CN109555792B - An electric hammer clutch device - Google Patents

Abstract

The present invention relates to the technical field of electric hammers, and in particular to an electric hammer clutch device. An electric hammer clutch device includes an electric hammer body, a cylinder, a rotating shaft, clutch teeth, meshing teeth, a first transmission component, a second transmission component for driving the rotation of the rotating shaft, and a knob component connected to the clutch teeth. The first One end of the transmission assembly and the main body of the electric hammer are connected to both ends of the piston of the cylinder respectively. The meshing teeth are installed on the cylinder to drive the cylinder to rotate. The knob assembly rotates to drive the clutch teeth to slide axially on the rotating shaft, thereby making the clutch teeth and the first The other end of the transmission component is engaged or separated, and the clutch teeth are engaged or separated from the meshing teeth. The present invention drives the clutch teeth to move laterally along the rotation axis by rotating the knob assembly, thereby driving the clutch teeth to engage or separate from the meshing teeth, driving the clutch teeth to engage or separate from the first transmission assembly, and driving the knob assembly to engage or separate from the meshing teeth. It is convenient to realize the conversion of the four working states of the electric hammer.

Description

An electric hammer clutch device

Technical field

The present invention relates to the technical field of electric hammers, and in particular to an electric hammer clutch device.

Background technique

An electric hammer is an electric rotary hammer drill with a safety clutch and a pneumatic hammering mechanism. An electric hammer is a device that uses the principle of piston motion to compress gas to impact a drill bit to drill holes in hard materials such as concrete, bricks, and stones, thereby improving the drilling efficiency.

In order to meet the needs of customers and switch working modes, most of the electric hammers in the existing market need to be equipped with a clutch. The structure is complex and the stroke is increased, which is not conducive for users to quickly switch the working mode of the electric hammer.

Contents of the invention

In order to solve the technical problem in the related art that it is inconvenient for users to quickly change the working mode of an electric hammer, an embodiment of the present invention provides an electric hammer clutch device, which aims to simplify the structure and eliminate the increase in stroke caused by the clutch, which makes it inconvenient to quickly switch the work. Pattern effects.

The invention provides an electric hammer clutch device, which includes an electric hammer body, a cylinder, a rotating shaft, clutch teeth, meshing teeth, a first transmission component, a second transmission component for driving the rotation of the rotating shaft, and a knob connected to the clutch teeth. assembly, one end of the first transmission component of the body and the main body of the electric hammer are connected to both ends of the piston of the cylinder respectively. The meshing teeth are installed on the cylinder to drive the cylinder to rotate. The knob assembly rotates to drive the clutch teeth to slide axially on the rotating shaft, thereby causing the clutch teeth to slide axially on the rotating shaft. The clutch teeth are engaged or separated from the other end of the first transmission component, and the clutch teeth are engaged or separated from the meshing teeth to realize switching of the four states of drilling, hammer drilling, hammering and angle adjustment of the electric hammer body.

The second transmission component drives the rotation of the rotating shaft to drive the clutch teeth to rotate. When the clutch teeth and the meshing teeth are engaged, the meshing teeth drive the cylinder to rotate driven by the clutch teeth; by rotating the knob assembly, the clutch teeth are driven to slide along the rotation axis. The clutch teeth are engaged or separated from the meshing teeth, thereby adjusting the rotational state of the cylinder. In addition, by rotating the knob assembly to drive the clutch teeth to slide along the rotation axis, the clutch teeth can also be engaged or separated from the first transmission component, thereby causing the second transmission component to be engaged or separated. Whether a transmission component drives the piston to reciprocate; through the settings of the above-mentioned clutch teeth, meshing teeth, first transmission component, second transmission component, cylinder and knob component, it is convenient to adjust the relative motion state of the knob component by adjusting the knob component, thereby realizing the electric Conversion of four working states of hammer drill, hammer drill, angle adjustment and hammer.

Optionally, the knob assembly includes a knob, a transmission pin, a guide rail pin and a shift block. The transmission pin is connected to the shift block. The shift block is slidably mounted on the guide rail pin. The clutch teeth are provided with a first slot, and the shift block is provided with a card. , the card is set in the first card slot, and the knob is rotated to drive the shifting block to slide axially on the guide rail pin through the transmission pin.

It is driven by the transmission pin to convert the rotation of the knob into the lateral movement of the dial, and the clutch teeth are pushed through the dial to perform the lateral reciprocating movement; by connecting the card of the dial with the first card slot, In order to facilitate the shifting block to push the clutch teeth to slide along the rotation axis; through the arrangement of the guide rail pin, it is convenient to guide the moving path of the shifting block.

Optionally, the shifting block is also provided with a toothed end. When the knob drives the clutch tooth to engage with the first transmission component and separate from the meshing tooth, the meshing tooth engages or separates from the toothed end.

A toothed end is provided at the end of the shifting block, so that when the clutch teeth are engaged with the first transmission component and the clutch teeth are separated from the meshing teeth, the meshing teeth mesh with the toothed end, thereby limiting the movement of the cylinder and preventing its rotation.

Optionally, the knob assembly also includes a torsion spring and a fixed frame slidably installed on the guide rail pin. The fixed frame is set outside the dial block, the torsion spring is set on the fixed frame, and the torsion spring and dial block are respectively located on both sides of the fixed frame. The torsion spring is provided with a first through hole, and the fixed frame is provided with a second through hole at a position relative to the first through hole. One end of the transmission pin is connected to the knob, and the other end of the transmission pin passes through the first through hole and the second through hole. Through hole and connected with the dial block.

The setting of the torsion spring is to improve the stability of the transmission pin transmission. Specifically, the knob rotates and transmits kinetic energy through the transmission pin to drive the clutch teeth to perform lateral reciprocating movements along the rotation axis. When the transmission pin drives During the process, shaking is easy to occur, so the torsion spring is used to stabilize the transmission; the installation bracket is installed to facilitate the installation of the torsion spring.

Optionally, the first transmission component includes a swing rod bearing and a yaw bearing that is engaged or separated from the clutch teeth. The yaw bearing is set on the rotating shaft. The swing rod bearing includes a swing ring and a swing rod connected to the swing ring. The other end of the rod is rotatably connected to the piston, the outer circumferential side of the yaw bearing is provided with an inclined guide groove, and the pendulum ring has a slider that slides along the guide groove.

Through the arrangement of the pendulum ring, the pendulum rod and the yaw bearing, it is convenient for the yaw bearing to rotate synchronously with the clutch teeth after the yaw bearing is engaged with the clutch teeth. The slider of the pendulum ring slides along the guide groove, thereby driving the pendulum rod to move, and then Drive the cylinder piston to make reciprocating movements.

Optionally, the cylinder is provided with a tripping spring, a tripping buckle, a first circlip and a second circlip. One side of the meshing teeth is engaged with one side of the tripping buckle, and the other side of the tripping buckle is engaged with the tripping buckle. The first circlip is connected, and the tripping spring clip is installed between the other side of the meshing tooth and the second circlip.

By engaging the release buckle with the meshing teeth, the meshing teeth are initially restricted from sliding along the cylinder surface, and then by setting a first circlip on the other side of the release buckle, the side of the meshing teeth without the release buckle is provided with a third circlip. The second circlip is used to further fix the meshing teeth and prevent them from sliding along the cylinder. In addition, the trip spring is arranged between the second circlip and the meshing teeth to buffer and use its own elasticity when the meshing teeth slide along the cylinder. The action causes the meshing teeth to return to their original position.

Optionally, the second transmission component includes a driving bevel gear and a driven bevel gear. The driven bevel gear is provided at one end of the rotating shaft, and the driving bevel gear meshes with the driven bevel gear for transmission.

Through the arrangement of the driving bevel gear and the driven bevel gear, it is convenient for the driving bevel gear and the driven bevel gear to form a gear pair to drive the rotating shaft to perform axial rotation.

Optionally, the knob assembly drives the clutch teeth to slide axially along the rotation axis, so that the clutch teeth are engaged with the meshing teeth, and the clutch teeth are engaged or separated from the first transmission component, where: when the clutch teeth are engaged with the first transmission component, The clutch teeth drive the first transmission component to rotate and the meshing teeth to rotate, so that the cylinder rotates and the first transmission component drives the piston to reciprocate, switching the electric hammer body to the hammer drill state; when the clutch teeth are separated from the first transmission component, the clutch teeth The meshing teeth drive the cylinder to rotate, switching the main body of the electric hammer to the drilling state.

When the clutch teeth and the meshing teeth are engaged, the clutch teeth are controlled to engage or separate from the first transmission component, so that the electric hammer body is in a drilling or hammer drilling state. Specifically, when the clutch teeth are engaged with the first transmission component, the first transmission component is forced to drive the piston to make a reciprocating motion, that is, an impact motion in the cylinder, thereby realizing the function of the electric hammer drill; when the clutch teeth are engaged with the first transmission component, When the transmission component is separated, the first transmission component is not stressed and does not drive the cylinder piston to make reciprocating movements, so that the electric hammer does not output impact while drilling, realizing the function of the electric hammer drill.

Optionally, the knob assembly drives the clutch teeth to slide axially along the rotation axis to separate the clutch teeth from the meshing teeth. The clutch teeth snap into place with the first transmission component, and the tooth-shaped end snaps into or separates from the meshing teeth, where: tooth shape When the toothed end is separated from the meshing teeth, the cylinder performs radial rotation, and the main body of the electric hammer switches to the angle adjustment state; when the toothed end is engaged with the meshing teeth, the cylinder is stationary, and the clutch teeth drive the first transmission component to rotate, so that the second transmission component rotates. A transmission component drives the piston to make reciprocating movements, switching the electric hammer to the hammer state.

When the clutch teeth and meshing teeth are separated, the clutch teeth are engaged with the first transmission assembly, and the first transmission assembly drives the piston to reciprocate. By controlling the toothed end to engage or separate from the meshing teeth, the cylinder is free from radial force. Or the cylinder is fixed and cannot rotate, so that the main body of the electric hammer is in the angle adjustment or hammering state.

It should be understood that the above general description and the following detailed description are only exemplary and do not limit the present invention.

Description of the drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can also be obtained based on these drawings without exerting creative efforts.

Figure 1 is a schematic structural diagram of an electric hammer clutch device provided by the present invention;

Figure 2 is an exploded view of the electric hammer clutch device shown in Figure 1;

Figure 3 is a schematic structural diagram of the knob assembly shown in Figure 1;

Figure 4 is an exploded schematic diagram of the knob assembly shown in Figure 3;

Figure 5 is a schematic structural diagram of the plate release buckle shown in Figure 1.

In the picture: 100. Electric hammer body; 110. Cylinder; 120. Piston; 200. First transmission component; 220. Swing bar bearing; 221. Swing bar; 222. Swing ring; 230. Yaw bearing; 231. First Tooth-shaped hole; 232, guide groove; 300, meshing teeth; 310, groove; 320, release plate buckle; 321, convex plate; 330, release spring; 340, second circlip; 350, first circlip; 400. Clutch teeth; 410. First card slot; 420. Third through hole; 500. Second transmission component; 510. Active bevel gear; 520. Driven bevel gear; 600. Knob assembly; 610. Knob; 611. Fourth through hole; 620, fixed frame; 621, second through hole; 630, dialing block; 631, toothed end; 632, guide rail pin; 640, transmission pin; 650, torsion spring; 651, first through hole; 700. Rotation axis.

Implementation

Embodiments of the invention are described in detail below, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are exemplary and are intended to explain the present invention and are not to be construed as limiting the present invention.

In order to meet the needs of customers and switch working modes, most of the electric hammers in the existing market need to be equipped with a clutch. The structure is complex and the stroke is increased, which is not conducive for users to quickly switch the working mode of the electric hammer.

In order to solve the technical problem in the related art that it is inconvenient for users to quickly change the working mode of an electric hammer, an embodiment of the present invention provides an electric hammer clutch device, which aims to simplify the structure and eliminate the increase in stroke caused by the clutch, which makes it inconvenient to quickly switch the work. Pattern effects. The following is an example of the structure of the electric hammer clutch device with reference to Figures 1-5.

The electric hammer clutch device includes an electric hammer body 100, a cylinder 110, a rotating shaft 700, clutch teeth 400, meshing teeth 300, a first transmission component 200, a second transmission component 500 for driving the rotation of the rotating shaft 700 and the clutch teeth 400. The connected knob assembly 600, one end of the first transmission assembly 200 and the electric hammer body 100 are respectively connected to both ends of the piston 120 of the cylinder 110. The meshing teeth 300 are installed on the cylinder 110 to drive the cylinder 110 to rotate, and the knob assembly 600 rotates to drive the clutch. The teeth 400 slide axially on the rotating shaft 700, thereby causing the clutch teeth 400 to engage or separate from the other end of the first transmission assembly 200, and the clutch teeth 400 to engage or separate from the meshing teeth 300, so as to realize the rotation of the electric hammer cylinder. Switching between four states of drill, hammer drill, hammer and angle adjustment.

In the actual design process, the meshing teeth 300 are fixed on the cylinder 110 , and the clutch teeth 400 perform a lateral reciprocating motion relative to the meshing teeth 300 . In this embodiment, the cylinder 110 is provided with a tripping spring 330, a tripping buckle 320, a first circlip 350 and a second circlip 340. One side of the meshing tooth 300 is engaged with one side of the tripping buckle 320. , the other side of the trip plate buckle 320 is connected to the first circlip 350 , and the trip spring 330 is sandwiched between the other side of the meshing tooth 300 and the second circlip 340 .

Optionally, the second circlip 340 is a flat circlip, and the first circlip 350 is a steel wire circlip.

Optionally, the meshing tooth 300 is provided with a groove 310 on the side adjacent to the tripping plate 320, and the tripping plate buckle 320 is provided with a convex plate 321 on the side adjacent to the meshing tooth 300. By clamping the convex plate 321 It is disposed in the groove 310 to realize the engagement between the meshing teeth 300 and the stripper buckle 320 .

In order to facilitate the knob assembly 600 to drive the clutch teeth 400 to perform lateral reciprocating movements along the rotation axis 700, the clutch teeth 400 are provided with a first slot 410 and a third through hole 420. The knob assembly 600 is connected to the first slot 410, and the rotation axis 700 is configured to be disposed through the third through hole 420, and the rotating shaft 700 is respectively provided with locking parts at the extending end and the extending end relative to the third through hole 420 to fix the position of the clutch teeth 400 relative to the rotating shaft 700, The clutch teeth 400 are caused to rotate synchronously with the rotating shaft 700 .

Specifically, the knob assembly 600 includes a knob 610, a drive pin 640, a guide rail pin 632 and a dial block 630. The drive pin 640 is connected to the dial block 530. The dial block 630 is slidably installed on the guide rail pin 632. A card is provided on the dial block 630. , the card is inserted into the first card slot 410 , and the knob 610 is rotated to drive the dial 630 to slide axially on the guide pin 632 through the transmission pin 640 .

In this embodiment, the shifting block 630 is also provided with a toothed end 631. When the knob 610 drives the clutch tooth 400 to engage with the first transmission component 200 and separate from the meshing tooth 300, the meshing tooth 300 meshes with the toothed end 631 or separation. In a specific implementation manner, the toothed end 631 of the shifting block 630 is set according to the toothed shape of the meshing teeth 300 .

In practical applications, the knob 610 rotates to drive the dial 630 to move the clutch teeth 400, causing the clutch teeth 400 to move laterally along the rotation axis 700, so that the clutch teeth 400 perform a lateral reciprocating motion relative to the meshing teeth 300, and the clutch teeth 400 are in contact with the meshing teeth 300. The meshing teeth 300 are engaged or separated. In addition, since the card of the shifting block 630 is set in the first slot 410, the shifting block 630 performs a synchronous transverse movement relative to the meshing teeth 300 and the clutch teeth 400. One end of the shifting block 630 The toothed end 631 is engaged or separated from the meshing teeth 300 .

In this embodiment, the knob assembly 600 further includes a torsion spring 650 and a fixing bracket 620 slidably installed on the guide rail pin 632. The fixing bracket 620 is sleeved outside the dial block 630. The torsion spring 650 is disposed on the fixing bracket 620, and The torsion spring 650 and the dialing block 630 are respectively located on both sides of the fixed frame 620. The torsion spring 650 is provided with a first through hole 651, and the fixed frame 620 is provided with a second through hole 621 at a position relative to the first through hole 651. One end of the transmission pin 640 is connected to the knob 610 , and the other end of the transmission pin 640 passes through the first through hole 651 and the second through hole 621 and is connected to the dial block 630 .

Furthermore, the fixed frame 620 is provided with a receiving space for accommodating the guide rail pin 632 and the shifting block 630. The two ends of the guide rail pin 632 are respectively connected to both sides of the fixed frame 620. The shifting block 630 is disposed on the guide rail pin 632.

In a specific implementation manner, the transmission pin 640 includes a first cylinder, a second cylinder and a third cylinder. The ends of the second cylinder and the third cylinder are respectively vertically connected to both ends of the first cylinder. The third cylinder The second cylinder and the third cylinder are parallel, and the second cylinder and the third cylinder are respectively located on both sides of the vertical plane where the axis of the first cylinder is located. The second cylinder passes through the first through hole 651 and the second through hole 651 . Hole 621, the knob 610 is provided with a fourth through hole 611, and the third column is configured to be inserted into the fourth through hole 611.

Optionally, the first transmission assembly 200 includes a swing rod bearing 220 and a yaw bearing 230. The yaw bearing 230 is mounted on the rotating shaft 700. When the clutch teeth 400 perform traverse reciprocating motion along the rotating shaft 700, the yaw bearing 230 It is engaged or separated from the clutch teeth 400 . Furthermore, the end of the yaw bearing 230 adjacent to the clutch teeth 400 is provided with a first tooth-shaped hole 231 , and the first tooth-shaped hole 231 is provided according to the tooth shape of the clutch teeth 400 to facilitate engagement with the clutch teeth 400 . catch.

When the yaw bearing 230 is engaged with the clutch teeth 400, since the rotating shaft 700 drives the clutch teeth 400 to rotate, the meshing teeth 300 can drive the yaw bearing 230 to rotate, so that the swing rod bearing 220 is forced to drive the piston 120 in the cylinder 110 Making an impact action, that is, the piston 120 makes a traverse reciprocating action in the cylinder 110; when the deflection bearing 230 is separated from the second clutch assembly 400, the swing rod bearing 220 is not stressed and the piston 120 does not move.

In a specific implementation, the swing rod bearing 220 includes a swing rod 221 and a swing ring 222. One end of the swing rod 221 is connected to the swing ring 222, and the other end of the swing rod 221 is rotationally connected to the piston 120. The outer circumference of the yaw bearing 230 is provided with There is an inclined guide groove 232 , and the swing ring 222 has a slider that slides along the guide groove 232 . Furthermore, the end of the swing rod 221 is connected to the piston 120 through a pin.

Optionally, the guide groove 232 is biased on the outer surface of the yaw bearing 230 . Specifically, the guide groove 232 is a closed annular structure, and part of the ring is biased toward one end of the yaw bearing 230 , and the remaining part of the ring is biased toward the other end of the yaw bearing 230 , that is, the plane where the guide groove 232 is located is aligned with the side surface of the yaw bearing 230 . A certain angle.

The second transmission component 500 includes a driving bevel gear 510 and a driven bevel gear 520. The driven bevel gear 520 is provided at one end of the rotating shaft 700. The driving bevel gear 510 meshes with the driven bevel gear 520 for transmission. In this embodiment, the driving bevel gear 510 and the driven bevel gear 520 form a gear pair to drive the rotating shaft 700 to perform axial rotation.

In one possible implementation, the knob assembly 600 drives the clutch teeth 400 to slide axially along the rotation axis 700 so that the clutch teeth 400 mesh with the meshing teeth 300 , and the clutch teeth 400 engage or disengage from the first transmission assembly 200 .

When the clutch teeth 400 are separated from the yaw bearing 230, that is, when the knob 600 rotates for the first time, the clutch teeth 400 slide toward the meshing teeth 300 along the rotation axis 700, and the clutch teeth 400 mesh with the meshing teeth 300. At this time, the yaw bearing 230 is separated from the clutch teeth 400, the swing rod bearing 220 is not stressed, and the piston 120 does not move to prevent impact action in the cylinder 110. The clutch teeth 400 drive the cylinder 110 to rotate through the meshing teeth 300 to achieve drilling when the electric hammer is output. Without impact, that is, the electric hammer is in drilling state.

When the clutch teeth 400 are engaged with the yaw bearing 230, that is, when the knob 610 rotates for the second time, the clutch teeth 400 mesh with the meshing teeth 300. At this time, the clutch teeth 400 slide along the rotation axis 700 in the opposite direction to the meshing teeth 300, and the deflection The pendulum bearing 230 is engaged with the clutch teeth 400. The pendulum bearing 220 is forced to drive the piston 120 to perform a reciprocating motion to generate an impact in the cylinder 110. The clutch teeth 400 drive the cylinder 110 to perform a rotational motion through the meshing teeth 300 to achieve the electric hammer output. When drilling and impacting, the electric hammer is in the drill hammer state.

In another possible implementation, the knob assembly 600 drives the clutch teeth 400 to slide axially along the rotation axis 700 to separate the clutch teeth 400 from the meshing teeth 300. The clutch teeth 400 are engaged with the first transmission assembly 200. The tooth shape The end 631 is engaged or separated from the meshing teeth 300 .

When the toothed end 631 separates from the meshing teeth 300, that is, when the knob 610 rotates for the third time, the clutch teeth 400 continue to slide along the rotation axis 700 in the opposite direction to the meshing teeth 300, and the clutch teeth 400 separate from the meshing teeth 300, and the yaw bearing 230 is engaged with the clutch teeth 400, and the swing rod bearing 220 is forced to drive the piston 120 to reciprocate to generate an impact in the cylinder 110. At this time, because the clutch teeth 400 and the meshing teeth 300 are separated, the meshing teeth 300 are not stressed, so the cylinder 110 There is no force in the radial direction, and the angle of the electric hammer can be adjusted at the output end, that is, the electric hammer is in the angle adjustment state.

When the toothed end 631 meshes with the meshing teeth 300, that is, when the knob 610 rotates for the fourth time, the clutch teeth 400 slide toward the meshing teeth 300 along the rotation axis 700. At this time, the clutch teeth 400 and the meshing teeth 300 are still in a separated state. However, the toothed end 631 of the shifting block 630 meshes with the meshing teeth 300, and the cylinder 110 cannot rotate radially. The yaw bearing 230 engages with the clutch teeth 400, and the swing rod bearing 220 is forced to drive the piston 120 to make an impact action in the cylinder 110. , so that the electric hammer only has impact when outputting, that is, the electric hammer is in the hammer working state.

In the actual design process, the first rotation, the second rotation, the third rotation, the fourth rotation and the movement state of the corresponding parts after the rotation are all based on the electric hammer to realize the four functions of drilling, drill hammer, angle adjustment and hammer in sequence. The working status is matched and set. When the working status corresponding to the rotation changes, the action mode of the corresponding component also changes accordingly, which is not further limited in this application.

In this embodiment, the rotation angle of the knob 610 may be 30°; or the rotation angle of the knob 610 may be 45°; or the rotation angle of the knob 610 may be 60°; or the rotation angle of the knob 610 may be 60°. Each rotation angle can be 90°. In the actual design process, the rotation angle of the knob 610 can be determined according to the actual design requirements or the operator's comfort level. In addition, the number of rotations of the knob 610 is set according to the type of functions that the electric hammer needs to implement. This is discussed in this application. shall not be further limited.

To sum up, the method for realizing the four functions provided by the embodiment of the present application is to rotate the knob assembly to drive the clutch teeth to perform a lateral reciprocating motion along the rotation axis, thereby driving the clutch teeth to engage or separate from the meshing teeth, and then through the second The transmission component drives the rotation of the rotating shaft to drive the clutch teeth to rotate, thereby driving the meshing teeth and the cylinder to rotate or not, and drives the clutch teeth to engage or separate from the first transmission component to drive the first transmission component to drive the piston cluster to reciprocate in the cylinder. An impact is generated inside, and the knob assembly is driven to engage or separate from the meshing teeth, so as to facilitate the adjustment or restriction of the cylinder rotation, and facilitate the conversion of the four working states of electric hammer drill, hammer drill, angle adjustment and hammer, and is easy to operate.

In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", " The directions or positional relationships indicated by "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc. are based on the directions or positions shown in the accompanying drawings. The positional relationship is only for the convenience of describing the present invention and simplifying the description. It does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention.

In addition, the terms “first” and “second” are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of indicated technical features. Therefore, features defined as "first" and "second" may explicitly or implicitly include at least one of these features. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise expressly and specifically limited.

In the present invention, unless otherwise clearly stated and limited, the terms "installation", "connection", "connection", "fixing" and other terms should be understood in a broad sense. For example, it can be a fixed connection or a detachable connection. , or integrated; it can be mechanically connected, electrically connected or communicable with each other; it can be directly connected or indirectly connected through an intermediate medium; it can be the internal connection of two elements or the interaction between two elements, Unless otherwise expressly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

The above are only specific embodiments of the present invention, but the technical features of the present invention are not limited thereto. Any changes or modifications made by those skilled in the art within the field of the present invention are covered by the patent scope of the present invention. among.

Claims (6)

1. An electric hammer clutch device, characterized in that it includes an electric hammer body, a cylinder, a rotating shaft, clutch teeth, meshing teeth, a first transmission component, a second transmission component for driving the rotation of the rotating shaft, and a clutch. A knob assembly with tooth connection, one end of the first transmission assembly and the main body of the electric hammer are respectively connected to both ends of the cylinder piston, the meshing teeth are installed on the cylinder to drive the cylinder to rotate, the The knob assembly rotates to drive the clutch teeth to slide axially on the rotating shaft, thereby causing the clutch teeth to engage or separate from the other end of the first transmission component, and to engage the clutch teeth with the The teeth engage or separate to realize the switching of the four states of the drill, hammer drill, hammer and angle adjustment of the electric hammer body; the knob assembly includes a knob, a transmission pin, a guide rail pin and a dial block, and the transmission pin and the dial The shifting block is connected with the block, the shifting block is slidably installed on the guide rail pin, the clutch tooth is provided with a first card slot, the shifting block is provided with a card, and the card card is arranged in the first card slot , the knob rotates to drive the shifting block to slide axially on the guide rail pin through the transmission pin; the shifting block is also provided with a toothed end, and the knob drives the clutch tooth and the third When a transmission component is engaged and separated from the meshing teeth, the meshing teeth engage or separate from the toothed end; the knob assembly also includes a torsion spring and a fixed frame slidably installed on the guide rail pin. The frame is sleeved outside the dial block, the torsion spring is arranged on the fixed frame, and the torsion spring and the dial block are respectively located on both sides of the fixed frame, and a first through hole is provided on the torsion spring , a second through hole is opened on the fixed frame relative to the first through hole, one end of the transmission pin is connected to the knob, and the other end of the transmission pin passes through the first through hole and the second through hole. 2. An electric hammer clutch device according to claim 1, characterized in that the first transmission component includes a swing rod bearing and a yaw bearing that is engaged or separated from the clutch teeth, and the yaw bearing Set on the rotating shaft, the swing rod bearing includes a swing ring and a swing rod connected to the swing ring. The other end of the swing rod is rotationally connected to the piston. The outer peripheral side of the swing bearing is provided with an inclined Guide groove, the swing ring has a slider sliding along the guide groove. 3. An electric hammer clutch device according to claim 1, characterized in that the cylinder is provided with a trip spring, a trip plate buckle, a first circlip and a second circlip, and one of the meshing teeth One side of the tripping buckle is engaged with one side of the tripping buckle, the other side of the tripping buckle is connected to the first circlip, and the tripping spring is clamped on the other side of the meshing tooth and the between the second circlips. 4. An electric hammer clutch device according to claim 1, characterized in that the second transmission component includes a driving bevel gear and a driven bevel gear, and the driven bevel gear is arranged at one end of the rotating shaft. , the driving bevel gear meshes with the driven bevel gear for transmission. 5. An electric hammer clutch device according to claim 1, characterized in that the knob assembly drives the clutch teeth to slide axially along the rotation axis so that the clutch teeth mesh with the meshing teeth. , the clutch teeth are engaged or separated from the first transmission component, where: When the clutch teeth are engaged with the first transmission component, the clutch teeth drive the first transmission component to rotate and the meshing teeth to rotate, so that the cylinder rotates and the first transmission component drives the The piston makes reciprocating motion, switching the main body of the electric hammer to the hammer drill state; When the clutch teeth are separated from the first transmission component, the clutch teeth drive the cylinder to rotate through the meshing teeth, switching the electric hammer body to the drilling state. 6. An electric hammer clutch device according to claim 1, characterized in that the knob assembly drives the clutch teeth to slide axially along the rotation axis to separate the clutch teeth from the meshing teeth. , the clutch teeth are engaged with the first transmission component, and the toothed end is engaged or separated from the meshing teeth, wherein: When the toothed end is separated from the meshing teeth, the cylinder performs a radial rotation and the electric hammer body switches to the angle adjustment state; When the toothed end is engaged with the meshing teeth, the cylinder is stationary, and the clutch teeth drive the first transmission component to rotate, so that the first transmission component drives the piston to make reciprocating movements, and the electric motor is moved back and forth. Hammer switches to hammer state.