Power tool

Abstract

The application discloses a power tool, and relates to the technical field of construction equipment, which comprises a shell, a motor, a transmission mechanism, an output mechanism and an impact mechanism, wherein the shell comprises a main shell and a cover, the main shell is provided with an inspection opening, and the cover can cover the inspection opening; the power tool is further provided with a first sealing element and a second sealing element, and the first sealing element and the second sealing element are combined to form a sealing path which can block the internal space of the power tool from being communicated with the external environment through the inspection opening. In the power tool, the inspection opening and the first opening corresponding in position are formed on the main shell and the gear box shell respectively, and the inspection opening and the first opening are sealed by the cover and the first sealing element and the second sealing element. The split sealing mode can improve the sealing property of the shell, is convenient to install and disassemble, and can not affect the working stability of the internal components.

Description

[Technical Field]

[0001] This application relates to the field of construction equipment technology, and in particular to a power tool. [Background Technology]

[0002] Heavy-duty hammer and pick power tools typically have access ports on their housings for easy lubrication and maintenance, and use a custom-shaped sealing ring between the top cover and the gearbox for sealing. However, for some users... Figure 28 The locking device shown in the diagram enables the locking function of the pick and chisel. When using this structure, there is interference between the top cover and the pick and chisel locking device in the disassembly direction. It is necessary to remove the handle assembly by removing additional screws to separate the locking device from the top cover before the top cover can be removed. This makes it inconvenient for machine disassembly, lubrication, inspection, etc.

[0003] Therefore, it is indeed necessary to provide an improved power tool to overcome the shortcomings of the prior art. [Summary of the Invention]

[0004] To address the shortcomings of existing technologies, the purpose of this application is to provide a power tool that uses a cover and a first and a second sealing element to seal the inspection port and the first opening. This split sealing method not only improves the sealing performance of the housing but also eliminates the need to disassemble the handle housing along with the locking mechanism beforehand, while maintaining the operational stability of its internal components.

[0005] The technical solution adopted by this application to solve the problem of the prior art is: a power tool, comprising:

[0006] A housing, comprising a main housing and a cover, wherein the main housing has an access port and the cover can cover the access port;

[0007] The first seal and the second seal, together, form a sealed path that prevents the internal space of the power tool from communicating with the external environment through the inspection port.

[0008] A further improvement is proposed: the power tool also includes:

[0009] The motor is housed within the main housing;

[0010] A transmission mechanism for transmitting the power generated by the motor;

[0011] An output mechanism is used to receive the working head and drive the working head to rotate under the drive of the transmission mechanism;

[0012] An impact mechanism, driven by the drive mechanism, applies an impact force to the working head.

[0013] A further improvement is as follows: the power tool further includes a gearbox housing housed within the main housing, and the transmission mechanism, impact mechanism, and output mechanism are distributed sequentially from back to front and are at least partially housed within the gearbox housing.

[0014] A further improvement is that the gearbox housing has a first opening, which is located radially outside at least one of the transmission mechanism, impact mechanism, and output mechanism.

[0015] A further improvement is that the main housing has an inspection port corresponding to the position of the first opening.

[0016] A further improvement is that the gearbox housing is also connected to a pressure plate for limiting the transmission mechanism, and the pressure plate partially covers the first opening.

[0017] A further improvement is that the first sealing element and the second sealing element respectively cooperate with the upper and lower end faces of the pressure plate to form a closed sealing path.

[0018] A further improvement is as follows: the gearbox housing has a first height portion and a second height portion with a height less than the first height portion, the first seal abuts against the first height portion, and the second seal abuts against the second height portion.

[0019] A further improvement is that the height difference between the first height portion and the second height portion is less than the sum of the thicknesses of the pressure plate and the second sealing element, but greater than the thickness of the pressure plate.

[0020] Another technical solution of this application is: a power tool, comprising:

[0021] A housing, comprising a main housing and a cover, wherein the main housing has an access port and the cover can cover the access port;

[0022] The first seal and the second seal, together, form a sealed path that prevents the internal space of the power tool from communicating with the external environment through the inspection port.

[0023] A further improvement is proposed: the power tool also includes:

[0024] The motor is housed within the main housing;

[0025] The working component is driven by the motor to perform external operations.

[0026] A further improvement is that the power tool also includes a gearbox housing housed in the main housing and a pressure plate connected to the gearbox housing.

[0027] A further improvement is that the first sealing element and the second sealing element respectively cooperate with the upper and lower end faces of the pressure plate to form a closed sealing path.

[0028] A further improvement is as follows: the first sealing element is an annular elastic pad, which includes a first sealing part that presses against the upper end face of the gearbox housing and the lower end face of the cover, and a second sealing part that presses against the upper end face of the pressure plate and the lower end face of the cover.

[0029] A further improvement is as follows: the second sealing element is an annular elastic pad, which includes a third sealing part that presses against the lower end face of the pressure plate and the upper end face of the gearbox housing, and a fourth sealing part that extends upward from the lower end face of the pressure plate and abuts against the first sealing element.

[0030] Compared with the prior art, this application has the following beneficial effects:

[0031] In the power tool of this application, a corresponding access port and a first opening can be formed on the main housing and the gearbox housing, respectively, and the access port and the first opening are sealed by a cover and a first sealing element and a second sealing element. The locking mechanism extending above the access port and the first opening does not interfere with the operation, and it is not necessary to disassemble the handle housing along with the locking mechanism beforehand. This separate sealing method not only improves the sealing performance of the housing but also facilitates installation and disassembly, while maintaining the operational stability of its internal components. [Image Description]

[0032] The specific embodiments of this application will be described in further detail below with reference to the accompanying drawings:

[0033] Figure 1 This is a three-dimensional schematic diagram of the power tool of this application;

[0034] Figure 2 yes Figure 1 A cross-sectional view of the power tool shown;

[0035] Figure 3 yes Figure 1 The diagram shows the connection between the power tool transmission mechanism and the impact mechanism.

[0036] Figure 4 yes Figure 1 An exploded view of the power tool impact mechanism shown in the diagram;

[0037] Figure 5 yes Figure 1 A cross-sectional view of the power tool impact mechanism shown in the figure;

[0038] Figure 6 yes Figure 1The diagram shows the first position state of each component of the power tool impact mechanism during loading.

[0039] Figure 7 yes Figure 1 The diagram shows the second position state of each component of the power tool impact mechanism during loading.

[0040] Figure 8 yes Figure 1 The diagram shows the third position state of each component of the power tool impact mechanism during loading.

[0041] Figure 9 yes Figure 1 The diagram shows the first position state of each component of the power tool impact mechanism when unloaded.

[0042] Figure 10 yes Figure 1 The diagram shows the second position state of each component of the power tool impact mechanism when unloaded.

[0043] Figure 11 yes Figure 1 The diagram shows the third position state of each component of the power tool impact mechanism when unloaded.

[0044] Figure 12 yes Figure 1 A schematic diagram showing the engagement between the power tool's working head and the locking protrusion;

[0045] Figure 13 yes Figure 12 The diagram shows the contact state between the power tool's working head and the locking protrusion.

[0046] Figure 14 yes Figure 1 A schematic diagram of a first embodiment of the power tool locking protrusion shown in the figure;

[0047] Figure 15 yes Figure 1 A schematic diagram of a second embodiment of the power tool locking protrusion shown in the figure;

[0048] Figure 16 yes Figure 1 A schematic diagram of the third embodiment of the power tool locking protrusion shown in the figure;

[0049] Figure 17 yes Figure 1 A schematic diagram of the fourth embodiment of the power tool locking protrusion shown in the figure;

[0050] Figure 18 yes Figure 1 A schematic diagram of the fifth embodiment of the power tool locking protrusion shown in the figure;

[0051] Figure 19 yes Figure 1 A schematic diagram of the sixth embodiment of the power tool locking protrusion shown in the figure;

[0052] Figure 20 yes Figure 1 A schematic diagram showing the connection between the cover and the housing of the power tool shown.

[0053] Figure 21 yes Figure 1 An exploded view of the housing, first seal, and second seal of the power tool shown in the diagram;

[0054] Figure 22 yes Figure 21 An enlarged view of the power tool shown at point A;

[0055] Figure 23 yes Figure 1 A top view of the power tool shown after removing the cover;

[0056] Figure 24 yes Figure 1 A schematic diagram of the mating of the first and second seals of the power tool shown in the figure;

[0057] Figure 25 yes Figure 1 Exploded view of the housing and gearbox housing of the power tool shown;

[0058] Figure 26 yes Figure 1 A schematic diagram of the gearbox housing structure of the power tool shown;

[0059] Figure 27 yes Figure 1 Side view of the gearbox housing of the power tool shown;

[0060] Figure 28 This is a schematic diagram of the fit between the top cover and the housing of a heavy-duty hammer or pick-type power tool in the prior art.

[0061] Meaning of the reference numerals in the diagram:

[0062] 100. Power tool; 200. Working head; 201. Locking groove;

[0063] 10. Housing; 11. Main housing; 12. Handle housing; 121. Start switch; 13. Inspection port; 14. Cover; 141. Second mounting groove; 15. Pressure plate; 151. Connecting lug; 16. First seal; 161. First sealing part; 162. Second sealing part; 17. Second seal; 171. Third sealing part; 172. Fourth sealing part; 18. Gearbox housing; 18a. First height part; 18b. Second height part; 18c. Stepped surface; 181. First opening; 182. First mounting groove; 183. Third mounting groove;

[0064] 20. Motor; 21. Rotor shaft; 22. Output gear;

[0065] 30. Transmission mechanism; 31. Reciprocating assembly; 32. Rotating assembly;

[0066] 40. Output mechanism;

[0067] 50. Impact mechanism; 51. Cylinder; 51a. Receiving cavity; 51b. Driving cavity; 511. Guide section; 512. Clearance section; 513. Stop section; 514. Locking protrusion; 5141. Abutting inclined surface; 515. First inclined cone surface; 516. Impact protrusion; 52. Piston; 53. Hammer; 54. Impact rod; 541. Front impact part; 542. Body part; 543. Rear impact part; 544. Annular groove; 545. Sealing ring.

[0068] 60. Clamping mechanism; 61. Snap-fit ​​component;

[0069] 70. Mode switching mechanism;

[0070] 80. Locking mechanism;

[0071] 90. Fastener; 91. First screw; 92. Second screw. [Detailed Implementation]

[0072] 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.

[0073] 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.

[0074] See Figures 1-2As 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, an energy source for providing energy to the power tool 100, and a mode switching mechanism 70 for switching the output mode of the power tool 100. In the power tool 100 disclosed in this application, the operation mode switching mechanism 70 can change the connection state between the transmission mechanism 30, the output mechanism 40, and the impact mechanism 50, thereby allowing the power tool 100 to switch between a pickaxe mode and a hammer drill mode.

[0075] 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.

[0076] like Figure 1 As shown, the housing 10 includes a main housing 11 and a handle housing 12. The main housing 11 is used to form the main body outline of the power tool 100 and to house the main components of the power tool 100. The handle housing 12 can form an approximate D-shape with the main housing 11. The start switch 121 of the power tool 100 can be configured in the handle housing 12. The start switch 121 can be specifically implemented as a trigger switch.

[0077] like Figure 2 As shown, the motor 20 can obtain energy from the energy source to rotate and output power to the outside. It can be housed in the main housing 11 in the vertical direction. The upper end of its rotor shaft 21 is fitted with an output gear 22 that can be connected to the transmission mechanism 30 for transmission. Power is transmitted to the outside through gear meshing.

[0078] like Figure 2 , Figure 3 As shown, the transmission mechanism 30 includes a reciprocating component 31 and a rotating component 32. The reciprocating component 31 can be connected to the impact mechanism 50 to provide impact power, and the rotating component 32 can be connected to the output mechanism 40 to provide rotational power.

[0079] In some embodiments, the reciprocating component 31 may be a crank-connecting rod structure or a rocker arm bearing structure, which can drive the impact mechanism 50 to reciprocate in the front-back direction to generate a forward impact force.

[0080] In some embodiments, the rotating component 32 may be a gear set structure that can be selectively meshed with the output gear 22, thereby allowing the output mechanism 40 to switch between a rotating state and a stationary state.

[0081] like Figure 4 , Figure 5 As shown, the impact mechanism 50 includes a cylinder 51 and a piston 52, a hammer 53, and an impact rod 54, which are housed in the cylinder 51 from back to front.

[0082] The cylinder 51 is a cylindrical structure with openings at both ends. It extends in the front-rear direction and is rotatably supported on the main housing 11 via bearings. The aforementioned rotating assembly 32 is fitted onto the outer circumferential surface of the cylinder 51, allowing the cylinder 51 to rotate around its own central axis under the drive of the transmission mechanism 30. The rear end of the working head 200 is inserted into the front end of the cylinder 51, and the two are fixed relative to each other in the circumferential direction. When the cylinder 51 is driven to rotate by the transmission mechanism 30, it also drives the working head 200 to rotate, thereby providing rotational output.

[0083] In some embodiments, the cylinder 51 has an internal cavity, which can be divided into a receiving cavity 51a and a driving cavity 51b arranged coaxially. The receiving cavity 51a is located in the front half of the cavity and is used to receive the working head 200, while the driving cavity 51b is located in the rear half of the cavity and is used to receive components such as the piston 52, the hammer 53, and the impact rod 54.

[0084] The working head 200 is housed in the aforementioned receiving cavity 51a, and the working head 200 and the cylinder 51 are fixed relative to each other in the axial and circumferential directions. The two are fixed relative to each other in the axial direction by a chuck mechanism 60, which is sleeved on the outer periphery of the front end of the cylinder 51, and uses an operable snap-fit ​​member 61 to axially snap the working head 200 into the receiving cavity 51a of the cylinder 51, thereby preventing the working head 200 from disengaging from the power tool 100 during operation. The two are relatively fixed in the circumferential direction by locking protrusions 514 formed on the inner wall of the receiving cavity 51a. The inner wall of the receiving cavity 51a has one or more locking protrusions 514 extending radially inward, and the length extension direction of the locking protrusions 514 is consistent with the length extension direction of the cylinder 51. The outer peripheral surface of the working head 200 also has a locking groove 201 extending from the rear end face towards the front. When the working head 200 is inserted into the cylinder 51, the locking groove 201 and the locking protrusions 514 must be aligned first. As the working head 200 is inserted into the cylinder 51, the locking protrusions 514 are also inserted and fitted into the locking groove 201, thereby locking the working head 200 and the cylinder 51 in the circumferential direction. When the cylinder 51 is driven to rotate, it transmits force through the locking protrusions 514 and the locking groove 201, thereby driving the working head 200 to rotate outward for output.

[0085] The piston 52 is movably housed in the cavity of the cylinder 51 and is connected to the reciprocating assembly 31. The reciprocating assembly 31 drives the piston 52 to move back and forth along the length extension direction of the cylinder 51.

[0086] The hammer 53 is movably housed in the cavity of the cylinder 51 and is positioned in front of the piston 52. When the piston 52 moves forward, it compresses the air in the cylinder 51 located between the piston 52 and the hammer 53. The compressed air pushes the hammer 53 forward and generates a forward impact force.

[0087] The impact rod 54 is also movably housed in the cavity of the cylinder 51. It is positioned in front of the hammer 53. When the hammer 53 moves forward, it strikes the impact rod 54, which then transmits the impact force to the working head 200 housed at the front end of the cylinder 51, thus providing an external impact output. In some embodiments, the impact rod 54 may structurally include, from front to back, a front impact portion 541, a body portion 542, and a rear impact portion 543. The body portion 542 is generally spindle-shaped, with the diameters at both ends smaller than the diameter in the middle. The front impact portion 541 and the rear impact portion 543 can be integrally formed at the front and rear ends of the body portion 542, respectively. The front impact portion 541 impacts the working head 200, and the rear impact portion 543 receives the impact force transmitted by the hammer 53. When the hammer 53 moves forward and strikes the rear impact portion 543, the impact rod 54 moves forward until its front impact portion 541 strikes the working head 200, thereby causing the working head 200 to provide an external impact output.

[0088] The aforementioned impact rod 54 reciprocates linearly between the rear limit position and the front limit position in the cavity of the cylinder 51 along the front-rear direction. Near the rear limit position, the impact rod 54 receives the impact force of the hammer 53 and moves forward. When it moves to the vicinity of the front limit position, it transmits the impact force to the working head 200.

[0089] See Figure 5 In some embodiments, the inner wall of the cavity of cylinder 51 located between the rear limit position and the front limit position during the movement of the impact rod 54 can be divided from back to front into a guide section 511, a clearance section 512, and a stop section 513.

[0090] The inner wall of the guide section 511 is clearance-fitted with the outer peripheral surface of the impact rod 54. The inner wall of the guide section 511 can provide guidance and support for the impact rod 54. When the impact rod 54 moves along the inner wall of the guide section 511, its central axis coincides with the central axis of the cylinder 51.

[0091] The clearance section 512 is located in front of the guide section 511, and its diameter is larger than that of the guide section 511. When the impact rod 54 moves to the clearance section, the clearance section 512 provides space for the impact rod 54 to deflect in the radial direction (i.e., the front or rear end of the impact rod 54 can be tilted relative to each other). This causes the central axis of the impact rod 54 to tilt relative to the central axis of the cylinder 51 after it impacts forward, thereby transferring part of the impact energy of the impact rod 54 to the inner wall of the cylinder 51. This arrangement helps to prevent the power tool 100 from impacting the working head 200 under no-load conditions.

[0092] The stop section 513 is located in front of the clearance section 512. It extends forward and gradually narrows in diameter to form a slope that is inclined radially inward. The impact rod 54 also has a slope that matches the stop section 513. When the impact rod 54 moves forward, the stop section 513 can prevent the impact rod 54 from continuing to move forward, thus preventing the impact rod 54 from exceeding the front limit position.

[0093] During operation, the power tool 100 operates in two states: an unloaded state and a loaded state. In the unloaded state, the working head 200, located at the front end of the power tool 100, is detached from the work surface. In this state, a locking gap exists between the aforementioned locking member 61 and the working head 200, allowing the working head 200 to move forward a short distance. Generally, the power tool 100 is in the unloaded state when it finishes processing one work surface and moves to the next. Alternatively, the power tool 100 may not have the working head 200 installed, in which case it is also in the unloaded state. In the loaded state, the working head 200 is pressed against the work surface and outputs work. Therefore, in the loaded state, the working head 200 is pressed and moves a short distance inwards towards the power tool 100, thereby eliminating the locking gap between the locking member 61 and the working head 200. Generally, the power tool 100 is always in the loaded state while processing a work surface.

[0094] like Figures 6 to 8 The diagram shows the different positions of the components in the impact mechanism 50 before and after the power tool 100 impacts the working head 200 in the loaded state.

[0095] Figure 6 This is a diagram showing the positional state of each component in the impact mechanism 50 when the piston 52 moves forward under the drive of the reciprocating assembly 31 in the loaded state. During the forward movement, the piston 52 continuously compresses the air between the piston 52 and the impact hammer 53 until the compressed air pressure reaches a level that can push the impact hammer 53 forward.

[0096] Figure 7This is a diagram showing the position of each component in the impact mechanism 50 before the hammer 53 moves forward and impacts the impact rod 54 under load. At this time, the impact rod 54 is in the rear limit position, and its front impact part 541 has a certain distance from the rear end of the working head 200. The rear impact part 543 is close to the front end of the hammer 53, and the body part 542 is supported in the guide section 511 of the cylinder 51.

[0097] Figure 8 This diagram illustrates the positional state of each component in the impact mechanism 50 after the impact hammer 53 strikes the impact rod 54 in the loaded state. After being struck by the hammer 53, the impact rod 54 moves forward along the length of the guide section 511. Because the working head 200 is pressed against the power tool 100 in the loaded state, it moves a short distance towards the interior, eliminating the locking gap between the locking member 61 and the working head 200. This restricts the impact rod 54 to the guide section 511 by the rear end of the working head 200, preventing it from moving further forward to the clearance section 512. When the impact rod 54 can only move back and forth within the area of ​​the guide section 511, the inner wall of the guide section 511 supports the body portion 542 of the impact rod 54. At this time, the central axis of the impact rod 54 coincides with the central axis of the cylinder 51. The impact rod 54 moves forward within the area of ​​the guide section 511 until its front impact portion 541 strikes the rear end face of the working head 200, causing the working head 200 to output an impact.

[0098] like Figures 9 to 11 The diagram shows the different positions of each component in the impact mechanism 50 before and after the power tool 100 impacts the working head 200 in an unloaded state.

[0099] Figure 9 This is a diagram showing the positional states of each component in the impact mechanism 50 when the piston 52 moves forward under the drive of the reciprocating assembly 31 in an unloaded state. Figure 6 The positions of all the components shown are consistent.

[0100] Figure 10 This is a diagram showing the positional state of each component in the impact mechanism 50 before the impact hammer 53 moves forward and strikes the impact rod 54 under no-load conditions. Figure 7 The positions of all the components shown are consistent.

[0101] Figure 11This diagram shows the positional state of each component in the impact mechanism 50 after the impact hammer 53 strikes the impact rod 54 in an unloaded state. At this time, after receiving the impact of the impact hammer 53, the impact rod 54 moves forward along the length extension direction of the guide section 511. Since the working head 200 is disengaged from the working surface in an unloaded state, there is a locking gap between the aforementioned locking member 61 and the working head 200. The working head 200 can move a small distance towards the outside of the power tool 100, allowing the impact rod 54 to continue moving forward to the area of ​​the clearance section 512 until the impact rod 54 strikes forward. At this time, since the clearance section 512 provides space for the impact rod 54 to deflect in the radial direction, the central axis of the impact rod 54 is tilted relative to the central axis of the cylinder 51 after the impact. This tilted configuration allows the impact energy of the impact rod 54 to be partially transferred to the housing 10. By consuming the impact energy of the impact rod 54, the power tool 100 is prevented from moving backward rapidly and striking the hammer 53 when it is unloaded, thereby preventing repeated impacts from occurring in the unloaded state.

[0102] In the embodiments of this application, the guide section 511 and the clearance section 512 can be formed by machining the inner cavity of the cylinder 51. A reaming cutter is mounted on a lathe or other machining equipment and extends into the cylinder 51. Its inner wall is machined by turning or other machining processes to meet design requirements for dimensions and surface roughness. During this machining process, since the diameter of the clearance section 512 is larger than the diameter of the guide section 511, and the clearance section 512 is located at the front end of the guide section 511, the reaming cutter can be extended from the rear end of the cylinder 51 into the inner cavity to machine its inner wall. First, the guide section 511 is machined, and the unloading groove that will inevitably form during this machining process is lengthened and used as the clearance section 512. This allows the clearance section 512 to provide space for the impact rod 54 to deflect radially, preventing repeated impacts from occurring in the power tool 100 under no-load conditions. Compared to other measures to avoid repeated impacts from power tools under no-load conditions, in the embodiments of this application, the relief groove that is inevitably formed during machining is used as a relief section 512 to avoid repeated impacts from power tools under no-load conditions. This setting can effectively prevent the power tool 100 from hitting empty without increasing costs.

[0103] When machining the inner cavity of cylinder 51, the length L1 of guide section 511 can be in the range of 30mm-40mm, the length L2 of clearance section 512 can be in the range of 3mm-8mm, and when impact rod 54 is tilted, the angle α formed by its central axis and the central axis of cylinder can be in the range of 0.5°-3°.

[0104] In some embodiments, the length L1 of the guide section 511 can be specifically implemented as 30 mm, the length L2 of the clearance section 512 can be specifically implemented as 3 mm, and when the impact rod 54 is tilted, the angle α formed by its central axis and the central axis of the cylinder can be specifically implemented as 0.5°.

[0105] In some embodiments, the length L1 of the guide section 511 can be specifically implemented as 40 mm, the length L2 of the clearance section 512 can be specifically implemented as 8 mm, and when the impact rod 54 is tilted, the angle α formed by its central axis and the central axis of the cylinder can be specifically implemented as 3°.

[0106] In some embodiments, the length L1 of the guide section 511 can be specifically implemented as 35 mm, the length L2 of the clearance section 512 can be specifically implemented as 5 mm, and when the impact rod 54 is tilted, the angle α formed by its central axis and the central axis of the cylinder can be specifically implemented as 1.5°.

[0107] In some embodiments, the length L1 of the guide section 511 can be specifically implemented as 32.3 mm, the length L2 of the clearance section 512 can be specifically implemented as 5 mm, and when the impact rod 54 is tilted, the angle α formed by its central axis and the central axis of the cylinder can be specifically implemented as 1.2°.

[0108] In some embodiments, the guide section 511 and the clearance section 512 are connected by a first inclined conical surface 515. The front diameter of the first inclined conical surface 515 is the same as the diameter of the clearance section 512, and the rear diameter is the same as the diameter of the guide section 511. The outer periphery of the body portion 542 of the impact rod 54 also has an annular groove 544 recessed radially inward. The annular groove 544 is used to accommodate a sealing ring 545 to isolate the front and rear spaces of the impact rod 54. The inner side of the elastic ring abuts against the annular groove 544, and the outer side abuts against the guide section 511. The position of the annular groove 544 is designed to ensure that when the impact rod 54 moves to its front limit position, the sealing ring 545 remains abutting within the area of ​​the guide section 511, preventing the sealing ring 545 from entering the area of ​​the clearance section 512 and causing a deterioration in the sealing effect. Furthermore, when the impact rod 54 moves backward from the clearance section 512, the front wall of the annular groove 544 will strike the first inclined cone surface 515, thereby further dissipating the impact energy of the impact rod 54 and preventing the power tool 100 from emptying.

[0109] like Figure 12 , Figure 13In some embodiments, to further ensure that the central axis of the impact rod 54 can tilt relative to the central axis of the cylinder 51 when it impacts forward in an unloaded state, the length of the rearward extension of the locking protrusion 514 can be increased. Furthermore, the length of the locking protrusion 514 allows the impact of the impact rod 54 with the locking protrusion 514 to precede the impact of the impact rod 54 with the stop section 513. When the impact rod 54 impacts the locking protrusion 514, the locking protrusion 514 can apply a non-uniform impact force, causing the central axis of the impact rod 54 to tilt relative to the central axis of the cylinder 51. To prevent the rear end face of the locking protrusion 514 from cracking or wearing due to frequent impacts from the impact rod 54, an inclined abutment slope 5141 can be provided on its rear end face. This inclined abutment slope 5141 not only prevents cracking due to impact but also provides partial guidance, allowing the impact rod 54 to move along the abutment slope 5141 and making it easier for it to tilt. Moreover, this method of preventing hollow hammers does not increase the number of parts or complicate the part processing technology. It achieves the purpose of preventing hollow hammers without increasing costs excessively.

[0110] To ensure that the force exerted by the locking protrusion 514 on the impact rod 54 is a non-uniform impact force, the inner wall of the receiving cavity 51a can be formed with multiple non-uniformly circumferentially distributed locking protrusions 514, and each locking protrusion 514 has the same length. When the power tool 100 is in an unloaded state, and the impact rod 54 is driven forward by the hammer 53, it can simultaneously impact each of the aforementioned locking protrusions 514. Each locking protrusion 514 can exert a reaction force on the edge of the front impact portion 541 of the impact rod 54. Therefore, the multiple non-uniformly distributed locking protrusions 514 can cause the impact rod 54 to be subjected to uneven force, thereby causing it to deflect in the radial direction. The aforementioned clearance section 512 provides space for the deflection of the impact rod 54, causing the central axis of the impact rod 54 to be inclined relative to the central axis of the cylinder 51.

[0111] like Figure 14 As shown, in some embodiments, the inner wall of the receiving cavity 51a may be formed with a locking protrusion 514, which is used both to circumferentially fix the cylinder 51 and the working head 200, and to apply a reaction force to the impact rod 54 to cause it to deflect.

[0112] like Figure 15 As shown, in some embodiments, the inner wall of the receiving cavity 51a may be formed with two locking protrusions 514, and the two locking protrusions 514 are asymmetrically arranged around the working head 200. When the impact rod 54 strikes the two locking protrusions 514 at the same time, the force will be uneven and the sway will occur.

[0113] like Figure 16As shown, in some embodiments, the inner wall of the receiving cavity 51a may be formed with three locking protrusions 514, and the three locking protrusions 514 are arranged around the working head 200 in a non-uniformly distributed manner. When the impact rod 54 strikes the three locking protrusions 514 at the same time, it will be subjected to uneven force and wobble.

[0114] In this application, the inner wall of the receiving cavity 51a may also form a plurality of evenly circumferentially distributed locking protrusions 514, but the length of at least one of the locking protrusions 514 is greater than the length of the other locking protrusions 514. With this configuration, when the power tool 100 is in an unloaded state and the impact rod 54 is driven forward by the hammer 53, it can simultaneously impact the aforementioned longer locking protrusion 514. The longer locking protrusion 514 can exert a reaction force on the edge of the front impact portion 541 of the impact rod 54, thus causing the impact rod 54 to be subjected to uneven force and thus deflect in the radial direction. The aforementioned clearance section 512 provides space for the deflection of the impact rod 54, causing the central axis of the impact rod 54 to be inclined relative to the central axis of the cylinder 51.

[0115] like Figure 17 As shown, in some embodiments, the inner wall of the receiving cavity 51a may have two symmetrically distributed locking protrusions 514, but the length of one locking protrusion 514 is greater than the length of the other locking protrusion 514. When the impact rod 54 strikes the longer locking protrusion 514, it will be subjected to uneven force and wobble.

[0116] like Figure 18 As shown, in some embodiments, the inner wall of the receiving cavity 51a may be formed with three evenly distributed locking protrusions 514, but the length of one locking protrusion 514 is greater than the length of the other two locking protrusions 514 or the length of two locking protrusions 514 is greater than the length of the other locking protrusion 514. When the impact rod 54 strikes the locking protrusion 514, it will be subjected to uneven force and wobble.

[0117] Of course, the shape, structure and number of locking protrusions 514 are not limited to this. As long as the impact rod 54 can cause the impact rod 54 to swing due to uneven force when it strikes the locking protrusion 514 forward, it can be used as an implementation method of this application.

[0118] See Figure 19In other embodiments, to further ensure that the central axis of the impact rod 54 can be tilted relative to the central axis of the cylinder 51 when it impacts forward in an unloaded state, an impact protrusion 516 can be provided on the inner wall of the cylinder 51 cavity. The position of the impact protrusion 516 allows the impact of the impact rod 54 against the impact protrusion 516 to precede the impact of the impact rod 54 against the stop section 513. When the impact rod 54 collides with the impact protrusion 516, the impact protrusion 516 can apply a non-uniform impact force, causing the central axis of the impact rod 54 to tilt relative to the central axis of the cylinder 51. Furthermore, to ensure that the force applied by the impact protrusion 516 to the impact rod 54 is a non-uniform impact force, the shape, structure, and number of the impact protrusion 516 can be set with reference to the locking protrusion 514 in the above embodiments. As long as the impact rod 54 can cause the impact rod 54 to deflect due to uneven force when it impacts the impact protrusion 516 forward, it can be used as an implementation method of this application. In this embodiment, the impact protrusion 516 can also be integrally formed with the locking protrusion 514 in order to reduce production costs.

[0119] like Figures 20-27 As shown, in some embodiments of this application, an inspection port 13 may be formed at the location of the main housing 11 that houses the transmission assembly 30 and the impact assembly 50. The power tool 100 is provided with a removable cover 14 to cover the inspection port 13. When the power tool 100 malfunctions during use or needs to be lubricated, the user can remove the cover 14 to troubleshoot or add lubricating grease. The inspection port 13 is located near the handle housing 12, and its projection in the side view direction is approximately U-shaped. The inspection port 13 is formed by a part of the notch on the upper end face of the main housing 11 and part of the notches on the two side walls.

[0120] Within the coverage area of ​​the access port 13, a locking mechanism 80 for locking the start switch 121 is also provided. This mechanism is linked to a mode switching mechanism 70 disposed on the cover 14, thereby allowing the power tool 100 to be locked in the selected output mode. The specific implementation of the mode switching mechanism 70 and the locking mechanism 80 is consistent with the technical solution disclosed in Chinese Invention Patent Application No. CN201811537231.0. One end of the locking mechanism 80 is connected to the handle housing 12, and the other end extends forward to above the access port 13, thereby linking with the mode switching mechanism 70 on the cover 14.

[0121] See Figure 20A gearbox housing 18 is provided inside the main housing 11, which can be used to sequentially house the transmission mechanism 30, the impact mechanism 50, and the output mechanism 40 from back to front. A first opening 181 is formed on the gearbox housing 18, corresponding to the position of the inspection port 13. The first opening 181 is formed on the upper end surface of the gearbox housing 18 and can be located radially outside any one of the transmission mechanism 30, the impact mechanism 50, and the output mechanism 40. Of course, the first opening 181 can also be located radially outside any two or all of the three. The size of the first opening 181 is not limited to this. As long as the user sequentially accesses the inspection port 13 and the first opening 181 to perform fault repair or add lubricating grease to the internal structural components of the power tool 100, it can be considered a specific embodiment of this application.

[0122] A pressure plate 15 for limiting the transmission mechanism 30 is also provided between the locking mechanism 80 and the first opening 181. It can be fixed to the gearbox housing 18 by fasteners 90 and at least partially covers the first opening 181, thereby preventing the transmission mechanism 30 housed in the main housing 11 from disengaging through the first opening 181. The pressure plate 15 is a generally semi-circular thin plate, with one arc-shaped end located on the rear side and matching the edge contour of the gearbox housing 18. Connecting lugs 151 are formed on its opposite sides. A first screw 91 passes through the connecting lugs 151 to fasten the pressure plate 15 to the upper end face of the gearbox housing 18.

[0123] The outer contour of the cover 14 is adapted to the outer contour of the access port 13, and it covers the access port 13 and encloses the aforementioned locking mechanism 80 and baffle 15. The cover 14 can be fitted with the main housing 11 to form the overall outer contour of the power tool 100. When the internal components of the power tool 100 malfunction and need to be repaired or lubricated, the user can simply remove the cover 14.

[0124] In order to isolate the internal space of the power tool 100 from the external environment and prevent grease from leaking out of the power tool 100 through the access port 13, a first seal 16 and a second seal 17 can be provided between the inner wall of the cover 14 and the gearbox housing 18. The first seal 16 and the second seal 17 can be combined to form an annular sealing path. This annular sealing path can isolate the internal space of the power tool 100 from the external environment at the access port 13, which can prevent grease from leaking out of the power tool 100 and also prevent dust from entering the power tool 100.

[0125] like Figure 21 , Figure 24As shown in the embodiments of this application, the first sealing element 16 can be specifically implemented as a closed annular elastic pad, which consists of two parts: a first sealing part 161 that presses against the upper end face of the gearbox housing 18 and the lower end face of the cover 14, and a second sealing part 162 that presses against the upper end face of the pressure plate 15 and the lower end face of the cover 14. The first sealing part 161 and the second sealing part 162 are connected end to end to form a complete annular structure. In order to ensure that the first sealing element 16 can be installed more stably between the cover 14 and the gearbox housing 18, and to prevent the vibration of the power tool 100 during operation from causing the first sealing element 16 to deviate from its initial installation position, a first mounting groove 182 can be formed on the upper end face of the gearbox housing 18 along the edge of the first opening 181, and a second mounting groove 141 that is adapted in position to the first mounting groove 182 can be formed on the inner wall of the cover 14. After the cover 14 is placed onto the main housing 11, the first mounting groove 182 and the second mounting groove 141 cooperate to clamp the first sealing part 161 of the first sealing member 16 between them. The first sealing member 16 is deformed under pressure, with its lower half pressing against the bottom wall of the first mounting groove 182 and its upper half pressing against the bottom wall of the second mounting groove 141. At the same time, the second sealing part 162 of the first sealing member 16 is also deformed under pressure, with its lower half pressing against the upper end face of the pressure plate 15 and its upper half pressing against the bottom wall of the second mounting groove 141.

[0126] like Figure 21 , Figure 24 As shown in the embodiments of this application, the second seal 17 can be specifically implemented as a generally U-shaped elastic pad, which also consists of two parts: a third sealing part 171 that presses against the lower end face of the pressure plate 15 and the upper end face of the gearbox housing 18, and a fourth sealing part 172 that extends upward from the lower end face of the pressure plate 15 and abuts against the first seal 16. In order to ensure that the second seal 17 can be installed more securely between the pressure plate 15 and the gearbox housing 18, and to prevent the vibration of the power tool 100 during operation from causing the second seal 17 to deviate from its initial installation position, a third mounting groove 183 can be formed on the upper end face of the gearbox housing 18 along the edge of the first opening 181. After the pressure plate 15 is fastened to the upper end face of the gearbox housing 18 by the first screw 91, the pressure plate 15 and the third mounting groove 183 cooperate to clamp the third sealing part 171 of the second seal 17 between them. The second seal 17 is deformed by pressure so that its lower half abuts against the bottom wall of the third mounting groove 183 and its upper half abuts against the lower end face of the pressure plate 15.

[0127] As described above, the first seal 16 and the second seal 17 respectively cooperate with the upper and lower end faces of the pressure plate 15 to form a closed sealing path. In a top-view projection, the first seal 16 and the second seal 17 together form an annular structure that encloses the first opening 181, with the first seal 16 distributed along the front half edge of the first opening 181 and the second seal 17 distributed along the rear half edge of the first opening 181. The inner wall of the cover 14, the first seal 16, the pressure plate 15, and the second seal 17 are sequentially arranged from top to bottom to abut against each other and together form a sealing path. This sealing path can isolate the internal space of the power tool from the external environment through the inspection port 13.

[0128] like Figures 22-27 As shown, in the above embodiment, the gearbox housing 18 has a first height portion 18a and a second height portion 18b at the edge of the first opening 181, wherein the first height portion 18a is higher than the second height portion 18b, and a first mounting groove 182 is formed in the first height portion 18a, and a third mounting groove 183 is formed in the second height portion 18b. There is a height difference between the first height portion 18a and the second height portion 18b, and a stepped surface 18c is formed at the connection between the two. When the second seal 17 is pressed against the third mounting groove 183 by the pressure plate 15, the fourth sealing portion 172 extends upward to the first seal 16, and the fourth sealing portion 172 is clamped between the front end face of the pressure plate 15 and the stepped surface 18c. This arrangement not only allows the second seal 17 to be installed more securely between the pressure plate 15 and the gearbox housing 18, preventing the vibration of the power tool 100 during operation from causing the second seal 17 to deviate from its original installation position, but also prevents the two elastic components, the first seal 16 and the second seal 17, from failing to fit tightly due to excessive elastic deformation, which would lead to a deterioration in the sealing performance between the fourth sealing part 172 and the first seal 16.

[0129] Furthermore, to prevent the pressure plate 15 from sinking into the second height portion 18b, thus creating a gap between the lower end face of the first seal 16 and the upper end face of the pressure plate 15, the height difference between the first height portion 18a and the second height portion 18b can be set to be less than the sum of the thicknesses of the pressure plate 15 and the second seal 17, ensuring that the upper end face of the pressure plate 15 is slightly higher than the surface of the first height portion 18a. Simultaneously, to prevent the pressure plate 15 from excessively raising the first seal 16, thus creating a gap between the first seal 16 and the first height portion 18a near the stepped surface 18c, the height difference between the first height portion 18a and the second height portion 18b can be set to be greater than the thickness of the pressure plate 15. Furthermore, to prevent the fourth sealing portion 172 from failing to abut and adhere tightly to the first seal 16, the extension length of the fourth sealing portion 172 can be set to be slightly greater than the height difference between the first height portion 18a and the second height portion 18b.

[0130] In the power tool 100 of this application, in order to ensure that the cover 14 and the first seal 16 and the second seal 17 can close the access port 13 or the first opening 181, the height difference H1 between the first height portion 18a and the second height portion 18b on the gearbox housing 18 can be in the range of 0.5mm-5mm, the thickness D1 of the pressure plate 15 can be in the range of 0.5mm-3mm, the thickness D2 of the second seal 17 can be in the range of 0.5mm-1mm, and the extension length L3 of the fourth sealing portion 172 can be in the range of 1mm-4mm.

[0131] In some embodiments, the height difference H1 between the first height portion 18a and the second height portion 18b can be specifically implemented as 0.5mm, the thickness D1 of the pressure plate 15 can be specifically implemented as 0.5mm, the thickness D2 of the second seal 17 can be specifically implemented as 0.5mm, and the extension length L3 of the fourth seal portion 172 can be specifically implemented as 1mm.

[0132] In other embodiments, the height difference H1 between the first height portion 18a and the second height portion 18b can be specifically implemented as 4 mm, the thickness D1 of the pressure plate 15 can be specifically implemented as 3 mm, the thickness D2 of the second seal 17 can be specifically implemented as 1 mm, and the extension length L3 of the fourth seal portion 172 can be specifically implemented as 5 mm.

[0133] In other embodiments, the height difference H1 between the first height portion 18a and the second height portion 18b can be specifically implemented as 2.0 mm, the thickness D1 of the pressure plate 15 can be specifically implemented as 1.5 mm, the thickness D2 of the second seal 17 can be specifically implemented as 0.7 mm, and the extension length L3 of the fourth seal portion 172 can be specifically implemented as 2.3 mm.

[0134] In some embodiments of this application, the transmission mechanism 30, impact mechanism 50, and output mechanism 40 of the power tool 100 can also be directly housed inside the main housing 11. In this case, the cover 14, together with the first seal 16 and the second seal 17, directly forms a sealing path at the inspection port 13 of the main housing 11, blocking the communication passage between the internal space of the power tool 100 and the external environment. The connection method between the cover 14, the first seal 16, the second seal 17 and the main housing 11 is the same as the connection method between the three and the gearbox housing 18 in the above embodiments, and will not be described again here.

[0135] See Figure 24 In the embodiments of this application, the pressure plate 15 has two opposing connecting lugs 151, which are fastened to the upper end face of the gearbox housing 18 by two first screws 91. Both sides of the cover 14 can be fastened to the upper end face of the gearbox housing 18 by three second screws 92. Figure 23 As shown, in the top view projection of the power tool 100, two first screws 91 and six second screws 92 are distributed around the sealing path formed by the combination of the first seal 16 and the second seal 17. This arrangement ensures the sealing between the cover 14 and the gearbox housing 18, effectively preventing the leakage of lubricating grease inside the power tool 100 through the first opening 181.

[0136] See Figure 21 In the embodiments of this application, in order to link the mode switching mechanism 70 configured on the cover 14 with the start switch configured on the handle housing 12 through the locking mechanism 80, the locking mechanism 80 can be set between the first opening 181 and the cover 14. Then, the first opening 181 is sealed by two separate sealing elements (first sealing element 16 and second sealing element 17) in conjunction with the cover 14. This arrangement not only avoids interference from the locking mechanism 80 when assembling the cover 14 and the first sealing element 16 and the second sealing element 17, thus improving the sealing performance of the first sealing element 16 and the second sealing element 17, but also allows the second screw 92 on the cover 14 to be loosened directly when disassembling the cover 14, without having to disassemble the handle housing 12 beforehand to remove the locking mechanism 80 from between the first opening 181 and the cover 14.

[0137] In the embodiments of this application, the process of assembling the cover 14 to the main housing 11 is as follows: First, the second sealing member 17 is arranged along the third mounting groove 183 on the upper end face of the gearbox housing 18. Then, the pressure plate 15 is fixed to the gearbox housing 18 by two first screws 91 and presses against the third sealing part 171 of the second sealing member 17. At the same time, the front end face of the pressure plate 15 presses the fourth sealing part 172 of the second sealing member 17 against the stepped surface 18c. Then, the first sealing member 16 is arranged along the first mounting groove 182 on the upper end face of the gearbox housing 18. The cover 14 is then fixed to the gearbox housing 18 by six second screws 92. During this process, the second mounting groove 141 on the inner wall of the cover 14 presses the first sealing member 16 downward, so that the first sealing part 161 of the first sealing member 16 is clamped between the first mounting groove 182 and the second mounting groove 141, and the second sealing part 162 of the first sealing member 16 is clamped between the second mounting groove 141 and the upper end face of the pressure plate 15.

[0138] In the embodiments of this application, the process of disassembling the cover 14 from the housing 11 is as follows: First, remove the six second screws 92 on the cover 14 to remove the cover 14 and the first seal 16. Then, remove the two first screws 91 on the pressure plate 15 to remove the pressure plate 15 and the second seal 17. During this process, the locking mechanism 80 extending above the access port 13 and the first opening 181 will not interfere, and it is not necessary to remove the handle housing 12 together with the locking mechanism 80 beforehand. Moreover, when the cover 14 is removed to add lubricating oil, the pressure plate 15 can also limit the transmission mechanism 30, impact mechanism 50, and output mechanism 40 inside the power tool 100, so that the power tool 100 disclosed in this application can maintain the position of its internal components and the connection relationship between the components even when the cover 14 is removed.

[0139] The power tool 100 disclosed in this application has corresponding access ports 13 and first openings 181 formed on the main housing 11 and gearbox housing 18, respectively, and the access ports 13 and first openings 181 are sealed by a cover 14 and a first seal 16 and a second seal 17. This split sealing method not only improves the sealing performance of the housing 10, but also facilitates installation and disassembly, while not affecting the working stability of its internal components.

[0140] 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: A housing, comprising a main housing and a cover, wherein the main housing has an access port and the cover can cover the access port; The first seal and the second seal, together, form a sealed path that prevents the internal space of the power tool from communicating with the external environment through the inspection port.

2. The power tool according to claim 1, characterized in that, The power tool also includes: The motor is housed within the main 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 drive mechanism, applies an impact force to the working head.

3. The power tool according to claim 2, characterized in that: The power tool also includes a gearbox housing housed within the main housing, and the transmission mechanism, impact mechanism, and output mechanism are distributed sequentially from back to front and are at least partially housed within the gearbox housing.

4. The power tool according to claim 3, characterized in that: The gearbox housing has a first opening, which is located radially outward of at least one of the transmission mechanism, impact mechanism, and output mechanism.

5. The power tool according to claim 4, characterized in that: The main housing has an inspection port corresponding to the position of the first opening.

6. The power tool according to claim 5, characterized in that: The gearbox housing is also connected to a pressure plate for limiting the transmission mechanism, and the pressure plate partially covers the first opening.

7. The power tool according to claim 6, characterized in that: The first and second sealing elements respectively mate with the upper and lower end faces of the pressure plate to form a closed sealing path.

8. The power tool according to claim 6, characterized in that: The gearbox housing has a first height portion and a second height portion with a height less than the first height portion. The first seal abuts against the first height portion, and the second seal abuts against the second height portion.

9. The power tool according to claim 8, characterized in that: The height difference between the first height portion and the second height portion is less than the sum of the thicknesses of the pressure plate and the second sealing element, but greater than the thickness of the pressure plate.

10. A power tool, characterized in that, include: A housing, comprising a main housing and a cover, wherein the main housing has an access port and the cover can cover the access port; The first seal and the second seal, together, form a sealed path that prevents the internal space of the power tool from communicating with the external environment through the inspection port.

11. The power tool according to claim 10, characterized in that, The power tool also includes: The motor is housed within the main housing; The working component is driven by the motor to perform external operations.

12. The power tool according to claim 11, characterized in that: The power tool also includes a gearbox housing housed within the main housing and a pressure plate connected to the gearbox housing.

13. The power tool according to claim 12, characterized in that: The first seal and the second seal respectively cooperate with the upper and lower end faces of the pressure plate to form a closed sealing path.

14. The power tool according to claim 13, characterized in that: The first sealing element is an annular elastic pad, which includes a first sealing part that presses against the upper end face of the gearbox housing and the lower end face of the cover, and a second sealing part that presses against the upper end face of the pressure plate and the lower end face of the cover.

15. The power tool according to claim 13, characterized in that: The second sealing element is an annular elastic pad, which includes a third sealing portion that presses against the lower end face of the pressure plate and the upper end face of the gearbox housing, and a fourth sealing portion that extends upward from the lower end face of the pressure plate and abuts against the first sealing element.

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