (131) and the second guide groove (132), respectively.

5. A drive mechanism for a fastener driving machine according to claim 1, wherein: the meshing element (122) and the supporting element (123) are both distributed on the driving frame (121) along the circumference by taking the rotation axis of the driving frame (121) as the center of a circle, and when the circumferential radius distributed by the meshing element (122) is equal to the distance between the rotation axis of the crank (11) and the rotation axis of the driving frame (121), the crank (11) drives the driving frame (121) to rotate, the motion trail of the meshing element (122) is a straight line; when the circumferential radius of the support elements (123) is equal to the distance between the rotation axis of the crank (11) and the rotation axis of the driving frame (121), and the crank (11) drives the driving frame (121) to rotate, the motion trail of the support elements (123) is a straight line.

6. A drive mechanism for a fastener driving machine according to claim 4, wherein: the first guide groove (131) and the second guide groove (132) are arranged in a crossing manner.

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

8. A drive mechanism for a fastener driving machine according to any one of claims 1 to 7, wherein: the locking mechanism (2) is rotatably arranged at the upper end of the engaging element (122), wherein the locking mechanism (2) comprises a swing rod (21) and a reset element (22) positioned at the side of the swing rod (21), one end of the swing rod (21) is formed with a shaft hole (211), and the other end of the swing rod is provided with a locking shaft (212) used for being engaged and positioned with a firing pin (31) in the impact unit (3).

9. A drive mechanism for a fastener driving machine according to claim 8, wherein: the striker (31) is slidably mounted in the guide rail (4); the guide rail (4) is arranged on the base (5), and the resetting 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 be disengaged from the swing rod (21).

10. A drive mechanism for a fastener driving machine according to claim 9, wherein: the release mechanism (6) comprises a release seat (61) arranged on the side surface of the guide rail (4), and a release guide surface (611) used for guiding the swing rod (21) to be separated from the striker (31) is arranged on the release seat (61).