WO2024083067A1 - 冲击工具 - Google Patents

冲击工具 Download PDF

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Publication number
WO2024083067A1
WO2024083067A1 PCT/CN2023/124691 CN2023124691W WO2024083067A1 WO 2024083067 A1 WO2024083067 A1 WO 2024083067A1 CN 2023124691 W CN2023124691 W CN 2023124691W WO 2024083067 A1 WO2024083067 A1 WO 2024083067A1
Authority
WO
WIPO (PCT)
Prior art keywords
impact
transmission
output
shaft
motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2023/124691
Other languages
English (en)
French (fr)
Inventor
郑玉亿
刘少波
童树彬
吴迪
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nanjing Chervon Industry Co Ltd
Original Assignee
Nanjing Chervon Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nanjing Chervon Industry Co Ltd filed Critical Nanjing Chervon Industry Co Ltd
Priority to EP23879056.2A priority Critical patent/EP4585368A4/en
Publication of WO2024083067A1 publication Critical patent/WO2024083067A1/zh
Priority to US19/172,197 priority patent/US20250229403A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member

Definitions

  • the present application relates to an electric tool, for example, to an impact tool.
  • Impact tools are capable of outputting rotational motion with a certain impact frequency, including but not limited to impact wrenches and impact screwdrivers.
  • impact wrenches are used to tighten bolts and nuts
  • impact screwdrivers are usually used to loosen or tighten screws.
  • impact tools need to include an output component for outputting rotational force, and also need to include an impact mechanism that periodically impacts the output component.
  • the impact mechanism includes an impact block, an anvil that cooperates with the impact block, and a main shaft connected to a motor.
  • the impact block When the conditions for starting the impact mechanism are met, the impact block performs axial or radial reciprocating motion, and then periodically engages with the anvil to output an impact force in the rotation direction.
  • impact tools basically change the motor speed by electronically adjusting the input current of the motor to achieve speed regulation of the output part and impact torque regulation.
  • this requires high performance of electrical components, and on the other hand, in order to match the performance of electronic control and motor, the working conditions applicable to impact tools are limited.
  • One object of the present application is to solve or at least alleviate part or all of the above problems.
  • the present application provides an impact tool to be applicable to more working conditions.
  • an embodiment of the present application provides an impact tool, comprising: an impact mechanism for applying an impact force to an output shaft; a transmission mechanism, comprising: a multi-stage transmission assembly, in which at least one stage of the transmission assembly is provided with an adjustable transmission ratio.
  • the output transmission ratio of the multi-speed transmission assembly is greater than 1.
  • it also includes a motor, including a motor shaft rotating around a first axis; an output shaft for outputting power; the output shaft rotates around the output axis; and a transmission mechanism for transmitting power between the motor shaft and the impact mechanism.
  • a motor including a motor shaft rotating around a first axis; an output shaft for outputting power; the output shaft rotates around the output axis; and a transmission mechanism for transmitting power between the motor shaft and the impact mechanism.
  • the transmission mechanism has at least two transmission states that enable the output shaft to output at different rotational speeds.
  • the output transmission ratio of the transmission mechanism in any transmission state is greater than 1.
  • it also includes a switching mechanism for driving the transmission mechanism to switch between different transmission states.
  • the transmission mechanism includes: a first-stage planetary gear set and a second-stage planetary gear set.
  • the first stage planetary gear set is close to the motor shaft, and the second stage planetary gear set is close to the impact mechanism.
  • the second stage planetary gear set has two gear ratios.
  • At least one gear ratio of the second stage planet gears is greater than 1.
  • the second stage planet gear includes a second inner ring gear.
  • the second annular gear is configured to move between a first position and a second position.
  • the second internal gear ring when the second internal gear ring is in the first position, the second internal gear ring is restricted from rotating.
  • the transmission mechanism further includes a locking ring for restricting the second inner gear ring.
  • the locking ring is coupled to a first bearing for supporting the main shaft.
  • the impact mechanism includes: a main shaft driven by a motor shaft and a main shaft for supporting The first bearing is closer to the output shaft than the multi-stage transmission assembly along the first axis.
  • the impact mechanism includes an impact block driven by the main shaft and a hammer anvil that cooperates with and is struck by the impact block.
  • the hammer anvil drives the output shaft to rotate
  • the impact block rotates integrally with the main shaft through the ball, and can reciprocate relative to the main shaft along the first axis direction at a specified stroke to periodically cooperate with the hammer anvil.
  • the impact mechanism further comprises: an elastic element for providing a force for the impact block to approach the anvil, the elastic element having at least two different elastic coefficients.
  • the elastic element is configured as a coil spring having different pitches.
  • it also includes: a power supply, the power supply provides a nominal voltage of at least 4V, and the power supply provides electrical energy for the motor.
  • an embodiment of the present application provides an impact tool, comprising: an impact mechanism for applying impact force to an output shaft; the impact mechanism comprises: a main shaft driven by a motor shaft; a transmission mechanism for transmitting power between the motor shaft and the main shaft, and the output transmission ratio of the transmission mechanism is adjustable.
  • the output shaft outputs at different speeds.
  • the output transmission ratio of the transmission mechanism is greater than 1.
  • the invention further comprises: a motor, comprising a motor shaft rotating about a first axis; an output shaft for outputting power; the output shaft rotates about the output axis;
  • an embodiment of the present application provides an impact tool, comprising:
  • the impact mechanism is used to apply impact force to the output shaft; the impact mechanism comprises: a main shaft driven by a motor shaft; along the first axis direction, a first bearing for supporting the main shaft is closer to the output shaft than the multi-stage transmission group.
  • the transmission mechanism is further included, which is used to transmit power between the motor shaft and the main shaft; the transmission mechanism includes a multi-stage transmission group, wherein at least two stages of reduction transmission are provided in the multi-stage transmission group. move.
  • it also includes a motor, including a motor shaft rotating around a first axis; an output shaft for outputting power; and the output shaft uses the output axis as a rotation axis.
  • the output transmission ratio of the transmission mechanism is adjustable.
  • the output transmission ratio of the multi-speed transmission assembly is greater than 1.
  • it also includes: a power supply, the power supply provides a nominal voltage of at least 4V, and the power supply provides electrical energy for the motor.
  • FIG1 is a schematic structural diagram of a first embodiment of the present application.
  • FIG2 is a structural diagram of the motor, transmission mechanism, impact mechanism, output mechanism and switching mechanism of the first embodiment in FIG1 ;
  • Fig. 3 is a cross-sectional view of Fig. 2;
  • FIG4 is an exploded view of the structure in FIG2 ;
  • FIG5 is another perspective of the impact mechanism in FIG4 ;
  • FIG. 6 is a structural diagram of the transmission mechanism, the impact mechanism, the output mechanism and the switching mechanism in FIG. 2 , wherein the impact block is located at the second position and the second inner gear ring is located at the first position;
  • FIG7 is a cross-sectional view of FIG6
  • FIG. 8 is a structural diagram of the transmission mechanism, the impact mechanism, the output mechanism and the switching mechanism in FIG. 2 , wherein the impact block is located at the first position and the second inner gear ring is located at the second position;
  • FIG9 is a cross-sectional view of FIG8
  • FIG10 is a schematic structural diagram of the structure of the elastic element
  • FIG11 is an assembly diagram of the main shaft, the second planetary gear and the second planetary carrier
  • FIG. 12 is an assembly diagram of the first housing and the locking ring.
  • the term "and/or” is a description of the association relationship between related objects, indicating that three relationships can exist.
  • a and/or B can represent: A exists alone, A and B exist at the same time, and B exists alone.
  • the character "/" in this application generally indicates that the related objects before and after are in an "and/or” relationship.
  • connection may refer to direct connection, combination, coupling, or installation, or indirect connection, combination, coupling, or installation.
  • direct connection refers to two parts or components being connected together without the need for an intermediate piece
  • indirect connection refers to two parts or components being connected to at least one intermediate piece respectively, and the two parts or components being connected via the intermediate piece.
  • connect and “couple” are not limited to physical or mechanical connection or coupling, and may include electrical connection or coupling.
  • relative terms e.g., "about,””approximately,””substantially,” etc.
  • the relative term includes at least the degree of error associated with the measurement of a specific value, the tolerance caused by manufacturing, assembly, use, etc. associated with the specific value.
  • Such terms should also be regarded as disclosing the range defined by the absolute values of the two endpoints.
  • Relative terms may refer to plus or minus a certain percentage (e.g., 1%, 5%, 10% or more) of the indicated value.
  • Numerical values that do not adopt relative terms should also be disclosed as specific values with tolerances.
  • substantially when expressing a relative angular position relationship (e.g., substantially parallel, substantially perpendicular) may refer to plus or minus a certain degree (e.g., 1 degree, 5 degrees, 10 degrees or more) on the basis of the indicated angle.
  • the function performed by a component can be performed by one component, multiple components, one part, or multiple parts.
  • the function performed by a part can also be performed by one part, one component, or a combination of multiple parts.
  • controller In this application, the terms “controller”, “processor”, “central processing unit”, “CPU”, and “MCU” are interchangeable. When a unit “controller”, “processor”, “central processing unit”, “CPU”, or “MCU” is used to perform a specific function, unless otherwise specified, these functions can be performed by a single unit or multiple units.
  • the terms “calculate”, “judge”, “control”, “determine”, “identify”, etc. refer to the operations and processes of a computer system or similar electronic computing device (e.g., controller, processor, etc.).
  • FIG1 shows an impact tool of the first embodiment of the present application.
  • the impact tool is an impact wrench 100.
  • the impact tool is a rotary tool.
  • the rotary tool can be equipped with different working accessories. Through these different working accessories, the impact tool can be other impact tools such as an impact screwdriver and an impact drill.
  • FIG1 shows an impact wrench 100 of the first embodiment of the present application, including a power supply 30.
  • the power supply 30 is used to provide electrical energy to the impact wrench 100.
  • the power supply 30 is a battery pack, and the battery pack cooperates with a corresponding power supply circuit to power the corresponding components in the impact wrench 100.
  • the power supply 30 is not limited to the scenario of using a battery pack, and can also be powered by a mains power supply, an AC power supply, and corresponding rectification, filtering and voltage regulation circuits to realize power supply to the corresponding components in the machine.
  • the impact wrench 100 includes a housing 11, a motor 12, an output mechanism 13, a transmission mechanism 14 and an impact mechanism 15.
  • the housing 11 includes a motor housing 111 for accommodating the motor 12 and an output housing 112 for accommodating at least part of the output mechanism 13, and the output housing 112 is connected to the front end of the motor housing 111.
  • the housing 11 is also formed or connected with a grip 113 for user operation.
  • the grip 113 and the motor housing 111 form a T-shaped or L-shaped structure, which is convenient for the user to hold and operate.
  • One end of the grip 113 is connected to a power supply 30.
  • the power supply 30 is detachably connected to the grip 113.
  • the motor 12 includes a motor shaft 121 that rotates about the first axis 101 .
  • 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 provided at the front end of the output shaft 131, which can clamp the corresponding working accessory when implementing different functions, such as Screwdrivers, drill bits, sockets, etc.
  • the output shaft 131 is used to output power, and the output shaft 131 rotates around the output axis.
  • the output axis is the second axis 102.
  • the first axis 101 coincides with the second axis 102.
  • the second axis 102 is arranged at a certain angle to the first axis 101.
  • the first axis 101 and the second axis 102 are arranged parallel to each other but do not coincide.
  • the impact mechanism 15 is used to provide an impact force to the output shaft 131.
  • the impact mechanism 15 includes a main shaft 151, an impact block 152 sleeved on the outer periphery of the main shaft 151, an anvil 153 and an elastic element 154 arranged at the front end of the impact block 152.
  • the anvil 153 is connected to the output shaft 131.
  • the anvil 153 includes an anvil seat 1531, and the output shaft 131 is formed or connected to the front end of the anvil seat 1531. It can be understood that the anvil seat 1531 and the output shaft 131 can be integrally formed or separately formed as independent parts.
  • the impact block 152 is driven by the main shaft 151, and the anvil 1531 cooperates with the impact block 152 and is struck by it.
  • the impact block 152 includes an impact block body 1521 and a pair of first end teeth 1523 radially symmetrically protruded on the front end surface of the impact block body 1521.
  • a pair of second end teeth 1532 are radially symmetrically protruded on the rear end surface of the anvil 1531 opposite to the impact block 152.
  • the output shaft 131 extends out of the output housing 112.
  • the impact block 152 is supported on the main shaft 151 and rotates integrally with the main shaft 151 and can reciprocate relative to the main shaft 151 in the axial direction of the main shaft.
  • the axis of the main shaft coincides with the axis of the motor shaft, so the impact block 152 reciprocates and rotates relative to the main shaft 151 along the direction of the first axis 101.
  • the axis of the main shaft can be parallel to the axis of the motor shaft but not coincident, or the axis of the main shaft and the axis of the motor shaft are arranged at a certain angle.
  • the elastic element 154 provides a force for the impact block 152 to approach the anvil 153.
  • the elastic element 154 is a coil spring.
  • the impact block 152 rotates integrally with the spindle.
  • the prescribed stroke reciprocates forward and backward relative to the main shaft 151 along the direction of the first axis 101.
  • the impact block 152 includes a first position moving forward to the farthest end and a second position moving backward to the farthest end. Among them, as shown in Figures 6 to 7, the impact block is located in the second position. As shown in Figures 8 to 9, the impact block is located in the first position. In the first position, the first end tooth 1523 of the impact block 152 is engaged with the anvil 153, that is, the front end of the stroke of the impact block 152 is stopped by the anvil 153.
  • a pair of first ball grooves 1522 are also provided on the front end surface of the impact block body 1521, which are opened forward and extend backward in the front-to-back direction.
  • a pair of V-shaped second ball grooves 1511 are also formed on the outer surface of the main shaft 151.
  • the first ball groove 1522 and the second ball groove 1511 have semicircular groove bottoms.
  • the impact mechanism 15 also includes a rolling ball 155.
  • the rolling ball 155 spans the first ball groove 1522 and the second ball groove 1511, so that the impact block 152 is connected to the main shaft 151 and moves together.
  • the rolling ball 155 is a steel ball.
  • the rolling ball 155 is arranged between the impact block 152 and the main shaft 151 and embedded in the ball track, so that the main shaft 151 can drive the impact block 152 to rotate through the rolling ball 155, and the impact block 152 drives the anvil 153 to rotate through the cooperation of the anvil 153, and further drives the output shaft 131 to rotate.
  • the impact mechanism When the impact tool is unloaded, the impact mechanism does not impact, and the impact mechanism plays a transmission role, transferring the rotation of the motor to the output shaft.
  • the rotation of the output shaft When a load is applied to the impact tool, the rotation of the output shaft is hindered. Due to different load sizes, the output shaft may reduce its speed or stop rotating completely.
  • the anvil When the output shaft stops rotating completely, the anvil also stops rotating. Due to the circumferential limiting effect of the anvil on the impact block, the impact block also stops rotating, but the spindle continues to rotate, which causes the ball to be squeezed and move along the ball track, thereby driving the impact block to produce a backward displacement along the spindle axis, that is, to move to the second position of the impact block.
  • the elastic element is squeezed until the anvil and the impact block are completely disengaged, and the impact block is in the second position.
  • the spindle drives the impact block to rotate at a certain speed, and the elastic element rebounds axially, that is, it moves to the first position of the impact block.
  • the relative speed between the impact block and the anvil is the speed of the impact block.
  • the transmission mechanism 14 is disposed between the motor 12 and the impact mechanism 15 , and is used to achieve power transmission between the motor shaft 121 and the main shaft 151 .
  • the transmission mechanism 14 includes a multi-stage transmission group.
  • the multi-stage transmission group is a multi-stage planetary transmission group 140.
  • the planetary transmission group includes planetary wheels, a planetary wheel carrier for mounting the planetary wheels, and an inner gear ring meshing with the planetary wheels.
  • the transmission ratio of at least one of the first-stage planetary transmission groups in the multi-stage planetary transmission group 140 is adjustable.
  • the output transmission ratio of the multi-stage planetary transmission group 140 is greater than 1.
  • the planetary wheel carrier in the planetary transmission group close to the impact mechanism 15 in the multi-stage planetary transmission group 140 is formed or connected to the main shaft 151.
  • the inner gear ring of at least one of the first-stage planetary transmission groups is configured to move between a first position and a second position.
  • the first bearing 1512 for supporting the main shaft 151 is closer to the output shaft 131 than the multi-stage planetary transmission group 140.
  • setting a multi-stage planetary transmission group and adjusting the transmission ratio of the planetary wheel group to achieve speed regulation and then implement torque regulation is equivalent to adding a mechanical method to adjust the speed and torque.
  • the mechanical adjustment method of the present application can be used alone, or the motor speed adjustment method and the mechanical method can be used simultaneously. The adjustment methods are diversified and the adjustment options are more.
  • the transmission ratio of the above-mentioned planetary transmission group is adjustable, that is, the planetary transmission group has at least two different transmission ratios, one of which is greater than 1, which is a deceleration and torque increase transmission.
  • the other transmission ratio is basically equal to 1, and the planetary gear set only performs a transmission function.
  • the mechanical method of adjusting the speed and torque of the present application does not change the output power of the motor.
  • the efficiency of the motor can be improved.
  • the speed and torque of the motor are adjusted within the high efficiency range.
  • the output of torque is achieved by adjusting the transmission ratio of the transmission mechanism to adjust the speed.
  • the output speed is reduced by reducing the current when outputting at low speed.
  • the brushless DC motor (BLDC) is controlled by the modulation method of the pulse width modulation (PWM) signal. Due to the performance limitations of the motor's duty cycle and controllable semiconductor power devices (such as Mosfet metal oxide semiconductor field effect transistors), the threshold of the minimum speed of the motor output is also limited.
  • the addition of a transmission mechanism with an adjustable transmission ratio has also expanded the range of compatible motors for impact tools to a certain extent.
  • the output torque threshold of the motor used on the impact tool is higher than that of the motor used on the tool that only performs rotational output. The reason is that when the impact is started, the torque transmitted to the spindle needs to be able to drive the impact block to overcome the pressure of the elastic element. When the output power and output torque of the motor cannot meet this condition, the impact process cannot be started. At this time, the motor will be blocked.
  • the present application utilizes a multi-stage deceleration and torque increase method to realize the application of low-power motors in impact tools, such as a small screwdriver using a small motor with a 4V voltage (built-in battery).
  • the adjustable function is conducive to the use of different working conditions. It is conducive to the miniaturization of products and the development of portable impact tools.
  • the transmission mechanism 14 has two transmission states that enable the output shaft 131 to output at different speeds.
  • the transmission mechanism 14 includes a housing assembly 14a, a first-stage planetary gear set 144, and a second-stage planetary gear set 145.
  • two transmission states and two-stage planetary gear sets are set.
  • the transmission mechanism can be set with more than two transmission states and more than two-stage planetary gear sets. The above does not affect The substantive content of this application.
  • the first-stage planetary gear set 144 and the second-stage planetary gear set 145 are at least partially located in the housing assembly 14a.
  • the first-stage planetary gear set 144 is close to the motor shaft 121, and the second-stage planetary gear set 145 is close to the main shaft 151.
  • the first-stage planetary gear set 144 outputs at only one transmission ratio. That is, the first-stage planetary gear set 144 outputs at a first transmission ratio, and the first transmission ratio is greater than 1.
  • the first-stage planetary gear set 144 performs an operation of decelerating and increasing torque, and the output speed of the first-stage planetary gear set 144 is less than the input speed of the planetary gear set, and the output torque is greater than the input torque of the planetary gear set.
  • the first-stage planetary gear set 144 includes: a first planetary gear 1441, a first planetary gear carrier 1442 for mounting the first planetary gear 1441, and a first inner gear ring 1443 meshing with the first planetary gear 1441.
  • the motor shaft 121 forms or is connected to a first sun gear 122 that rotates at a first speed.
  • the first sun gear 122 rotates coaxially with the motor shaft 121.
  • the first sun gear 122 rotates around the first axis 101.
  • the first sun gear 122 is connected to the motor shaft 121.
  • the first sun gear 122 drives the first planetary gear 1441.
  • the first planetary gear 1441 is configured to mesh with the first sun gear 122.
  • a plurality of first planetary gears 1441 are provided, and the plurality of first planetary gears 1441 are configured to mesh with the first sun gear 122.
  • four first planetary gears 1441 are evenly arranged around the circumference of the first axis 101.
  • the first sun gear 122 and the first planetary gears 1441 form a meshing tooth portion for transmitting power.
  • the tooth top circle diameter of the meshing tooth portion of the first sun gear 122 is set to be smaller than the tooth top circle diameter of the first-stage planetary gear set 144, so that the number of teeth of the meshing teeth of the first-stage planetary gear set 144 is greater than the number of teeth of the meshing tooth portion of the sun gear.
  • the first inner ring gear 1443 meshes with the periphery of the plurality of first planetary gears 1441.
  • the first planetary gear carrier 1442 includes a first transmission disc 1442a, a first support frame 1442b and a first output portion. The first support frame 1442b and the first output portion are respectively formed on both sides of the first transmission disc 1442a.
  • the first output portion rotates synchronously with the first transmission disc 1442a.
  • the first support frame 1442b is inserted into the first planetary gear 1441 and is rotationally connected with the first planetary gear 1441, so that the first planetary gear
  • the gear 1441 can drive the first planetary gear carrier 1442 to rotate around the first axis 101.
  • Meshing teeth are formed on the circumference of the first output part, and the first output part is used to mesh with the second-stage planetary gear set 145, thereby realizing the transmission connection between the first-stage planetary gear set 144 and the second-stage planetary gear set 145.
  • the first output part is the second sun gear 1444 of the second-stage planetary gear set 145.
  • the second-stage planetary gear set 145 includes: a second planetary gear 1451, a second planetary gear carrier 1452 for mounting the second planetary gear 1451, and a second inner gear ring 1453 meshing with the second planetary gear 1451.
  • the second sun gear 1444 drives the second planetary gear 1451.
  • the second sun gear 1444 rotates coaxially with the motor shaft 121, and optionally, the second sun gear 1444 rotates with the first axis 101 as the axis.
  • the second planetary gear 1451 is configured to mesh with the second sun gear 1444.
  • a plurality of second planetary gears 1451 are provided, and the plurality of second planetary gears 1451 are configured to mesh with the second sun gear 1444 respectively.
  • five second planetary gears 1451 are evenly arranged around the circumference of the first axis 101.
  • the meshing relationship between the second planetary gear 1451, the second planetary gear carrier 1452, and the second inner gear ring 1453 is the same as the meshing relationship in the first-stage planetary gear set 144, which is well known to those skilled in the art and will not be repeated here.
  • the second planetary gear carrier 1452 includes a second transmission disc 1452a and a second support frame 1452b.
  • the second support frame 1452b is inserted into the second planetary gear 1451 and is rotatably connected with the second planetary gear 1451, so that the second planetary gear 1451 can drive the second transmission disc 1452a to rotate around the first axis 101.
  • the second transmission disc 1452a is formed at the rear end of the main shaft 151.
  • the second planetary gear 1451 drives the main shaft 151 to rotate through the second planetary gear carrier 1452.
  • the second transmission disc 1452a and the main shaft 151 can be independent components, and the second transmission disc 1452a is connected to the main shaft 151. As long as the second planetary gear 1451 can drive the main shaft 151 to rotate.
  • the second-stage planetary gear set 145 has two transmission ratios.
  • the second transmission ratio is substantially equal to 1, that is, the second-stage planetary gear set 145 only plays a transmission role.
  • the second-stage planetary gear set 145 is in the second transmission state.
  • the third transmission ratio is greater than 1, that is, it is a reduction transmission.
  • the third transmission ratio is greater than 1, that is, it is a reduction transmission.
  • the secondary planetary gear set 145 is in the second speed change state.
  • the second inner gear ring 1453 When in the second speed change state, the second inner gear ring 1453 is fixed. In this embodiment, the second inner gear ring 1453 cannot rotate around the first axis 101, and the second-stage planetary gear set 145 plays a speed change role.
  • the second inner gear ring 1453 When the second-stage planetary gear set 145 is in the second transmission state, the second inner gear ring 1453 is released, and the second inner gear ring 1453 is allowed to be driven and rotated by the second sun gear 1444.
  • the second inner gear ring 1453 and the first planetary wheel carrier 1442 rotate synchronously around the first axis 101, and the second-stage planetary gear set 145 does not have a deceleration effect.
  • meshing teeth are formed on the outer peripheral side of the first transmission plate 1442a.
  • the second inner gear ring 1453 meshes with the meshing teeth of the first transmission plate 1442a and rotates synchronously.
  • the housing assembly 14a includes: a first housing 141, a first cover 142 installed at one end of the first housing 141, and a locking ring 143 at the other end of the first housing 141.
  • the first housing 141 extends along the first axis 101 and forms a cylindrical accommodation space.
  • the first-stage planetary gear set 144 and the second-stage planetary gear set 145 are at least partially accommodated in the first housing 141.
  • the first cover 142 extends in a direction perpendicular to the first axis 101, and the first cover 142 is installed at one end of the first housing 141 close to the motor 12.
  • a second bearing 123 for supporting the motor shaft 121 is provided on the motor shaft 121.
  • the second bearing 123 is a front bearing of the motor.
  • a receiving portion 1422 is provided on the first cover 142, and the second bearing 123 is accommodated in the receiving portion 1422.
  • the motor shaft 121 extends out of the first cover 142 through the accommodating portion 1422 and extends into the first housing 141 , and then the first sun gear 122 is arranged at the front end of the motor shaft 121 and extends into the first housing 141 .
  • the first housing 141 or the first cover 142 is formed or connected with a locking portion 1425 for limiting the rotation of the first inner gear ring 1443.
  • the locking portion 1425 is a plurality of locking portions arranged at intervals in the circumferential direction of the first axis 101.
  • the first locking teeth 1425a extend in the axial direction of the first housing 141, that is, extend in the direction of the first axis 101.
  • the first inner gear ring 1443 includes a plurality of first mating teeth 1443a arranged at intervals in the circumferential direction of the first inner gear ring 1443.
  • the first mating teeth 1443a extend in the axial direction of the first inner gear ring 1443, that is, extend in the direction of the first axis 101.
  • the first locking teeth 1425a and the first mating teeth 1443a are staggered in the circumferential direction of the first axis 101.
  • the first locking teeth 1425a limit the rotation of the first mating teeth 1443a relative to the first locking teeth 1425a.
  • the first inner gear ring 1443 is fixed.
  • the first inner ring gear is immovable.
  • the first inner ring gear can also translate forward and backward along the first axis direction.
  • the first housing is provided with a flange portion extending into the first housing, and the flange portion is formed or fixed with a locking portion for limiting the rotation of the first inner ring gear.
  • the locking portion is the same as described above.
  • a locking ring 143 is formed or connected to one end of the first housing 141 close to the output shaft 132, and the locking ring 143 is used to lock the second inner gear ring 1453.
  • the locking ring 143 has a plurality of second locking teeth 1431 arranged at intervals in the circumferential direction of the first axis 101, and the second locking teeth 1431 extend in the axial direction of the first housing 141, that is, extend in the direction of the first axis 101.
  • Second mating teeth 1453a are provided on the second inner gear ring 1453. The second mating teeth 1453a extend in the axial direction of the second inner gear ring 1453, that is, extend in the direction of the first axis 101.
  • the second locking teeth 1431 and the second mating teeth 1453a are staggered in the circumferential direction of the first axis 101.
  • the second locking teeth 1431 limit the rotation of the second mating teeth 1453a relative to the second locking teeth 1431.
  • the second inner gear ring 1453 is fixed.
  • the second inner gear ring 1453 is driven to move backward, the second inner gear ring 1453 is released by the locking portion 1425.
  • the second inner gear ring 1453 meshes with the meshing teeth of the first transmission plate 1442a and rotates synchronously.
  • the second-stage planetary gear set is in a transmission state.
  • the second-stage planetary gear set does not have a deceleration effect.
  • the locking ring 143 is fixed in the first shell 141 in the form of an embedded component.
  • the impact wrench 100 further includes a switching mechanism 16 for driving the transmission mechanism to switch between different transmission states.
  • the switching mechanism 16 includes an operating member 163 for user operation.
  • the switching mechanism 16 includes a shifting frame.
  • the operating member 163 drives the shifting frame to move.
  • the shifting frame includes a first shifting frame 161 for driving the second inner gear ring 1453, and the first shifting frame 161 is connected to the second inner gear ring 1453.
  • the first shifting frame 161 is operated to drive the second inner gear ring 1453 to move toward the impact mechanism 15 along the first axis 101 until the second inner gear ring 1453 is locked and connected with the locking ring 143, and the rotation of the second inner gear ring 1453 with the first axis 101 as the rotation axis is restricted, and at this time, the second inner gear ring 1453 is in the first position.
  • the first rack 161 is operated to drive the second inner gear ring 1453 to move along the first axis 101 toward the first planetary gear carrier 1442 until the second inner gear ring 1453 is locked and disconnected from the locking ring 143, and the second inner gear ring 1453 is in the second position.
  • the second inner gear ring 1453 meshes with the meshing teeth of the first planetary gear carrier 1442 and rotates synchronously, which is equivalent to rotating the second inner gear ring 1453 and the second sun gear 1444 synchronously.
  • the shifting frame when the transmission state of the first-stage planetary gear set can be adjusted, the shifting frame further includes a second shifting frame that drives the first inner gear ring, and the second shifting frame is connected to the first inner gear ring.
  • the second shifting frame is operated to drive the first inner gear ring to move along the first axis toward the first cover body until the first locking tooth and the first matching tooth are engaged and contacted, and the rotation of the first inner gear ring with the first axis as the rotation axis is restricted.
  • the second shifting frame The first inner gear ring is operated to drive the first inner gear ring to move along the first axis in a direction away from the first cover body until the first locking tooth and the first matching tooth are disengaged from each other, and at this time, the first inner gear ring is in the second position.
  • the impact mechanism 15 further includes a first bearing 1512 for supporting the main shaft 151.
  • the first bearing 1512 is a ball bearing or a needle bearing.
  • the first bearing 1512 is closer to the output shaft 131 than the multi-stage planetary transmission group. It can be understood that the first bearing 1512 is sleeved on the periphery of the main shaft 151 and is located in front of the planetary gear. In this embodiment, the first bearing 1512 is located in front of the second planetary gear 1451.
  • the locking ring 143 is provided with a second locking tooth 1431 on one side and an open annular groove 1432 is formed on the other side.
  • the opening of the annular groove 1432 faces the impact mechanism 15.
  • the outer side of the first bearing 1512 at least partially abuts against the side wall of the annular groove 1432.
  • the radial displacement of the first bearing 1512 in the direction of the first axis 101 is limited.
  • the rear end face of the first bearing 1512 abuts against the bottom wall of the annular groove 1432.
  • the main shaft 151 extends a stop surface in a direction perpendicular to the first axis 101, and the diameter of the stop surface is larger than the inner diameter of the first bearing 1512.
  • the front end surface of the first bearing 1512 abuts against the stop surface.
  • the axial displacement of the first bearing 1512 along the direction of the first axis 101 is thereby limited. This not only ensures the stability of the rotation support of the main shaft 151, but also makes the mechanism of the present application more compact.
  • the first inner gear ring and the second inner gear ring are both restricted in their rotational motion, and the switching mechanism is canceled or fixed.
  • the use of multi-stage reduction torque increase realizes the application of low-power motors in impact tools.
  • the elastic element has at least two different elastic coefficients.
  • the elastic element includes a first elastic coefficient K1 and a second elastic coefficient K2.
  • the first elastic coefficient K1 is smaller than the second elastic coefficient K2, so that when a small impact force or During a rapid impact, the first elastic coefficient K1 is used.
  • both the first elastic coefficient K1 and the second elastic coefficient K2 are activated.
  • the elastic element in order to realize that the elastic element has at least two different elastic coefficients, is configured as a helical spring with pitches of T1 and T2, wherein T1 is less than T2.
  • the elastic element can be a conical spring.
  • the elastic element is configured with two single spring elements with different elastic coefficients, and the two single spring elements are connected in parallel or in series with each other.

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Abstract

一种冲击工具，包括：电机轴（121）；输出轴（131），用于输出动力；输出轴以输出轴线为转轴；冲击机构（15），用于提供冲击力；传动机构（14），用于在电机轴和冲击机构之间进行动力传递，传动机构包括多级传动组件，在多级传动组件中，至少设置一级传动组件的传动比可调，多级传动组件的输出传动比大于1。通过机械方式调节工具的转速和扭矩，从而不改变电机输出功率，一定程度上提高了电机效率。

Description

冲击工具
本申请要求在2022年10月20日提交中国专利局、申请号为202211285800.3的中国专利申请的优先权，该申请的全部内容通过引用结合在本申请中。
技术领域
本申请涉及一种电动工具，例如涉及一种冲击工具。
背景技术
冲击工具是能够输出具有一定冲击频率的旋转运动，包括但不限于冲击扳手、冲击螺丝批。例如冲击扳手用于拧螺栓、螺母，冲击螺丝批通常将螺钉拧松或拧紧等。冲击工具为了实现具有一定冲击频率的旋转运动，因此需要包括用于输出旋转力的输出件，还需要包括对输出组件进行周期性冲击的冲击机构。
冲击机构包括冲击块、与冲击块配合锤砧和连接在电机上的主轴。当达到启动冲击机构的条件时，冲击块进行轴向移动或径向移动的往复运动，进而周期性与锤砧啮合，以输出旋转方向上的冲击力。
在相关技术中，冲击类工具基本是通过电子调节电机的输入电流来改变电机转速从而实现对输出件的速度调节以及冲击扭矩的调节。这一方面对电气部件的性能要求很高，另一方面为匹配电子控制和电机的性能，冲击工具适用的工况有限。
本部分提供了与本申请相关的背景信息，这些背景信息不一定是相关技术。
发明内容
本申请的一个目的是解决或至少减轻上述问题的一部分或者全部。本申请提供一种冲击工具，以适用更多工况。
本申请采用如下技术方案：
第一方面，本申请一实施例提供了一种冲击工具，包括：冲击机构，用于对输出轴施加冲击力；传动机构，包括：多级传动组件，在多级传动组件中，至少设置一级传动组件的传动比可调。
在一些实施例中，多级传动组件的输出传动比大于1。
在一些实施例中，还包括电机，包括绕第一轴线转动的电机轴；输出轴，用于输出动力；输出轴以输出轴线为轴转动；传动机构，用于在电机轴和冲击机构之间动力的传递。
在一些实施例中，传动机构具有使得输出轴以不同的转速进行输出的至少两个传动状态。
在一些实施例中，任意一种传动状态的传动机构的输出传动比大于1。
在一些实施例中，还包括，切换机构，用于驱动传动机构在不同的传动状态之间切换。
在一些实施例中，传动机构包括：第一级行星轮组和第二级行星轮组。
在一些实施例中，第一级行星轮组靠近电机轴，第二级行星轮组靠近冲击机构。
在一些实施例中，第二级行星轮组具有两种传动比。
在一些实施例中，第二级行星轮的至少一种传动比大于1。
在一些实施例中，第二级行星轮包括第二内齿圈。
在一些实施例中，第二内齿圈被配置为在第一位置和第二位置间移动。
在一些实施例中，第二内齿圈处于第一位置时，第二内齿圈被限制旋转。
在一些实施例中，传动机构还包括用于限制第二内齿圈的锁定环。
在一些实施例中，锁定环与用于支撑主轴的第一轴承连接。
在一些实施例中，冲击机构，包括：由电机轴驱动的主轴和用于支撑主轴 的第一轴承，沿第一轴线方向，第一轴承比多级传动组件更靠近输出轴。
在一些实施例中，冲击机构包括被主轴驱动的冲击块和与冲击块相配合并受其打击的锤砧。
在一些实施例中，锤砧驱动输出轴转动，冲击块通过滚球与主轴一体旋转，并且能够以规定的行程沿第一轴线方向相对于主轴往复移动，以周期性与锤砧配合。
在一些实施例中，冲击机构还包括：为冲击块提供使其靠近锤砧的力的弹性元件，弹性元件具有至少两个不同的弹性系数。
在一些实施例中，弹性元件被配置为具有不同节距的螺旋弹簧。
在一些实施例中，还包括：供电电源，供电电源提供至少4V的标称电压，供电电源为电机提供电能。
第二方面，本申请一实施例提供了一种冲击工具，包括：冲击机构，用于对输出轴施加冲击力；冲击机构包括：由电机轴驱动的主轴；传动机构，用于在电机轴和主轴之间进行动力的传递，传动机构的输出传动比可调。
在一些实施例中，输出轴以不同的转速进行输出，
在一些实施例中，传动机构的输出传动比大于1。
在一些实施例中，还包括：电机，包括绕第一轴线转动的电机轴；输出轴，用于输出动力；输出轴以输出轴线为轴转动；
第三方面，本申请一实施例提供了一种冲击工具，包括：
冲击机构，用于对输出轴施加冲击力；冲击机构包括：由电机轴驱动的主轴；沿第一轴线方向，用于支撑主轴的第一轴承比多级传动组更靠近输出轴。
在一些实施例中，还包括，传动机构，用于在电机轴和主轴之间进行动力的传递；传动机构包括多级传动组，其中，多级传动组中至少设置两级减速传 动。
在一些实施例中，还包括，电机，包括绕第一轴线转动的电机轴；输出轴，用于输出动力；输出轴以输出轴线为转轴。
在一些实施例中，传动机构的输出传动比可调。
在一些实施例中，多级传动组件的输出传动比大于1。
在一些实施例中，还包括：供电电源，供电电源提供至少4V的标称电压，供电电源为电机提供电能。
附图说明
图1是本申请中的第一实施例的结构示意图；
图2是图1中的第一实施例电机、传动机构、冲击机构、输出机构和切换机构的结构图；
图3是图2中的剖视图；
图4是图2中的结构的爆炸图；
图5是图4中冲击机构的另一个视角；
图6是图2中的传动机构、冲击机构、输出机构和切换机构的结构图，其中，冲击块位于第二位置，第二内齿圈处于第一位置；
图7是图6的剖视图；
图8是图2中的传动机构、冲击机构、输出机构和切换机构的结构图，其中，冲击块位于第一位置，第二内齿圈处于第二位置；
图9是图8的剖视图；
图10是弹性元件的结构的结构示意图；
图11是主轴、第二行星齿轮和第二行星轮架的装配图；
图12是第一壳体和锁定环的装配图。
具体实施方式
在详细解释本申请的任何实施方式之前，应当理解，本申请不限于其应用到以下描述中阐述的或以上附图中所示的结构细节和组件布置。
在本申请中，术语“包括”、“包含”、“具有”或者其任何其他变体意在涵盖非排他性的包含，从而使得包括一系列要素的过程、方法、物品或者装置不仅包括那些要素，而且还包括没有明确列出的其他要素，或者是还包括为这种过程、方法、物品或者装置所固有的要素。在没有更多限制的情况下，由语句“包括一个……”限定的要素，并不排除在包括该要素的过程、方法、物品或者装置中还存在另外的相同要素。
在本申请中，术语“和/或”，是一种描述关联对象的关联关系，表示可以存在三种关系。例如，A和/或B，可以表示：单独存在A，同时存在A和B，单独存在B这三种情况。另外，本申请中字符“/”，一般表示前后关联对象是一种“和/或”的关系。
本申请中，术语“连接”、“结合”、“耦合”、“安装”可以是直接连接、结合、耦合或安装，也可以是间接连接、结合、耦合或安装。其中，进行举例示范，直接连接指的是两个零件或组件之间不需设置中间件而连接在一起，间接连接指的是两个零件或组件分别与至少一个中间件连接，这两个零件或组件通过中间件实现连接。此外，“连接”和“耦合”不限于物理或机械连接或耦合，并且可以包括电连接或耦合。
在本申请中，本领域普通技术人员将理解，结合数量或条件使用的相对术语(例如，“约”，“大约”，“基本”等)为包括所述值并且具有上下文所指示的 含义。例如，该相对术语至少包括与特定值的测量相关的误差程度，与特定值相关的由制造，组装，使用造成的公差等。这种术语也应被视为公开了由两个端点的绝对值限定的范围。相对术语可指代所指示的值的一定百分比(例如1％，5％，10％或更多)的加或减。未采用相对术语的数值，也应该被揭示为具有公差的特定值。此外，“基本”在表达相对的角度位置关系时(例如，基本平行，基本垂直)，可指代在所指示的角度的基础上加或减一定度数(例如1度，5度，10度或更多)。
在本申请中，本领域普通技术人员将理解，由组件执行的功能可以为由一个组件，多个组件，一个零件，或多个零件执行。同样的，由零件执行的功能也可以由一个零件，一个组件，或多个零件组合来执行。
在本申请中，术语“上”、“下”、“左”、“右”、“前”、“后”等方位词是以附图所示的方位和位置关系来进行描述的，不应理解为对本申请实施例的限定。此外，在上下文中，还需要理解的是，当提到一个元件连接在另一个元件“上”或者“下”时，其不仅能够直接连接在另一个元件“上”或者“下”，也可以通过中间元件间接连接在另一个元件“上”或者“下”。还应当理解的，上侧、下侧、左侧、右侧、前侧、后侧等方位词不仅代表正方位，也可以理解为侧方位。例如，下方可以包括正下方、左下方、右下方、前下方以及后下方等。
在本申请中，术语“控制器”、“处理器”、“中央处理器”、“CPU”、“MCU”可以互换。在使用单元“控制器”、“处理器”、“中央处理器”、“CPU”、或“MCU”来执行特定功能，除非另有说明，否则这些功能则可以由单个上述单元或多个上述单元来执行。
在本申请中，术语“装置”、“模块”或“单元”为了实现特定的功能，它们可以 通过硬件或软件的形式来实现。
在本申请中，术语“计算”、“判断”、“控制”、“确定”、“识别”等指的是计算机系统或类似电子计算设备(例如，控制器，处理器等)的操作和过程。
为了清楚的说明本申请的技术方案，还定义了如图1-图3所示的上侧、下侧、左侧、右侧、前侧和后侧。
如图1示出了本申请的第一实施例的冲击工具，在本实施例中，冲击工具为一种冲击扳手100。可以理解的，冲击工具为一种旋转类工具，在其他可替换实施例中，该旋转类工具可安装不同的工作附件，通过这些不同的工作附件使得冲击工具可以为例如冲击螺丝批、冲击钻等其他冲击工具。
如图1示出了本申请的第一实施例的冲击扳手100,包括供电电源30。其中，供电电源30用于为冲击扳手100提供电能。在本实施例中，供电电源30为电池包，电池包配合相应的电源电路，为冲击扳手100内的相应部件供电。本领域技术人员应当理解，供电电源30并不限于使用电池包的场景，还可通过市电、交流电源，配合相应的整流、滤波和调压电路，实现对机内的相应部件供电。
冲击扳手100包括外壳11、电机12、输出机构13、传动机构14和冲击机构15。其中，外壳11包括用于容纳电机12的电机壳体111和容纳至少部分输出机构13的输出壳体112，输出壳体112连接于电机壳体111的前端。外壳11还形成或连接有一供用户操作的握持部113。握持部113与电机壳体111形成T型或L型结构，方便用户握持及操作。握持部113的一端连接有供电电源30。供电电源30可拆卸地连接至握持部113。
如图1至图4所示，电机12包括以第一轴线101为轴转动的电机轴121。
输出机构13包括用于连接工作附件并驱动工作附件旋转的输出轴131。输出轴131前端设有夹持组件，可在实现不同功能时夹持相应的工作附件，例如 螺丝批、钻头、套筒等。
输出轴131用于输出动力，输出轴131以输出轴线为轴转动，在本实施例中，输出轴线为第二轴线102。在本实施例中，第一轴线101与第二轴线102重合。在其他可替换实施例中，第二轴线102与第一轴线101之间呈一定角度的夹角设置。在其他替换实施例中，第一轴线101与第二轴线102相互平行但不重合设置。
如图3至图5所示，冲击机构15用于向输出轴131提供冲击力。冲击机构15包括主轴151、套设在主轴151外周的冲击块152、设置在冲击块152前端的锤砧153和弹性元件154。其中，锤砧153连接输出轴131。在本实施例中，锤砧153包括砧座1531，输出轴131形成或连接在砧座1531的前端。可以理解的是，砧座1531与输出轴131可以是一体成形或是分开形成的独立零件。
冲击块152被主轴151驱动，砧座1531与冲击块152相配合并受其打击。冲击块152包括冲击块主体1521和冲击块主体1521的前端面径向对称凸设有一对第一端齿1523。砧座1531与冲击块152相对的后端面上径向对称的凸出设置有一对第二端齿1532。输出轴131伸出输出壳体112。冲击块152支撑在主轴151上与主轴151一体旋转并可在主轴的轴线方向上相对于主轴151往复滑动。在本实施例中，主轴的轴线与电机轴的轴线重合，因此，冲击块152沿第一轴线101方向相对于主轴151往复滑动和旋转。在其他可替换实施例中，主轴的轴线可以与电机轴的轴线平行但不重合，或者，主轴的轴线与电机轴的轴线呈一定夹角设置。
弹性元件154为冲击块152提供使其靠近锤砧153的力。在本实施例中，弹性元件154为螺旋弹簧。
在冲击扳手100在工作过程中，冲击块152在与主轴一体旋转的同时，以 规定行程沿第一轴线101方向相对于主轴151前后往复运动。如图6至图9所示，冲击块152包括向前运动到最远端的第一位置和向后运动至最远端的第二位置。其中，如图6至图7所示，冲击块位于第二位置。如图8至图9所示，冲击块位于第一位置。第一位置时冲击块152的第一端齿1523与锤砧153接合，即是说，冲击块152的行程前端通过锤砧153进行止位。
冲击块主体1521前端面上还设置有一对开口朝前并沿前后方向向后延伸的第一球槽1522。主轴151外表面还形成有一对V字形第二球槽1511。第一球槽1522和第二球槽1511具有均半圆形的槽底。冲击机构15还包括滚球155。滚球155横跨第一球槽1522与第二球槽1511，从而使冲击块152与主轴151连接并一起运动。在本实施例中，滚球155为钢球。
在相关技术中，由于冲击块与主轴上分别设置有向内凹陷的V形槽，进而共同形成球道，滚球155设置于冲击块152与主轴151之间并嵌入至球道，从而主轴151通过滚球155即可驱动冲击块152转动，冲击块152通过锤砧153的配合驱动锤砧153转动进一步地驱动输出轴131转动。
当冲击工具空载时，冲击机构不发生冲击，冲击机构起到传动作用，将电机的转动传递至输出轴。当冲击工具被施加负载时，输出轴的转动受阻，由于负载的大小不同，输出轴可能转速降低也可能完全停止转动。当输出轴完全停止转动时，锤砧也停止转动，由于锤砧对冲击块在周向上的限位作用冲击块也停止转动，但是主轴继续转动，这使得滚球受挤压沿着球道轨迹移动，从而带动冲击块产生沿主轴轴线向后的位移，即向冲击块的第二位置运动。同时挤压弹性元件直至锤砧与冲击块完全脱开，此时冲击块处于第二位置。主轴驱动冲击块以一定转速转动，弹性元件沿轴向回弹，即向冲击块的第一位置运动。冲击块与锤砧之间的相对转速即为冲击块的转速，当冲击块转动至与锤砧接触时， 便会对锤砧施加一个冲击力，此时冲击块处于第一位置。在此冲击力的作用下，输出轴克服负载继续转动一定角度，之后输出轴再次停转，重复以上过程，由于冲击频率足够大，便会对输出轴产生一个相对连续的冲击力，从而使得工作附件持续工作。
如图2至图4所示，传动机构14设置在电机12和冲击机构15之间，用于在电机轴121和主轴151之间实现动力的传递。
传动机构14包括多级传动组。在本实施例中，多级传动组为多级行星传动组140。行星传动组包括行星轮、用于安装行星轮的行星轮架和与行星轮啮合的内齿圈。多级行星传动组140中至少设置其中的一级行星传动组的传动比可调。在本实施例中，多级行星传动组140的输出传动比大于1。多级行星传动组140中靠近冲击机构15的行星传动组中的行星轮架形成或连接于主轴151。在本实施例中，至少一级行星传动组的内齿圈被配置为在第一位置和第二位置间移动。沿第一轴线101方向，用于支撑主轴151的第一轴承1512比多级行星传动组140更靠近输出轴131。相较于相关技术中已有的通过改变电机转速的电子调速方式来实现扭矩调节，设置多级行星传动组并通过调节行星轮组的传动比来实现转速调节进而实施扭矩调节，相当于增加机械方式调节转速和扭矩。在产品应用中，可以单独使用本申请的机械方式调节，也可以同时使用电机调速方式和机械方式。调节方式多样化，调节选择更多。在本实施例中，上述行星传动组的传动比可调，即是说，行星传动组至少具有两种不同的传动比，其中，一种传动比大于1，为减速增矩传动。另一种传动比基本等于1，此时行星轮组仅做传动作用。
而且本申请的机械方式调节转速和扭矩，不会改变电机输出功率。在一定程度上，可以提高电机的效率。即是说，使电机在高效率区间内进行转速和扭 矩的输出，通过调节传动机构的传动比来实现转速的调节。另一方面，因为通过电子方式，在低速输出时是通过降低电流来降低输出转速。无刷直流电机(BLDC)采用脉冲宽度调制(PWM)信号的调制方式控制，受到电机的占空比和可控半导体功率器件(例如Mosfet金氧半场效晶体管)的性能限制，电机输出的最低转速的阈值也受到限制。而增加了机械方式的调节，突破了电子调速的阈值限制，可以进一步的降低输出转速。以使的电机的输出转速和输出轴的输出转速之间的比值变大。使得输出轴在低输出转速时，电机不容易发生不启动或堵转。还可以实现输出轴低输出转速时发生冲击。进一步扩展了冲击工具的转速区间。在高速使用工况时，通过将传动比调节至基本为1的传动状态，进而对高速输出的使用环境不造成影响。
增加了可调传动比的传动机构，在一定程度上也扩展了冲击工具的适配电机的范围。在相关技术中，在冲击工具上使用的电机的输出扭矩阈值要高于仅做旋转输出的工具上使用的电机。其原因在于，启动的冲击时，传递到主轴上的扭矩需要能够驱动冲击块克服弹性元件的压力。而当电机的输出功率和输出扭矩不能达到此条件时，冲击过程无法启动。此时，电机会发生堵转。本申请利用多级减速增扭矩的方式，实现了低功率电机在冲击工具上的应用例如，使用4V电压(内置电池)的小电机的小型螺丝批。而且可调节的功能有利于不同工况的使用。有利于产品小型化和便携式冲击工具的发展。
在本实施例中，传动机构14具有使得输出轴131以不同的转速进行输出的两个传动状态。如图3所示，传动机构14包括壳体组件14a、第一级行星轮组144和第二级行星轮组145。可以理解的，本实施例为尽可能保证冲击扳手的整机长度的紧凑，所以设置两个传动状态和两级行星轮组。但根据产品的实际要求，传动机构可以设置两种以上传动状态，两级以上的行星轮组。以上并不影 响本申请的实质性内容。
如图3-4所示，第一级行星轮组144和第二级行星轮组145至少部分位于壳体组件14a中。第一级行星轮组144靠近电机轴121，第二级行星轮组145靠近主轴151。在本实施例中，第一级行星轮组144仅以一种传动比输出。即第一级行星轮组144以第一传动比输出，第一传动比大于1。即是说，第一级行星轮组144执行减速增加扭力的操作，第一级行星轮组144的输出转速小于输入该行星轮组的输入转速，输出扭力大于输入该行星轮组的输入扭力。
可选的，第一级行星轮组144包括：第一行星齿轮1441、用于安装第一行星齿轮1441的第一行星轮架1442和与第一行星齿轮1441啮合的第一内齿圈1443。电机轴121形成或连接以第一转速旋转的第一太阳轮122。在本实施例中，第一太阳轮122与电机轴121同轴转动。可选的，第一太阳轮122以第一轴线101为轴转动。其他可替换实施例中，第一太阳轮122连接于电机轴121。
第一太阳轮122驱动第一行星齿轮1441。第一行星齿轮1441被设置为与第一太阳轮122啮合。第一行星齿轮1441被设有多个，且多个第一行星齿轮1441被设置都与第一太阳轮122啮合。在本实施例中，第一行星齿轮1441绕第一轴线101的周向均匀设置4个。第一太阳轮122和第一行星齿轮1441形成传递动力的啮合齿部。由于第二传动比大于1，因此第一太阳轮122的啮合齿部的齿顶圆直径被设置小于第一级行星轮组144的齿顶圆直径，使得第一级行星轮组144的啮合齿的齿数大于太阳轮的啮合齿部的齿数。第一内齿圈1443啮合在多个第一行星齿轮1441的外围。第一行星轮架1442包括第一传动盘1442a、第一支撑架1442b以及第一输出部，第一支撑架1442b和第一输出部分别形成于第一传动盘1442a两侧。第一输出部与第一传动盘1442a同步转动。第一支撑架1442b插入第一行星齿轮1441，且与第一行星齿轮1441构成转动连接，从而第一行星 齿轮1441可以驱动第一行星轮架1442绕第一轴线101转动。第一输出部周侧上都形成有啮合齿，第一输出部用于和第二级行星轮组145啮合，从而实现第一级行星轮组144和第二级行星轮组145的传动连接。在本实施例中，第一输出部为第二级行星轮组145的第二太阳轮1444。
第二级行星轮组145包括：第二行星齿轮1451、用于安装第二行星齿轮1451的第二行星轮架1452和与第二行星齿轮1451啮合的第二内齿圈1453。第二太阳轮1444驱动第二行星齿轮1451。在本实施例中，第二太阳轮1444与电机轴121同轴转动，可选的，第二太阳轮1444以第一轴线101为轴转动。第二行星齿轮1451被设置为与第二太阳轮1444啮合。第二行星齿轮1451被设有多个，且多个第二行星齿轮1451被设置分别与第二太阳轮1444啮合。在本实施例中，第二行星齿轮1451绕第一轴线101的周向均匀设置5个。第二行星齿轮1451、第二行星轮架1452和第二内齿圈1453它们三者之间的啮合关系与第一级行星轮组144中的啮合关系相同，为本领域技术人员所熟知，这里不再赘述。
第二行星轮架1452包括第二传动盘1452a和第二支撑架1452b。第二支撑架1452b插入第二行星齿轮1451，且与第二行星齿轮1451构成转动连接，从而第二行星齿轮1451可以驱动第二传动盘1452a绕第一轴线101转动。在本实施例中，如图11所示，第二传动盘1452a形成于主轴151的后端。第二行星齿轮1451通过第二行星轮架1452驱动主轴151旋转。在其他可替换实施例中，第二传动盘1452a与主轴151可以独立的部件，第二传动盘1452a连接与主轴151。只要能够实现第二行星齿轮1451驱动主轴151旋转即可。
如图6至图8所示，第二级行星轮组145具有两种传动比。其中，第二传动比基本等于1，即是说，此时第二级行星轮组145仅起传动作用。此时第二级行星轮组145为第二传动状态。第三传动比大于1，即是说为减速传动。此时第 二级行星轮组145为第二变速状态。
当处于第二变速状态时，第二内齿圈1453被固定。在本实施例中，第二内齿圈1453绕第一轴线101不可转动，此时第二级行星轮组145起到变速作用。当第二级行星轮组145处于第二传动状态时，第二内齿圈1453被释放，第二内齿圈1453被允许被第二太阳轮1444驱动旋转。第二内齿圈1453和第一行星轮架1442同步绕第一轴线101转动，第二级行星轮组145不具有减速作用。在本实施例中，第一传动盘1442a外周侧上都形成有啮合齿，第二级行星轮组145处于第二传动状态时，第二内齿圈1453与第一传动盘1442a的啮合齿啮合并同步旋转。
以下具体介绍传动机构14中内齿圈的固定和释放以及调节传动比的结构和过程。
如图3至图9和图12所示，壳体组件14a，包括：第一壳体141、安装于第一壳体141一端的第一盖体142和第一壳体141另一端的锁定环143。其中，第一壳体141沿第一轴线101延伸并形成一个柱形的容纳空间。第一级行星轮组144和第二级行星轮组145至少部分被收容于第一壳体141中。第一盖体142沿垂直于第一轴线101方向延伸，第一盖体142被安装于第一壳体141靠近电机12的一端。电机轴121上设置有用于支撑电机轴121的第二轴承123。在本实施例中，第二轴承123为电机前轴承。第一盖体142上设置有容纳部1422，第二轴承123被收容在容纳部1422内。电机轴121通过容纳部1422伸出第一盖体142伸入第一壳体141内，进而电机轴121前端设置第一太阳轮122伸入第一壳体141内。
如图12所示，第一壳体141或第一盖体142形成或连接有用于限制第一内齿圈1443转动的锁定部1425。锁定部1425为第一轴线101周向间隔设置的多 个第一锁定齿1425a，第一锁定齿1425a沿第一壳体141的轴向延伸，即沿第一轴线101方向延伸。如图4所示，第一内齿圈1443包括多个沿第一内齿圈1443周向间隔设置的第一配合齿1443a。第一配合齿1443a沿第一内齿圈1443的轴线方向延伸，即沿第一轴线101方向延伸。第一锁定齿1425a和第一配合齿1443a在第一轴线101的周向方向上被交错地设置。当第一配合齿1443a与第一锁定齿1425a连接时，第一锁定齿1425a限制第一配合齿1443a的相对于第一锁定齿1425a的旋转。第一锁定齿1425a与第一配合齿1443a咬合接触时，第一内齿圈1443被固定。
在本实施例中，由于第一级行星轮组仅以一种传动比输出，因此，第一内齿圈不可移动。在其他可替换实施例中，第一内齿圈也可以沿第一轴线方向前后平移。此时，第一壳体设有伸入第一壳体内的凸缘部，凸缘部形成或固定有用于限制第一内齿圈转动的锁定部。锁定部与上述相同。当第一内齿圈被驱动向前运动，以使第一内齿圈被锁定部释放。第一内齿圈与第一传动盘的啮合齿啮合并同步旋转。此时，第一级行星轮组为传动状态。第一级行星轮组不具有减速作用。
针对第二内齿圈1453的锁定和释放。第一壳体141靠近输出轴132的一端形成或连接有锁定环143，锁定环143有用于锁定第二内齿圈1453。锁定环143沿第一轴线101周向间隔设置的多个第二锁定齿1431，第二锁定齿1431沿第一壳体141的轴向延伸，即沿第一轴线101方向延伸。第二内齿圈1453上设置有第二配合齿1453a。第二配合齿1453a沿第二内齿圈1453的轴线方向延伸，即沿第一轴线101方向延伸。第二锁定齿1431和第二配合齿1453a在第一轴线101的周向方向上被交错地设置。当第二配合齿1453a与第二锁定齿1431连接时，第二锁定齿1431限制第二配合齿1453a的相对于第二锁定齿1431的旋转。第 二锁定齿1431与第二配合齿1453a咬合接触时，第二内齿圈1453被固定。当第二内齿圈1453被驱动向后运动，以使第二内齿圈1453被锁定部1425释放。第二内齿圈1453与第一传动盘1442a的啮合齿啮合并同步旋转。此时，第二级行星轮组为传动状态。第二级行星轮组不具有减速作用。其中，为方便第一壳体141的模具制作，锁定环143采用内嵌部件的形式固定第一壳体141内。
如图1所示，冲击扳手100还包括切换机构16用于驱动所述传动机构在不同的所述传动状态之间切换。切换机构16包括供用户操作的操作件163。如图6至图9所示，切换机构16包括拨架。操作件163驱动拨架位移。在本实施例中，拨架包括驱动第二内齿圈1453的第一拨架161，第一拨架161与第二内齿圈1453连接。当需要第二级行星轮组145处于第二变速状态时，第一拨架161被操作进而驱动第二内齿圈1453沿第一轴线101向冲击机构15运动，直至第二内齿圈1453与锁定环143锁定连接，第二内齿圈1453以第一轴线101为转轴的转动被限制，此时第二内齿圈1453处于第一位置。当需要第二级行星轮组145处于第二传动状态时，第一拨架161被操作进而驱动第二内齿圈1453沿第一轴线101向第一行星轮架1442的方向运动，直至第二内齿圈1453与锁定环143锁定连接脱离，此时第二内齿圈1453处于第二位置。第二内齿圈1453与第一行星轮架1442的啮合齿啮合并同步旋转。相当于将第二内齿圈1453与第二太阳轮1444同步旋转。
在其他可替换实施例中，当第一级行星轮组的传动状态可以调整时，拨架还包括驱动第一内齿圈的第二拨架，第二拨架与第一内齿圈连接。当需要第一级行星轮组处于变速状态时，第二拨架被操作进而驱动第一内齿圈沿第一轴线向第一盖体运动，直至第一锁定齿与第一配合齿咬合接触，第一内齿圈以第一轴线为转轴的转动被限制。当需要第一级行星轮组处于传动状态时，第二拨架 被操作进而驱动第一内齿圈沿第一轴线向远离第一盖体方向运动，直至第一锁定齿与第一配合齿相互脱离，此时第一内齿圈处于第二位置。
冲击机构15还包括用于支撑主轴151的第一轴承1512。在本实施例中，第一轴承1512为滚珠轴承或滚针轴承。沿第一轴线101方向，第一轴承1512比多级行星传动组更靠近所述输出轴131。可以理解的，第一轴承1512套设在主轴151外围且位于行星轮前方。在本实施例中，第一轴承1512位于第二行星齿轮1451前方。锁定环143沿第一轴线101方向上，一侧设置有第二锁定齿1431，另一侧形成开口式环形槽1432。环形槽1432的开口朝向冲击机构15。第一轴承1512的外侧至少部分抵接在环形槽1432的侧壁。进而将第一轴承1512在第一轴线101方向的径向位移限制。第一轴承1512后端面抵接在环形槽1432的底壁上。主轴151沿垂直于第一轴线101方向延伸出止挡面，止挡面的直径大于第一轴承1512的内层直径。第一轴承1512的前端面抵接在止挡面。进而将第一轴承1512沿第一轴线101方向的轴向位移限制。既保证主轴151的旋转支撑的稳定，也使本申请的机构更为紧凑。
而在一些实施例中,将第一内齿圈和第二内齿圈均限制其旋转运动，同时取消或固定切换机构。以使多级行星传动组均为减速传动。增加多级减速以使电机的输出转速和输出轴的输出转速之间的比值变大。使得输出轴在低输出转速时，电机不容易发生不启动，进而还可以实现输出轴低输出转速时可以发生冲击。另一方面，利用多级减速增扭的方式，实现了小功率电机在冲击工具上的应用。
为进一步扩展冲击扳手的使用工况，本实施例中，弹性元件具有至少两个不同的弹性系数。示例性的，弹性元件包括第一弹性系数K1和第二弹性系数K2。其中，第一弹性系数K1小于第二弹性系数K2，从而在需要小冲击力或者 快速冲击时，第一弹性系数K1被使用。在需要高冲击力时，第一弹性系数K1和第二弹性系数K2均被启动。如图10所示，为实现弹性元件具有至少两个不同的弹性系数，弹性元件被配置为具有节距为T1和T2的螺旋弹簧，其中，T1小于T2。在其他可替换实施例中，弹性元件可以为锥形弹簧。在其他可替换实施例中，弹性元件被配置两个不同弹性系数的单弹簧元件，两个单弹簧元件彼此并联或者彼此串联。
以上显示和描述了本申请的基本原理、主要特征和优点。本行业的技术人员应该了解，上述实施例不以任何形式限制本申请，凡采用等同替换或等效变换的方式所获得的技术方案，均落在本申请的保护范围内。

Claims (20)

  1. 一种冲击工具，包括：
    电机，包括绕第一轴线转动的电机轴；
    输出轴，用于输出动力；所述输出轴以输出轴线为轴转动；
    冲击机构，用于对所述输出轴施加冲击力，
    传动机构，用于在所述电机轴和所述冲击机构之间动力的传递；
    其中，所述传动机构，包括：多级传动组件，在所述多级传动组件中，至少设置一级传动组件的传动比可调，所述多级传动组件的输出传动比大于1。
  2. 根据权利要求1所述的冲击工具，其中，所述传动机构具有使得所述输出轴以不同的转速进行输出的至少两个传动状态。
  3. 根据权利要求2所述的冲击工具，其中，任意一种传动状态的所述传动机构的输出传动比大于1。
  4. 根据权利要求2所述的冲击工具，还包括，切换机构，用于驱动所述传动机构在不同的所述传动状态之间切换。
  5. 根据权利要求1所述的冲击工具，其中，所述冲击机构包括由所述电机轴驱动的主轴和用于支撑所述主轴的第一轴承。
  6. 根据权利要求5所述的冲击工具，其中，所述传动机构包括：第一级行星轮组和第二级行星轮组，所述第一级行星轮组靠近所述电机轴，所述第二级行星轮组靠近所述冲击机构。
  7. 根据权利要求6所述的冲击工具，其中，所述第二级行星轮组具有两种传动比，所述第二级行星轮的至少一种所述传动比大于1。
  8. 根据权利要求6所述的冲击工具，其中，所述第二级行星轮包括第二内齿圈，所述第二内齿圈被配置为在第一位置和第二位置间移动。
  9. 根据权利要求8所述的冲击工具，其中，所述第二内齿圈处于所述第一位 置时，所述第二内齿圈被限制旋转。
  10. 根据权利要求8所述的冲击工具，其中，所述传动机构还包括用于限制所述第二内齿圈的锁定环，所述锁定环与用于支撑所述主轴的第一轴承连接。
  11. 根据权利要求5所述的冲击工具，其中，所述冲击机构，还包括：，沿所述第一轴线方向，所述第一轴承比所述多级传动组件更靠近所述输出轴。
  12. 根据权利要求11所述的冲击工具，其中，所述冲击机构包括被所述主轴驱动的冲击块和与所述冲击块相配合并受其打击的锤砧，所述锤砧驱动所述输出轴转动，所述冲击块通过滚球与所述主轴一体旋转，并且能够以规定的行程沿第一轴线方向相对于主轴往复移动，以周期性与所述锤砧配合。
  13. 根据权利要求12所述的冲击工具，其中，所述冲击机构还包括：为所述冲击块提供使其靠近所述锤砧的力的弹性元件，所述弹性元件具有至少两个不同的弹性系数。
  14. 根据权利要求11所述的冲击工具，其中，弹性元件被配置为具有不同节距的螺旋弹簧。
  15. 根据权利要求1所述的冲击工具，还包括：供电电源，所述供电电源提供至少4V的标称电压，所述供电电源为所述电机提供电能。
  16. 一种冲击工具，包括：
    电机，包括绕第一轴线转动的电机轴；
    输出轴，用于输出动力；所述输出轴以输出轴线为轴转动；
    冲击机构，用于对所述输出轴施加冲击力；所述冲击机构包括：由所述电机轴驱动的主轴；
    传动机构，用于在所述电机轴和所述主轴之间进行动力的传递；
    所述传动机构的输出传动比可调，以使所述输出轴以不同的转速进行输出。
  17. 一种冲击工具，包括：
    电机，包括绕第一轴线转动的电机轴；
    输出轴，用于输出动力；所述输出轴以输出轴线为转轴；
    冲击机构，用于对所述输出轴施加冲击力；所述冲击机构包括：由所述电机轴驱动的主轴；
    传动机构，用于在所述电机轴和所述主轴之间进行动力的传递；
    所述传动机构包括多级传动组，其中，多级传动组中至少设置两级减速传动，沿所述第一轴线方向，用于支撑所述主轴的第一轴承比所述多级传动组更靠近所述输出轴。
  18. 根据权利要求17所述的冲击工具，其中，所述传动机构的输出传动比可调。
  19. 根据权利要求18所述的冲击工具，其中，所述多级传动组的输出传动比大于1。
  20. 根据权利要求18所述的冲击工具，还包括：供电电源，所述供电电源提供至少4V的标称电压，所述供电电源为所述电机提供电能。
PCT/CN2023/124691 2022-10-20 2023-10-16 冲击工具 Ceased WO2024083067A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4644022A1 (en) * 2024-04-26 2025-11-05 Nanjing Chervon Industry Co., Ltd. Electric drill and handheld power tool

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN219380519U (zh) * 2023-02-17 2023-07-21 南京泉峰科技有限公司 冲击工具

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3129974U (ja) * 2006-12-25 2007-03-08 鍾李杏枝 多機能インパクト電動工具
CN101342693A (zh) * 2007-07-12 2009-01-14 苏州宝时得电动工具有限公司 动力工具
CN102431013A (zh) * 2011-09-13 2012-05-02 南京久驰机电实业有限公司 一种具有驱动模式切换的电钻
CN104070490A (zh) * 2013-03-29 2014-10-01 南京德朔实业有限公司 电动工具
CN105215915A (zh) * 2014-06-30 2016-01-06 南京德朔实业有限公司 扭力输出工具
DE202016001685U1 (de) * 2016-03-15 2016-06-27 Trinity Precision Technology Co., Ltd. Mehrstufiger Geschwindigkeits-Übertragungs-Mechanismus
CN113858134A (zh) * 2020-06-30 2021-12-31 南京德朔实业有限公司 扭力输出工具
CN113858135A (zh) * 2020-06-30 2021-12-31 南京德朔实业有限公司 扭力输出工具

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5744669B2 (ja) * 2011-08-05 2015-07-08 株式会社マキタ 電動工具
DE102014212157A1 (de) * 2014-06-25 2015-12-31 Robert Bosch Gmbh Gehäusevorrichtung für eine Handwerkzeugmaschine
DE102015209406A1 (de) * 2015-05-22 2016-11-24 Robert Bosch Gmbh Handwerkzeugmaschine mit einem mechanischen Drehschlagwerk
CN110614393B (zh) * 2018-05-18 2021-05-14 宝时得科技（中国）有限公司 动力工具
US11964375B2 (en) * 2019-11-27 2024-04-23 Black & Dekcer Inc. Power tool with multispeed transmission

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3129974U (ja) * 2006-12-25 2007-03-08 鍾李杏枝 多機能インパクト電動工具
CN101342693A (zh) * 2007-07-12 2009-01-14 苏州宝时得电动工具有限公司 动力工具
CN102431013A (zh) * 2011-09-13 2012-05-02 南京久驰机电实业有限公司 一种具有驱动模式切换的电钻
CN104070490A (zh) * 2013-03-29 2014-10-01 南京德朔实业有限公司 电动工具
CN105215915A (zh) * 2014-06-30 2016-01-06 南京德朔实业有限公司 扭力输出工具
DE202016001685U1 (de) * 2016-03-15 2016-06-27 Trinity Precision Technology Co., Ltd. Mehrstufiger Geschwindigkeits-Übertragungs-Mechanismus
CN113858134A (zh) * 2020-06-30 2021-12-31 南京德朔实业有限公司 扭力输出工具
CN113858135A (zh) * 2020-06-30 2021-12-31 南京德朔实业有限公司 扭力输出工具

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4585368A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4644022A1 (en) * 2024-04-26 2025-11-05 Nanjing Chervon Industry Co., Ltd. Electric drill and handheld power tool

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