CN214443584U

CN214443584U - Electric hammer

Info

Publication number: CN214443584U
Application number: CN202022143274.XU
Authority: CN
Inventors: 韩言; 姚久玲; 蔡建恒; 孙红波
Original assignee: Nanjing Chervon Industry Co Ltd
Current assignee: Nanjing Chervon Industry Co Ltd
Priority date: 2020-09-25
Filing date: 2020-09-25
Publication date: 2021-10-22
Anticipated expiration: 2030-09-25

Abstract

The utility model discloses an electric hammer includes: the host comprises a machine shell and a motor at least arranged in the machine shell; the battery pack is detachably mounted on the machine shell; the host computer also includes: the output assembly includes a sleeve rotatable about a first axis; the impact assembly comprises a swing rod bearing and an impact block, and the impact block can output impact force forwards when moving in the sleeve; the mounting shaft is used for mounting the swing rod bearing and can be driven by the motor to rotate around a second axis; the electric hammer has a drill mode and a hammer drill mode; when the electric hammer is in a drilling mode, the sleeve rotates; when the electric hammer is in a hammer drill mode, the sleeve rotates, and the impact block reciprocates in the sleeve; the host computer also includes: a first bearing mounted to the mounting shaft to support the mounting shaft; a second bearing mounted to the mounting shaft to support the mounting shaft; wherein the product of the distance between the first bearing and the second bearing and the weight of the main machine is greater than or equal to 27 mm-kg and less than or equal to 58 mm-kg. The electric hammer is light and small.

Description

Electric hammer

Technical Field

The utility model relates to an electric tool, concretely relates to electric hammer.

Background

The electric hammer is an electric tool with wide application, is mainly used for drilling holes in concrete, floor slabs, brick walls and stone materials, and a plurality of electric hammers exist in the market at present, can be adjusted to a proper position to be matched with a proper drill bit to replace a common electric drill while realizing the drilling function, namely a hammer drilling mode and a drilling mode.

However, in manufacturing such an electric hammer, in order to implement the functions of the hammer drill mode and the drill mode, structures for implementing different functions are often added, which may increase the size and weight of the electric hammer. After a user holds the electric hammer for a long time, fatigue is easy to occur, and further the working efficiency is influenced.

SUMMERY OF THE UTILITY MODEL

In order to solve the defects of the prior art, the utility model aims to provide an electric hammer with small structure and light weight.

In order to achieve the above object, the utility model adopts the following technical scheme: an electric hammer comprising: the main machine comprises a machine shell and a motor at least partially arranged in the machine shell, wherein the motor rotates along the axis of the motor; the battery pack is used for providing an energy source for the motor, and the battery pack is detachably arranged on the machine shell; the host computer also includes: an output assembly including a sleeve rotatable about a first axis; the impact assembly comprises a swing rod bearing and an impact block which can be driven by the swing rod bearing to reciprocate in the sleeve, and the impact block can output impact force forwards when moving in the sleeve; the mounting shaft is used for mounting the swing rod bearing and can be driven by the motor to rotate around a second axis; the electric hammer has a drill mode and a hammer drill mode; when the electric hammer is in a drilling mode, the sleeve rotates; when the electric hammer is in a hammer drill mode, the sleeve rotates, and the impact block reciprocates in the sleeve; the host computer also includes: a first bearing mounted to the mounting shaft to support the mounting shaft; a second bearing mounted to the mounting shaft to support the mounting shaft; wherein the product of the distance between the first bearing and the second bearing and the weight of the main machine is greater than or equal to 27 mm-kg and less than or equal to 58 mm-kg.

Further, the swing rod axis includes: a bearing core mounted on the mounting shaft, and a swing lever mounted on the bearing core; the swinging rod comprises a ring sleeved on the bearing core and a connecting rod which is integrally formed with the ring and extends along a first straight line direction; when the bearing core is driven, the swinging rod moves along with the bearing core, and at least comprises a first limit position in the moving process of the swinging rod; when the swing rod is at the first limit position, the connecting rod is inclined forwards to a first limit angle, and a first straight line is parallel to or coincided with the axis of the motor; wherein, the distance between the first straight line and the axis of the motor is more than or equal to 0mm and less than or equal to 20 mm.

Further, the swing rod axis includes: a bearing core mounted on the mounting shaft, and a swing lever mounted on the bearing core; the swinging rod comprises a ring sleeved on the bearing core and a connecting rod which is integrally formed with the ring and extends along a first straight line direction; when the bearing core is driven, the swinging rod moves along with the bearing core, and at least comprises a first limit position in the moving process of the swinging rod; when the swing rod is at the first limit position, the connecting rod is inclined forwards to a first limit angle, and a first straight line intersects with the axis of the motor; wherein, the intersection point of the first axis and the motor axis is on the motor.

Further, the output power of the motor is equal to or greater than 360W and equal to or less than 440W.

Furthermore, the ratio of the weight of the main machine to the output power of the motor is more than or equal to 2.2g/W and less than or equal to 4.5 g/W.

Further, the swing rod axis includes a bearing core mounted to the mounting shaft; the first bearing and the second bearing are respectively arranged on two sides of the bearing core.

Further, the electric hammer further includes: the supporting bracket is fixedly connected with the shell or integrally formed, and is used for integrating the mounting shaft and the sleeve into a whole; the first bearing is mounted on the mounting shaft and located on the front side of the bearing core, and the first bearing is arranged in the supporting bracket.

Further, the electric hammer comprises a first transmission piece for transmitting the power of the motor to the mounting shaft, a second bearing is mounted on the mounting shaft and located on the rear side of the first transmission piece, and the second bearing is arranged in the machine shell.

Further, the electric hammer further comprises a clutch assembly for switching the electric hammer between the hammer drill mode and the hammer drill mode, wherein the clutch assembly can drive the swing rod bearing to rotate around the second axis; the second bearing is arranged at the rear side of the clutch assembly and is arranged in the shell.

Further, the distance between the first bearing and the second bearing in the direction along the second axis is greater than or equal to 30mm and less than or equal to 50 mm.

The utility model discloses an useful part lies in: through being arranged in the electric hammer in the first bearing and the second bearing of location installation axle to optimize the setting to make the host computer structure light, small and exquisite.

Drawings

Fig. 1 is a perspective view of an electric hammer according to a first embodiment of the present invention;

FIG. 2 is a plan view of a portion of the structure of the hammer shown in FIG. 1;

FIG. 3 is a plan view of the electric hammering machine shown in FIG. 1;

FIG. 4 is a cross-sectional view of the hammer shown in FIG. 3 taken along the line A-A;

FIG. 5 is a perspective view of a portion of the electric hammer of FIG. 1 in a drill mode;

fig. 6 is a plan view of a portion of the hammer shown in fig. 1 in a hammer drill mode;

FIG. 7 is a cross-sectional view of the hammer shown in FIG. 3 taken along the direction B-B;

FIG. 8 is a schematic view of a portion of the structure of the hammer shown in FIG. 1;

FIG. 9 is a schematic view of a portion of the structure of the hammer shown in FIG. 1;

fig. 10 is a plan view of a part of the structure of the electric hammer shown in fig. 1;

fig. 11 is an exploded view of a portion of the structure of the hammer shown in fig. 1;

fig. 12 is an exploded view from another perspective of the partial structure of the electric hammer shown in fig. 11;

fig. 13 is a partial exploded view of the hammer of fig. 1;

FIG. 14 is a top plan view of the impact assembly of the hammer of FIG. 1;

FIG. 15 is a cross-sectional view of the rocker bearing of FIG. 14 taken along the A-A direction;

fig. 16 is a perspective view of an electric hammer in a second embodiment of the present invention;

FIG. 17 is a cross-sectional view of the hammer shown in FIG. 16, taken along a second axis;

fig. 18 is a partial schematic structural view of the hammer of fig. 16 in a hammer drill mode;

fig. 19 is a partial schematic view of the hammer of fig. 16 in a drill mode;

FIG. 20 is an enlarged partial view of the structure shown in FIG. 19;

fig. 21 is a partial exploded view of the hammer shown in fig. 16;

fig. 22 is a perspective view of a switching member in the electric hammer shown in fig. 21;

fig. 23 is a perspective view of another angle of view of the switching element shown in fig. 21.

Detailed Description

The electric hammer 100 shown in fig. 1 is a commonly used electric tool, and can drive the functional element 61 to rotate, and the functional element 61 can be a drill, so that the electric hammer 100 can drive the functional element 61 to punch holes on hard materials such as wall surfaces, concrete, bricks, stones, and the like.

For clarity of explanation of the technical solution of the present application, upper, lower, front, rear, left and right as shown in fig. 1 are defined.

As shown in fig. 1 to 2, the electric hammer 100 includes: host 100a and energy source, host 100a includes: the power assembly comprises a casing 10, a power assembly 20, a transmission assembly 30, an impact assembly 40, an output assembly 50, a clamping assembly 60 and an energy source, wherein the energy source can be a battery pack 110 in the embodiment.

The housing 10 is formed with a receiving space 11, and the receiving space 11 is used for receiving various components inside the electric hammer 100. Namely, the power assembly 20, the output assembly 50, the transmission assembly 30 and the impact assembly 40 are at least partially disposed within the accommodating space 11. The housing 10 forms or is connected to a handle portion 12 that can be held by a user. The user can operate the electric hammer 100 by holding the grip portion 12.

The power assembly 20 is used to power the electric hammer 100, and the power assembly 20 includes a motor 21, and the motor 21 includes a motor shaft 22 rotatable about a motor axis 101.

The transmission assembly 30 is used for transmitting the power output by the motor shaft 22 to the output assembly 50 and the impact assembly 40.

The output assembly 50 includes: a sleeve 51, the sleeve 51 being drivable by the transmission assembly 30 to rotate about the first axis 102. Specifically, the sleeve 51 is formed with a housing cavity for housing the functional element 61, and the functional element 61 can be inserted into the housing cavity. The clamping assembly 60 can hold the functional element 61 on the sleeve 51. When the sleeve 51 is rotated about the first axis 102, the functional element 61 can be driven to rotate.

The impact assembly 40 includes a rocker bearing 40a that can be driven by the transmission assembly 30 to impact the impact block 44, and the impact block 44 can contact a functional element 61 mounted within the sleeve 51. Thus, when the rocker bearing 40a impacts the impact block 44 in a reciprocating manner, the impact block 44 can intermittently output an impact force to the functional element 61, thereby allowing the functional element 61 to be more efficiently perforated.

The energy source is used for providing an energy source for the electric hammer 100, the energy source may be ac or dc, in this embodiment, dc is used, that is, the energy source is specifically a battery pack 110, the battery pack 110 and the casing 10 may be inserted into each other, or may be separately arranged, that is, the battery pack 110 is not directly installed on the surface of the casing 10, and the specific installation manner is not limited herein, as long as the power source can be provided.

Electric hammer 100 also includes a clutch assembly 80. The clutch assembly 80 is used to open or close the power transmission between the transmission assembly 30 and the impact assembly 40. The clutch assembly 80 has a first state and a second state. When the clutch assembly 80 is in the first state, the clutch assembly 80 can transmit the power output by the transmission assembly to the impact assembly 40, and the impact assembly 40 can output an impact force to the functional element 61. When the clutch assembly 80 is in the first state, the functional element 61 is driven by the output assembly 50 to rotate about the first axis 102, and the functional element 61 receives the driving force output by the impact assembly 40, so that the electric hammer 100 is in the hammer drill mode. When the clutch assembly 80 is in the second state, the clutch assembly 80 disconnects the power transmission between the transmission assembly 30 and the impact assembly 40, the transmission assembly 30 no longer drives the impact assembly 40, and the impact assembly 40 cannot output an impact force to the functional element 61. Thus, when the clutch assembly 80 is in the second state, the functional element 61 cannot be driven by the impact assembly 40, but only by the output assembly 50 to rotate about the first axis 102, and the hammer 100 is in the drill mode.

Hammer 100 also includes a switching assembly 70. The switching assembly 70 is used to switch the hammer 100 between a drill mode and a hammer drill mode. The switching assembly 70 is capable of transmitting a driving force from the output assembly 50 to the clutch assembly 80, thereby switching the clutch assembly 80 to the first state. Specifically, when the user needs to put the electric hammer 100 into the hammer drill mode, the sleeve 51 is moved along the first axis 102 by pressing the functional element 61, so that the switching assembly 70 drives the clutch assembly 80 to switch to the first state, thereby switching the electric hammer 100 to the hammer drill mode. That is, the user can switch the electric hammer 100 to the hammer drill mode without excessive operation steps, thereby facilitating the user's use, saving time, and improving work efficiency.

As shown in fig. 3 to 5 and 9 to 12, the transmission assembly 30 includes: the mounting shaft 31 and the first and

second transmission members

32 and 23. The second transmission member 23 is fixedly connected with the motor shaft 22, and the first transmission member 32 is engaged with the second transmission member 23 to receive the power output by the motor 21. The mounting shaft 31 is fixedly connected to the first transmission member 32, that is, when the first transmission member 32 rotates, the mounting shaft 31 rotates. In this way, the motor 21 can output power to the mounting shaft 31 through the first transmission member 32 and the second transmission member 23 to drive the mounting shaft 31 to rotate around the second axis 103, wherein the second axis 103 and the first axis 102 are parallel to each other. In the present embodiment, the first transmission member 32 is a bevel gear, and the second transmission member 23 is a bevel gear portion formed by the motor shaft 22 itself to mesh with the bevel gear. The first transmission member 32 and the second transmission member 23 may have other structures, and the specific structure is not limited thereto as long as the force transmission can be achieved.

The output assembly 50 further includes: the first transmission section 52 has a second transmission section 311 formed on the mounting shaft 31. The first transmission portion 52 is fixedly mounted to the sleeve 51, and the second transmission portion 311 is fixedly mounted to the mounting shaft 31 to rotate synchronously with the mounting shaft 31. The first transmission part 52 and the second transmission part 311 are both transmission teeth, and the first transmission part 52 is meshed with the second transmission part 311. Thus, when the electric hammer 100 is started, the motor drives the mounting shaft 31 to transmit power, the second transmission part 311 on the mounting shaft 31 drives the first transmission part 52 and the sleeve 51 to integrally rotate, and the sleeve 51 drives the functional element 61 to rotate.

The swing rod bearing 40a in the impact assembly 40 includes: a striking member 41, a swing lever 42, and a bearing core 43. The striking element 41 can reciprocate in the sleeve 51 to strike the impact block 44, and the impact block 44 strikes the functional element 61. The striking member 41 is connected to a swing lever 42, and the swing lever 42 is mounted to a bearing core 43, and the bearing core 43 is used to mount the swing lever bearing 40a to the mounting shaft 31. The bearing core 43 can rotate with the mounting shaft 31, and the bearing core 43 cannot rotate with the mounting shaft 31. Thus, when the bearing core 43 rotates along with the mounting shaft 31, the bearing core 43 drives the swinging rod 42 to reciprocate, the swinging rod 42 drives the striking element 41 to reciprocate in the sleeve 51 to strike the impact block 44, so that the impact block 44 can output an impact force to the functional element 61, at this time, the functional element 61 is also impacted by the impact block 44 while rotating, and the electric hammer 100 is in the hammer drill mode. When the bearing core 43 does not rotate with the mounting shaft 31, the striking element 41 cannot strike the impact block 44, and the impact block 44 does not output impact force to the functional element 61, so that the functional element 61 only rotates, and the electric hammer 100 is in the drill mode.

When the clutch assembly 80 is in the first state, the clutch assembly 80 can drive the bearing core 43 to rotate along with the mounting shaft 31, so that the striking element can reciprocate in the sleeve 51 to drive the impact block 44 to output impact force to the functional element 61, and the electric hammer 100 is in the hammer drill mode. When the clutch assembly 80 is in the second state, the clutch assembly 80 no longer drives the bearing core 43 to rotate with the mounting shaft 31, the mounting shaft 31 can rotate relative to the impact assembly 40, the mounting shaft 31 drives the output assembly 50 to rotate and further drives the functional element 61 to rotate, and at this time, the functional element 61 only rotates, that is, the electric hammer 100 is in the drill mode.

Specifically, the clutch assembly 80 includes: an input section 81 and an output section 82. The input portion 81 rotates in synchronization with the mounting shaft 31, and the output portion 82 rotates in synchronization with the bearing core 43 of the rocker bearing 40 a. The output section 82 is movable relative to the input section 81 so that the input section 81 can be brought into engagement with the output section 82 and the input section 81 can be disengaged from the output section 82. When the clutch assembly 80 is in the first state, the output portion 82 moves relative to the input portion 81 to a position where it engages the input portion 81, and the clutch assembly 80 drives the rocker bearing 40a to impact the impact block 44. When the clutch assembly 80 is in the second state, the output portion 82 moves relative to the input portion 81 to a position disengaged from the input portion 81, and the clutch assembly 80 cannot drive the rocker bearing 40a, and the rocker bearing 40a cannot drive the impact block 44.

As shown in fig. 2 to 6, the switching assembly 70 includes a switching element 71, and the switching element 71 includes a force receiving end 711 and a driving end 712. The force receiving end 711 is in contact with the output assembly 50 and is capable of being driven by the output assembly 50 to move along the first axis 102, and the driving end 712 is in contact with the clutch assembly 80 to drive the clutch assembly 80 between the first state and the second state. When the output member 50 moves along the first axis 102 relative to the housing 10, the output member 50 drives the force-bearing end 711 to move, and the force-bearing end 711 drives the driving end 712 to move together to drive the clutch assembly 80 to switch from the second state to the first state. The switching member 71 is disposed on the lower side of the first axis 102 in the up-down direction. The arrangement can enable the whole size of the electric hammer 100 to be reasonable. The force bearing end 711 of the switching element 71 is directly connected with the output assembly 50, and the driving end 712 of the switching element 71 directly drives the clutch assembly 80, so that in the embodiment, the switching of the state of the clutch assembly 80 can be realized only by the switching element 71 arranged on the lower side of the first axis 102 of the sleeve 51, the structure is simple, the space on the lower side of the first axis 102 is fully utilized, the structure of the whole machine is compact, and the arrangement is more reasonable. In fact, the sleeve 51 has a relatively large dimension in the direction of the first axis 102 in order to accommodate part of the impact assembly 40, so that the sleeve 51 needs to occupy a relatively large space in the direction of the first axis 102, whereas the arrangement of the switching element 71 on the lower side of the first axis 102 makes it possible to make full use of the space on the lower side of the sleeve 51. Due to the arrangement, the sleeve 51 and the switching element 71 can be prevented from being large in size in the left-right direction when the switching element 71 is arranged on the left side or the right side of the sleeve 51, so that the case 10 can be prevented from being too large in size in the left-right direction, and the electric hammer 100 can be conveniently punched along the left side wall and the right side wall. In addition, this arrangement also prevents the upper surface of the housing 10 from being spaced further from the first axis when the switching member 71 is disposed above the first axis 102, thereby allowing the hammer 100 to be conveniently punched against the upper wall.

An orthogonal projection of the switching element 71 in a plane perpendicular to the first axis 102 at least partially overlaps an orthogonal projection of the first transmission part 52 in a plane perpendicular to the first axis 102. That is, an orthographic projection of the first transmission portion 52 in a plane perpendicular to the first axis 102 has a highest point and a lowest point, and an orthographic projection of the switching element 71 in the plane is located between the highest point and the lowest point. In one embodiment, the force receiving end 711 of the switching element 71 abuts against the first transmission part 52, and the driving end 712 of the switching element 71 is connected to the clutch assembly 80, that is, when the sleeve 51 is forced to move along the first axis 102, the first transmission part 52 moves along the first axis 102 along with the sleeve 51, so that the force receiving end 711 abutting against the first transmission part 52 is forced to slide along the first axis 102, and the driving end 712 drives the clutch assembly 80 to switch to the first state, and then the electric hammer 100 is in the hammer drill mode. That is to say, the switching element 71 fully utilizes the space below the sleeve 51, and further, the structure and position of the mounting shaft 31 or other components can be well planned, so that the layout of the whole machine is more reasonable. Further, the dimension of the switching element 71 in the vertical direction is smaller than the dimension of the first transmission portion 52 in the vertical direction, that is, the dimension of the switching element 71 in the vertical direction is smaller than the diameter of the first transmission portion 52, and the switching element 71 is located at the lower side of the sleeve 51, but it can be understood that the switching element 71 is arranged between the first axis 102 and the second axis 103, and the first transmission portion 52 is engaged with the mounting shaft 31, so that a certain height difference exists between the engagement of the first transmission portion 52 and the mounting shaft 31 in the vertical direction, and by the above arrangement, the height difference can be fully utilized, that is, the space between the lower side of the sleeve 51 and the upper side of the mounting shaft 31 can be fully utilized by the switching element 71, and the mode switching can be realized by the switching element 71 without adjusting the structural arrangement. Of course, the force-bearing end 711 of the switching element 71 may abut against the driving portion formed on the sleeve 51, and the switching function can be realized by this arrangement as well, and the specific principle and function are basically the same as those of the force-bearing end 711 abutting against the first transmission portion 52, and therefore, the detailed description thereof is omitted.

The sleeve 51 is arranged substantially symmetrically with respect to a vertical plane P, wherein the vertical plane is a plane in the up-down direction, the first axis 102 is located in the plane P, the portion of the switching element 71 located between the first axis 102 and the second axis 103 is distributed on both sides of the plane P, and the switching element 71 is made of wear-resistant materials to realize the switching function, so as to ensure the operation of the machine, such as high-density steel, which has a heavy weight.

As shown in fig. 1 and 5, to effect switching of the operating mode of the electric hammer 100, the electric hammer 100 further includes a shift assembly 90 that is adjustable by a user. The shift assembly 90 includes a stopper portion 91 for preventing the sleeve 51 or the shift element 71 from retreating in the direction of the first axis 102. The user can adjust the shift assembly 90 such that the stopper portion 91 moves to the release position and the restricting position. The stop portion 91 allows the sleeve 51 and the switching element 71 to move along the first axis 102 when the shift assembly 90 is in the release position, and the stop portion 91 prevents the sleeve 51 and the switching element 71 from moving in the direction of the first axis 102 when the shift assembly is in the stop position. Specifically, the switching element 71 is fixedly connected to or integrally formed with a stopper 714 for cooperating with the limiting portion 91. When the user adjusts the gear shift assembly 90 to move the limiting portion 91 to the limiting position, the limiting portion 91 abuts against the stopping portion 714, and the limiting portion 91 prevents the switching element 71 from moving in a direction parallel to the first axis 102, that is, the switching element 71 cannot drive the output portion 82 to be combined with the input portion 81, so that the electric hammer 100 is in the drilling mode. When the user adjusts the shift assembly 90 to move the position-limiting portion 91 to the release position, the position-limiting portion 91 disengages from the stopping portion 714, the position-limiting portion 91 allows the sleeve 51 and the stopping element to move along the first axis 102, the sleeve 51 moves backward by the external force, the switching element 71 moves in a direction parallel to the first axis 102 when receiving the driving force from the sleeve 51, and thus the switching element 71 can drive the output portion 82 to be combined with the input portion 81, so that the electric hammer 100 enters the hammer drill mode.

In the present embodiment, the clutch assembly 80 is disposed on the rear side of the rocker bearing 40a in the direction along the second axis 103. The input part 81 of the clutch assembly 80 is fixedly connected to or integrally formed with the first transmission 32, and the output part 82 is fixedly connected to or integrally formed with the bearing core 43. The input portion 81 is specifically a first meshing tooth formed on the first transmission member 32 and extending toward the bearing core 43, and the output portion 82 is specifically a second meshing tooth formed on the bearing core 43 of the rocker bearing 40a and extending toward the first transmission member 32. The clutch assembly 80 is in the first state when the input 81 and output 82 are engaged. When the input 81 and output 82 are disengaged, the clutch assembly 80 is in the second state. The switching element 71 is in contact with the bearing core 43 of the rocker bearing 40 a. When the switching member 71 receives the driving force of the sleeve 51, the switching member 71 drives the bearing core 43 to move toward the first transmission member 32 along the second axis 103, and the output portion 82 of the bearing core 43 moves to a position engaging with the input portion 81 of the first transmission member 32, so that the clutch assembly 80 is switched to the first state, and the electric hammer 100 enters the hammer drill mode. The clutch assembly 80 further includes a reset member 83, the reset member 83 being biasedly disposed between the rocker bearing 40a and the first transmission member 32, the reset member 83 being for biasing the output member such that the clutch assembly 80 has a tendency to switch toward the second state. Thus, when the switching element 71 does not receive the driving force from the sleeve 51, the reset member 83 drives the rocker bearing 40a to move along the second axis 103 to a state where the output portion 82 is disengaged from the input portion 81, and the clutch assembly 80 is in the second state, and the electric hammer 100 is in the drill mode.

Specifically, the input portion 81 is formed by an end surface of the first transmission 32 being recessed inward. The end face of the first transmission member 32 is recessed inwardly to form a groove, and the groove wall of the groove projects toward the second axis 103 to form a projecting tooth to constitute the output portion 82. Thus, on the one hand, the reduction in size of the output portion 82 and the first transmission member 32 as a whole facilitates the reduction in size of the transmission assembly 30 in the direction of the second axis 103. On the other hand, when the output part 82 is engaged with the input part, the output part 82 is inserted into the groove, so that the moving stroke of the output part 82 can be increased, the reliability of the clutch assembly 80 is improved, the reset piece 83 is placed in a proper space, the size of the transmission assembly 30 along the direction of the second axis 103 can be further reduced, and the length of the electric hammer 100 in the front-back direction can be reduced. The output portion 82 extends rearward from the end surface of the bearing core 43, the bearing core 43 extending rearward forming an annular portion, the end surface of which is provided with teeth to form the output portion 82. A restoring member 83 is arranged between the output 82 and the input 81, the restoring member 83 being embodied as a spring which is at least partially arranged in the annular portion. With the above arrangement, it can be understood that when the sleeve 51 is forced to move along the first axis 102, the first transmission part 52 drives the switching element 71 to slide, so that the driving end 712 of the switching element 71 drives the impact assembly 40 to move along the second axis 103, and the impact assembly 40 is forced to compress the spring, the spring is deformed, so that the engaging part of the bearing core 43 is engaged with the input part 81 of the first transmission part 32, and the clutch assembly 80 is switched to the first state. When the force applied to the sleeve 51 is removed, the spring disengages the engaging portion of the driving bearing core 43 from the input portion 81 according to its own elastic force, and the impact assembly 40 rotates relative to the mounting shaft 31 to switch the impact assembly 40 to the second state. With the arrangement, the output portion 82 of the bearing core 43 extends into the first transmission piece 32, that is, the position of the joint of the bearing core 43 and the first transmission piece 32 is located on the first transmission piece 32, so that the inner space of the first transmission piece 32 is utilized, and the size of the whole machine in the left-right direction can be saved under the condition of ensuring the stable structure. Of course, the input portion 81 may be configured to be toothed to project outward from the first transmission member 32, and the output portion 82 may be configured to be toothed to project rearward. Thereby set up the structural strength who strengthens the connection between the two, guarantee the stability of complete machine operation.

As shown in fig. 14 to 15, the bearing core 43 is mounted on the mounting shaft 31, the bearing core 43 is movable along the second axis 103, and the housing chamber 431 for housing the lubricating oil is provided in the bearing core 43. The housing chamber 431 is provided with lubricating oil therein, so that the frictional force of the bearing core 43 rotating or sliding with respect to the mounting shaft 31 can be reduced. Because the bearing core 43 and the mounting shaft 31 rotate relative to each other, a gap is formed between the mounting shaft 31 and the bearing core 43. When the electric hammer 100 is at rest, the bearing core 43 may have two contact surfaces, specifically, a first contact surface 432 and a second contact surface 433, with the mounting shaft 31 under the influence of gravity, and a receiving cavity 431 is formed between the two contact surfaces. In the direction along the second axis 103, the accommodating cavity 431 has a first length a, the first contact surface 432 has a second length B, and the second contact surface 433 has a third length C, wherein the first length a is greater than the sum of the second length B and the third length C, and by the above arrangement, the space for accommodating the cavity 431 is larger, so that more lubricating oil can be accommodated in the accommodating cavity 431, the friction force is reduced, the condition of impact when the electric hammer 100 is in the drill mode is prevented, the machine damage is avoided, and the service life of the impact assembly 40 can be prolonged. The value range of the first length A is more than or equal to 8mm and less than or equal to 20mm, the value range of the second length B is more than or equal to 0.5mm and less than or equal to 4mm, and the value range of the third length C is more than or equal to 0.5mm and less than or equal to 4 mm. The arrangement within the above range can ensure that the accommodating cavity 431 has enough accommodating space, and can avoid the bearing core 43 from being overlong in the length direction, thereby prolonging the size of the whole machine.

The swing lever 42 includes a ring 421 fitted over the bearing core 43 and a connecting rod 422 formed integrally with the ring 421. The swing rod bearing 40a further includes a movable sleeve 411 mounted to one end of the connecting rod 422, the striking member being disposed within the movable sleeve 411, the movable sleeve 411 being capable of driving the striking member to strike the impact block 44. The connecting rod 422 extends along the first straight line 104, and the movable sleeve 411 and the ring 421 are arranged at two ends of the connecting rod 422. As bearing core 43 moves, sway bar 42 is able to move to first and second extreme positions, as can also be appreciated, connecting bar 422 is able to move to first and second extreme positions. When swing lever 42 is in the first limit position, connecting rod 422 is tilted forward to the first limit angle. That is, when the connecting rod 422 is at the first limit angle, the movable sleeve 411 moves forward to the farthest distance that it can move, and the first straight line 104 is parallel to the motor axis 101, wherein the distance between the first straight line 104 and the motor axis 101 is greater than or equal to 0mm and less than or equal to 20 mm. Of course, the first line 104 may not be parallel to the motor axis 101, but this arrangement may cause the movable sleeve 411 to move forward, thereby extending the length of the sleeve 51 in the forward-rearward direction and thus the overall size. Alternatively, the first straight line 104 is not parallel to the motor axis 101, and the position of the bearing core 43 is set further rearward than the position of the parallel arrangement, so that the dimension of the mounting shaft 31 in the front-rear direction needs to be increased, and the dimension of the entire machine in the longitudinal direction needs to be increased. That is, by arranging the first straight line 104 in parallel with or overlapping the motor axis 101 and setting the gap therebetween within the above range, the dimension of the entire machine in the front-rear direction can be set within a relatively reasonable range, and further, by arranging the distance between the first straight line 104 and the motor axis 101 to be not less than 10mm and not more than 20mm, the effect is further improved. Or, in other embodiments, when the swing rod is at the first limit position, the connecting rod is at the first limit angle, the first straight line intersects with the motor axis to form an included angle greater than or equal to 0 degree and less than or equal to 5 degrees, and the intersection point of the first straight line and the motor axis is on the motor, so that the size of the whole formed by the swing rod bearing 40a and the movable sleeve 411 along the direction of the first axis 102 can be reduced as much as possible. When the swing lever 42 is at the second limit position, the connecting rod 422 is tilted backward to the second limit angle, that is, when the connecting rod 422 is at the second limit angle, the movable sleeve 411 moves backward to the farthest distance that it can move, and the first line 104 intersects with the first axis 102.

In the present embodiment, the ratio of the weight of the impact assembly 40 to the output power of the motor 21 is greater than or equal to 0.09g/W and less than or equal to 0.16 g/W. In some other embodiments, the ratio of the weight of the impact assembly 40 to the output power of the motor 21 is greater than or equal to 0.06g/W and less than or equal to 0.12 g/W. Thus, when the motor 21 can output a sufficiently large output power while reducing the weight of the impact assembly 40, the performance can be ensured and the weight of the entire machine can be reduced.

As shown in fig. 2, 11 and 12, the electric hammer 100 further includes a support bracket 13 for supporting the mounting shaft 31. The supporting bracket 13 is fixedly connected to or integrally formed with the casing 10, the supporting bracket 13 divides the casing 10 into a first space 15 and a second space 16, the bearing core 43 is located in the second space 16, that is, in the front-rear direction, the first space 15 is located at the front side of the second space 16. The supporting bracket 13 is sleeved on the sleeve 51 and used for positioning the sleeve 51, and the mounting shaft 31 penetrates through the supporting bracket 13 to ensure that the distance between the sleeve 51 and the mounting shaft 31 is constant. The sleeve 51 and the mounting shaft 31 are both rotatable relative to the support bracket 13, and the mounting shaft 31 is disposed below the sleeve 51 in the vertical direction. The support bracket 13 is disposed on the front side of the clutch assembly 80 in the front-rear direction.

As shown in fig. 2 to 4, the electric hammer 100 further includes a positioning assembly for positioning the mounting shaft 31, the positioning assembly including a first bearing 17 and a second bearing 18, the first bearing 17 and the second bearing 18 being respectively disposed on both sides of the clutch assembly 80. The first bearing 17 is mounted to the mounting shaft 31 and located on the front side of the clutch assembly 80, the first bearing 17 being disposed within the support bracket 13. The support bracket 13 is formed with a mounting hole for mounting the first bearing 17. The second bearing 18 is mounted to the mounting shaft 31 and located at the rear side of the clutch assembly 80, the second bearing 18 being disposed within the housing 10. In the present embodiment, the product of the distance between the first bearing 17 and the second bearing 18 and the weight of the main unit 100a is 27mm · kg or more and 58mm · kg or less. Further, the product of the distance between the first bearing 17 and the second bearing 18 and the weight of the main unit 100a is 40mm · kg or more and 58mm · kg or less. Through the arrangement of the structures and the positions of the clutch assembly 80, the switching assembly 70 and the impact assembly 40, the distance between the first bearing 17 and the second bearing 18 is reduced, so that the size of the transmission assembly 30 along the direction of the second axis 103 is shortened, the size of the main machine 100a along the front-back direction is reduced, and the electric hammer 100 is favorably miniaturized. And the weight of the main machine 100a is greatly reduced by the arrangement of the structures and the positions of the clutch assembly 80, the switching assembly 70 and the impact assembly 40, so that a small-sized and light-weight electric hammer 100 is obtained. Furthermore, the output power of the motor 21 is greater than or equal to 360W and less than or equal to 440W, so that the electric hammer 100 can have a large power under the premise of small size and light weight of the electric hammer 100.

The second transmission portion is disposed on the front side of the first bearing in the front-rear direction, that is, the first transmission portion is disposed on the front side of the first bearing. So configured, the structure and location of the clutch assembly 80, the switching assembly 70 and the impact assembly 40 can be arranged appropriately,

in the present embodiment, the distance D between the first bearing 17 and the second bearing 18 along the second axis 103 is greater than or equal to 30mm and less than or equal to 50mm, and in some other embodiments, the distance D between the first bearing 17 and the second bearing 18 along the second axis 103 is greater than or equal to 40mm and less than or equal to 46mm, so that the distance between the first bearing 17 and the second bearing 18 is set within a proper range, that is, a sufficient space is provided between the first bearing 17 and the second bearing 18 for arranging the impact assembly 40, the switching assembly 70 and the clutch assembly 80, and simultaneously, the situation that the overall length is too long due to an excessively large distance between the first bearing 17 and the second bearing 18 can be avoided.

Further, the ratio of the weight of the main machine 100a to the output power of the motor 21 is greater than or equal to 2.2g/W and less than or equal to 4.5g/W, and in some other embodiments, the ratio of the weight of the main machine 100a to the output power of the motor 21 is greater than or equal to 3g/W and less than or equal to 4g/W, so that the weight of the main machine 100a is greatly reduced when the maximum output power of the motor 141 meets the working requirement, and the operation by a user is further facilitated.

As shown in fig. 11 to 12, at least one guide groove 131 for guiding the movement of the switching member 71 is formed on the support bracket 13. The switching member 71 partially passes through the guide groove 131 and is capable of reciprocating along the guide groove 131, and when the output assembly 50 moves along the first axis 102, the force receiving end 711 is capable of transmitting a driving force from the output assembly 50, which is transmitted to the clutch assembly 80 through the driving end 712, thereby switching the clutch assembly 80 to the first state. Of course, the support bracket 13 may be formed with two guide grooves 131 respectively disposed at both sides of the plane P. The switching member 71 is formed with two protrusions 713 spaced apart corresponding to the guide groove 131, each protrusion 713 is formed with a corresponding force-bearing end 711, and specifically, the switching member 71 is forced to slide along the guide groove 131, that is, the switching member 71 is capable of applying a driving force to the clutch assembly 80 during the movement, so as to switch the electric hammer 100 from the drill mode to the hammer drill mode. The guide groove 131 is provided on the outer edge of the support bracket 13, thereby facilitating the processing of the parts and simplifying the processing process of the parts. The guide groove 131 is parallel to the first axis 102 to minimize the length of the switching element 71 in the direction along the first axis 102 while ensuring that the functional conversion can be achieved. Of course, the switching element 71 may not be in a sliding manner, for example, a spring or the like may also be used, and the characteristic of the spring itself is used to drive the clutch assembly 80.

The support bracket 13 is formed with at least one vent hole that can penetrate the first space 15 and the second space 16, and in this application, the vent hole can be replaced by a guide groove, that is, in this embodiment, the guide groove 131 can be used not only to guide the movement of the switching element 71, but also to vent and suck air, so as to ensure the normal operation of the machine.

As shown in fig. 4 and 13, the first transmission part 52 is fixedly connected to the sleeve 51, and the force receiving end 711 of the switching member 71 abuts against the first transmission part 52. A positioning member 53 is fixedly coupled to the sleeve 51 for limiting the backward movement of the first transmission part 52 on the sleeve 51, and a positioning groove 54 for fitting the positioning member 53 is formed on the sleeve 51, and the positioning groove 54 is radially recessed inward along the outer circumference of the sleeve 51 to fit and fix the positioning member 53. The first transmission part 52 includes an intermediate member 521 and a rotation member 522, the intermediate member 521 is used for contacting with the switching element 71, and the rotation member 522 is used for contacting with the second transmission part to receive the power output by the transmission assembly 30. The rotation member 522 is formed with a receiving space 5221, the receiving space 5221 is recessed from the rotation member 522, and the intermediate member 521 is at least partially received in the receiving space 5221. In this embodiment, the switching element 71 abuts against the middle member 521, the positioning member 53 is a snap spring, the middle member 521 is specifically a washer, and the rotating member 522 is a gear. In the operation process, the clamp spring and the gear move relatively, so that the gear is abraded, the service life of the gear is influenced, and meanwhile, if the switching element 71 abuts against the gear, the gear is abraded by the switching element 71, and the service life of the gear is further influenced. By providing the spacer on the rear end surface of the gear, the switching member 71 can be prevented from directly wearing the gear, thereby prolonging the life of the gear. Of course, the spacer may be directly attached to the rear end portion of the gear, but this increases the axial dimension of the gear and the spacer, and further increases the axial dimension of the sleeve 51, and the provision of the accommodating space 5221 in the gear can avoid the increase in the axial dimension of the entire gear and the spacer in the direction of the first axis 102, and the weight of the gear and the weight of the entire gear can be reduced due to the existence of the accommodating space 5221.

The accommodating space 5221 is specifically provided at the rear end surface of the gear, and is formed by forward recessing the rear end surface of the gear, and the diameter of the accommodating space 5221 is smaller than the diameter of the root circle of the gear. Thus, under the condition that the accommodating space 5221 is ensured to have sufficient space for accommodating the gasket, the effective tooth width of the gear can not be influenced, and the stability of connection between the gear and the mounting shaft 31 is ensured.

In the embodiment, the sleeve 51 has a length L1 along the first axis 102, the main unit 100a has a length L2 along the first axis 102, and the housing 10 has a length L3 perpendicular to the first axis 102, wherein a ratio of the length L2 to the length L1 is greater than or equal to 2.5 and less than or equal to 4, and a value of the length L3 is greater than or equal to 55mm and less than 70 mm. In other embodiments, the ratio of length L2 to length L1 ranges from 3 or greater to 4 or less. Thus, through the arrangement of the positions and the structures of the clutch assembly 80, the impact assembly 40 and the output assembly 50 in the main machine 100a, the length and the width of the main machine 100a are reduced, and meanwhile, the sleeve 51 can have enough space to enable the striking part to do reciprocating motion, so that the running stability of the whole machine is ensured, the arrangement can enable the impact assembly 41 to have enough movable stroke, meanwhile, the length of the sleeve 51 in the direction of the first axis 102 can be within a reasonable range, the structure of the whole machine is small and exquisite, the condition that the length of the whole machine in the direction along the first axis 102 is overlong is avoided, and the operation of a user is facilitated. In this embodiment, the length L1 is greater than or equal to 80mm and less than or equal to 101 mm. It should be noted that the length L3 refers to the width of the housing 10 surrounding the sleeve 51.

As shown in fig. 7-8, hammer 100 further includes a locking assembly for locking impact assembly 40, which includes locking member 14. When the clutch assembly 80 is in the first state, the locking member 14 releases the movement of the impact assembly 40. When the clutch assembly 80 is in the second state, the locking member 14 prevents movement of the impact assembly 40. It is of course understood that the swing rod bearing 40a has a first position and a second position during sliding on the mounting shaft 31, and when the swing rod bearing 40a is in the first position, the bearing core 43 and the mounting shaft 31 are configured to rotate synchronously, i.e., when the electric hammer 100 is in the hammer drill mode, and when the swing rod bearing 40a is in the second outboard position, the bearing core 43 can rotate relative to the mounting shaft 31, i.e., when the electric hammer 100 is in the drill mode. In order to prolong the service life of the impact assembly 40 and facilitate the sliding of the swing rod bearing 40a on the mounting shaft 31, lubricating oil is often added into the bearing core 43, but the arrangement may cause friction between the mounting shaft 31 and the bearing core 43 due to the presence of the lubricating oil, that is, when the electric hammer 100 is in the drill mode, the friction may cause the mounting shaft 31 to rotate and drive the swing rod bearing 40a to move, so that in the drill mode, the striking member reciprocates in the sleeve 51 to strike the impact block 44, and the impact block 44 outputs impact force to the functional element, which may damage the processing workpiece and affect the working schedule. By providing the locking element 14 for preventing the impact assembly 40 from striking the impact block 44, the above situation can be avoided, thereby ensuring the operation progress of the machine and improving the experience of the user. And meanwhile, the failure rate of the machine is also reduced.

When the rocker bearing 40a is in the first position, the locking element 14 is disengaged from the bearing core 43, and the bearing core 43 can be configured to rotate synchronously with the mounting shaft 31, and when the rocker bearing 40a is in the second position, the locking element 14 is engaged with the bearing core 43, i.e., the mounting shaft 31 can rotate relative to the bearing core 43. In this embodiment, the locking element 14 is fixedly connected to or integrally formed with the housing 10, the locking element 14 includes a locking portion 141, and a clamping portion 434 matched with the locking portion 141 is provided on the bearing core 43, specifically, the bearing core 43 protrudes forward to form the clamping portion 434, so as to be matched with the locking portion 141, but of course, the bearing core 43 may also be inwardly recessed to form the clamping portion 434. Under the driving of no external force, the reset piece 83 drives the bearing core 43 to be separated from the first transmission piece 32, and the bearing core 43 moves along the second axis 103 to the position where the clamping portion 434 is matched with the locking portion 141. Further, the snap-in portion 434 is provided on the front side of the bearing core 43, and the lock portion 141 is provided at an arbitrary position in the circumferential direction of the snap-in portion 434. The locking portion 141 may be a pin, a fork, etc. fixedly connected to the housing 10, in this embodiment, the locking portion 141 is formed by a rib extending from the housing 10, and the locking portion 41 is made of an abrasion-resistant material. Of course, other embodiments are possible as long as the rotation of the bearing core 43 with the mounting shaft 31 is allowed when the swing rod bearing 40a is in the first position and the rotation of the bearing core 43 is limited when the swing rod bearing 40a is in the second position.

Fig. 16 to 23 are schematic views showing the internal structure of the electric hammer in the second embodiment. The motor, output assembly, support bracket, functional accessories, etc. in this embodiment are substantially the same as in the first embodiment, except for the specific configuration of the switching assembly, transmission assembly and locking assembly. That is, all the portions of the first embodiment corresponding to those of the present embodiment can be applied to the present embodiment, and only the differences between the present embodiment and the first embodiment will be described below.

As shown in fig. 16-18, the electric hammer 200 includes a clutch assembly 270, the clutch assembly 270 being used to switch the electric hammer 200 between the drill mode and the hammer drill mode. The impact assembly includes: the swing rod bearing 240, the swing rod bearing 240 includes a first operating state and a second operating state, when the swing rod bearing 240 is in the first operating state, the bearing core 241 of the swing rod bearing 240 rotates with the mounting shaft 231, and the electric hammer 200 is in the hammer drill mode. When the swing rod bearing 240 is in the second operating state, the bearing core 241 of the swing rod bearing 240 rotates relative to the mounting shaft 231 while the electric hammer 200 is in the drill mode.

The clutch assembly 270 includes a clutch member 271 and a resilient member 272, wherein the resilient member 272 can apply a resilient force to the clutch member 271 close to the swing rod bearing 240, so as to bring the swing rod bearing 240 into the first operating state, i.e., the hammer 200 is in the hammer drill mode. When the clutch 271 is driven to overcome the elastic force and move in a direction away from the swing rod bearing 240, the swing rod bearing 240 enters the second operation state, that is, the electric hammer 200 enters the drill mode. That is to say, only need to adopt clutch member 271 and elastic component 272 just can realize the function mode switching, great saving the part, not only can reduce the volume, shorten whole machine size, can also simplify the structure, the processing of being convenient for. Further can also lighten the complete machine weight through above-mentioned setting, convenience of customers operation machine.

As shown in fig. 16, 21 to 23, the electric hammer 200 further includes a shift assembly 290, the shift assembly 290 includes a shift member 291 for driving the clutch member 271, and the shift member 291 is for operation by a user. The user switches between the drill mode and the hammer drill mode of the electric hammer 200 by driving the shift piece 291.

Specifically, the clutch 271 and the bearing core 241 of the rocker bearing 240 rotate synchronously. An engagement portion 2712 is formed on the clutch 271, and a connection portion 2311 for engaging with the engagement portion 712 on the clutch 271 is formed on the mounting shaft 231. When the connection portion 2311 and the engagement portion 2712 are engaged, the clutch assembly is in a first state in which the bearing core 241 of the swing rod bearing 240 rotates with the mounting shaft 231, and the impact assembly can output an impact force, so that the electric hammer 200 is in a hammer drill mode. When the connection portion 2311 and the engagement portion 2712 are disengaged, the clutch 271 is in the second state in which the power transmission between the mounting shaft 231 and the bearing core 241 is disconnected, at which time the impact assembly cannot output an impact force, and the electric hammer 200 is in the drill mode.

Specifically, the clutch 271 is sleeved on the mounting shaft 231, and the clutch 271 can slide on the mounting shaft 231 along the second axis 203. The clutch 271 can rotate relative to the mounting shaft 231, and the inner wall of the clutch 271 forms an engaging portion 2712, and the engaging portion 2712 is specifically a first engaging tooth formed on the inner wall of the clutch 271. The connecting portion 2311 is a first driving tooth fixedly connected to or integrally formed with the mounting shaft 231. When the clutch 271 moves in a direction to approach the rocker bearing 240, the engagement portion 2712 of the clutch 271 moves to a state of engaging with the connection portion 2311 on the mounting shaft 231. When the clutch 271 is moved in a direction away from the rocker bearing 240, the engagement portion 2712 of the clutch 271 is moved to a state of being disengaged from the connection portion 2311.

The shift piece 291, when operated by a user, can drive the clutch 271 to move along the second axis 203 to switch the rocker bearing 240 between the first state and the second state. The shift member 291 includes a driving portion 292, and the driving portion 292 is capable of applying a driving force to the clutch member 271 so as to move the clutch member 271 away from the rocker bearing 240, thereby bringing the rocker bearing 240 into the first operation state. Specifically, the clutch 271 is provided with a force receiving portion 2711 engaged with the driving portion 292. When the user operates the switch member 291, the driving portion 292 drives the force receiving portion 2711 to move forward, so that the engaging portion 2712 of the clutch member 271 is separated from the connecting portion 2311 of the mounting shaft 231, and the mounting shaft 231 can move relative to the bearing core 241. An engaging portion 2713 is formed on the clutch 271, an extending portion 2411 for engaging with the engaging portion 2713 on the clutch 271 is formed on the bearing core 241, and the clutch 271 and the bearing core 241 of the rocker bearing 240 rotate synchronously. An engaging portion 2713 is provided at the rear end of the engaging portion 2712, the engaging portion 2713 being embodied as a second engaging tooth formed on the inner wall of the clutch 271. The extending portion 2411 is a second driving tooth fixedly connected to or integrally formed with the bearing core 241. The second engagement teeth and the second driving teeth are always kept engaged in the process of the sliding of the clutch 271.

The elastic member 272 is fitted on the mounting shaft 231, the elastic member 272 is disposed at least partially inside the clutch member 271, and the elastic member 272 is disposed on the front side of the clutch member 271 in the direction along the second axis. In this embodiment, the front end of the elastic member 272 is connected to the first bearing 217 on the mounting shaft 231, and the rear end of the elastic member 272 is connected to the engaging portion 2712 on the clutch 271.

As shown in fig. 19-23, the electric hammer 200 further includes a locking assembly 214 for locking the swing rod bearing 240, i.e., the locking assembly 214 prevents the bearing core 241 of the swing rod bearing 240 from rotating when the electric hammer 200 is in the drill mode. When the hammer 200 is in the hammer drill mode, the locking assembly 214 allows the bearing core 241 of the swing rod bearing 240 to rotate.

In this embodiment, the locking assembly 214 includes a locking member 215, a deformable locking portion 216 is connected to the locking member 215, and a catching portion 2714 engaged with the locking portion 216 and used for preventing the clutch 271 from rotating is connected to the clutch 271. The housing 210 has a receiving portion 211 formed thereon, and the locking member 215 is at least partially disposed in the receiving portion 211. The locking member 215 is preferably made of a flexible member such as a spring pin, a resilient post, etc., and in this embodiment the locking member 215 is a torsion spring mounted in the receiving portion 211 with an end portion thereof extending upwardly to be engageable with the clutch 271. The catching portion 2714 is a stopper tooth formed to protrude forward on the clutch 271. When the hammer 200 is in the drill mode, the torsion spring is engaged with the stopping teeth of the clutch 271, that is, the clutch 271 cannot rotate, so that the bearing core 241 cannot move. When the electric hammer 200 is in the hammer drill mode, the torsion spring does not contact the stop teeth, i.e., the bearing core 2411 can rotate along with the rotation of the clutch 271. Wherein the deformation means that, when the stopping teeth are engaged with the locking part 216, the stopping teeth lower the pressure of the locking part 216, i.e., the stopping teeth exert a contact force on the locking part 216, the locking part 216 receives the contact force and generates a certain degree of deformation, thereby avoiding damaging parts, and meanwhile, the locking part 216 generates a force for avoiding the stopping teeth from disengaging from the locking part 216, thereby ensuring the stability of the structure.

It should be noted that the host mentioned herein refers to a bare machine with the functional accessories, energy source and auxiliary handle removed.

The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It should be understood by those skilled in the art that the above embodiments do not limit the present invention in any way, and all technical solutions obtained by using equivalent alternatives or equivalent variations fall within the scope of the present invention.

Claims

1. An electric hammer comprising:

the main machine comprises a machine shell and a motor at least partially arranged in the machine shell, wherein the motor rotates along the axis of the motor;

a battery pack for providing a source of energy to the motor, the battery pack being removably mounted to the housing;

the host further comprises:

an output assembly including a sleeve rotatable about a first axis;

the impact assembly comprises a swing rod bearing and an impact block which can be driven by the swing rod bearing to reciprocate in the sleeve, and the impact block can output impact force forwards when moving in the sleeve;

the mounting shaft is used for mounting the swing rod bearing and can be driven by the motor to rotate around a second axis;

the electric hammer has a drill mode and a hammer drill mode;

the sleeve rotates when the electric hammer is in the drill mode;

when the electric hammer is in the hammer drill mode, the sleeve rotates, and the impact block reciprocates in the sleeve;

the method is characterized in that:

the host further comprises:

a first bearing mounted to the mounting shaft to support the mounting shaft;

a second bearing mounted to the mounting shaft to support the mounting shaft;

wherein a product of a distance between the first bearing and the second bearing and a weight of the main machine is not less than 27 mm-kg and not more than 58 mm-kg.

2. The electric hammer of claim 1, wherein:

the swing rod bearing includes: a bearing core mounted to the mounting shaft, and a swing lever mounted to the bearing core;

the swinging rod comprises a ring sleeved on the bearing core and a connecting rod which is integrally formed with the ring and extends along a first linear direction;

when the bearing core is driven, the swinging rod moves along with the bearing core, and at least a first limit position is included in the movement process of the swinging rod;

when the swing rod is at a first limit position, the connecting rod is inclined forwards to a first limit angle, and the first straight line is parallel to or coincided with the motor axis;

wherein, the distance between the first straight line and the axis of the motor is more than or equal to 0mm and less than or equal to 20 mm.

3. The electric hammer of claim 1, wherein:

when the swing lever is at a first limit position, the connecting rod is tilted forward to a first limit angle, and the first line intersects the motor axis;

wherein an intersection point of the first axis and the motor axis is on the motor.

4. The electric hammer of claim 1, wherein:

the output power of the motor is more than or equal to 360W and less than or equal to 440W.

5. The electric hammer of claim 1, wherein:

the ratio of the weight of the main machine to the output power of the motor is more than or equal to 2.2g/W and less than or equal to 4.5 g/W.

6. The electric hammer of claim 1, wherein:

the swing rod bearing comprises a bearing core mounted to the mounting shaft;

the first bearing and the second bearing are respectively arranged on two sides of the bearing core.

7. The electric hammer of claim 6, wherein:

the electric hammer further comprises: the supporting bracket is fixedly connected with the shell or integrally formed, and is used for integrating the mounting shaft and the sleeve into a whole;

the first bearing is installed to the installation shaft and located on the front side of the bearing core, and the first bearing is arranged in the supporting bracket.

8. The electric hammer of claim 7, wherein:

the electric hammer comprises a first transmission piece for transmitting the power of the motor to the mounting shaft,

the second bearing is installed to the installation shaft and located on the rear side of the first transmission piece, and the second bearing is arranged in the machine shell.

9. The electric hammer of claim 7, wherein:

the electric hammer further comprises a clutch assembly for switching the electric hammer between the hammer drill mode and the hammer drill mode, the clutch assembly being capable of driving the swing rod bearing to rotate about a second axis;

the second bearing is arranged at the rear side of the clutch component and is arranged in the shell.

10. The electric hammer of claim 1, wherein:

the distance between the first bearing and the second bearing along the second axis is greater than or equal to 30mm and less than or equal to 50 mm.