Patent Application
20250205857
This application claims the benefit under 35 U.S.C. § 119(a) of Chinese Patent Application No. 202311788228.7, filed on Dec. 22, 2023, and Chinese Patent Application No. 202323530966.X, filed on Dec. 22, 2023, which applications are incorporated herein by reference in their entireties.
The present application relates to the field of power tools and, in particular, to an impact tool.
An impact tool refers to a tool capable of outputting rotational movements at a certain impact frequency. Common impact tools include an impact wrench, an impact screwdriver, an impact drill, and the like. The impact wrench is typically used for screwing bolts, nuts, and the like. The impact screwdriver is typically used for loosening or tightening screws and the like. The impact drill is typically used for drilling holes through impact.
To output the rotational movements at a certain impact frequency, the impact tool typically includes an output assembly for outputting a rotational force and an impact mechanism for impacting the output assembly cyclically.
Among products in the related art, impact tools outputting higher impact torque require higher output power from direct current power supplies to output higher torque.
This part provides background information related to the present application, and the background information is not necessarily the existing art.
An impact tool includes: a motor including a drive shaft that rotates about a first axis; an output shaft including an output axis defined by the output shaft, where the output shaft rotates about the output axis to output power; an impact mechanism applying an impact force to the output shaft, where the impact mechanism includes an impact block driven by the motor and a hammer anvil mating with the impact block and impacted by the impact block; a transmission mechanism configured to transmit torque outputted from the drive shaft to the output shaft, where the transmission mechanism includes a multi-stage transmission assembly; and a direct current power supply powering at least the motor, where the nominal voltage of the direct current power supply is less than 18 V, and fastening torque of the output shaft on a workpiece is greater than or equal to 170 N·m.
In some examples, the multi-stage transmission assembly includes at least two stages of planet gear reduction assemblies.
In some examples, the multi-stage transmission assembly includes: a first planet carrier disposed in front of the motor; first planet gears supported by the first planet carrier; a second planet carrier disposed in front of the first planet carrier; second planet gears supported by the second planet carrier; and an inner ring gear causing at least the second planet gears to perform a planetary motion.
In some examples, the outer diameter of the inner ring gear is less than or equal to 50 mm.
In some examples, the impact mechanism further includes a main shaft connecting the impact block to the drive shaft and a first bearing supporting the rotation of the main shaft, and the first bearing restrains axial displacement of the inner ring gear.
In some examples, the first bearing overlaps with the second planet carrier along the direction of the first axis.
In some examples, the ratio of a rotational speed of the drive shaft to a rotational speed of the main shaft is substantially a constant value.
In some examples, the gear ratio from the drive shaft to the main shaft is higher than or equal to 9.
In some examples, the inner ring gear separately causes the first planet gears and the second planet gears to perform planetary motions.
In some examples, the maximum rotational speed of the output shaft is less than or equal to 3000 rpm.
In some examples, the nominal voltage of the direct current power supply is greater than or equal to 3 V and less than or equal to 9 V.
In some examples, a housing is further included and is configured to have an accommodation space, where the motor is disposed in the accommodation space, and the distance L1 from the rear end of the housing to the front end of the output shaft is less than or equal to 145 mm.
In some examples, the distance L1 from the rear end of the housing to the front end of the output shaft is less than or equal to 135 mm.
In some examples, the transmission mechanism further includes a housing assembly, the housing assembly includes first recesses provided on the outer side of the housing assembly and extending inward and second recesses provided on the inner side of the housing assembly and extending outward, where the first recesses and the second recesses are circumferentially spaced apart.
In some examples, the diameter of the impact block is greater than or equal to 40 mm, and the mass of the impact block is greater than or equal to 120 g.
An impact tool includes: a motor including a drive shaft that rotates about a first axis; an output shaft including an output axis defined by the output shaft, where the output shaft rotates about the output axis to output power; an impact mechanism applying an impact force to the output shaft, where the impact mechanism includes an impact block driven by the motor and a hammer anvil mating with the impact block and impacted by the impact block; a transmission mechanism configured to transmit torque outputted from the drive shaft to the output shaft; and a direct current power supply powering at least the motor, where the nominal voltage of the direct current power supply is greater than or equal to 3 V and less than or equal to 9 V. Fastening torque of the output shaft on a workpiece is greater than or equal to 170 N·m.
An impact tool includes: a motor including a drive shaft that rotates about a first axis; an output shaft including an output axis defined by the output shaft, where the output shaft rotates about the output axis to output power; an impact mechanism applying an impact force to the output shaft, where the impact mechanism includes an impact block driven by the motor, a hammer anvil mating with the impact block and impacted by the impact block, and a main shaft connecting the impact block to the drive shaft; a transmission mechanism configured to transmit torque outputted from the drive shaft to the main shaft, where the gear ratio from the drive shaft to the main shaft is higher than or equal to 9; and a direct current power supply powering at least the motor, where the nominal voltage of the direct current power supply is greater than or equal to 3 V and less than or equal to 9 V. Fastening torque of the output shaft on a workpiece is greater than or equal to 170 N·m.
In some examples, the transmission mechanism includes a multi-stage transmission assembly, and the multi-stage transmission assembly includes at least two stages of planet gear reduction assemblies.
In some examples, the transmission mechanism includes: a first planet carrier disposed in front of the motor; first planet gears supported by the first planet carrier; a second planet carrier disposed in front of the first planet carrier; second planet gears supported by the second planet carrier; and an inner ring gear causing at least the second planet gears to perform a planetary motion.
In some examples, the ratio of a rotational speed of the drive shaft to a rotational speed of the main shaft is substantially a constant value.
Before any examples of this application are explained in detail, it is to be understood that this application is not limited to its application to the structural details and the arrangement of components set forth in the following description or illustrated in the above drawings.
In this application, the terms “comprising”, “including”, “having” or any other variation thereof are intended to cover an inclusive inclusion such that a process, method, article or device comprising a series of elements includes not only those series of elements, but also other elements not expressly listed, or elements inherent in the process, method, article, or device. Without further limitations, an element defined by the phrase “comprising a . . . ” does not preclude the presence of additional identical elements in the process, method, article, or device comprising that element.
In this application, the term “and/or” is a kind of association relationship describing the relationship between associated objects, which means that there can be three kinds of relationships. For example, A and/or B can indicate that A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character “/” in this application generally indicates that the contextual associated objects belong to an “and/or” relationship.
In this application, the terms “connection”, “combination”, “coupling” and “installation” may be direct connection, combination, coupling or installation, and may also be indirect connection, combination, coupling or installation. Among them, for example, direct connection means that two members or assemblies are connected together without intermediaries, and indirect connection means that two members or assemblies are respectively connected with at least one intermediate members and the two members or assemblies are connected by the at least one intermediate members. In addition, “connection” and “coupling” are not limited to physical or mechanical connections or couplings, and may include electrical connections or couplings.
In this application, it is to be understood by those skilled in the art that a relative term (such as “about”, “approximately”, and “substantially”) used in conjunction with quantity or condition includes a stated value and has a meaning dictated by the context. For example, the relative term includes at least a degree of error associated with the measurement of a particular value, a tolerance caused by manufacturing, assembly, and use associated with the particular value, and the like. Such relative term should also be considered as disclosing the range defined by the absolute values of the two endpoints. The relative term may refer to plus or minus of a certain percentage (such as 1%, 5%, 10%, or more) of an indicated value. A value that did not use the relative term should also be disclosed as a particular value with a tolerance. In addition, “substantially” when expressing a relative angular position relationship (for example, substantially parallel, substantially perpendicular), may refer to adding or subtracting a certain degree (such as 1 degree, 5 degrees, 10 degrees or more) to the indicated angle.
In this application, those skilled in the art will understand that a function performed by an assembly may be performed by one assembly, multiple assemblies, one member, or multiple members. Likewise, a function performed by a member may be performed by one member, an assembly, or a combination of members.
In this application, the terms “up”, “down”, “left”, “right”, “front”, and “rear” and other directional words are described based on the orientation or positional relationship shown in the drawings, and should not be understood as limitations to the examples of this application. In addition, in this context, it also needs to be understood that when it is mentioned that an element is connected “above” or “under” another element, it can not only be directly connected “above” or “under” the other element, but can also be indirectly connected “above” or “under” the other element through an intermediate element. It should also be understood that orientation words such as upper side, lower side, left side, right side, front side, and rear side do not only represent perfect orientations, but can also be understood as lateral orientations. For example, lower side may include directly below, bottom left, bottom right, front bottom, and rear bottom.
In this application, the terms “controller”, “processor”, “central processor”, “CPU” and “MCU” are interchangeable. Where a unit “controller”, “processor”, “central processing”, “CPU”, or “MCU” is used to perform a specific function, the specific function may be implemented by a single aforementioned unit or a plurality of the aforementioned unit.
In this application, the term “device”, “module” or “unit” may be implemented in the form of hardware or software to achieve specific functions.
In this application, the terms “computing”, “judging”, “controlling”, “determining”, “recognizing” and the like refer to the operations and processes of a computer system or similar electronic computing device (e.g., controller, processor, etc.).
To clearly illustrate the technical solutions of the present application, an upper side, a lower side, a front side, and a rear side shown in
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The housing 11 includes an electric motor housing 111 for accommodating the electric motor 12 and an output housing 112 for accommodating at least part of the output mechanism 13. The output housing 112 is connected to the front end of the electric motor housing 111. The housing 11 is further formed with or connected to a grip 113 to be operated by a user. The grip 113 and the electric motor housing 111 form a T-shaped or L-shaped structure, which is convenient for the user to hold and operate. The battery pack 30 is connected to an end of the grip 113. The battery pack 30 is detachably connected to the grip 113.
The output mechanism 13 includes an output shaft 131 for connecting a working accessory and driving the working accessory to rotate. A clamping assembly is disposed at the front end of the output shaft 131 and can clamp different working accessories such as a bit, a drill bit, and a socket to implement corresponding functions.
The output shaft 131 is used for outputting power and rotates about an output axis 102. In this example, the first axis 101 coincides with the output axis 102. In other alternative examples, an angle of a certain degree exists between the output axis 102 and the first axis 101. In other alternative examples, the first axis 101 and the output axis 102 are parallel to each other but do not coincide with each other.
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The impact block 152 is driven to rotate by the drive shaft 121. The anvil 1531 mates with the impact block 152 and is impacted by the impact block 152. The main shaft 151 connects the impact block 152 to the drive shaft 121. In this example, the drive shaft 121 drives the main shaft 151, and the main shaft 151 drives the impact block 152 to rotate.
The impact block 152 includes an impact block body 1521 and a pair of first end teeth 1523 which are symmetrically disposed on and protrude from the front end face of the impact block body 1521 radially. A pair of second end teeth 1532 are symmetrically disposed on and protrude from the rear end surface of the anvil 1531 opposite to the impact block 152 radially. The output shaft 131 extends out of the output housing 112. The impact block 152 is supported on the main shaft 151 to rotate integrally with the main shaft 151 and is slidable back and forth relative to the main shaft 151 in the axial direction of the main shaft. In this example, the axis of the main shaft 151 coincides with the axis of the drive shaft 121. Therefore, the impact block 152 slides and rotates back and forth along the direction of the first axis 101 relative to the main shaft 151. In other alternative examples, the axis of the main shaft may be parallel to the axis of the drive shaft 121 but does not coincide with it. Alternatively, an included angle of a certain degree exists between the axis of the main shaft and the axis of the drive shaft 121.
The elastic element 154 provides a force for the impact block 152 to approach the hammer anvil 153. In this example, the elastic element 154 is a coil spring.
In a working process of the impact wrench 100, the impact block 152 moves back and forth along the direction of the first axis 101 at a predetermined stroke relative to the main shaft 151 while rotating integrally with the main shaft 151. A pair of first ball grooves 1522 that open forward and extend backward along a front and rear direction are provided on the front end surface of the impact block body 1521. A pair of V-shaped second ball grooves 1511 are formed on the outer surface of the main shaft 151. The first ball grooves 1522 and the second ball grooves 1511 each have semicircular groove bottoms. The impact mechanism 15 further includes rolling balls 155. The rolling balls 155 straddle the first ball grooves 1522 and the second ball grooves 1511 so that the impact block 152 and the main shaft 151 are connected to each other and move together. In this example, each of the rolling balls 155 is a steel ball.
In the related art, since the impact block and the main shaft are separately provided with inwardly recessed V-shaped grooves to form ball channels together, the rolling balls 155 are disposed between the impact block 152 and the main shaft 151 and embedded into the ball channels. Thus, the main shaft 151 can drive, through the rolling balls 155, the impact block 152 to rotate, and the impact block 152 mates with the hammer anvil 153 to drive the hammer anvil 153 to rotate so as to further drive the output shaft 131 to rotate.
When the impact wrench 100 works with no load, the impact mechanism 15 does not impact and plays a transmission role in transmitting the rotation of the electric motor 12 to the output shaft 131. When a load is applied to the impact wrench 100, the rotation of the output shaft 131 is blocked. The output shaft 131 may reduce a rotational speed or may completely stop rotating due to a different magnitude of the load. When the output shaft 131 completely stops rotating, the hammer anvil 153 also stops rotating. Due to the limitation of the hammer anvil 153 on the impact block 152 in a circumferential direction, the impact block 152 also stops rotating.
However, the main shaft 151 continues rotating such that the rolling balls 155 are pressed to move along the ball channels, thereby driving the impact block 152 to be displaced backward along the axis of the main shaft 151. At the same time, the elastic element 154 is pressed until the hammer anvil 153 is completely separated from the impact block 152. The main shaft 151 drives the impact block 152 to rotate at a certain rotational speed, and the elastic element 154 springs back along an axial direction. The relative rotational speed between the impact block 152 and the hammer anvil 153 is the rotational speed of the impact block 152. When the impact block 152 rotates to be in contact with the hammer anvil 153, the impact block 152 applies an impact force to the hammer anvil 153. Under the action of this impact force, the output shaft 131 overcomes the load and continues rotating by a certain angle, and then the output shaft 131 stops rotating again. The preceding process is repeated. Since an impact frequency is high enough, a relatively continuous impact force is applied to the output shaft 131 so that the working accessory works continuously.
As shown in
The switching portion 163 is disposed on the upper side of the trigger switch and configured to be operated to cause the motor to rotate in a forward rotation direction in which a fastener is fastened or a reverse rotation direction in which the fastener is loosened.
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The transmission mechanism 14 reduces an output rotational speed of the drive shaft 121 and increases the torque of the drive shaft 121 so that when a load on the output shaft 131 exceeds a certain threshold, the main shaft 151 can drive the impact block 152 to compress the elastic element 154 to move backward. In this example, the nominal voltage of the battery pack 30 is less than 18 V. That is, when the battery pack 30 with a nominal voltage of less than 18 V powers the electric motor 12, fastening torque of the output shaft 131 of the impact wrench 100 on a workpiece is greater than or equal to 170 N·m. It is to be understood that the output shaft 131 transmits continuous rotational impacts on the workpiece and generates the fastening torque of at least 170 N·m when the battery pack 30 supplies the nominal voltage of less than 18V to the electric motor 12. The term “fastening torque” refers to the torque applied to the fastener in a direction in which tension is increased (that is, in a tightening direction). In this example, a gear ratio provided by the transmission mechanism 14 from the drive shaft 121 to the main shaft 151 is higher than or equal to 9 so that the output rotational speed of the electric motor 12, which is adapted for the nominal voltage of less than 18 V, can be reduced to a proper speed for the impact mechanism 15 to impact. In this example, the transmission mechanism 14 includes a multi-stage transmission assembly 140 to cause the gear ratio from the drive shaft 121 to the main shaft 151 to be higher than or equal to 9. In some examples, the nominal voltage of the battery pack 30 is greater than or equal to 3 V and less than or equal to 11 V. In some examples, the nominal voltage of the battery pack 30 is greater than or equal to 3 V and less than or equal to 9 V.
It can be learned from the related art that the output torque of the electric motor 12 is positively correlated with the power of the electric motor 12 while the output torque of the electric motor 12 is negatively correlated with the output rotational speed of the electric motor 12. Moreover, the power of the electric motor 12 is the product of a voltage applied to the electric motor 12 and a bus current. As can be seen, when the voltage applied to the electric motor 12 is reduced, if the electric motor 12 is required to output the same output torque or the same output power, it becomes necessary to increase the bus current, which means that the bus current is increased to compensate for a gap created by the voltage reduction. As a result, the cost of the electric motor 12 is increased. In addition, switching elements (for example, the switching elements include controllable semiconductor power devices (such as field-effect transistors (FETs), bipolar junction transistors (BJTs), or insulated-gate bipolar transistors (IGBTs)) or include bipolar junction transistors (BJTs) or insulated-gate bipolar transistors (IGBTs)) are used in the impact tool, and the ratio of the on time of the switching elements to the off time of the switching elements is controlled based on the pulse-width modulation (PWM) signal such that the movement state of the electric motor 12 is controlled. Therefore, when the bus current of the electric motor 12 is increased, higher requirements are also imposed on the switching elements. For the use of the switching elements, not only is the cost increased, but also requirements concerning heat dissipation and service lives are added. Therefore, for an impact tool in the related art, it is substantially impossible to use the battery pack with the nominal voltage of less than 18 V to power the impact tool when the fastening torque of the output shaft 131 on the workpiece is greater than or equal to 170 N·m.
However, an object of the present application is to ensure the usability and safety of the electric motor 12 and components in control circuits related to the electric motor 12. In the impact tool, the electric motor 12 is powered by the battery pack with the nominal voltage of less than 18 V, and the output torque, output rotational speed, or output power of the electric motor 12 is maintained through the increase in the gear ratio of the transmission mechanism 14 so that the output torque outputted from the electric motor 12 powered at the nominal voltage of less than 18 V to the impact mechanism 15 is maintained at an original level (the level in the case where the nominal voltage of a power supply battery pack is greater than or equal to 18 V). In this example, the gear ratio provided by the transmission mechanism 14 from the drive shaft 121 to the main shaft 151 is higher than or equal to 9. In some examples, the gear ratio provided by the transmission mechanism 14 from the drive shaft 121 to the main shaft 151 is higher than or equal to 9.5, 10, 10.5, 11, 11.5, or 12. In some examples, the gear ratio provided by the transmission mechanism 14 from the drive shaft 121 to the main shaft 151 is higher than or equal to 12 and lower than or equal to 14.
In this example, the fastening torque of the output shaft 131 of the impact wrench 100 on the workpiece is greater than or equal to 170 N·m. In some examples, the fastening torque of the output shaft 131 of the impact wrench 100 on the workpiece is greater than or equal to 180 N·m. The fastening torque of the output shaft 131 of the impact wrench 100 on the workpiece is greater than or equal to 190 N·m. The fastening torque of the output shaft 131 of the impact wrench 100 on the workpiece is greater than or equal to 200 N·m. In some examples, the fastening torque of the output shaft 131 of the impact wrench 100 on the workpiece is greater than or equal to 210 N·m and less than or equal to 400 N·m.
An object of this example is to ensure the usability and safety of the electric motor 12 and the components in the control circuits related to the electric motor 12. In the impact tool, the electric motor 12 is powered by the battery pack with the nominal voltage of less than 18 V, and the output torque, output rotational speed, or output power of the electric motor 12 is maintained through the increase in an torque output of the transmission mechanism 14 so that the output torque outputted from the electric motor 12 powered at the nominal voltage of less than 18 V to the impact mechanism 15 is maintained at the original level (the level in the case where the nominal voltage of the power supply battery pack is greater than or equal to 18 V). In this example, the transmission mechanism 14 includes the multi-stage transmission assembly 140. Optionally, the multi-stage transmission assembly 140 includes multiple stages of planetary transmission sets. For example, the multi-stage transmission assembly 140 includes at least two stages of planet gear reduction assemblies. The multi-stage transmission is used for reducing the speed and increasing the torque so that it can be ensured that the transmission mechanism 14 has a relatively high gear ratio. To obtain the same gear ratio, the multi-stage transmission assembly 140 has lower strength requirements on a single gear than a single-stage transmission assembly, which is more beneficial to the service lives of transmission elements.
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Optionally, the first-stage planetary gear set 144 includes first planet gears 1441, a first planet carrier 1442 for mounting the first planet gears 1441, and a first inner ring gear 1443 meshing with the first planet gears 1441. The drive shaft 121 is formed on or connected to a first sun gear 122 rotating at a first rotational speed. In this example, the first sun gear 122 and the drive shaft 121 rotate coaxially. Optionally, the first sun gear 122 rotates about the first axis 101. In other alternative examples, the first sun gear 122 is connected to the drive shaft 121.
The first sun gear 122 drives the first planet gears 1441. The first planet gears 1441 mesh with the first sun gear 122. Multiple first planet gears 1441 are provided, and all of the multiple first planet gears 1441 mesh with the first sun gear 122. In this example, three first planet gears 1441 are circumferentially disposed around the first axis 101 uniformly.
The first sun gear 122 and the first planet gears 1441 are formed with meshing tooth portions for transmitting the power. The tip circle diameter of the meshing tooth portion of the first sun gear 122 is smaller than the tip circle diameter of the first-stage planetary gear set 144 so that the number of meshing teeth of the first-stage planetary gear set 144 is greater than the number of teeth of the meshing tooth portion of the first sun gear 122. In some examples, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is larger than the tip circle diameter of each of the first-stage planet gears 1441. The tip circle diameter of the meshing tooth portion of the first sun gear 122 is greater than or equal to 8 mm. The tip circle diameter of each of the first planet gears 1441 is less than 8 mm. Optionally, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is greater than or equal to 9 mm. Optionally, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is greater than or equal to 10 mm. Optionally, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is greater than or equal to 11 mm. Optionally, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is greater than or equal to 12 mm. Optionally, the tip circle diameter of the meshing tooth portion of the first sun gear 122 is 13 mm. Optionally, the tip circle diameter of each of the first planet gears 1441 is 7.7 mm.
The first inner ring gear 1443 meshes with the periphery of the multiple first planet gears 1441. The first planet carrier 1442 includes a first drive disk 1442a, a first support frame 1442b, and a first output portion. The first support frame 1442b and the first output portion are formed on two sides of the first drive disk 1442a, respectively. The first output portion rotates in synchrony with the first drive disk 1442a. The first support frame 1442b is inserted into the first planet gears 1441 and rotatably connected to the first planet gears 1441 so that the first planet gears 1441 can drive the first planet carrier 1442 to rotate about the first axis 101. Meshing teeth are formed on the circumferential side of the first output portion. The first output portion is configured to mesh with the second-stage planetary gear set 145 so that the first-stage planetary gear set 144 and the second-stage planetary gear set 145 are drivingly connected to each other. In this example, the first output portion is a second sun gear 1444 in the second-stage planetary gear set 145.
The second-stage planetary gear set 145 includes second planet gears 1451, a second planet carrier 1452 for mounting the second planet gears 1451, and a second inner ring gear 1453 meshing with the second planet gears 1451. The second sun gear 1444 drives the second planet gears 1451. In this example, the second sun gear 1444 and the drive shaft 121 rotate coaxially. Optionally, the second sun gear 1444 rotates about the first axis 101. The second planet gears 1451 are configured to mesh with the second sun gear 1444. Multiple second planet gears 1451 are provided, and the multiple second planet gears 1451 mesh with the second sun gear 1444 separately. In this example, three second planet gears 1451 are circumferentially disposed around the first axis 101 uniformly. Meshing relationships between the second planet gears 1451, the second planet carrier 1452, and the second inner ring gear 1453 are the same as the meshing relationships in the first-stage planetary gear set 144 and are well-known to those skilled in the art. The details are not repeated here.
The second planet carrier 1452 includes a second drive disk 1452a and a second support frame 1452b. The second support frame 1452b is inserted into the second planet gears 1451 and rotatably connected to the second planet gears 1451 so that the second planet gears 1451 can drive the second drive disk 1452a to rotate about the first axis 101. In this example, the second drive disk 1452a is formed at the rear end of the main shaft 151. The second planet gears 1451 drive, through the second planet carrier 1452, the main shaft 151 to rotate. In other alternative examples, the second drive disk 1452a and the main shaft 151 may be independent components, and the second drive disk 1452a is connected to the main shaft 151 as long as the second planet gears 1451 can drive the main shaft 151 to rotate.
In this example, the ratio of the rotational speed of the drive shaft 121 to a rotational speed of the main shaft 151 is substantially a constant value. That is to say, the gear ratio from the drive shaft 121 to the main shaft 151 is substantially the constant value. Optionally, the first inner ring gear 1443 and the second inner ring gear 1453 are an integrally formed component. Optionally, the first inner ring gear 1443 and the second inner ring gear 1453 are the same component. That is, the transmission mechanism 14 includes an inner ring gear 146. The inner ring gear 146 separately causes the first planet gears 1441 and the second planet gears 1451 to perform planetary motions. The inner ring gear 146 not only meshes with the first planet gears 1441 to cause the first planet gears 1441 to perform the planetary motion but also meshes with the second planet gears 1451 to cause the second planet gears 1451 to perform the planetary motion. In some alternative examples, the first inner ring gear 1443 and the second inner ring gear 1453 are two components, and the first inner ring gear 1443 and the second inner ring gear 1453 are not displaced relative to each other to ensure that the gear ratio remains substantially constant.
It is to be noted that the electric motor 12, the transmission mechanism 14, and the impact mechanism 15 may share part of the structures. Therefore, the present disclosure does not intend to define the preceding devices as completely independent portions.
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It is to be understood that the nominal voltage of the battery pack 30 is related to the number of cell units 323 connected in series in the battery pack 30. For example, when the number of cell units 323 in the battery pack 30 is 1, the nominal voltage of the battery pack 30 may be considered 3.6 V to 4.2 V and specifically, 3.6 V, 4 V, or 4.2 V.
In some examples, the nominal voltage of the battery pack 30 is greater than or equal to 3 V and less than 18 V. Similarly, when the number of cell units 323 connected in series in the battery pack 30 is 3, the nominal voltage of the battery pack 30 may be considered 10.8 V to 12.6 V and specifically, 10.8 V, 12 V, or 12.6 V. Similarly, when the number of cell units 323 connected in series in the battery pack 30 is 4, the nominal voltage of the battery pack 30 may be considered 14.4 V to 16.8 V and specifically, 14.4 V, 16 V, or 16.8 V.
In this example, the nominal voltage of the battery pack 30 is greater than or equal to 7 V and less than or equal to 9 V. For example, in this example, if the number of cell units 323 is 2 and the two cell units 323 are connected in series, the nominal voltage of the battery pack 30 may be considered 7.2 V to 8.4 V and specifically, 7.2 V, 8 V, or 8.4 V.
In some other examples, the number of cell units 323 in the battery pack 30 is less than or equal to 4. Four cell units 323 may be connected in series. Alternatively, four cell units 323 may constitute two cell groups, the two cell groups are connected in parallel, and two cell units 323 in each cell group are connected in series. When the four cells constitute the two cell groups, similarly, the nominal voltage of the battery pack 30 may be considered 8 V. In some examples, the nominal voltage of the battery pack 30 is less than or equal to 9 V. In some examples, the nominal voltage of the battery pack 30 is greater than or equal to 7 V.
In some examples, the nominal voltage of the battery pack 30 is less than or equal to 13 V. For example, the battery pack 30 includes three cell units 323 connected in series, and the nominal voltage of the battery pack 30 may be 10.8 V, 12 V, or 12.6 V.
The battery pack 30 may be a lithium battery pack, a solid-state battery pack, or a pouch battery pack. The battery pack 30 includes a first portion 33 and a second portion 34. When the battery pack 30 is coupled to the grip 113, the first portion 33 is at least partially located inside the grip 113, and the second portion 34 is located outside the grip 113. Optionally, the first portion 33 includes a first group of cells, and the second portion 34 includes a second group of cells. For convenience of description, in this example, a cell unit 323 in the first group of cells may be defined as a first cell unit 323a, and a cell unit 323 in the second group of cells may be defined as a second cell unit 323b. The first cell unit 323a and the second cell unit 323b are each a pouch cell. The first cell unit 323a is partially or entirely located inside the grip 113, and the second cell unit 323b is located outside the grip 113. An extension plane of the first cell unit 323a is parallel to a first straight line. An extension plane of the second cell unit 323b is perpendicular to the first straight line. The extension plane of the second cell unit 323b is perpendicular to the extension plane of the first cell unit 323a. The battery pack housing 31 is used for accommodating the first cell unit 323a and the second cell unit 323b. The battery pack housing is substantially T-shaped. Thus, the capacity of the battery pack 30 is increased and the volume of the battery pack can be reduced. Alternatively, in some examples, the battery pack housing may be substantially L-shaped.
In this example, as shown in
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In some alternative examples, the illumination assembly is disposed on the output housing. Optionally, the illumination assembly includes multiple light emitters disposed along the circumferential direction of the output shaft 131 or annularly. Each of the light emitters includes a light bead and a light plate. In some examples, the illumination assembly includes light beads and a reflector to provide a surface light source. Optionally, the reflector is annular. In some examples, the illumination assembly is controlled by the trigger switch. In some examples, an independent control manipulation portion is provided to control the illumination assembly. In some examples, the illumination assembly has an adjustable working mode. The working mode includes brightness, a color temperature, a turn-on delay, a turn-off delay, being constantly on or flashing, and other modes that affect an illumination effect.
The basic principles, main features, and advantages of this application are shown and described above. It is to be understood by those skilled in the art that the aforementioned examples do not limit the present application in any form, and all technical solutions obtained through equivalent substitutions or equivalent transformations fall within the scope of the present application.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202311788228.7 | Dec 2023 | CN | national |
| 202323530966.X | Dec 2023 | CN | national |
