Electric hammer

Abstract

The present application provides a kind of electric hammer, the overall weight of the electric hammer is between 0.9Kg to 1.6Kg, it includes: motor, intermediate shaft, swing lever bearing and cylinder assembly;The motor is drivingly connected with intermediate shaft;The cylinder assembly includes: cylinder, the ram housed in the cylinder and the ram matched with the ram;The swing lever bearing is sleeved on the intermediate shaft, and the swing lever of the swing lever bearing is connected with the cylinder;The ratio of the distance from the center line of the cylinder to the center line of the intermediate shaft to the inner diameter of the cylinder is 1.20 to 1.44.The electric hammer of the present application realizes small size while ensuring the work efficiency basically unchanged.

Description

Technical Field

[0001] This invention relates to an electric hammer, belonging to the field of power tool technology. Background Technology

[0002] Various power tools are often used in engineering construction, such as using electric hammers to drill holes in concrete, floor slabs, brick walls, and stone.

[0003] Existing electric hammers with a total weight between 0.9 kg and 1.6 kg mainly consist of a motor, transmission mechanism, impact mechanism, and chuck. The total weight refers to the weight of the electric hammer after removing the battery pack, auxiliary handle, and working head. Specifically, the transmission mechanism includes: an intermediate shaft connected to the motor, a rocker arm bearing and an intermediate gear mounted on the intermediate shaft, which rotate together with the intermediate shaft. The impact mechanism includes: a cylinder connected to a rocker arm mounted on the rocker arm bearing, a hammer housed within the cylinder, and a striking rod that cooperates with the hammer. A chuck is fixed at the front end of the impact mechanism to hold different types of working heads, thereby achieving drilling purposes under different working conditions.

[0004] However, the existing electric hammers are quite large, making them uncomfortable for operators to hold and causing inconvenience. Summary of the Invention

[0005] This invention provides an electric hammer to solve the above-mentioned or other potential technical problems existing in the prior art.

[0006] According to some embodiments of the present invention, an electric hammer is provided, the weight of which is between 0.9 kg and 1.6 kg, and it includes: a motor, an intermediate shaft, a rocker arm bearing, and a cylinder assembly; the motor is drivenly connected to the intermediate shaft; the cylinder assembly includes: a cylinder, a hammer housed in the cylinder, and a striking rod cooperating with the hammer; the rocker arm bearing is sleeved on the intermediate shaft, and the rocker arm of the rocker arm bearing is connected to the hammer; the ratio of the distance from the centerline of the cylinder to the centerline of the intermediate shaft to the inner diameter of the cylinder is 1.20 to 1.75.

[0007] In the electric hammer described above, the distance from the centerline of the cylinder to the centerline of the intermediate shaft is 23.5 mm to 25.5 mm.

[0008] In the electric hammer described above, the distance from the centerline of the cylinder to the centerline of the intermediate shaft is 24.5 mm.

[0009] The electric hammer described above further includes an input gear and a chuck assembly. The input gear is sleeved on the intermediate shaft and is connected to the motor for transmission. The chuck assembly is located in front of the impact rod. The ratio of the distance from the input gear to the chuck assembly to the inner diameter of the cylinder is 6.32 to 7.11.

[0010] In the electric hammer described above, the distance from the input gear to the chuck assembly is 120mm to 135mm.

[0011] The electric hammer as described above, wherein the striking rod comprises: a first part and a second part, the end face of the first part mates with the hammer, the end face of the second part mates with the working head, and the cross-sectional area of ​​the second part is larger than the cross-sectional area of ​​the first part.

[0012] In the electric hammer described above, the ratio of the length of the striking rod to the inner diameter of the cylinder is 0.667 to 0.865.

[0013] The electric hammer described above, wherein the length of the striking rod is 13mm to 16mm.

[0014] The electric hammer described above, wherein the outer diameter of the motor is no greater than 46 mm.

[0015] In the electric hammer described above, the stack length of the motor is no more than 15mm, where the stack length of the motor refers to the overlap length of the rotor and stator in the motor.

[0016] In the electric hammer described above, the inner diameter of the cylinder is 18.5 mm to 19.5 mm.

[0017] The electric hammer described above, wherein the inner diameter of the cylinder is 19 mm.

[0018] The electric hammer described above, wherein the weight of the hammer is 36 grams to 46 grams.

[0019] The electric hammer described above, wherein the weight of the hammer is 42 grams.

[0020] The electric hammer described above, wherein the frequency of the hammer striking the striking rod is 5400 to 6000 times per minute.

[0021] The electric hammer described above has a total weight of 1.4 kg.

[0022] According to the technical solution of the present invention, when the ratio of the distance from the center line of the cylinder to the center line of the intermediate shaft to the inner diameter of the cylinder is 1.20 to 1.75, the electric hammer is small in size and its working efficiency remains basically unchanged. It is more convenient for the operator to hold the electric hammer and more flexible in operation.

[0023] The advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The above and other objects, features, and advantages of embodiments of the present invention will become more readily understood from the following detailed description with reference to the accompanying drawings. In the drawings, various embodiments of the invention will be described by way of example and non-limitation, wherein:

[0025] Figure 1 This is a schematic diagram of the structure of the electric hammer provided in an embodiment of the present invention;

[0026] Figure 2 for Figure 1 A schematic diagram of the impact rod.

[0027] In the picture:

[0028] 11. Motor; 121. Intermediate shaft;

[0029] 122. Input gear; 123. Rocker arm bearing;

[0030] 124. Output gear; 131. Cylinder;

[0031] 132. Strike hammer; 133. Strike bar;

[0032] 1331. Rear end face; 1332. Front end face;

[0033] 1333, Boss; 1334, Sealing groove;

[0034] 141. Rotating sleeve; 142. Transmission gear;

[0035] 143. Locking block; 15. Housing;

[0036] 16. Handle; 171. Slide sleeve;

[0037] 172. Dust cover; 173. Washer;

[0038] 174. Pressure plate; 175. Spring;

[0039] D: Distance from the centerline of the cylinder to the centerline of the intermediate shaft;

[0040] L: Distance from the input gear to the chuck assembly;

[0041] d: The inner diameter of the cylinder. Detailed Implementation

[0042] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0043] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0044] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0045] Example 1

[0046] Figure 1 This is a schematic diagram of the electric hammer provided in this embodiment. Figure 2 for Figure 1 A schematic diagram of the impact rod structure. It should be noted that the electric hammer of this embodiment is suitable for electric hammers with a total weight between 0.9 kg and 1.6 kg. Preferably, the total weight of the electric hammer is between 1.2 kg and 1.6 kg, and further, the total weight of the electric hammer is 1.4 kg. Here, the total weight refers to the weight of the electric hammer after removing the battery pack, auxiliary handle, and working head.

[0047] like Figure 1 As shown, the electric hammer of this embodiment includes a housing 15, a motor 11, a transmission mechanism, a cylinder assembly, and a rotating sleeve 141. The front end of the housing 15 ( Figure 1 The right end of the machine casing 15 is the working end of the electric hammer during operation. Figure 1 The left end of the hammer is the grip for the user to hold it, and a handle 16 is provided at the rear end of the housing 15. A rotating sleeve 141 is installed inside the housing 15, and the handle 16 is tilted relative to the axis of the rotating sleeve 141.

[0048] The rotating sleeve 141 houses a cylinder assembly that provides power for the hammering operation of the working head. This cylinder assembly includes: a cylinder 131 housed within the rotating sleeve 141 and capable of reciprocating motion; a hammer 132 housed within the cylinder 131; and striking rods 133 with their ends respectively cooperating with the hammer 132 and the working head. Please refer to... Figure 2 Optionally, a sealing groove 1334 is provided on the hammer 132, and a sealing ring is installed in the sealing groove 1334 to improve the sealing performance between the hammer 132 and the rotating sleeve 141. Similarly, a sealing groove 1334 can also be provided on the striking rod 133, and a sealing ring can be installed in the sealing groove 1334 to improve the sealing performance between the striking rod 133 and the rotating sleeve 141. It can be understood that when both the hammer 132 and the striking rod 133 have sealing grooves 1334, they can play a sealing role, thereby preventing grease leakage.

[0049] The front of the rotating sleeve 141 has a long groove that radially penetrates the outer wall of the rotating sleeve 141 and closes in a direction parallel to the axis of the rotating sleeve 141. The groove wall is set with an inclined surface, and a roughly spherical locking block 143 is installed in the long groove. When the locking block 143 is engaged in the long groove, the locking block 143 can only partially extend into the rotating sleeve 141 under the restriction of the inclined surface to cooperate with the groove opened on the working head, so that the locking block 143 will not fall into the rotating sleeve 141. A chuck assembly for holding the working head is also sleeved on the front of the rotating sleeve 141, that is, a chuck assembly is provided in front of the strike bar 133. The chuck assembly includes: a sliding sleeve 171 sleeved on the outer periphery of the rotating sleeve 141, and a dust cover 172 installed on the front end of the sliding sleeve 171. A washer 173, which mates with the locking block 143, is fixed inside the sliding sleeve 171 to restrict the locking block 143 and prevent it from dislodging from the long groove. A pressure plate 174, which mates with the locking block 143, is fixed at the rear of the washer 173. A spring 175 is provided between the pressure plate 174 and the rotating sleeve 141. The rotating sleeve 141 includes a front part, a rear part, and a stepped surface connecting the front part and the rear part, with the diameter of the front part being smaller than the diameter of the rear part. One end of the spring 175 abuts against the stepped surface, and the other end abuts against the rear surface of the pressure plate 174.

[0050] A transmission gear 142, which is connected to the transmission mechanism, is also fixed on the rotating sleeve 141 to drive the rotating sleeve 141 to rotate. In this embodiment, the transmission mechanism includes an input gear 122, a rocker arm bearing 123, an intermediate shaft 121, and an output gear 124. The input gear 122 of the transmission mechanism is fixed on the intermediate shaft 121 and meshes with the gear on the output shaft of the motor 11 to drive the intermediate shaft 121 of the transmission mechanism to rotate. The output gear 124 of the transmission mechanism is mounted on the intermediate shaft 121 and meshes with the transmission gear 142 fixed on the rotating sleeve 141 to drive the rotating sleeve 141 to rotate.

[0051] Continue to refer to Figure 1 The rocker arm bearing 123 of the transmission mechanism includes an inner ring and an outer ring. The inner ring is sleeved on the second shaft portion of the intermediate shaft 121 and can rotate around the central axis. The rocker arm, which is integrally formed with the outer ring, is hinged to the cylinder 131 of the cylinder assembly. Thus, when the intermediate shaft 121 drives the inner ring to rotate, the rocker arm can swing along the axis of the intermediate shaft 121, causing the cylinder 131 to reciprocate along the axis of the rotating sleeve 141. This compresses the air between the inner wall of the cylinder 131 and the hammer 132, pushing the hammer 132 to strike the striking rod 133, thereby driving the working head to reciprocate along the axis of the rotating sleeve 141 for chiseling operations.

[0052] It can be imagined that when the transmission gear 142 on the rotating sleeve 141 and the hammer 132 in the cylinder assembly are driven simultaneously through the intermediate shaft 121, drilling and chiseling operations can be performed simultaneously if the working head is held in the chuck assembly.

[0053] However, existing electric hammers are too bulky, making them inconvenient for operators. To reduce the size of electric hammers, those skilled in the art have attempted to miniaturize some individual components. For example, some solutions involve adjusting the motor 11 from its length direction to an angle relative to the length of the hammer. However, while this reduces the length to some extent, it increases the width. Furthermore, such hammers remain very inconvenient to operate in confined spaces. Another example is the reduction of the inner diameter d of the cylinder 131; however, this significantly decreases the hammer's efficiency. Therefore, how to reduce the size of the electric hammer while maintaining its efficiency remains a difficult problem that has yet to be solved in this field.

[0054] To obtain a compact electric hammer that maintains essentially the same working efficiency, the applicant conducted extensive testing and experiments on various components affecting the hammer's size and efficiency (including but not limited to the motor 11, transmission mechanism, rotating sleeve 141, chuck assembly, and cylinder assembly) and their interoperability. The results showed that controlling the ratio between the distance D (the distance between the center line of cylinder 131 and the center line of intermediate shaft 121) and the inner diameter d of cylinder 131 can make the electric hammer more compact while maintaining essentially the same working efficiency. This makes it easier for the operator to grip the hammer and facilitates drilling, chiseling, and other operations. Specifically, when the ratio of the center distance D to cylinder 131d is between 1.20 and 1.75, the hammer's volume is reduced by at least 15% compared to electric hammers of the same weight class on the market, while ensuring that the hammer's working efficiency is not reduced.

[0055] Furthermore, in order to make the electric hammer have a smaller width ( Figure 1 The center distance (vertical distance) is used to reduce the overall size of the machine. The center distance D can be any value from 23.5mm to 31.5mm, for example, D can be 23.5mm, 24.5mm, 25.5mm, or 31.5mm. Actual testing has shown that when the center distance D is between 23.5mm and 25.5mm, the fit between the size and operability of the electric hammer is relatively good. Preferably, when the center distance D is 24.5mm, the electric hammer is compact and easy for the operator to hold and operate, while ensuring sufficient space for movement of various parts inside the electric hammer.

[0056] It should be understood that in this embodiment, when the center distance D takes any value from 23.5mm to 31.5mm, it is only necessary for the inner diameter d of the cylinder 131 to satisfy the ratio of the center distance D to it to be 1.20 to 1.75. In this embodiment, the value of the inner diameter d of the cylinder 131 is not limited.

[0057] Specifically, each center distance D can correspond to the same inner diameter value of the cylinder 131, such as 17mm, 19mm, or 20mm. Of course, during design, each center distance D can also correspond to different inner diameter values ​​d of the cylinder 131. For example, in some optional embodiments, the center distance D is 31.5mm, and the inner diameter d of the cylinder 131 is 18mm, meaning the ratio is 1.75. In this case, the volume of the electric hammer is already smaller than that of electric hammers of the same weight class on the market, making it more convenient for users to operate. In other optional embodiments, the preferred center distance D is 24.5mm, in which case the inner diameter d of the cylinder 131 is 19mm, meaning the ratio is 1.29. This allows for further reduction in the volume of the electric hammer, enhances its ease of operation, and further strengthens the compatibility between the hammer's size and operability. In some other embodiments, the center distance D is 23.5 mm and the inner diameter d of the cylinder 131 is 19.5 mm, that is, the ratio of the two is 1.20, at which point the volume of the electric hammer is further reduced.

[0058] In this embodiment, the electric hammer can reduce its size by controlling the ratio between the center distance D and the inner diameter d of the cylinder 131, making it more compact and easier for the operator to use it to perform drilling, chiseling, and other operations on the surface of the workpiece, while ensuring that the working efficiency of the electric hammer remains basically unchanged.

[0059] Example 2

[0060] This implementation improves upon Example 1 by modifying the distance L (hereinafter referred to as "box length") from the input gear 122 of the electric hammer to the chuck assembly, in order to further reduce the volume of the electric hammer.

[0061] Specifically, in this embodiment, the ratio of the box length L to the inner diameter d of the cylinder 131 is set to 6.32 to 7.11 to reduce the length of the electric hammer, thereby reducing its volume. Optionally, the box length L can be set to 120mm to 135mm to make the overall structure of the electric hammer more compact while still allowing the internal structure to be installed, thus reducing its volume. For example, if the box length L is 120mm and the inner diameter d of the cylinder 131 is 19mm, the center distance D can be selected as 24.5mm. Another example: if the box length L is 123.7mm and the inner diameter d of the cylinder 131 is 19mm, the center distance D can be selected as 24.1mm. Yet another example: if the box length L is 135mm and the inner diameter d of the cylinder 131 is 19mm, the center distance D can be selected as 25.35mm.

[0062] Optionally, such as Figure 2 As shown, in order to make the distance L from the input gear 122 to the chuck assembly satisfy the above value, the cross-sectional area of ​​the end face of the second part of the impact rod 133 that mates with the working head can be set to be greater than the cross-sectional area of ​​the end face of the first part of the impact rod 133 that mates with the hammer 132. That is, the inner diameter of the front end face 1332 of the impact rod 133 that mates with the working head is greater than the inner diameter of the rear end face 1331 of the impact rod 133 that mates with the hammer 132. Specifically, the rear end of the striking rod 133 that mates with the hammer 132 is formed into a boss 1333, while the front end of the striking rod 133 that mates with the working head is not formed into a boss 1333. This prevents the front end of the striking rod 133 from extending into the smaller front part of the rotating sleeve 141 as in the existing hammer 132. Correspondingly, in order to accommodate the shortened striking rod 133, the distance between the rotating sleeve 141 and the chuck assembly of the electric hammer in this embodiment is reduced so that the rear end of the working head can contact the striking rod 133 when it is working, so as to transfer the hammering energy to the surface of the workpiece.

[0063] Optionally, the ratio of the length of the impact rod 133 to the inner diameter d of the cylinder 131 can be 0.667 to 0.865, thereby minimizing energy loss between the hammer 132 and the impact rod 133, improving the working efficiency of the hammer 132, and reducing the size of the electric hammer.

[0064] In practical design, the length of the impact rod can be from 13mm to 16mm, preferably 15.5mm. For example, the length of the impact rod 133 can be 13mm, and the inner diameter d of the cylinder 131 is 19.5mm. In this case, the length L of the housing can be selected as 135mm, and the center distance D can be selected as 25.5mm. As another example, the length of the impact rod 133 can be 15.5mm, and the inner diameter d of the cylinder 131 is 19mm. In this case, the length L of the housing can be selected as 120mm, and the center distance D can be selected as 24.5mm. Yet another example, the length of the impact rod 133 can be 16mm, and the inner diameter d of the cylinder 131 is 18.5mm. In this case, the length L of the housing can be selected as 130mm, and the center distance D can be selected as 24.1mm. In this embodiment, the length of the impact rod is preferably 15.5mm, and the inner diameter d of the cylinder 131 is preferably 19mm.

[0065] In this embodiment, by setting the ratio of the housing length L to the inner diameter d of the cylinder 131 to 6.32 to 7.11, the length of the electric hammer can be reduced, thereby shrinking its volume. Furthermore, when the housing length L is 120mm to 135mm, it not only provides sufficient length for arranging the transmission mechanism, rotating sleeve 141, sliding sleeve 171, and cylinder assembly, but also makes the electric hammer's structure compact and reduces energy loss from the hammer 132 and impact rod 133.

[0066] Example 3

[0067] This embodiment further reduces the width of the electric hammer based on any of the above embodiments, in order to reduce the volume of the electric hammer.

[0068] Specifically, in this embodiment, the outer diameter of the motor 11 is no greater than 46mm to reduce the volume occupied by the motor 11, thereby reducing the size of the electric hammer. Optionally, the stacking length of the motor 11 can also be set to no greater than 15mm, which can further reduce the volume occupied by the motor 11 while ensuring that the working capacity of the motor 11 can meet the requirements for drilling, chiseling, and other operations on the surface of the workpiece. Furthermore, when the outer diameter of the motor 11 is 46mm and the stacking length is 15mm, the size of the electric hammer can be reduced compared to electric hammers with the same hammering weight on the market. In this embodiment, the stacking length of the motor 11 refers to the overlap length of the rotor and stator in the motor 11.

[0069] The electric hammer in this embodiment can further reduce its size while ensuring that the working efficiency of the electric hammer basically meets the requirements, thereby making the electric hammer more compact.

[0070] Example 4

[0071] This embodiment is an improvement based on any of the above embodiments, aimed at increasing the working efficiency of the electric hammer, that is, the efficiency of the electric hammer in performing operations such as drilling and chiseling on the surface of a workpiece. Specifically, working efficiency refers to the inverse ratio of the time required for the electric hammer to drill holes of the same diameter and depth using a working head of the same diameter.

[0072] Although the above embodiments reduce the volume of the electric hammer by at least 15% compared to electric hammers of the same weight class on the market, while ensuring that the working efficiency of the electric hammer remains basically unchanged or only slightly reduced, the applicant once again conducted extensive tests and experiments on the components affecting the working efficiency of the electric hammer (including but not limited to the motor 11, the rotating sleeve 141, the cylinder assembly, etc.) and their coordination. The results showed that when the inner diameter d of the cylinder 131 is set to 18.5mm to 19.5mm, the working efficiency of the electric hammer can be improved while reducing its volume.

[0073] Specifically, the working power of the working head held in the hammer chuck assembly comes from the hammering kinetic energy of the impact rod 133 in the cylinder assembly and the rotational torque of the working head driven by the rotating sleeve 141. Generally, to improve the working efficiency of the hammer and reduce the drilling time on the workpiece, it is necessary to increase the frequency of the impact rod 133 striking the working head per unit time, or the number of rotations of the working head per unit time. When the diameter of the cylinder 131 is 18.5mm to 19.5mm, the single impact energy of the hammer 132 striking the impact rod 133 can be increased. Matching the corresponding center distance D, the working efficiency of the hammer 132 can be improved while reducing its volume. After actual testing, it was found that the hammer of this embodiment, compared with hammers 132 of the same weight class on the market, can not only reduce its volume by at least 15%, but also increase its working efficiency by at least 20%.

[0074] In the specific design, the inner diameter d of cylinder 131 and the center distance D can be arbitrarily matched, as long as the ratio in Embodiment 1 is satisfied. For example, when the inner diameter d of cylinder 131 is 18.5mm, the center distance D can be selected as 31.5mm. As another example, when the inner diameter d of cylinder 131 is 19mm, the center distance D can be selected as 24.5mm; these values ​​are also preferred values ​​in this embodiment. The electric hammer with these values ​​not only has a smaller size and higher working efficiency, but also better matching between the two. As yet another example, when the inner diameter d of cylinder 131 is 19.5mm, the center distance D can be selected as 23.5mm.

[0075] Furthermore, the weight of the hammer 132 can be set to 34g to 42g to further increase the single impact energy when the hammer 132 strikes the striking rod 133, thereby improving the working efficiency of the electric hammer. For example, when the weight of the hammer 132 is 34g, the diameter of the cylinder 131 can be selected as 18.5mm. As another example, when the weight of the hammer 132 is 38g, the diameter of the cylinder 131 can be selected as 19mm. Preferably, when the weight of the hammer 132 is 42g, the diameter of the cylinder 131 can be selected as 19.5mm.

[0076] After testing, in a specific test prototype, the electric hammer weighed 1.4 kg, with a center distance D of 24.5 mm, a housing length L of 123.7 mm, a striker length of 15.5 mm, a motor outer diameter * stack length of 46 mm * 15 mm, a hammer mass of 38 g, and a cylinder inner diameter d of 19 mm. When using this electric hammer to drill holes with a depth of 50 mm and diameters of 6 mm, 8 mm, and 10 mm, the time required was only 5.3 seconds, 6.8 seconds, and 9.5 seconds respectively. This is at least 1.8 seconds, 2.3 seconds, and 0.7 seconds shorter than the time required by electric hammers of the same weight class on the market to drill holes of the same depth and diameter. The test data shows that the working efficiency of the electric hammer in this embodiment is significantly improved compared to existing electric hammers.

[0077] In this embodiment, the electric hammer can further improve its working efficiency while ensuring the compact size of the hammer body by controlling the inner diameter d of the cylinder 131.

[0078] Example 5

[0079] This embodiment is an improvement upon Embodiment 1, Embodiment 2, or Embodiment 3 to enhance the working efficiency of the electric hammer. Specifically, the frequency of the hammer 132 striking the striking rod 133 is set to 5400 to 6000 times per minute. By controlling the striking frequency of the hammer 132, good working efficiency can be achieved.

[0080] Specifically, in actual design, the frequency of the hammer 132 striking the rod 133 can be adjusted by selecting and matching the motor 11, the rocker arm bearing, and the number of teeth and the module of the gears, thereby improving the working efficiency of the electric hammer.

[0081] Example 6

[0082] Based on any of the above embodiments, optionally, the electric hammer can operate normally at high temperatures by selecting high-temperature resistant grease and using high-temperature resistant materials to manufacture the transmission mechanism. Alternatively, a figure-eight bracket can be used to support and position the intermediate shaft 121 and the cylinder 131 to improve the positioning strength of the cylinder 131 and the intermediate shaft 121, thereby enhancing the stability of the cylinder 131. See Chinese Patent Publication No. CN206066361U, the entirety of which is incorporated herein by reference. Further optionally, a sealing ring can be provided between the motor 11 bracket and the housing 15, and a pressure relief hole can be provided between the output gear 124 and the transmission gear 142 to improve the sealing performance of the grease. See Chinese Patent Publication No. CN204913815U, the entirety of which is incorporated herein by reference.

[0083] In the description of this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0084] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. An electric hammer, wherein the total weight of the electric hammer is between 0.9 kg and 1.6 kg, the total weight referring to the weight of the electric hammer excluding the battery pack, auxiliary handle, and working head, the electric hammer comprising: Motor, intermediate shaft, rocker arm bearing, and cylinder assembly; The motor is connected to the intermediate shaft for transmission. The cylinder assembly includes: a cylinder, a hammer housed within the cylinder, and a striking rod cooperating with the hammer; The rocker arm bearing is sleeved on the intermediate shaft, and the rocker arm of the rocker arm bearing is connected to the cylinder; The feature is that the ratio of the distance from the centerline of the cylinder to the centerline of the intermediate shaft to the inner diameter of the cylinder is 1.20 to 1.

44.

2. The electric hammer according to claim 1, characterized in that, The distance from the centerline of the cylinder to the centerline of the intermediate shaft is 23.5 mm to 25.5 mm.

3. The electric hammer according to claim 1, characterized in that, It also includes an input gear and a chuck assembly. The input gear is sleeved on the intermediate shaft and is connected to the motor drive. The chuck assembly is installed in front of the striker. The ratio of the distance from the input gear to the chuck assembly to the inner diameter of the cylinder is 6.32 to 7.

11.

4. The electric hammer according to claim 3, characterized in that, The distance from the input gear to the chuck assembly is 120mm to 135mm.

5. The electric hammer according to claim 4, characterized in that, The ratio of the length of the impact rod to the inner diameter of the cylinder is 0.667 to 0.865; and / or the length of the impact rod is 13 mm to 16 mm.

6. The electric hammer according to claim 1, characterized in that, The outer diameter of the motor is no greater than 46mm.

7. The electric hammer according to any one of claims 1-6, characterized in that, The cylinder has an inner diameter of 18.5 mm to 19.5 mm.

8. The electric hammer according to claim 7, characterized in that, The hammer weighs between 36 and 46 grams.

9. The electric hammer according to any one of claims 1-6, characterized in that, The frequency of the hammer striking the batter is 5400 to 6000 times per minute.

10. The electric hammer according to any one of claims 1-6, characterized in that, The electric hammer weighs 1.4 kg.

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