TWI720760B - Power tool strike group - Google Patents

Abstract

The present invention is a striking assembly of a power tool, which includes a main body, a driving part and a tool shaft, wherein the main body includes a striking part and an elastic part, the elastic part is arranged inside the striking part, and the driving part is provided with Inside the striking member and sleeved on the elastic member, the cam groove of the driving member is locked with the cam structure of the body through a ball, and the first position of the cam groove of the cam groove faces the second at least one cam groove The extension direction of the position is at an included angle with the tangential direction of the driving member. Since the driving member is sleeved on the elastic member, the striking group can make the cam groove have a smaller included angle under the premise of the same overall size. The actuation process of the ball is smoother, so as to enhance the effectiveness of the strike group, so as to provide a strike group with a power tool.

Description

Power tool strike group

The invention relates to a device for transmitting impact force to the blade of a screwdriver or a nut socket wrench, in particular to a striking group of a power tool.

Press, the high-torque impact structure of the power tool shown in the Republic of China Patent No. M319826, please refer to Figure 9 and Figure 10. The high-torque impact structure 90 includes a drive shaft 91, a hammer block 92 and A return spring 93, wherein the outer surface of the transmission shaft 91 is provided with two spiral grooves 911, the hammer block 92 is an annular member, sleeved on the transmission shaft 91, and the hammer block 92 is on the inner periphery Two spiral grooves 921 respectively corresponding to the two spiral grooves 911 are provided, and a ball 94 is provided between each spiral groove 911 and one of the spiral grooves 921, and the ball 94 can be in the corresponding spiral groove 911 and Moving between the spiral grooves 921, the return spring 93 is sleeved on the transmission shaft 91, and the return spring 93 abuts against the hammer block 92 along an axial direction of the transmission shaft 91, the hammer block 92 can It rotates relative to the return spring 93.

When the transmission shaft 91 is driven to rotate by a power mechanism, the hammer block 92 is driven to rotate through the two balls 94, and further drives an output shaft that abuts against the hammer block 92. When the output shaft is in operation due to The resistance gradually increases to stop rotating. The hammer block 92 will stop rotating. As the transmission shaft 91 continues to rotate, the two balls 94 will move between the corresponding spiral groove 911 and the spiral groove 921 and drive it. The hammer block 92 moves along the axial direction toward the transmission shaft 91 and compresses the return spring 93, and is separated from the output shaft, and then receives the elastic force of the return spring 93 to return the hammer block 92 in the opposite direction. Push and impact the output shaft, so that the workpiece that the output shaft acts on by the impact, such as a bolt, can be completely locked to achieve the effect of the torque value set by the user.

However, since the return spring 93 of the high-torque impact structure 90 of the existing electric tool is sleeved on the transmission shaft 91, the transmission shaft 91 has a smaller outer diameter. Therefore, as shown in FIG. 11, the transmission shaft 91 The angle θ formed between the spiral grooves 911 obliquely extending toward both sides and the horizontal direction is large. In other words, the smaller outer diameter of the transmission shaft 91 makes the spiral lead of the spiral grooves 911 large and causes the The included angle θ is large, so the two balls 94 will receive greater resistance during the movement, so that the hammer block 92 compresses the return spring 93 in the axial direction and does not work smoothly, which reduces the use efficiency of the existing electric tools. In addition, due to the smaller outer diameter of the transmission shaft 91, in order to reduce the value of the included angle θ as much as possible, the distance I ₀ between the two spiral grooves 911 must be reduced as much as possible (that is, the two spiral grooves 911 are very close). When the above-mentioned balls 94 are subjected to a large force during the movement in the corresponding spiral groove 911, it is easy to cause the gap to be broken by any of the balls 94 to form a hole, or in another case, in order to avoid the distance I ₀ If it is too small to reduce the width of each spiral groove 911 and the diameter of the ball 94, the ball 94 receives a greater force when moving in the corresponding spiral groove 911, which may cause the ball 94 itself to be broken. Both situations will lead to the existing problem. The high-torque impact structure 90 of the electric tool fails and cannot be used continuously. In summary, the high-torque impact structure 90 of the existing electric tool does have its points to be improved.

In order to solve the problem of the high torsion impact structure of the existing electric tool, the ball will receive greater resistance during the movement, so that the hammer block compresses the return spring in the axial direction and the actuation process is not smooth, which reduces the use efficiency of the electric tool , And it is easy to damage the spiral grooves and balls of the transmission shaft. The present invention provides a power tool strike group, which effectively improves the above problems, which are further explained as follows.

The present invention is a striking assembly of a power tool, which includes: a body including a striking piece and an elastic piece, wherein the striking piece is provided with a cam structure and a striking portion, and the cam structure is formed with the striking portion Arranged at intervals, the elastic piece is arranged inside the striking piece; A driving member, the driving member is in a cylindrical shape, the driving member is movably combined with the main body, the driving member extends into the inside of the striking member, and is sleeved on the elastic member, and the outer surface of the driving member At least one cam groove is recessed, the at least one cam groove and the cam structure are locked by a ball; and a tool shaft, the tool shaft is movably connected with the body, and the tool shaft and the striker The striker leaned against each other.

In the striking assembly of the above power tool, the body is provided with a mandrel, the striking member is provided with a through hole extending in the axial direction, the through hole is for the mandrel to pass through, and the inner diameter of the through hole is smaller than the outer diameter of the driving member path.

In the striking assembly of the power tool, the striking part and the cam structure are arranged in a front and rear arrangement along the axial direction of the striking member.

Further, in the striking assembly of the power tool, the at least one cam groove includes a first position of the cam groove and a second position of the at least one cam groove. The first position of the cam groove extends toward the second position of the at least one cam groove. The tangential direction of the driving element is an included angle, and the included angle is between 10 degrees and 35 degrees.

Furthermore, in the striking group of the power tool, the included angle is 18 degrees.

Preferably, in the striking assembly of the above-mentioned power tool, the striking portion and the cam structure are integrally formed, and the cam structure is at least one cam groove penetrating the striker radially, the at least one cam groove and the At least one cam groove of the driving member is locked through the ball phase, and the body includes a sleeve, and the sleeve is sleeved on the outside of the striking member, so that the ball is between the driving member and the sleeve.

Furthermore, in the striking assembly of the power tool, the striking member is convexly provided with a plurality of engaging parts, the sleeve is convexly provided with a plurality of engaging blocks, and the plurality of engaging blocks are engaged with the plurality of engaging parts.

Preferably, in the striking assembly of the above-mentioned power tool, the striking part is provided with a strengthening ring and two striking blocks, the strengthening ring is arranged on a side of the striking part away from the cam structure, and the two striking blocks are convexly arranged at intervals On the inner periphery of the strengthening ring.

Preferably, in the striking assembly of the above power tool, the cam structure is a cam ring, the cam ring assembly is arranged inside the striking member, and one end of the cam ring forms at least one set of cam rims, the at least one cam rim It is locked with the at least one cam groove of the driving part through the ball.

With the above technical features, the striking assembly of the power tool provided by the present invention is sheathed on the elastic part through the driving part, so that the striking assembly has a larger outer diameter under the premise that the overall size of the striking assembly is the same. Therefore, when the stroke of the striking member is the same, the cam grooves of the driving member can extend a longer length along the outer periphery of the driving member, so as to reduce the angle of the cam grooves and make the actuation process of the ball smoother. In order to improve the effectiveness of the striking group, in addition, because the driving member has a larger outer diameter, a larger gap can be retained between the two cam grooves. In addition, under this structure, the ball and the cam groove themselves are less stressed Naturally, it is not easy to cause the problem of broken holes or ball breaking. In summary, the present invention effectively improves the high torsion impact structure of the existing electric tool. The ball will receive greater resistance during the movement process, so that the hammer block The action process of compressing the return spring in the axial direction is not smooth, which reduces the shortcomings of the use efficiency of the electric tool, thereby providing a striking group of the power tool.

10: body

11: Strikes

110: cam groove

110A: Cam ring

111: open

112: Strike Department

113: Card Slot

114, 114A: the first position of the cam structure

115, 115A: the second position of the cam structure

116: hit block

117: Through hole

118: accommodating slot

119: Meshing part

119A: Protruding part

12: Elastic parts

13: Mandrel

14: sleeve

141: fixed parts

142: meshing block

15: Strengthening ring

20: Driver

201: Ball

21: binding end

22: cam groove

221: Cam groove first position

222: Cam groove second position

23: Combination groove

30: Tool shaft

31: Limit slot

32: Force block

33: output

501: Bolt

90: High-torque impact structure

91: drive shaft

911: Spiral groove

92: Hammer Block

921: Spiral Groove

93: return spring

94: Ball

φ, θ: included angle

D ₁ : Through hole inner diameter

D ₂ : Outer diameter

I ₀ , I ₁ : spacing

Fig. 1 is a perspective view of the first preferred embodiment of the present invention.

Figure 2 is a perspective exploded view of the first preferred embodiment of the present invention.

Fig. 3 is an exploded perspective view of the first preferred embodiment of the present invention from another perspective.

Fig. 3A is an expanded schematic view of the cam groove of the driving member of the first preferred embodiment of the present invention.

Fig. 4 is a partially enlarged side sectional view of the first preferred embodiment of the present invention.

Fig. 5 is an end sectional view of the first preferred embodiment of the present invention along the A-A cutting plane line.

Fig. 6 is a schematic diagram of the operation of the first preferred embodiment of the present invention.

Fig. 7 is an exploded perspective view of the second preferred embodiment of the present invention.

Fig. 8 is a side sectional view of the second preferred embodiment of the present invention.

Fig. 9 is a side sectional view of a high-torque impact structure of a conventional electric tool.

Fig. 10 is a perspective view of a transmission shaft of a conventional electric tool with a high-torque impact structure.

Fig. 11 is a schematic view showing the unfolding of the spiral groove of the transmission shaft of the high-torque impact structure of the existing electric tool.

In order to understand the technical features and practical effects of the present invention in detail, and to implement it in accordance with the content of the specification, the preferred embodiment shown in the drawings is further described in detail as follows: the present invention is a striking group of a power tool, which The first preferred embodiment is shown in FIGS. 1 to 3, which includes a body 10, a driving member 20, and a tool shaft 30, wherein: please refer to FIGS. 2 to 4, the body 10 includes a The striking member 11, an elastic member 12, a mandrel 13, and a sleeve 14, wherein the striking member 11 is a cylindrical shell, and is provided with a cam structure, an opening 111, a receiving groove 118, and a striking portion 112 And a latching groove 113, wherein in the first preferred embodiment of the present invention, the cam structure is two cam grooves 110, the two cam grooves 110 are spaced through the outer periphery of the percussion member 11, and An accommodating space formed inside the percussion member 11 is connected. The cam grooves 110 are slightly triangular in shape, and each cam groove 110 includes a first position 114 of a cam structure and a second position 115 of two cam structures. The first position 114 of the structure is located between the second positions 115 of the two cam structures, and the first position 114 of the cam structure is located on the striking member 11, and is opposite to the second position 115 of the two cam structures along the axial direction of the striking member 11 The different positions make the first position 114 of the cam structure and the second position 115 of the two cam structures located at the three end points of the triangle, and the first position 114 of the cam structure of the two cam grooves 110 are in a radial straight line. On the other hand, the second position 115 of each cam structure of each cam groove 110 is also linearly opposite to the second position 115 of one of the cam structures of the other cam groove 110, and further, the first position of the cam structure of each cam groove 110 114 relative to the two cam structure The second position 115 is close to a rear end of the striking member 11, and the second position 115 of the two cam structures of each cam groove 110 is close to a front end of the striking member 11 relative to the first position 114 of the cam structure.

The opening 111 is provided at the rear end of the percussion member 11, and the opening 111 communicates with the accommodating space of the percussion member 11; as shown in FIG. 4, the accommodating groove 118 is provided inside the percussion member 11, and The accommodating space of the percussion member 11 is in communication, and the accommodating groove 118 and the opening 111 are linearly opposed to each other along the axial direction; the percussion portion 112 is provided at the front end of the percussion member 11 and is close to the second position 115 of each cam structure , The striking portion 112 and the cam structure (two cam grooves 110) are arranged in a front and rear arrangement, and the striking portion 112 protrudes radially from the outer surface of the striking piece 11, and as shown in FIG. 3, the The striking portion 112 forms a strengthening ring 15 away from the front end of the cam structure, and the striking portion 112 is provided with two striking blocks 116 and a through hole 117. The two striking blocks 116 are protruding on the inner periphery of the strengthening ring 15 at intervals, The two striking blocks 116 are opposed to each other along the radial direction of the striking member 11, and each striking block 116 has two striking surfaces. The through hole 117 is located on the axis of the striking member 11, and the through hole 117 penetrates in the axial direction. 118 striking part 112 and communicated to the receiving groove, the through hole 117 and having a smooth inner peripheral edge of a through hole inner diameter D _1, and the through hole is smaller than the diameter D1 of the inner diameter of the opening 111; the engaging groove 113 is annularly recessed on the outer surface of the striking member 11 and located between the opening 111 and the two cam grooves 110 so that the two cam grooves 110 are located between the striking portion 112 and the catch groove 113.

Further, in the first preferred embodiment of the present invention, the cam structure formed by the striking portion 112 and the two cam grooves 110 is manufactured integrally, and since the striking portion 112 and the two cam grooves 110 are formed The front and rear arrangement, and the through hole 117 has a smooth inner periphery, so that the percussion member 11 of the first preferred embodiment of the present invention has the advantage of being easy to manufacture; preferably, the strengthening ring 15 connects the two The striking block 116 improves the structural strength of the striking portion 112, thereby increasing the service life of the striking piece 11.

Please refer to FIGS. 2 to 4, the elastic member 12 is a compression spring, the elastic member 12 is disposed inside the striking member 11 through the opening 111, and the front end of the elastic member 12 passes through the accommodating groove 118 and abut against the striking portion 112; the mandrel 13 passes through the elastic member 12 from the opening 111 and is connected to the The hole 117 protrudes from the front end of the striking portion 112; the sleeve 14 is sleeved on the outer surface of the striking member 11 and surrounds the two cam grooves 110, and the front end of the sleeve 14 is connected to the front end of the striking portion 112. The rear end abuts against each other, and a fixing member 141 is combined with the latching groove 113, so that the sleeve 14 is interposed between the striking portion 112 and the fixing element 141, thereby preventing the sleeve 14 from moving away from the striking element 11 Falling off. In the preferred embodiment, the fixing member 141 is a C-ring.

Furthermore, as shown in FIGS. 2 and 3, the striking member 11 is provided with a plurality of engaging portions 119, and the plurality of engaging portions 119 are projected at intervals on the rear side of the striking portion 112 (as described above, the striking portion 112 The outer surface of the striking member 11 protrudes in the radial direction); on the other hand, the front end of the sleeve 14 is protruded with a plurality of engaging blocks 142 at intervals, so that the front end of the sleeve 14 and the rear end of the striking part 112 When abutting, the plurality of engaging portions 119 and the plurality of engaging blocks 142 engage with each other, so that the sleeve 14 and the striking member 11 will not rotate relative to each other.

Please refer to FIGS. 2 to 4, the driving member 20 is combined with the main body 10 and has a cylindrical shape. The driving member 20 extends into the striking member 11 from the opening 111 and is sleeved on the elastic member 12 And abut against it, so that the driving member 20 is movably combined with the striking member 11, in other words, the outer diameter D _{2 of} the driving member 20 is smaller than the inner diameter of the opening 111, but the outer diameter of the driving member 20 D _{2 is} greater than the inner diameter D _{1 of} the through hole. The driving member 20 is provided with a coupling end 21, two cam grooves 22 and a coupling groove 23, wherein the coupling end 21 is provided at the rear end of the driving member 20 and extends out of the opening In addition, 111 is engaged with a driving mechanism of a power tool, so that the driving member 20 is rotated.

The two cam grooves 22 are recessed on the outer surface of the driving member 20 at intervals. Each cam groove 22 includes a first position 221 of a cam groove and a second position 222 of two cam grooves. As shown in FIG. The first position 221 of the cam groove is linearly opposite to the first position 114 of the cam structure of one of the cam grooves 110. As shown in FIG. 2, the second position 222 of the two cam grooves is located close to the first position 221 of the cam groove. At the rear end of the driving member 20, each cam groove 22 is formed in a V shape. Each cam groove 22 and the corresponding cam groove 110 are locked and combined by a ball 201, which is derived from the striking member 11 outer On the side, after passing through the two cam grooves 110, it is set at the overlap of the first position 114 of the two cam structures and the first position 221 of the two cam grooves, so as to lock the driving member 20 and the percussion member 11, and then pass through the sleeve after completion. The barrel 14 and the fixing member 141 cover the outside of the two cam grooves 110 to prevent the two balls 201 from falling out; the coupling groove 23 is formed concavely from the front end of the driving member 20, so that the elastic member 12 can accommodate It is placed in the coupling groove 23 so that the driving member 20 is sleeved on the outside of the elastic member 12 and the mandrel 13 abuts against the bottom of the coupling groove 23.

Furthermore, as shown in FIG. 3A, each cam groove 22 is formed from the direction in which the first cam groove 221 extends toward the second position 222 of each cam groove, and the horizontal direction (that is, the tangential direction of the driving member 20). The included angle φ; compared with the included angle θ formed by the spiral grooves 911 of the transmission shaft 91 of the high-torque impact structure 90 of the conventional electric tool as shown in FIGS. 9 to 11, the driving member 20 of the present invention is sleeved in The outside of the elastic member 12, and the transmission shaft 91 of the existing high torsion impact structure 90 is located inside the return spring 93. Therefore, when the overall structural dimensions of the tool are the same, the outer diameter of the driving member 20 of the present invention is larger than that of the existing The outer diameter of the drive shaft 91 of the high-torque impact structure 90, and the outer periphery of the drive member 20 is larger than the outer peripheral edge of the drive shaft 91. As a result, if the percussion member 11 (corresponding to the existing high-torque impact structure 90 The hammer block 92) moves the same distance in the axial direction, and the extendable length of each cam groove 22 is greater than the extendable length of each spiral groove 911, so that the included angle φ of each cam groove 22 is smaller than that of each spiral groove 911. The included angle θ enables the two balls 201 of the present invention to move on the two cam grooves 22, so that the striking member 11 moves in the axial direction more smoothly, and improves the effectiveness of the striking group of the present invention.

In the first preferred embodiment of the present invention, the included angle φ of each cam groove 22 is between 10 degrees and 35 degrees, preferably 18 degrees.

Please refer to Figures 2 to 5, the tool shaft 30 is combined with the body 10, the rear end of the tool shaft 30 abuts against the striking portion 112 of the striking member 11, and the tool shaft 30 includes a limit stop Groove 31, two force-receiving blocks 32, and an output end 33, wherein the limiting groove 31 is recessed at the rear end of the tool shaft 30, and the limiting groove 31 is provided on the axis of the tool shaft 30, so that The tool shaft 30 is opposite to the body 10 When abutting, the front end of the spindle 13 can be inserted into the limiting groove 31, so that the body 10, the driving member 20 and the tool shaft 30 are located on the same axis; the two force-receiving blocks 32 respectively protrude radially on On both sides of the rear end of the tool shaft 30, each force receiving block 32 has two force receiving surfaces. The two force receiving surfaces are respectively located on both sides of the force receiving block 32, and when the tool shaft 30 abuts against the body 10, The two force-receiving blocks 32 are combined with the striking portion 112, and as shown in FIG. 5, they respectively abut against one of the striking blocks 116; the output end 33 is arranged at the front end of the tool shaft 30, so as to perform a work on a workpiece. use.

Please refer to Figure 1, Figure 4 to Figure 6, when the driving member 20 drives the tool shaft 30 to rotate, because the two balls 201 lock the striking member 11 and the driving member 20 each other, therefore, the driving The member 20 will drive the body 10 to rotate, and the body 10 will abut against the corresponding force surface of one of the force blocks 32 through each of the striking blocks 116 of the striking member 11, thereby further pushing the tool The shaft 30 rotates. When the tool shaft 30 receives resistance, the main body 10 cannot rotate due to the abutment between the two striking blocks 116 and the two force-receiving blocks 32.

At this time, as shown in FIGS. 4 and 6, each ball 201 will be pushed by the force of the relative action between the striking member 11 and the driving member 20, and slide in the corresponding cam groove 22 and cam groove 110, and Due to the difference in the shape of the cam grooves 22 and the cam grooves 110, the percussion member 11 of the main body 10 is driven to move to the rear end toward the driving member 20, and the elastic member 12 is compressed. When the balls 201 move, the corresponding cam groove 22 is moved. The second position 222 of one of the cam grooves coincides with the second position 115 of a relative cam structure in the corresponding cam groove 110, and the striking portion 112 is completely separated from the tool shaft 30. Then, because the two striking blocks 116 and the The two force blocks 32 are separated and lose resistance. The restoring force of the compressed elastic member 12 will push the striking member 11 toward the front end, while the driving member 20 continues to drive the main body 10 to rotate. Therefore, when the striking When the part 112 is recombined with the tool shaft 30, the two striking blocks 116 will respectively strike one of the force-bearing blocks 32 at different positions from the original, so as to produce a striking effect and provide the user with a power tool. For processing, such as locking bolts, the bolts can be completely locked to achieve the effect of the torque value set by the user.

Further, the driving member 20 can rotate forward and backward in different directions according to the connected driving mechanism. When the driving member 20 rotates in the reverse direction, the difference from the previous paragraph is that the two striking blocks 116 correspond to the corresponding force The block 32 will abut against the force-receiving surface with different striking surfaces, and the two balls 201 will move to respectively make the corresponding cam groove 22 and the cam groove 110 different cam groove second position 222 and cam structure second position 115 The coincidence can achieve the effect of moving the main body 10 toward the rear end toward the driving member 20 to be separated from the tool shaft 30.

Please refer to FIG. 7, the difference between the second preferred embodiment of the present invention and the first preferred embodiment is that the cam structure of the percussion member 11 is a cam ring 110A, which is derived from the percussion member The rear end of the cam ring 11 is inserted into the accommodating space of the striking member 11, and the cam ring 110A can be fixedly connected to the striking member 11 through a plurality of pins 501. The front end of the cam ring 110A is provided with two protruding parts 119A. The protruding portions 119A are opposed to the front end of the cam ring 110A in a radial direction, so that the cam ring 110A forms a set of cam edges on both sides of each of the protruding portions 119A, and each set of cam edges is in a V shape Corresponding to one of the cam grooves 22 of the driving member 20, each set of cam edges includes a cam structure first position 114A and two cam structure second positions 115A located on both sides of the cam structure first position 114A, each of the cams The second position 115A of the structure is located at the end of the set of cam edges close to one of the protrusions 119A. In other words, the two sides of each protrusion 119A are respectively the second position 115A of the cam structure of the two sets of cam edges. The first position 114A of the cam structure corresponds to the first position 221 of the corresponding cam groove 22. Preferably, as shown in FIG. 8, the driving member 20 is also sleeved on the elastic member 12 Externally, the driving member 20 has a larger outer periphery, and each of the cam grooves 22 has a smaller included angle, as described in the first preferred embodiment.

In addition, the striking part 112 of the striking member 11 of the second preferred embodiment of the present invention can also be provided with a strengthening ring as in the first preferred embodiment, so that the two striking blocks of the striking part 112 are protruding from the strengthening ring at intervals. On the inner periphery.

With the above technical features, the striking assembly of the power tool provided by the present invention is sleeved on the outside of the elastic member 12 through the drive member 20, so that the striking assembly has the same overall size, and the drive member 20 has a relatively large size. A large outer diameter D ₂ , therefore, when the stroke of the striking member 11 is the same, the cam grooves 22 of the driving member 20 can extend a longer length along the outer periphery of the driving member 20, thereby reducing the cam grooves 22 The included angle φ of the ball 201 makes the actuation process of the ball 201 smoother, thereby enhancing the effectiveness of the striking group. In addition, as shown in FIG. 3A, since the driving member 20 has a larger outer diameter D ₂ , the two cam grooves 22 are _{A large distance I 1} can be kept between them. In addition, under this structure, the ball 201 and the cam groove 22 themselves are less stressed, so it is naturally not easy to cause the problem of broken holes or broken balls 201. In summary, the present invention is effective The ball 94, which improves the high-torque impact structure of the existing electric tool, will receive greater resistance during the movement, so that the hammer block 92 compresses the return spring 93 in the axial direction and does not act smoothly, which reduces the power tool’s performance. The shortcomings of the use of efficiency, in order to provide a power tool strike group.

The above are only preferred embodiments of the present invention, and do not limit the present invention in any form. Anyone with ordinary knowledge in the relevant technical field can use the present invention without departing from the scope of the technical solution proposed by the present invention. The disclosed technical content has partially changed or modified equivalent embodiments without departing from the technical solution content of the present invention, and all still fall within the scope of the technical solution of the present invention.

10: body

110: cam groove

112: Strike Department

114: Cam structure first position

117: Through hole

118: accommodating slot

12: Elastic parts

13: Mandrel

14: sleeve

141: fixed parts

20: Driver

201: Ball

21: binding end

22: cam groove

221: Cam groove first position

23: Combination groove

30: Tool shaft

32: Force block

D ₁ : Through hole inner diameter

D ₂ : Outer diameter

Claims (10)

A power tool strike group, which includes: A body, the body includes a striking piece and an elastic piece, wherein the striking piece is provided with a cam structure and a striking portion, the cam structure and the striking portion are arranged at intervals, and the elastic piece is arranged inside the striking piece; A driving member, the driving member is in a cylindrical shape, the driving member is movably combined with the main body, the driving member extends into the inside of the striking member, and is sleeved on the elastic member, and the outer surface of the driving member At least one cam groove is recessed, and the at least one cam groove is locked with the cam structure through a ball; and A tool shaft is movably connected with the main body, and the tool shaft abuts against the striking part of the striking member. The striking assembly of a power tool according to claim 1, wherein the body is provided with a mandrel, the striker is penetrated with a through hole in the axial direction, the through hole is for the mandrel to pass through, and the inner diameter of the through hole It is smaller than the outer diameter of the driving member. The striking assembly of a power tool according to claim 1, wherein the striking part and the cam structure are arranged in a front and rear arrangement along the axial direction of the striking member. The striking assembly of a power tool according to claim 1, wherein the at least one cam groove includes a first cam groove position and at least one second cam groove position, and the first position of the cam groove faces the second position of the at least one cam groove An included angle between the extending direction of and the tangential direction of the driving member, and the included angle is between 10 degrees and 35 degrees. The striking group of the power tool according to claim 4, wherein the included angle is 18 degrees. The striking assembly of a power tool according to any one of claims 1 to 5, wherein the striking part and the cam structure are integrally formed, and the cam structure is at least one cam groove radially penetrating the striking member, The at least one cam groove and the at least one cam groove of the driving member are locked through the ball. The body includes a sleeve that is sleeved on the outside of the striking member so that the ball is interposed between the driving member and the sleeve. Between the tubes. The striking set of a power tool according to claim 6, wherein the striking member is convexly provided with a plurality of engaging parts, the sleeve is convexly provided with a plurality of engaging blocks, and the plurality of engaging blocks are engaged with the plurality of engaging parts . The striking set of a power tool according to claim 6, wherein the striking part is provided with a strengthening ring and two striking blocks, the strengthening ring is arranged on the side of the striking part away from the cam structure, and the two striking blocks are convexly spaced apart Set on the inner periphery of the strengthening ring. The striking assembly of a power tool according to any one of claims 1 to 5, wherein the cam structure is a cam ring, the cam ring assembly is arranged inside the striking member, and one end of the cam ring forms at least one set of cams The at least one cam edge and the at least one cam groove of the driving member are locked by the ball. The striking set of a power tool according to claim 9, wherein the striking part is provided with a strengthening ring and two striking blocks, the strengthening ring is arranged on the side of the striking part away from the cam structure, and the two striking blocks are convexly spaced apart Set on the inner periphery of the strengthening ring.

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