Mode switching mechanism and power tool thereof

Abstract

The application discloses a power tool, and relates to the technical field of construction equipment, which comprises a mode switching mechanism, wherein the mode switching mechanism comprises a conversion sleeve, a first switching piece, a second switching piece, a second elastic member and an operating member; and any one of the first cantilever and the second cantilever is formed with a support part extending towards the other one, the support part abuts against the first cantilever or the second cantilever so that the first cantilever and the second cantilever have a gap for accommodating the eccentric pin. The power tool has the advantages that the support part extending towards the other one is formed in any one of the first switching piece and the second switching piece, the two switching pieces have a certain gap, the eccentric pin on the operating member can be inserted into the gap more easily, and the two switching pieces do not need to be separated in advance, so that the power tool is simple to assemble.

Description

Technical Field This application relates to the field of construction equipment technology, and in particular to a mode switching mechanism and its power tool. Background Technology Electric hammers are a common type of power tool. Users can select different working modes of electric hammers according to different usage scenarios. Existing electric hammers use a knob to drive two switching plates to move, thereby switching the transmission mode of the transmission mechanism and thus realizing the switching of working modes.

[0001] Existing electric hammer drills use a tension spring between the two switching plates to enable synchronous movement. When one switching plate is moved by the knob, the tension spring causes the other switching plate to move as well. However, this structure causes the two switching plates to remain pressed together. To allow the knob to move one of the switching plates, the two plates must be separated before the knob is inserted between them during assembly, making the assembly process rather cumbersome.

[0002] Therefore, it is indeed necessary to provide an improved power tool to overcome the shortcomings of the prior art. Utility Model Content To address the shortcomings of existing technologies, the purpose of this application is to provide a power tool in which either the first or the second switching plate forms a support portion extending toward the other, creating a certain gap between the two switching plates. The eccentric pin on the operating component can be easily inserted into this gap without prior separation of the two switching plates, simplifying assembly.

[0003] The technical solution adopted by this application to solve the problem of the prior art is: a power tool, comprising: case; The motor is housed within the housing; A transmission mechanism for transmitting the power generated by the motor; An output mechanism is used to receive the working head and drive the working head to rotate under the drive of the transmission mechanism; An impact mechanism, driven by the transmission mechanism, applies an impact force to the working head; A mode switching mechanism is operably configured in the housing, and the mode switching mechanism changes the working mode of the working head by switching the power transmission mode of the transmission mechanism. The mode switching mechanism includes: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the transmission mechanism; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

[0004] A further improvement is that the support portion is integrally bent from the second switching piece.

[0005] A further improvement is as follows: the second switching piece also has a fourth cantilever located away from the first cantilever, a bending notch formed by bending the support portion, one end of the second elastic element is connected to the first cantilever, and the other end passes through the bending notch and is connected to the fourth cantilever.

[0006] A further improvement is that the second elastic element is positioned near the side of the first and fourth cantilever arms.

[0007] A further improvement is as follows: the mode switching mechanism further includes a guide rod disposed on the inner wall of the housing and extending axially, the first switching plate and the second switching plate being sleeved on the guide rod and capable of reciprocating along the length extension direction of the guide rod.

[0008] A further improvement is proposed: the second elastic element is a tension spring.

[0009] A further improvement is as follows: the transmission mechanism includes a first toothed surface for driving the output mechanism and a second toothed surface for driving the impact mechanism, and the conversion sleeve can selectively engage with at least one of the first toothed surface and the second toothed surface.

[0010] A further improvement is as follows: when the conversion sleeve engages with the first toothed surface, the power tool is in drill stop mode; When the conversion sleeve engages with the second toothed surface, the power tool is in pickaxe stop mode; When the conversion sleeve is simultaneously engaged with the first toothed surface and the second toothed surface, the power tool is in hammer drill mode.

[0011] Another technical solution of this application is: a power tool, comprising: case; The motor is housed within the housing; A transmission mechanism for transmitting the power generated by the motor to the working head for external operation; A mode switching mechanism is operably configured in the housing, and the mode switching mechanism changes the working mode of the working head by switching the power transmission mode of the transmission mechanism. The mode switching mechanism includes: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the transmission mechanism; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

[0012] A further improvement is that the power tool further includes an output mechanism that drives the working head to rotate under the drive of the transmission mechanism, and an impact mechanism driven by the transmission mechanism to apply an impact force to the working head.

[0013] A further improvement is to operate the mode switching mechanism to switch the power of the transmission mechanism to be transmitted only to the output mechanism, so that the power tool is in the drill stop mode; Operate the mode switching mechanism to switch the power of the transmission mechanism to be transmitted only to the impact mechanism, and the power tool is in the pick and chisel stop mode; Operate the mode switching mechanism to switch the power transmission of the transmission mechanism to the output mechanism and the impact mechanism, and the power tool is in hammer drill mode.

[0014] Another technical solution of this application is: a mode switching mechanism, which is applied to an electric hammer and changes the working mode of the electric hammer by switching the power transmission mode of the electric hammer, the mode switching mechanism comprising: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the electric hammer; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

[0015] A further improvement is proposed: the second elastic element is a tension spring.

[0016] A further improvement is proposed: the operating element is a function knob.

[0017] Compared with the prior art, this application has the following beneficial effects: In the power tool of this application, either the first switching plate or the second switching plate forms a support portion extending toward the other. This support portion allows for a certain gap between the first switching plate and the second switching plate. This gap allows for easier insertion of an eccentric pin between the first switching plate and the second switching plate, thereby simplifying assembly and improving assembly efficiency. Attached Figure Description The specific embodiments of this application will be described in further detail below with reference to the accompanying drawings: Figure 1 This is a three-dimensional schematic diagram of the power tool of this application; Figure 2 yes Figure 1 A cross-sectional view of the power tool shown; Figure 3 yes Figure 1 A front view of the power tool shown; Figure 4 yes Figure 1A three-dimensional schematic diagram of the power tool shown after one side of its outer casing has been removed; Figure 5 yes Figure 1 A three-dimensional schematic diagram of the power tool transmission mechanism shown in the figure; Figure 6 yes Figure 1 A cross-sectional view of the power tool transmission mechanism and impact mechanism shown in the figure; Figure 7 yes Figure 1 A cross-sectional view of the power tool transmission mechanism and impact mechanism shown in the figure in another state; Figure 8 yes Figure 1 An exploded schematic diagram of the power tool impact mechanism shown in the figure; Figure 9 yes Figure 1 A cross-sectional view of the power tool rocker arm bearing at its maximum front and rear swing angles. Figure 10 yes Figure 1 A cross-sectional view of the power tool composite limiting component shown in the figure; Figure 11 yes Figure 1 A three-dimensional schematic diagram of the power tool shown in the image from another direction; Figure 12 yes Figure 1 The diagram shows the connection between the power tool mode switching mechanism and the transmission mechanism. Figure 13 yes Figure 1 A three-dimensional schematic diagram of the power tool mode switching mechanism shown in the figure; Figure 14 yes Figure 1 A three-dimensional schematic diagram of the power tool mode switching mechanism shown in the figure from another direction; Figure 15 yes Figure 1 The diagram shows the position and state of the mode switching mechanism of the power tool in pickaxe stop mode. Figure 16 yes Figure 1 The diagram shows the position and status of the mode switching mechanism of the power tool in drill stop mode. Figure 17 yes Figure 1 The diagram shows the position and status of the mode switching mechanism of the power tool in hammer drill mode. Figure 18 yes Figure 1 An exploded view of the power tool operating components assembled with the housing shown in the diagram; Figure 19 yes Figure 1 A schematic diagram of the gear position markings and mounting holes on the power tool housing shown in the figure; Figure 20 yes Figure 1 An exploded view of the assembly of the power tool operating component and housing in another direction; Figure 21 yes Figure 1 The diagram shows an exploded view of the power tool operating component and housing assembly from another direction.

[0018] Meaning of the reference numerals in the diagram: 100. Power tools; 200. Work heads; 10. Housing; 11. Main body; 12. Grip; 13. Secondary handle; 14. Mounting hole; 141. Locking notch; 142. Removal position; 143. Removal notch; 144. Arc segment. 20. Motor; 21. Rotor shaft; 30. Transmission mechanism; 31. Transmission shaft; 311. Transmission tooth profile; 32. First bevel gear; 33. Second bevel gear; 34. Rocker arm bearing; 341. Inner ring of bearing; 3411. Second tooth profile; 342. Outer ring of bearing; 343. Rocker arm; 35. Transmission gear set; 351. First transmission gear; 3511. First tooth profile; 352. Second transmission gear. 40. Output mechanism; 41. Receiving cavity; 42. Chuck assembly; 50. Impact mechanism; 51. Cylinder; 511. Third limiting part; 512. Second guide part; 52. Piston; 53. Hammer; 531. Limiting groove; 54. Impact rod; 541. Limiting flange; 55. Gas space; 56. Composite limiting component; 56a. First opening; 56b. Second opening; 561. First limiting part; 562. Second limiting part; 5621. First annular groove; 5622. First elastic component; 563. Inner sealing part; 5631. Second annular groove; 5632. First sealing component; 564. Outer sealing part; 5641. Third annular groove; 5642. Second sealing component; 565. Outer buffer part; 5651. Fourth annular groove; 5652. Shock absorber; 566. Positioning part; 5661. Abutting surface; 5662. Positioning component; 567. First guide part; 568. Fixed flange; 60. Mode switching mechanism; 61. Operating component; 611. Eccentric pin; 612. Moving component; 6121. Cylindrical part; 613. Biasing component; 614. Receiving groove; 615. Disassembly protrusion; 62. First switching plate; 621. First cantilever; 622. Third cantilever; 63. Second switching plate; 631. Second cantilever; 632. Fourth cantilever; 633. Support part; 634. Bending notch; 64. Conversion sleeve; 641. Force-bearing flange; 642. Internal toothed surface; 65. Guide rod; 66. Second elastic component; 70. Battery pack. Detailed Implementation To make the technical solution and beneficial effects of this application more apparent and understandable, a detailed description is provided below by listing specific embodiments. Unless otherwise defined, the technical and scientific terms used herein have the same meanings as those in the technical field to which this application pertains.

[0019] The terminology used in this application is for the purpose of describing specific embodiments only and is not intended to limit the application. For example, terms such as "upper," "lower," "front," and "rear" that indicate orientation or positional relationship are based solely on the orientation or positional relationship shown in the accompanying drawings and are used only for the convenience of describing the application and simplifying the description, and are not intended to indicate or imply that the device referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the application.

[0020] See Figures 1-2 As shown, the power tool 100 disclosed in this application can be an electric hammer, which includes a housing 10 forming the outer contour of the power tool 100, a motor 20 for providing power to the power tool 100, a transmission mechanism 30 for transmitting the power of the motor 20 forward, an output mechanism 40 for driving the working head 200 disposed on the power tool 100 to rotate, an impact mechanism 50 for applying impact force to the working head 200, and an energy source for providing power to the power tool 100. In the embodiments of this application, the energy source can be a battery pack 70 or AC mains power; its implementation is not limited here, as long as it can provide power to the power tool 100.

[0021] To facilitate a clear explanation of the specific content of the technical solution of this application, the following definitions are made: the central axis of the working head 200 and the direction parallel to it are defined as the axial direction; the radial direction of the circumference with the central axis of the working head 200 as the central axis is defined as the radial direction; the output direction of the working head 200 is defined as the forward direction; and the direction opposite to the output direction of the working head 200 is defined as the rearward direction.

[0022] See Figure 1 The housing 10 forms the outline of the power tool 100, and is roughly gun-shaped. The housing 10 may include a main body 11 for housing major components such as the motor 20, transmission mechanism 30, output mechanism 40, and impact mechanism 50, as well as a grip 12 for the user to hold. The housing 10 may also be provided with a secondary handle 13 so that the user can hold the power tool 100 more securely during operation.

[0023] See Figure 2 , Figure 3 Motor 20 is used to receive power from an energy source and generate rotational power.

[0024] See Figure 2 , Figure 3The transmission mechanism 30 is used to enable the motor 20 to drive the output mechanism 40 and the impact mechanism 50 respectively, so as to transmit the power generated by the motor 20 to the output mechanism 40 and the impact mechanism 50.

[0025] In one embodiment, the transmission mechanism 30 includes a transmission shaft 31 extending in the front-rear direction and rotatably supported on the inner wall of the main body 11, a first bevel gear 32 sleeved on the rotor shaft 21 of the motor 20 and rotating with the motor 20, and a second bevel gear 33 sleeved on the transmission shaft 31 and meshing with the first bevel gear 32. The motor 20 drives the transmission shaft 31 to rotate around its own axis through the meshing first bevel gear 32 and second bevel gear 33.

[0026] The transmission mechanism 30 also includes a rocker arm bearing 34 for transmitting power to the impact mechanism 50 and a transmission gear set 35 for transmitting power to the output mechanism 40. Driven by the transmission shaft 31, the rocker arm bearing 34 drives the impact mechanism to reciprocate in the forward-backward direction. The transmission gear set 35 includes a first transmission gear 351 connected to the transmission shaft 31 and a second transmission gear 352 connected to the output mechanism 40. The transmission shaft 31 drives the output mechanism 40 to rotate around its own axis through the meshing of the first transmission gear 351 and the second transmission gear 352.

[0027] See Figure 2 , Figure 3 The output mechanism 40 rotates under the drive of the transmission mechanism 30. Its front end houses the working head 200 for external output operations and drives the working head 200 to rotate together.

[0028] In one embodiment, the working head 200, driven by the output mechanism 40, can rotate at a speed ranging from 1000 r / min to 1200 r / min. For example, the working head 200 can rotate at a speed of 1100 r / min.

[0029] In one embodiment, the output mechanism 40 includes a receiving cavity 41 extending in the front-rear direction and a chuck assembly 42 sleeved on the outer periphery of the receiving cavity 41 to hold the working head 200 within the receiving cavity 41. In this embodiment, the receiving cavity 41 has a generally tubular structure, with an internal cavity for receiving the working head 200, and the chuck assembly 42 for axially limiting the working head 200 to prevent it from detaching from the receiving cavity 41. The chuck assembly 42 can be specifically implemented as the actual structure of the chuck assembly disclosed in application number CN200610107479.4. Of course, the implementation of the chuck assembly 42 is not limited here; any implementation that can hold the working head 200 on the receiving cavity 41 is acceptable.

[0030] In one embodiment, the overall length of the power tool 100 can be defined as the axial distance from the rear end face of the housing to the front end face of the chuck assembly, and the overall length L1 of the power tool 100 ranges from 270mm to 290mm. For example, the overall length of the power tool 100 can be 270mm, 280mm, 290mm, etc. In some embodiments, the overall length of the power tool 100 can be specifically implemented as 284mm.

[0031] See Figures 4-9 The impact mechanism 50 can be driven by the transmission mechanism 30 to reciprocate in the front-back direction, thereby applying an impact force in the front-back direction to the working head 200.

[0032] In one embodiment, the impact mechanism 50 includes a cylinder 51, a piston 52, a hammer 53, and an impact rod 54. The cylinder 51 is also generally tubular, with an internal cavity for housing the piston 52, hammer 53, and impact rod 54. In this embodiment, the cylinder 51 can be integrally formed with the aforementioned receiving cavity 41, with its internal cavity housing the piston 52, hammer 53, impact rod 54, and working head 200. Of course, in other embodiments, the cylinder 51 can also be separately arranged from the receiving cavity 41. The transmission mechanism 30 is connected to the piston 52 and drives it to reciprocate in the front-back direction, thereby driving the hammer 53 and impact rod 54 to reciprocate along the inner wall of the cylinder 51, so that the impact rod 54 can apply a front-back impact force to the working head 200, and the working head 200 outputs an impact torque.

[0033] The cylinder 51 is rotatably mounted on the inner wall of the housing 10 via a bearing assembly, and the second transmission gear 352 in the transmission mechanism 30 is sleeved on the outer circumference of the cylinder 51. The power generated by the motor 20 is transmitted to the cylinder 51 sequentially through the first bevel gear 32, the second bevel gear 33, the transmission shaft 31, the first transmission gear 351, and the second transmission gear 352, driving the cylinder 51 to rotate around its own axis. The cylinder 51 then drives the working head 200, which is housed in the receiving cavity 41, to rotate as well, and the working head 200 outputs rotational torque.

[0034] In one embodiment, the speed range of the motor 20 can be 26,000 r / min - 27,000 r / min. For example, the speed of the motor 20 can be 26,000 r / min, 26,500 r / min, 27,000 r / min, etc.

[0035] In one embodiment, the transmission ratio between the first bevel gear 32 and the second bevel gear 33 can be in the range of 3.5:1 to 4:1. In some embodiments, the transmission ratio between the first bevel gear 32 and the second bevel gear 33 can be specifically implemented as 34:9.

[0036] In one embodiment, the transmission ratio between the first transmission gear 351 and the second transmission gear 352 can be in the range of 4:1 to 5:1. In some embodiments, the transmission ratio between the first transmission gear 351 and the second transmission gear 352 can be specifically implemented as 49:11.

[0037] The piston 52 is capable of reciprocating in the front-to-back direction under the drive of the aforementioned rocker arm bearing 34. The rocker arm bearing 34 includes an inner bearing ring 341 that rotates with the drive shaft 31, an outer bearing ring 342 that is pivotally fitted onto the inner bearing ring 341, and a rocker arm 343 connected to the outer bearing ring 342. In one embodiment, one end of the rocker arm 343 is integrally formed with the outer bearing ring 342, and the other end is hinged to the rear end of the piston 52. When the drive shaft 31 drives the inner bearing ring 341 to rotate, the rocker arm 343 will swing back and forth with the outer bearing ring 342, thereby driving the piston 52 to reciprocate along the inner wall of the cylinder 51.

[0038] In one embodiment, the length L2 of the rocker arm 343 can be in the range of 35mm-45mm. For example, the length L2 of the rocker arm 343 is 35mm, 45mm, etc. In some embodiments, the length L2 of the rocker arm 343 can be specifically implemented as 40mm.

[0039] In one embodiment, the angle formed by the swing trajectory of the rocker arm 343 when it swings back and forth is the swing angle α of the rocker arm bearing 34, and the swing angle α can be in the range of 16°-18°. For example, the swing angle α of the rocker arm bearing 34 can be 16°, 16.5°, 17°, 17.5°, or 18°, etc.

[0040] In one embodiment, the oscillation frequency of the pendulum 343 can be in the range of 4800 times / min to 5000 times / min. For example, the oscillation frequency of the pendulum 343 is 4800 times / min, 5000 times / min, etc. In some embodiments, the oscillation frequency of the pendulum 343 can be specifically implemented as 4900 times / min.

[0041] In one embodiment, the maximum stroke L3 of the piston 52 can range from 16mm to 18mm. For example, the maximum stroke L3 of the piston 52 can be 16mm, 17mm, 18mm, etc. In some embodiments, the maximum stroke L3 of the piston 52 can be specifically implemented as 17.2mm.

[0042] The hammer 53 is movably housed within the cylinder 51, and a gas space 55 with a variable volume is formed between the hammer 53 and the piston 52. Driven by the rocker arm bearing 34, the piston 52 compresses the gas within this gas space 55, increasing its internal gas pressure and thus generating an impact force. Specifically, when the drive shaft 31 drives the rocker arm 343 to swing forward, the piston 52 also moves forward along the inner wall of the cylinder 51, thereby compressing the gas space 55 between the hammer 53 and the piston 52, reducing its volume and increasing its gas pressure. When the gas pressure within the gas space 55 is sufficiently high, it can push the hammer 53 forward to strike the impact rod 54. In this embodiment, the piston 52 has an internal cavity with an open front end, the hammer 53 is housed within the cavity of the piston 52, and the gas space 55 is also located within the internal cavity of the piston 52. In other embodiments, the piston 52 and the hammer 53 may be independently housed within the cylinder 51, with the hammer 53 located in front of the piston 52.

[0043] The impact rod 54 can also be movably housed in the cylinder 51 and is located in front of the hammer 53. When the hammer 53 is pushed forward by the gas pressure, its kinetic energy is transferred to the impact rod 54, enabling the impact rod 54 to move forward and impact the working head 200 located in front of it. The working head 200 receives the impact force applied by the impact rod 54 and outputs the impact torque.

[0044] See Figure 6 , Figure 7 , Figure 10 In one embodiment, the impact mechanism 50 further includes a composite limiting member 56 housed inside the cylinder 51, which is used to axially limit the impact hammer 53 and the impact rod 54 respectively, restricting the forward displacement of the impact hammer 53 and the backward displacement of the impact rod 54. The composite limiting member 56 is fixedly connected to the inner wall of the cylinder 51, and is generally cylindrical and extends in the front-rear direction. The front end (first end) of the composite limiting member 56 has a first opening 56a, and the rear end (second end) has a second opening 56b. The rear end of the impact rod 54 can enter the cavity of the composite limiting member 56 through the first opening 56a, and the front end of the impact hammer 53 can also enter the cavity of the composite limiting member 56 through the second opening 56b and transmit power to the impact rod 54 in the cavity.

[0045] The composite limiting member 56 has a first limiting portion 561 near the first end for axially limiting the impact rod 54 to the rear. The first limiting portion 561 is an annular inclined surface formed on the inner wall of the composite limiting member 56 and extending radially inward. It is located behind the first opening 56a. A limiting flange 541 adapted to it is formed on the outer periphery of the impact rod 54. When the impact rod 54 is subjected to the force applied to it by the working head 200 and moves backward until the limiting flange 541 abuts against the first limiting portion 561, the impact rod 54 is stopped by the first limiting portion 561 and cannot continue to move backward. The impact rod 54 then reaches the rear end limit position. Furthermore, the inner wall of the cylinder 51 has a third limiting portion 511 located in front of the composite limiting member 56. Specifically, the third limiting portion 511 can be implemented as an annular inclined surface formed on the inner wall of the cylinder 51 and extending radially inward. When the impact rod 54 is subjected to the impact force applied by the hammer 53 and moves forward until the limiting flange 541 abuts against the third limiting portion 511, the impact rod 54 is stopped by the third limiting portion 511 and cannot continue to move backward, thus reaching its front limit position. By limiting the axial range of motion of the impact rod 54 through the first limiting portion 561 and the third limiting portion 511, the impact rod 54 moves within the effective impact area, thereby ensuring that the impact mechanism 50 applies a suitable impact force to the working head 200, achieving the best impact effect. Moreover, by using the third limiting portion 511 formed on the inner wall of the cylinder instead of the front guide sleeve used in existing electric hammers to limit the front limit position of the impact rod 54, the overall length of the power tool 100 can be shortened.

[0046] See Figure 7 The composite limiting member 56 has a second limiting portion 562 near the second end for axially limiting the impact hammer 53 forward. The second limiting portion 562 includes a first annular groove 5621 formed on the inner wall of the composite limiting member 56 and recessed radially outward, and a first elastic member 5622 received in the first annular groove 5621. The center portion of the first elastic member 5622 also has a central through hole that allows the impact hammer 53 and the impact rod 54 to pass through. The diameter of the central through hole is larger than the diameter of the impact rod 54 and smaller than the diameter of the front end of the impact hammer 53. The outer periphery of the impact hammer 53 has a limiting groove 531 adapted to the second limiting portion 562. When the impact hammer 53 moves forward, enters the cavity of the composite limiting member 56 through the second opening 56b, passes through the central through hole of the first elastic member 5622, and then impacts the impact rod 54, the first elastic member 5622 can be engaged in the limiting groove 531, thereby preventing the impact hammer 53 from moving backward. By engaging the punch 53 with the second limiting part 562, the impact mechanism 50 will not apply impact force to the working head 200 when the power tool 100 is unloaded, thereby avoiding the phenomenon of the power tool 100 being unloaded.

[0047] The inner wall of the composite limiting member 56 is also provided with an inner sealing part 563, which is used to cooperate with the impact rod 54 to form a sealing structure, thereby preventing the lubricating grease inside the housing 10 from leaking outward through the gap between the inner wall of the composite limiting member 56 and the outer wall of the impact rod 54. The inner sealing part 563 includes a second annular groove 5631 formed in the inner wall of the composite limiting member 56 and a first sealing member 5632 housed in the second annular groove 5631. The outer side of the first sealing member 5632 abuts against the inner wall of the second annular groove 5631, and the inner side abuts against the outer periphery of the impact rod 54. During the movement of the impact rod 54 between the front end limit position and the rear end limit position, the inner side of the first sealing member 5632 always remains in contact with the outer periphery of the impact rod 54, thereby ensuring the sealing effect of the sealing structure formed by the inner sealing part 563 and the impact rod 54.

[0048] The outer periphery of the composite limiting member 56 is also provided with an outer sealing portion 564, which is used to cooperate with the cylinder 51 to form a sealing structure, thereby preventing the lubricating grease inside the housing 10 from leaking outward through the gap between the inner wall of the cylinder 51 and the outer wall of the composite limiting member 56. The outer sealing portion 564 includes a third annular groove 5641 formed on the outer peripheral surface of the composite limiting member 56 and a second sealing member 5642 received in the third annular groove 5641, wherein the inner side of the second sealing member 5642 abuts against the inner wall of the third annular groove 5641, and the outer side abuts against the inner wall of the cylinder 51.

[0049] An outer buffer portion 565 is also provided on the outer periphery of the composite limiting member 56, which is used to form a shock-absorbing structure between the composite limiting member 56 and the cylinder 51 to prevent damage to the two due to the force. The outer buffer portion 565 includes a fourth annular groove 5651 formed on the outer peripheral surface of the composite limiting member 56 and a shock absorber 5652 housed in the fourth annular groove 5651. The shock absorber 5652 is compressibly clamped between the cylinder and the composite limiting member. When the hammer 53 strikes the impact rod 54 forward, some kinetic energy is transferred to the composite limiting member 56, causing it to move forward in a small range. The composite limiting member 56 will compress the shock absorber 5652, thereby forming a buffer between the composite limiting member 56 and the cylinder 51.

[0050] The outer periphery of the composite limiting member 56 is also provided with a positioning part 566, which is used to lock the position of the composite limiting member 56 and prevent it from moving backward relative to the cylinder 51 due to external force. The positioning part 566 includes an abutment surface 5661 formed on the outer peripheral surface of the composite limiting member 56 and a positioning member 5662 disposed between the cylinder 51 and the composite limiting member 56. One end of the positioning member 5662 abuts against the abutment surface 5661, and the other end is embedded in the inner wall of the cylinder 51. In one embodiment, the positioning member 5662 can be specifically implemented as an elastic retaining ring, which is engaged in a retaining groove in the inner wall of the cylinder 51, and the front side of the elastic retaining ring abuts against the abutment surface 5661. This structure can prevent the composite limiting member 56 from moving backward relative to the cylinder 51. In one embodiment, a fixing flange 568 may be formed on the outer periphery of the composite limiting member 56. The rear end face of the fixing flange 568 may serve as an abutment surface 5661, used to cooperate with the positioning member 5662 to prevent the composite limiting member 56 from moving backward relative to the cylinder 51 due to external force. The front end face of the fixing flange 568 may cooperate with the cylinder 51 to clamp the aforementioned shock absorber 5652, thereby achieving a shock absorption effect.

[0051] The inner wall of the composite limiting member 56 is also provided with a first guide portion 567, which supports the impact rod 54, enabling it to perform linear reciprocating motion in the front-back direction. The first guide portion 567 includes an annular surface formed on the inner wall of the composite limiting member 56 and extending in the front-back direction. The outer peripheral surface of the impact rod 54 is supported on this annular surface and can move along the length extension direction of the annular surface, so that it can move linearly in the front-back direction when impacted by the hammer 53, thereby maximizing the transfer of kinetic energy to the working head 200 and enabling it to output a sufficiently large impact torque. The inner wall of the cylinder 51 is also formed with a second guide portion 512 located in front of the first guide portion 567, which also supports the impact rod 54, enabling it to perform linear reciprocating motion in the front-back direction. The second guide portion 512 includes an annular surface formed on the inner wall of the cylinder 51 and extending in the front-back direction. The outer peripheral surface of the impact rod 54 is supported on this annular surface and can move along the length extension direction of the annular surface. In this embodiment, the first guide portion 567 supports the rear half of the impact rod 54, and the second guide portion 512 supports the front half of the impact rod 54. Both support the impact rod 54 simultaneously, enabling it to move linearly in the front-back direction when it is struck by the impact hammer 53, without tilting, otherwise the impact energy will be lost.

[0052] Existing electric hammers use two limiting sleeves to guide and limit the movement of the hammer 53 and the impact rod 54. Therefore, the concentricity requirement between the two limiting sleeves is high when they are assembled, which makes the assembly of existing electric hammers difficult. In contrast, the power tool 100 disclosed in this application uses a composite limiting component 56 to guide and limit both the hammer 53 and the impact rod 54. The central axes of the first guide part 567 and the second guide part 512 coincide, which reduces the difficulty of assembly and also improves the concentricity of the hammer 53 and the impact rod 54 during movement.

[0053] See Figure 10 In some embodiments, the inner wall of the composite limiting member 56 may be sequentially formed from back to front with a second limiting part 562, an inner sealing part 563, a first guide part 567, and a first limiting part 561; the outer periphery of the composite limiting member 56 may be sequentially formed from back to front with a positioning part 566, an outer buffer part 565, and an outer sealing part 564. These structural designs enable the composite limiting member 56 to not only guide and limit the impact rod 54, but also limit the impact hammer 53 axially. In addition, it can buffer and dampen the impact movement inside the impact mechanism 50 to prevent damage to components due to long-term impact. Furthermore, the composite limiting member 56 can prevent the lubricating grease that lubricates the transmission mechanism 30 from leaking through the inner and outer walls of the cylinder 51, thereby ensuring the effective operation of the power tool 100. Furthermore, in the power tool 100 disclosed in this application, the composite limiting member 56 can replace the seal, two limiting sleeves, guide sleeves and other components in the existing electric hammer, which can greatly shorten the overall length of the power tool 100.

[0054] See Figures 11-21 As shown, the power tool 100 disclosed in this application also includes a mode switching mechanism 60 disposed on the housing 10, which changes the working mode of the working head 200 by switching the power transmission mode of the transmission mechanism 30. Under the action of the mode switching mechanism 60, the power tool 100 can switch between four mode positions: pickaxe stop, intermediate stop, hammer drill stop, and drill stop. Of course, the number of mode positions of the power tool 100 is not limited to this; it can have two mode positions, three mode positions, or even more than four mode positions. The mode switching mechanism 60 includes an operating member 61 rotatably disposed on the housing 10, a first switching plate 62 and a second switching plate 63 that can move synchronously under the drive of the operating member 61, and a conversion sleeve 64 that can move between a first position and a second position driven by the first switching plate 62 and the second switching plate 63. By moving the conversion sleeve 64, the power transmission mode of the transmission mechanism 30 can be switched, thereby changing the working mode of the working head 200.

[0055] In one embodiment, in the hammer drill mode of the power tool 100, the ratio of the number of times the impact mechanism 50 impacts the working head 200 per unit time to the number of rotations of the working head 200 driven by the output mechanism 40 can be defined as the hammer drill ratio of the power tool 100. This hammer drill ratio can range from 4:1 to 5:1. For example, the hammer drill ratio of the power tool 100 may be 4:1, 4.5:1, or 5:1. In some embodiments, the hammer drill ratio of the power tool 100 may specifically be 4.4545:1.

[0056] It should be noted that by controlling the hammer-to-drill ratio of the working head 200 to 4:1-5:1 and the swing angle of the rocker arm bearing to 16°-18°, not only can the contact angle between the cutting edge of the working head 200 and the drill hole be more suitable during hammering, thus improving drilling efficiency, but it can also ensure that the working head 200 has more appropriate impact energy. This enhances the drilling efficiency of the power tool 100 while preventing damage to the workpiece due to excessive operating torque. For example, when drilling a tile, if the hammer-to-drill ratio of the power tool 100 is not properly matched, the tile is very likely to break during drilling.

[0057] The operating element 61 has a generally circular plate-like structure and is rotatably fitted into the mounting hole 14 opened in the housing 10. The mounting hole 14 can be a generally circular through hole recessed inward from the end face of the housing 10. In one embodiment, the operating element 61 can be a function knob. The outer wall of the housing 10 is formed with position markings representing pickaxe stop, intermediate stop, hammer drill stop, and drill stop, respectively. The user can rotate the function knob to align it with one of the position markings to indicate the current working mode of the power tool 100.

[0058] The first switching plate 62 and the second switching plate 63 are movably disposed on the inner wall of the housing 10 via a guide rod 65. The guide rod 65 is fixed to the inner wall of the housing 10 by screws or other connecting members, and the length extension direction of the guide rod 65 is parallel to the length extension direction of the aforementioned drive shaft 31. The first switching plate 62 and the second switching plate 63 are sleeved on the guide rod 65 and move along the length extension direction of the guide rod 65 under the drive of the operating member 61. Both the first switching plate 62 and the second switching plate 63 have a generally U-shaped plate structure. The first switching plate 62 has a first cantilever 621 and a third cantilever 622 arranged parallel to each other, and the second switching plate 63 has a second cantilever 631 and a fourth cantilever 632 arranged parallel to each other, wherein the first cantilever 621 and the second cantilever 631 are arranged close to each other. The inner wall of the aforementioned operating member 61 has an eccentric pin 611 disposed off-center from its center. The eccentric pin 611 extends toward the first switching plate 62 and the second switching plate 63 and is clamped between the first cantilever 621 and the second cantilever 631. When the user rotates the operating component 61, the eccentric pin 611 can push the first cantilever 621 or the second cantilever 631, thereby causing the first switching plate 62 or the second switching plate 63 to move linearly along the length extension direction of the guide rod 65. In this embodiment, to ensure that the first switching plate 62 and the second switching plate 63 move synchronously, a second elastic element 66 can be provided between the first switching plate 62 and the second switching plate 63. The second elastic element 66 applies an elastic force towards the first switching plate 62 and the second switching plate 63 respectively, so that when one of the first switching plate 62 and the second switching plate 63 moves linearly by being driven by the eccentric pin 611, the other moves linearly in the same direction under the elastic force of the second elastic element 66. The second elastic element 66 can be specifically implemented as a tension spring, one end of which is connected to the second cantilever 631 and the other end is connected to the third cantilever 622. The tension spring applies a tension force to the two cantilever arms respectively, causing them to tend to move closer to each other. This tension force can cause the first switching plate 62 and the second switching plate 63 to move synchronously. The tension spring can also be connected at one end to the first cantilever 621 and at the other end to the fourth cantilever 632, so that the two cantilever arms tend to move closer to each other. Of course, the implementation of the second elastic element 66 is not limited to this, as long as it can realize the synchronous movement of the first switching piece 62 and the second switching piece 63, it is a specific implementation of this application.

[0059] The conversion sleeve 64 has a generally cylindrical structure and is movably sleeved on the outer periphery of the drive shaft 31. A force-bearing flange 641 is formed on the outer periphery of the conversion sleeve 64. The force-bearing flange 641 is clamped between the first cantilever 621 and the second cantilever 631 to receive the force of the first switching plate 62 or the second switching plate 63, thereby allowing the conversion sleeve 64 to move linearly between the first position and the second position along the length extension direction of the drive shaft 31.

[0060] The inner wall of the conversion sleeve 64 has an internal tooth profile 642, and the transmission shaft 31 has a transmission tooth profile 311 that is always meshed with the internal tooth profile 642. The first transmission gear 351 has a first tooth profile 3511 extending toward the conversion sleeve 64, and the inner ring 341 of the rocker arm bearing 34 has a second tooth profile 3411 extending toward the conversion sleeve 64. The internal tooth profile 642 can mesh with the first tooth profile 3511 and the second tooth profile 3411 to transmit power.

[0061] like Figure 15 As shown, when the conversion sleeve 64 is pushed to the first position, the internal toothed surface 642 is engaged with the transmission toothed surface 311 and the second toothed surface 3411, and disengaged from the first toothed surface 3511. At this time, the power of the motor 20 is first transmitted to the transmission shaft 31, and then transmitted to the rocker arm bearing 34 through the engaged transmission toothed surface 311 and the second toothed surface 3411, thereby driving the impact mechanism 50 to reciprocate in the front-back direction, thus applying an impact force in the front-back direction to the working head 200. However, the force transmission path between the motor 20 and the output mechanism 40 is broken, and the output mechanism 40 cannot drive the working head 200 to rotate together. Therefore, when the conversion sleeve 64 is in the first position, the power tool 100 is switched to the pickaxe stop mode.

[0062] like Figure 16 As shown, when the conversion sleeve 64 is pushed to the second position, the internal toothed surface 642 is engaged with the transmission toothed surface 311 and the first toothed surface 3511, and disengaged from the second toothed surface 3411. At this time, the power of the motor 20 is first transmitted to the transmission shaft 31, and then transmitted to the first transmission gear 351 through the engaged transmission toothed surface 311 and the first toothed surface 3511, thereby driving the output mechanism 40 to rotate around its own axis and causing the working head 200 to rotate together. However, the force transmission path between the motor 20 and the impact mechanism 50 is broken, and the impact mechanism 50 cannot apply an impact force in the front-to-back direction to the working head 200. Therefore, when the conversion sleeve 64 is in the second position, the power tool 100 is switched to drilling mode.

[0063] like Figure 17As shown, when the conversion sleeve 64 is pushed between the first and second positions, the internal toothed surface 642 is simultaneously engaged with the transmission toothed surface 311, the first toothed surface 3511, and the second toothed surface 3411. At this time, the power from the motor 20 is first transmitted to the transmission shaft 31, then through the engaged transmission toothed surfaces 311 and 3411 to the rocker arm bearing 34, and finally through the engaged transmission toothed surfaces 311 and 3511 to the first transmission gear 351. This drives the impact mechanism 50 to reciprocate in the front-to-back direction, applying a front-to-back impact force to the working head 200, and driving the output mechanism 40 to rotate around its own axis, causing the working head 200 to rotate as well. Therefore, when the conversion sleeve 64 is between the first and second positions, the power tool 100 is switched to the hammer drill mode.

[0064] See Figure 12 In one embodiment of this application, the user rotates the operating component 61, causing the eccentric pin 611 located between the first switching plate 62 and the second switching plate 63 to push the conversion sleeve 64 to reciprocate between a first position and a second position via the first switching plate 62 and the second switching plate 63, thereby switching the operating mode of the power tool 100. In one embodiment, the first switching plate 62 and the second switching plate 63 move synchronously via a second elastic member 66. The second elastic member 66 can be specifically implemented as a tension spring, with its two ends connected to the first switching plate 62 and the second switching plate 63 respectively to apply an elastic force that brings them closer together. When the eccentric pin 611 moves one of the first switching plate 62 and the second switching plate 63, the other will also move in the same direction under the action of the second elastic member 66. However, although the second elastic element 66 can ensure that the first switching piece 62 and the second switching piece 63 move synchronously, it also causes the power tool 100 to pull the first switching piece 62 and the second switching piece 63 together during assembly. During assembly, the first switching piece 62 and the second switching piece 63 need to be manually pulled apart by a certain distance so that the eccentric pin 611 on the operating piece 61 can be inserted into the gap between them.

[0065] In order to avoid the above-mentioned potential problems, in one embodiment of this application, a support portion 633 extending toward the other can be formed in either the first switching piece 62 or the second switching piece 63. The support portion 633 can make a certain gap between the first switching piece 62 and the second switching piece 63, and the gap can make it easier for the eccentric pin 611 to be inserted between the first switching piece 62 and the second switching piece 63.

[0066] See Figure 13The support portion 633 can be formed by bending the second cantilever 631 on the second switching plate 63 toward the first switching plate 62, and the support portion 633 abuts against the side wall of the first cantilever 621, thereby forming the gap for receiving the eccentric pin 611. Furthermore, after bending the support portion 633, the second switching plate 63 will have a bending notch 634, which allows one end of the second elastic member 66 to pass through and connect to the fourth cantilever 632. This arrangement allows the second elastic member 66 to be positioned close to the sides of the first switching plate 62 and the second switching plate 63, thereby facilitating the assembly of the mode switching mechanism 60. In another embodiment, the support portion 633 can also be formed by bending the first cantilever 621 toward the second switching plate 63 and abutting against the second cantilever 631, thereby forming the gap for receiving the eccentric pin 611. Of course, the implementation of the support part 633 is not limited to this. As long as it can form a gap between the first switching piece 62 and the second switching piece 63 for accommodating the eccentric pin 611, it is a specific implementation of this application.

[0067] See Figures 18-21 The housing 10 has a mounting hole 14 recessed inward from its end face on its side wall, and the operating member 61 is detachably rotatably supported in the mounting hole 14. The housing 10 also has multiple position markings arranged around the mounting hole 14 to indicate the current working mode of the power tool 100. In a clockwise direction, the multiple position markings are chisel stop, intermediate stop, hammer drill stop, and drill stop. The side wall of the mounting hole 14 also has locking notches 141 corresponding to the above-mentioned position markings. The operating member 61 is provided with a movable member 612 and a biasing member 613 to lock the operating member 61 in the locking notch 141 corresponding to the position marking.

[0068] The sidewall of the operating member 61 has a receiving groove 614 extending toward the inner wall of the mounting hole 14 and open at one end. The biasing member 613 and the movable member 612 are sequentially received in the receiving groove 614. The biasing member 613 can be specifically implemented as a compression spring, one end of which abuts against the inner wall of the receiving groove 614, and the other end abuts against the inner sidewall of the movable member 612. The compression spring applies a biasing force to the movable member 612 toward the locking notch 141, so that the movable member 612 can engage with the locking notch 141. In one embodiment of this application, the sidewall of the mounting hole 14 has four locking notches 141, and each locking notch 141 is smoothly connected to the sidewall of the mounting hole 14 by an arc segment to form a closed ring structure. The locking notch 141 can be specifically implemented as an arc groove structure. The movable part 612 has a cylindrical part 6121 that is adapted to the locking notch 141. The compression spring biases the movable part 612 so that the cylindrical part 6121 can engage with the locking notch 141.

[0069] The outer periphery of the mounting hole 14 also has a disassembly position 142. When the user rotates the operating member 61 to the drill stop position mark, the movable member 612 is locked to the locking notch 141 corresponding to the drill stop. If the user continues to rotate the operating member 61 clockwise, the mode switching mechanism 60 is switched to the disassembly position 142, at which point the user can remove the operating member 61 from the mounting hole 14. In one embodiment of this application, the disassembly position 142 and the locking notch 141 corresponding to the drill stop are also smoothly connected by an arc segment. When the user rotates the operating member 61 to move it from the locking notch 141 to the disassembly position 142, the arc segment 144 between them can squeeze the movable member 612 to counteract the biasing force applied to it by the biasing member 613, so that the movable member 612 can move away from the locking notch 141, thereby allowing the cylindrical portion 6121 on the movable member 612 to disengage from the locking notch 141 and enter the disassembly position 142. This design allows users to switch directly from the working mode position to the disassembly position simply by continuing to rotate the operating part 61, without having to manually press the movable part 612, making operation convenient.

[0070] like Figure 18 , Figure 19 , Figure 20 As shown, the operating member 61 is detachably and rotatably supported within the mounting hole 14 by a matching disassembly protrusion 615 and disassembly notch 143. The sidewall of the operating member 61 has multiple disassembly protrusions 615 extending toward the mounting hole 14, while the inner wall of the mounting hole 14 has corresponding disassembly notches 143. Their shapes, sizes, and positions correspond one-to-one. When assembling the operating member 61 into the mounting hole 14, the disassembly protrusions 615 and disassembly notches 143 must first be aligned. Then, the operating member 61 is pushed into the power tool 100, causing the disassembly protrusions 615 to insert into the aligned disassembly notches 143. Afterward, the operating member 61 is rotated to another position. At this point, because the disassembly protrusions 615 and disassembly notches 143 cannot be aligned one-to-one, the disassembly protrusions 615 are blocked by the inner wall of the housing 10 and cannot be pulled out. This arrangement prevents the operating member 61 from separating from the housing 10 and allows it to be rotatably supported within the mounting hole 14. When it is necessary to remove the operating component 61, the user needs to rotate the operating component 61 to the disassembly position 142. At this position, the disassembly protrusion 615 and the disassembly notch 143 can be aligned one by one. The disassembly protrusion 615 can be pulled out through the disassembly notch 143 without being blocked by the inner wall of the housing 10. The user only needs to pull the operating component 61 outward to separate the operating component 61 from the housing 10 and complete the removal of the operating component 61.

[0071] In one embodiment of this application, the sidewall of the operating member 61 has three disassembly protrusions 615 of different widths, and the inner wall of the mounting hole 14 has three disassembly notches 143 of different groove widths. The groove width and position of the three disassembly notches 143 correspond one-to-one with the width and position of the three disassembly protrusions 615. When the operating member 61 is rotated to a position other than the disassembly position 142, at least one pair of disassembly protrusions 615 and disassembly notches 143 are misaligned, and the operating member 61 cannot be separated from the housing 10. When the operating member 61 is rotated to the disassembly position 142, all three pairs of disassembly protrusions 615 and disassembly notches 143 are aligned, and the user can pull the operating member 61 outward to separate it from the housing 10. The disassembly protrusions 615 and disassembly notches 143 can also be modified by changing their shape, size, number, relative position, etc., so that the operating member 61 can only be removed when rotated to the disassembly position 142. Of course, the implementation of disassembling the protrusion 615 and the disassembly notch 143 is not limited to this. Any implementation that can achieve the detachable rotational support of the operating member 62 in the mounting hole 14 can be used as a specific implementation of this application.

[0072] It should be understood that the above embodiments are exemplary and are not intended to encompass all possible implementations included in the claims. Various modifications and changes can be made to the above embodiments without departing from the scope of this disclosure. Similarly, the various technical features of the above embodiments can be arbitrarily combined to form other embodiments of this application that may not be explicitly described. Therefore, the above embodiments only illustrate several implementations of this application and do not limit the scope of protection of this patent application.

Claims

1. A power tool, characterized in that, include: case; The motor is housed within the housing; A transmission mechanism for transmitting the power generated by the motor; An output mechanism is used to receive the working head and drive the working head to rotate under the drive of the transmission mechanism; An impact mechanism, driven by the transmission mechanism, applies an impact force to the working head; A mode switching mechanism is operably configured in the housing, and the mode switching mechanism changes the working mode of the working head by switching the power transmission mode of the transmission mechanism. The mode switching mechanism includes: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the transmission mechanism; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

2. The power tool according to claim 1, characterized in that: The support portion is formed by integrally bending the second switching plate.

3. The power tool according to claim 2, characterized in that: The second switching piece also has a fourth cantilever disposed away from the first cantilever, a bending notch formed by bending the support portion, one end of the second elastic member being connected to the first cantilever, and the other end passing through the bending notch and being connected to the fourth cantilever.

4. The power tool according to claim 3, characterized in that: The second elastic element is disposed near the side of the first cantilever and the fourth cantilever.

5. The power tool according to claim 1, characterized in that: The mode switching mechanism further includes a guide rod disposed on the inner wall of the housing and extending axially. The first switching plate and the second switching plate are sleeved on the guide rod and can reciprocate along the length extension direction of the guide rod.

6. The power tool according to claim 1, characterized in that: The second elastic element is a tension spring.

7. The power tool according to claim 1, characterized in that: The transmission mechanism includes a first toothed surface for driving the output mechanism and a second toothed surface for driving the impact mechanism. The conversion sleeve can selectively engage with at least one of the first toothed surface and the second toothed surface.

8. The power tool according to claim 7, characterized in that: When the conversion sleeve engages with the first toothed surface, the power tool is in drill stop mode; When the conversion sleeve engages with the second toothed surface, the power tool is in pickaxe stop mode; When the conversion sleeve is simultaneously engaged with the first toothed surface and the second toothed surface, the power tool is in hammer drill mode.

9. A power tool, characterized in that, include: case; The motor is housed within the housing; A transmission mechanism for transmitting the power generated by the motor to the working head for external operation; A mode switching mechanism is operably configured in the housing, and the mode switching mechanism changes the working mode of the working head by switching the power transmission mode of the transmission mechanism. The mode switching mechanism includes: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the transmission mechanism; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

10. The power tool according to claim 9, characterized in that: The power tool also includes an output mechanism that drives the working head to rotate under the drive of the transmission mechanism, and an impact mechanism driven by the transmission mechanism to apply an impact force to the working head.

11. The power tool according to claim 10, characterized in that: Operate the mode switching mechanism to switch the power of the transmission mechanism to be transmitted only to the output mechanism, and the power tool is in drill stop mode; Operate the mode switching mechanism to switch the power of the transmission mechanism to be transmitted only to the impact mechanism, and the power tool is in the pick and chisel stop mode; Operate the mode switching mechanism to switch the power transmission of the transmission mechanism to the output mechanism and the impact mechanism, and the power tool is in hammer drill mode.

12. A mode switching mechanism applied to an electric hammer, which changes the operating mode of the electric hammer by switching the power transmission mode of the electric hammer, characterized in that, The mode switching mechanism includes: A switching sleeve that can move between a first position and a second position to switch the power transmission mode of the electric hammer; A first switching plate has a first cantilever extending toward the switching sleeve, the first cantilever being able to push the switching sleeve to a first position; The second switching plate has a second cantilever extending toward the switching sleeve, the second cantilever being able to push the switching sleeve to a second position; The second elastic element applies an elastic force to the first switching plate and the second switching plate to bring them closer together, so that the first switching plate and the second switching plate move synchronously. An operating component has an eccentric pin disposed between the first cantilever and the second cantilever. Operating the operating component can drive the eccentric pin to move the first switching plate and the second switching plate between the first position and the second position. Either the first cantilever or the second cantilever has a support portion extending toward the other, and the support portion abuts against the first cantilever or the second cantilever to create a gap between the first cantilever and the second cantilever for accommodating the eccentric pin.

13. The mode switching mechanism according to claim 12, characterized in that: The second elastic element is a tension spring.

14. The mode switching mechanism according to claim 12, characterized in that: The operating component is a function knob.

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