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WO2009006845A1 - Outil de puissance - Google Patents

Outil de puissance Download PDF

Info

Publication number
WO2009006845A1
WO2009006845A1 PCT/CN2008/071589 CN2008071589W WO2009006845A1 WO 2009006845 A1 WO2009006845 A1 WO 2009006845A1 CN 2008071589 W CN2008071589 W CN 2008071589W WO 2009006845 A1 WO2009006845 A1 WO 2009006845A1
Authority
WO
WIPO (PCT)
Prior art keywords
impact
vibration
state
block
working shaft
Prior art date
Application number
PCT/CN2008/071589
Other languages
English (en)
Chinese (zh)
Inventor
Hongfeng Zhong
Shisong Zhang
Xiaotian Zeng
Original Assignee
Positec Power Tools (Suzhou) 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 Positec Power Tools (Suzhou) Co., Ltd. filed Critical Positec Power Tools (Suzhou) Co., Ltd.
Publication of WO2009006845A1 publication Critical patent/WO2009006845A1/fr

Links

Classifications

    • 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
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0023—Tools having a percussion-and-rotation mode
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
    • B25D2216/0007—Details of percussion or rotation modes
    • B25D2216/0038—Tools having a rotation-only mode

Definitions

  • This invention relates to a power tool, and more particularly to a gun drill-type power tool of various functions that can be selectively implemented.
  • impact wrenches electric drills, electric screwdrivers, and impact drills are usually included.
  • An impact wrench is used to tighten the bolt to the workpiece.
  • the structure generally includes an output shaft that is driven by the rotation of the motor, an impact block that is coupled to the output shaft through the spiral groove and the ball, and a working shaft that is located in front of the impact block and that cooperates with the impact block through the end teeth.
  • An impact spring is also provided behind the impact block, which compresses the impact block to maintain a secure fit of the impact block with the working shaft.
  • the impact block moves axially toward the motor with respect to the working shaft, and simultaneously compresses the spring thereafter.
  • the impact block and the end teeth of the working shaft are disengaged, the impact block axially moves forward and strikes the working shaft in the rotational direction under the action of the impact spring, so that the working shaft continues to tighten the bolt in the rotational direction.
  • This cycle through the intermittent intermittent impact of the impact block, ensures that the bolt is finally tightened onto the workpiece.
  • An electric screwdriver is used to tighten the screw to the workpiece. It generally includes an overload clutch structure consisting of a clutch actuating member and a follower member, the actuating member being integral with the reduction gear, and the follower member being rotationally fixed within the housing and axially movable relative to the housing.
  • a working spring acts on the end face teeth of the active member through the follower, so that the active member is fixed in the rotational direction and can transmit torque to rotate the screwdriver.
  • the torque of the motor is transmitted to the screwdriver through the planetary gear reduction mechanism to rotate it, and the screwdriver head and the screw head groove are engaged, so that the screw is quickly tightened.
  • the impact drill is mainly used for perforating a workpiece of a brittle material, and has a vibrating mechanism composed of a moving cam and a static cam having dog-toothed teeth on opposite end faces.
  • the moving cam is installed in the middle of the working shaft, the static cam is fixed on the casing, and a spring is arranged between the moving and static cams to separate the two.
  • the working shaft generates an axial backward thrust to the static cam fixed relative to the casing, so that the impact drill moves backward.
  • the impact drill moves back one tooth height. distance.
  • the static cam quickly impacts the cam with the impact drill, thereby generating a strong impact force on the surface of the workpiece.
  • the brittle material is broken under repeated strong impacts.
  • the debris is discharged from the drill groove, and holes are made in the masonry and concrete members.
  • the electric drill is used to drill holes on the workpiece. During the operation, the drill shaft continuously rotates.
  • users need to perform different types of operations, such as screwing, screwing, drilling, etc., when performing work. In this way, it is very troublesome for the user to prepare a plurality of different types of power tools, and to constantly change them to operate.
  • U.S. Published Patent Application No. US 2005/0199404 A1 discloses a power tool that can simultaneously perform the functions of an impact wrench and an electric drill on a tool.
  • the power tool simultaneously locks both of the impact block (7) and the outer circumference of the working shaft (8) by a function switching mechanism (the function conversion button 33 and the connecting member 25 shown in FIGS. 1 and 4).
  • the impact block and the working shaft are relatively fixed, thereby realizing the conversion of the impact wrench function to the electric drill function.
  • the user can adjust the impact wrench function and the electric drill function on the same tool by simply adjusting the function conversion button.
  • European patent application EP 1050381 A2 discloses another power tool having both an impact wrench function and an electric drill function.
  • the power tool simultaneously locks both on the axis of the impact block (5) and the working shaft (6) by a function switching mechanism (reference numerals 15, 16, 24, 35, 36 in the drawing of the patent application) to make the impact block and
  • the working shaft remains relatively fixed, thereby enabling the conversion of the impact wrench function to the electric drill.
  • the connector for use in the power tool disclosed in the above-mentioned U.S. Patent Application is a large-sized circular sleeve, thereby increasing the overall volume of the power tool and increasing the manufacturing cost, and the power tool disclosed in the above-mentioned European Patent Application
  • the function conversion mechanism needs to be implemented by multiple components, and its structure is complicated. This reduces reliability.
  • U.S. Patent Application No. US 2005/0199404 A1 further discloses a four-function drill that further realizes the functions of an electric screwdriver and a hammer drill based on the functions of an impact wrench and an electric drill.
  • the four-function drill includes an impact mechanism for realizing an impact wrench, a clutch structure for realizing an electric screwdriver, and a vibration structure for realizing a hammer drill function, and also includes a function of an impact mode switching member for switching an impact wrench, and a clutch mode switching member.
  • the function of switching the electric screwdriver and the function of the vibration mode switching member for switching the impact drill, and a common button can simultaneously control the three switching members, so that the operation of the common button can be implemented alternatively.
  • such a four-function drill has a large number of components and a complicated structure, which increases manufacturing difficulty and at the same time reduces reliability.
  • the invention provides a power tool capable of selectively implementing functions such as an impact wrench, an electric drill, an electric screwdriver or a hammer drill, which is simple in structure, convenient in production and manufacture, and has high reliability.
  • the invention also provides a power tool capable of selectively implementing an impact wrench, an electric drill, an electric screwdriver or a hammer drill through two mode adjusting members, which realizes a simple structure, is convenient for manufacturing, and has high reliability. .
  • a power tool comprising: a casing having a front end portion operable to be adjacent to the workpiece;
  • the working shaft extends toward the front end of the casing and can be mated with the external working head
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft, and transmits a rotation output of the power source to the working shaft, the planetary gear speed reduction mechanism includes an inner ring gear, and the inner ring gear has a load on the working shaft a rotatable state that can be rotationally driven when set, and a limited rotation state that cannot be rotationally driven regardless of the load of the working shaft;
  • Impact mechanism which includes:
  • the active impact block is rotationally driven by the output shaft of the planetary gear reduction mechanism
  • the passive impact block is rotatably driven by engaging with the active impact block, the passive impact block is disposed on the working shaft and rotationally drives the working shaft, and the passive impact block is axially movable relative to the working axis;
  • the active impact block is selectively disengaged from the passive impact block when the load on the working shaft is increased to a specific value, and then re-engaged with the passive impact block under the rotational drive of the output shaft, thereby rotating in the direction of rotation Apply intermittent impact to the working shaft;
  • An impact switching member that selectively limits axial movement of the passive impact block relative to the working shaft such that the impact mechanism is disengageable from each other between the active and passive impact blocks and the active and passive impact blocks are always Switching between the limited impact states that cannot be disengaged from each other;
  • the mode adjusting member is mounted on the casing, and movably cooperates with the impact switching member to drive the impact switching member to switch the working state of the impact mechanism, and at the same time, the mode adjustment The piece is movably cooperated with the pressing mechanism to control the working state of the ring gear;
  • the power tool can select one of the following working modes by adjusting the mode adjusting member:
  • Impact mode in which the impact mechanism is in an impactable state, and at the same time, the inner ring gear is in a restricted rotation state;
  • Drilling mode in which the impact mechanism is in a restricted impact state, and the inner ring gear is in a limited rotation state.
  • the power tool further includes:
  • the vibration switching member cooperates with the vibration mechanism to switch the vibration mechanism between a vibrating state capable of applying axial vibration to the working shaft and a limited vibration state capable of applying axial vibration to the working shaft; wherein the mode adjusting member is
  • the vibration switching device cooperates with the vibration switching device to switch the working state of the vibration mechanism, and the power tool can further select the vibration mode by adjusting the mode adjusting member outside the casing.
  • the impact mechanism is in a limited impact state
  • the inner ring gear is in a limited rotation state.
  • the vibration mechanism is in a vibrating state.
  • a power tool comprising: a casing having a front end portion operable to be adjacent to the workpiece;
  • the working shaft extends toward the front end of the casing and can be mated with the external working head
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft to rotate the power source Passed to the working shaft so that the working head can be driven by rotation;
  • Impact mechanism which includes:
  • the active impact block is rotationally driven by the output shaft of the planetary gear reduction mechanism
  • a passive impact block rotatably driven by the active impact block, the passive impact block being disposed on the working shaft and rotatably driving the working shaft, wherein the passive impact block is axially movable relative to the working axis; wherein the active The impact block is selectively disengaged from the passive impact block when the load on the working shaft is increased to a specific value, and then re-engaged with the passive impact block under the rotational drive of the output shaft, thereby applying the working shaft in the rotational direction. Intermittent impact;
  • An impact switching member that selectively limits axial movement of the passive impact block relative to the working shaft such that the impact mechanism is disengageable from each other between the active and passive impact blocks and the active and passive impact blocks are always Switching between the restricted impact states that cannot be disengaged from each other; the vibration mechanism that applies axial vibration to the working shaft;
  • the vibration switching member cooperates with the vibration mechanism to switch the vibration mechanism between a vibrating state capable of applying axial vibration to the working shaft and a limited vibration state capable of applying axial vibration to the working shaft; mode adjusting member, mounting On the casing, the movably cooperates with the impact switching member to drive the impact switching member to switch the working state of the impact mechanism, and cooperates with the vibration switching member to drive the vibration switching member to switch the working state of the vibration mechanism;
  • the power tool can select one of the following working modes by adjusting the mode adjusting member:
  • Impact mode in which the impact mechanism is in an impactable state, and at the same time, the vibration mechanism is in a limited vibration state;
  • Drilling mode in which the impact mechanism is in a restricted impact state, and at the same time, the vibration mechanism is in a limited vibration state;
  • Vibration mode in which the impact mechanism is in a restricted impact state, and the vibration mechanism is in a vibrating state.
  • a power tool comprising: a casing having a front end portion operable to be adjacent to the workpiece;
  • the working shaft extends toward the front end of the casing and can be mated with the external working head
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft to rotate the power source Passed to the working shaft, the planetary gear reduction mechanism includes an inner ring gear having a rotatable state that can be rotationally driven when the load of the working shaft reaches a preset value and no matter how much the load of the working shaft is large a rotationally limited state of rotation;
  • a pressing mechanism comprising an axial elastic member, the pressing mechanism pressing and fixing the inner ring gear by axial elastic deformation of the axial elastic member thereof, the axial elastic member having an axial critical length, when the axis of the axial elastic member When the dimension is larger than the axial critical length, the inner ring gear is in a rotatable state, and when the axial dimension of the axial elastic member is smaller than the axial critical length, the inner ring gear is in a restricted rotation state;
  • An impact mechanism that exerts an intermittent impact on the working shaft in the direction of rotation
  • the impact switching member which is selectively engageable with the impact mechanism to make the impact mechanism capable of exerting an intermittent impact on the working shaft in the rotational direction and the inability to apply an intermittent impact to the working shaft in the rotational direction. Switch between states;
  • the mode adjusting member is mounted on the casing and can be rotated.
  • the mode adjusting member cooperates with the impact switching member to switch the working state of the impact mechanism while rotating, and simultaneously cooperates with the pressing mechanism to switch the working state of the inner ring gear;
  • the mode adjusting members have different rotation angles, and respectively correspond to different working modes, wherein:
  • the first rotation angle corresponds to a clutch mode in which the impact mechanism is in a restricted impact state, and at the same time, the inner ring gear is in a rotatable state;
  • the second rotation angle corresponds to an impact mode in which the impact mechanism is in an impactable state, and at the same time, the inner ring gear is in a restricted rotation state;
  • the third rotation angle corresponds to the drilling mode, in which the impact mechanism is in a restricted impact state, and at the same time, the inner ring gear is in a restricted rotation state.
  • the first rotation angle includes at least two, corresponding to the axial pressure applied to the ring gear at different axial dimensions of the axial elastic member, and the axial pressure and the preset of the working shaft load The value corresponds to; when the load of the working shaft exceeds a preset value corresponding to the first rotation angle, the inner ring gear is rotationally driven against the axial pressure of the axial elastic member at this time.
  • a power tool comprising: a casing having a front end portion operable to be adjacent to the workpiece;
  • the working shaft extends toward the front end of the casing and can be mated with the external working head
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft to rotate the power source Passed to the working shaft, the planetary gear reduction mechanism includes an inner ring gear having a rotatable state that can be rotationally driven when the load of the working shaft reaches a preset value and no matter how much the load of the working shaft is large a rotationally limited state of rotation;
  • An impact mechanism that exerts an intermittent impact on the working shaft in the direction of rotation
  • the impact switching member which is selectively engageable with the impact mechanism to make the impact mechanism capable of exerting an intermittent impact on the working shaft in the rotational direction and the inability to apply an intermittent impact to the working shaft in the rotational direction. Switch between states;
  • the vibration switching member cooperates with the vibration mechanism to switch the vibration mechanism between a vibrating state capable of applying axial vibration to the working shaft and a limited vibration state capable of applying axial vibration to the working shaft; mode adjusting member, mounting On the casing, the movably cooperates with the impact switching member to drive the impact switching member to switch the working state of the impact mechanism, and movably cooperates with the pressing mechanism to control the working state of the inner ring gear, and cooperates with the vibration switching member.
  • Driving the vibration switching member to switch the working state of the vibration mechanism;
  • the power tool can select one of the following working modes by adjusting the mode adjusting member:
  • Impact mode in which the impact mechanism is in an impactable state, the inner ring gear is in a restricted rotation state, and the vibration mechanism is in a limited vibration state;
  • Drilling mode in which the impact mechanism is in a restricted impact state, the inner ring gear is in a restricted rotation state, and the vibration mechanism is in a limited vibration state;
  • Vibration mode in which the impact mechanism is in a restricted impact state, the inner ring gear is in a restricted rotation state, and the vibration mechanism is in a vibrating state;
  • the mode adjusting member has at least different first positions and second positions to respectively correspond to preset values of different working shaft loads required for the inner ring gear to be rotationally driven.
  • the technical solution of the present invention may also be:
  • a power tool including:
  • the working shaft extends toward the front end of the casing and can be mated with the external working head;
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft, and transmits the rotating output of the power source to the working shaft, thereby rotating the working head;
  • An impact mechanism that exerts an intermittent impact on the working shaft in the direction of rotation
  • the impact switching member which is selectively engageable with the impact mechanism to make the impact mechanism capable of exerting an intermittent impact on the working shaft in the rotational direction and the inability to apply an intermittent impact to the working shaft in the rotational direction. Switch between states;
  • the vibration switching member cooperates with the vibration mechanism to switch the vibration mechanism between a vibrating state capable of applying axial vibration to the working shaft and a limited vibration state capable of applying axial vibration to the working shaft;
  • the first mode adjusting member Mounted on the casing, movably cooperated with the impact switching member to drive the impact switching member to switch the working state of the impact mechanism;
  • the second mode adjusting member is mounted on the casing, and movably cooperates with the vibration switching member to drive the vibration switching member to switch the working state of the vibration mechanism;
  • the power tool can select one of the following working modes by adjusting the first and second mode adjusting members: an impact mode, in which the impact mechanism is in an impactable state, and at the same time, the vibration mechanism is in a limited vibration state;
  • Drilling mode in which the impact mechanism is in a restricted impact state, and at the same time, the vibration mechanism is in a limited vibration state;
  • Vibration mode in which the impact mechanism is in a restricted impact state, and the vibration mechanism is in a vibrating state.
  • the technical solution of the present invention may also be:
  • a power tool including:
  • a housing having a front end portion operable to be adjacent to the workpiece
  • the working shaft extends toward the front end of the casing and can be mated with the external working head
  • a power source disposed in the casing, and outputting rotational power
  • a planetary gear reduction mechanism is disposed between the power source and the working shaft, and transmits a rotation output of the power source to the working shaft, the planetary gear speed reduction mechanism includes an inner ring gear, and the inner ring gear has a working a rotatable state that can be rotationally driven when the load of the shaft reaches a preset value and a limited rotation state that cannot be rotationally driven regardless of the load of the working shaft;
  • An impact mechanism that exerts an intermittent impact on the working shaft in the direction of rotation
  • the impact switching member which is selectively engageable with the impact mechanism to make the impact mechanism capable of exerting an intermittent impact on the working shaft in the rotational direction and the inability to apply an intermittent impact to the working shaft in the rotational direction. Switch between states;
  • the vibration switching member cooperates with the vibration mechanism to switch the vibration mechanism between a vibrating state capable of applying axial vibration to the working shaft and a limited vibration state capable of applying axial vibration to the working shaft;
  • the first mode adjusting member Mounted on the casing, movably cooperated with the impact switching member to drive the impact switching member to switch the working state of the impact mechanism, and movably cooperate with the pressing mechanism to control the working state of the inner ring gear;
  • the second mode adjusting member is mounted on the casing, and movably cooperates with the vibration switching member to drive the vibration switching member to switch the working state of the vibration mechanism;
  • the power tool can select one of the following working modes to work: an impact mode, in which the impact mechanism is in an impactable state, the inner ring gear is in a limited rotation state, and the vibration The mechanism is in a state of limited vibration;
  • Vibration mode in which the impact mechanism is in a restricted impact state, the inner ring gear is in a restricted rotation state, and the vibration mechanism is in a vibrating state.
  • the power tool of the present invention is provided with a passive impact block independent of the working axis, and the impact switching member is used to restrict the passive impact block from moving or releasing the restriction together with the active impact block.
  • the function of the impact wrench and the function of the electric drill are switched; and on the basis of the realization and switching mechanism of the electric screwdriver, or/and the realization and switching mechanism of the impact drill, the three-function gun drill or the four-function gun drill is realized.
  • the structure is simpler and easier to manufacture.
  • the switching of the clutch mode of the power tool of the present invention does not require a separate switching member,
  • the switching can be realized by adjusting the mode adjusting member to control the axial size of the pressing spring, and the mode adjusting member can also realize the control of the tripping torque.
  • the power tool of the present invention realizes the switching of the impact wrench function and the function of the electric drill or the electric screwdriver through the first mode adjusting member, and the switching between the impact drilling function and the non-impact drilling function is realized by the second mode adjusting member.
  • switching of various functions is realized by the two mode adjusting members, thereby improving the reliability of the tool, and at the same time, the structure is relatively simple and easy to manufacture.
  • FIG. 1 is a perspective view of a power tool in accordance with an embodiment of the present invention.
  • Figure 2 is an exploded perspective view of the power tool of Figure 1.
  • Figure 3 is an exploded perspective view of the operating assembly of the power tool of Figure 2.
  • Figure 4 is a perspective view of another perspective view of the mode adjuster of the power tool of Figure 3.
  • Figure 5a is a cross-sectional view of the running assembly of Figure 2 taken along the line A-A, with the power tool selected to operate in the clutch mode and operate at a low speed.
  • Figure 5b is a cross-sectional view of the running assembly of Figure 2 taken along the line B-B, wherein the power tool selects the clutch mode to operate and operates at a low speed.
  • Figure 5c is similar to Figure 5a, but at this point the power tool is operating at high speed.
  • Figure 5d is similar to Figure 5b, but at this point the power tool is operating at high speed.
  • Figure 5 e is a cross-sectional view of the running assembly of Figure 5a taken along line E-E, in which the impact switch is in the normal section of the adjustment slot of the mode adjustment member.
  • Figure 5f is a cross-sectional view of the running assembly of Figure 5a along the F-F line, in which the mode adjuster and the vibration switching member are not yet mated.
  • Figure 6a is a cross-sectional view of the running assembly of Figure 2 taken along the line A-A, in which the power tool is selected to operate in the impact mode, and the load torque to the working shaft is low, and the active and passive impact blocks have not yet been disengaged.
  • Figure 6b is a cross-sectional view of the running assembly of Figure 2 taken along the line B-B, in which the power tool is selected to operate in the impact mode, and the working shaft is subjected to a lower load torque, and the active and passive impact blocks have not yet been disengaged.
  • Figure 6c is similar to Figure 6a, but at this time the working shaft is subjected to higher load torque, active and passive The block has been disengaged.
  • Figure 6d is similar to Figure 6b, but at this point the working shaft is subjected to higher load torque and the active and passive impact blocks are disengaged.
  • Figure 6e is a cross-sectional view of the running assembly of Figure 6a taken along the line E-E, in which the impact cutting member is in the abrupt section of the adjustment slot of the mode adjustment member.
  • Figure 6f is a cross-sectional view of the running assembly of Figure 6a along the line F-F, in which the mode adjuster and the vibration switching member are not yet mated.
  • Figure 7a is a cross-sectional view of the running assembly of Figure 2 taken along line A-A, wherein the power tool selects the drilling mode to operate, and the working shaft is subjected to a lower load torque, and the active impact block has not yet begun to retreat.
  • Figure 7b is a cross-sectional view of the running assembly of Figure 2 taken along the line B-B, wherein the power tool selects the drilling mode to operate, and the working shaft is subjected to a lower load torque, and the active impact block has not yet begun to retreat.
  • Figure 7c is similar to Figure 7a, but at this time the working shaft is subjected to a higher load torque and the passive impact block retreats with the active impact block.
  • Figure 7d is similar to Figure 7b, but at this time the working shaft is subjected to a higher load torque and the passive impact block retreats with the active impact block.
  • Figure 7e is a cross-sectional view of the running assembly of Figure 7a taken along the line E-E, in which the impact switching member re-enters the normal section of the adjustment slot of the mode adjustment member.
  • Figure 7f is a cross-sectional view of the running assembly of Figure 7a along the line F-F, in which mode mode adjusters and shock switching members are initially in contact.
  • Figure 8a is a cross-sectional view of the running assembly of Figure 2 taken along line A-A, with the power tool selected to operate in vibration mode.
  • Figure 8b is a cross-sectional view of the running assembly of Figure 2 taken along line B-B, with the power tool selected to operate in vibration mode.
  • Figure 8c is a cross-sectional view of the running assembly of Figure 8a taken along line E-E, in which the impact cutting member is located in the normal section of the adjustment slot of the mode adjustment member.
  • Figure 8d is a cross-sectional view of the running assembly of Figure 7a taken along the line F-F, in which the mode adjuster and the shock switching member cooperate in the direction of rotation.
  • Figure 9 is a schematic view showing the functions of the outer surface of the mode adjusting member and the respective tripping torque positions, and the adjusting groove provided in the mode adjusting member, and the axial size change of the pressing spring of the pressing mechanism during the rotation of the mode adjusting member The graph.
  • Figure 10 is another embodiment of the power tool of the present invention.
  • Figure 1 1 a is a schematic cross-sectional view of the power tool of Figure 10.
  • Figure l ib is a cross-sectional view taken along line H-H of Figure 11a.
  • the power tool is a four-function gun drill, which optionally implements an impact wrench function, an electric drill function, an electric screwdriver function, And impact drill function.
  • the power tool 100 includes a casing 30, a battery pack 40, and an operating assembly 10.
  • the casing 30 is assembled by screwing the two half-shells, which are bilaterally symmetrical, having a horizontal portion 31 and a handle portion 32 substantially perpendicular to the horizontal portion.
  • a push button switch 50 is provided at an upper portion of the handle portion 32, and the battery pack 40 is detachably inserted into the bottom of the handle portion 32 of the casing, and the running assembly 10 is partially housed in the horizontal portion 31 of the casing 30.
  • the running assembly 10 includes a motor 21, a planetary gear reduction mechanism 1 1 , an overload clutch mechanism and a pressing mechanism when the electric screwdriver function is realized, in order from the rear to the front (the left side of the drawing is the rear).
  • different working heads (not shown) are respectively clamped, such as clamping the fastening head when the impact wrench function is realized, and clamping when constructing the construction drill and the impact drill function when implementing the electric drill function Twist drill, hold the screwdriver head when implementing the electric screwdriver function.
  • the motor has a motor housing 21 1 and a motor shaft 212 extending from the front end of the motor housing.
  • a coupling cover 22 is fixedly coupled to the front end of the motor casing 211 by a screw (not shown), and the motor shaft 212 extends into the coupling cover 22.
  • a gear box 23 is fixed to the front end of the coupling cover 22 for accommodating the planetary gear reduction mechanism.
  • a middle cover 24 and a front cover 26 are axially fixedly coupled to the front of the gear box 23, and a mode adjusting member 25 for selecting each working mode is disposed on the middle cover 24, and is connected to the front case 26 and the casing 30 respectively. .
  • the planetary gear reduction mechanism is disposed within the coupling cover 22 and the gearbox 23.
  • the gear reduction mechanism has a two-stage reduction system including a first stage reduction system composed of a first planetary gear set 1 1 1 , a first ring gear 1 13 , and a first carrier 1 12 And a second stage reduction system consisting of the second planetary gear set 1 14 , the second inner ring gear 1 16 , and the second planet carrier 1 15 .
  • Each of the planetary gear sets includes a plurality of planet gears disposed on a bracket of the respective planet carrier.
  • the motor shaft 212 extends in the center of the plurality of first planetary gears 1 1 1 and meshes with the first planetary gears, and
  • the outer peripheral gears of the plurality of first planetary gears 111 mesh with the inner teeth of the first inner ring gear 113, and the outer teeth 1131 of the first inner ring gear 113 mesh with the inner teeth 221 of the connecting cover 22 to fix the two;
  • a sun gear 1122 is protruded from the front end of the frame 112, and extends in the center of the plurality of second planetary gears 114 and meshes with the second planetary gears 114, and the plurality of second planetary gears 114 mesh with the internal teeth of the second ring gear 116.
  • the second ring gear 116 is fixed relative to the casing 30 by the pressing of the pressing mechanism;
  • the motor shaft 212 drives the first planetary gear 111 to operate in the first ring gear 113, so that the output speed of the motor 21 is output by the sun gear 1122 through the first stage reduction system, similarly, the sun gear
  • the 1122 is output as a rotation input through an output shaft 1151 integrally extended from the front end of the second carrier 115 by the second stage reduction system.
  • the speed reduction mechanism is configured by a two-stage speed reduction system to obtain a desired output rotation speed.
  • the speed reduction mechanism may include only the first stage speed reduction system, or may include three Stage or more stage deceleration system.
  • the pressing mechanism is for axially pressing the second ring gear 116 to be fixed in the casing 30.
  • the pressing mechanism is disposed in the gear case 23, and includes a pressing ring 131 and an axial elastic member.
  • the axial elastic member is a spiral pressing spring 132.
  • the pressing ring 131 is directly engaged with the second ring gear 116, and a plurality of oblique teeth 1311 and 1161 which are engageable with each other are protruded from the opposite end faces.
  • the mating faces of the oblique teeth, that is, the teeth, are inclined to the end faces.
  • a plurality of convex keys 1312 project radially outward from the outer circumference of the pressing ring 131, and can be accommodated in the key grooves 232 extending in the axial direction inside the gear box 23, respectively.
  • the pressing ring 131 is rotationally fixed in the casing 30, and can only move axially relative to the casing, and the second ring gear 116 can be moved not only in the axial direction after being disengaged from the pressing ring 131. It can also be rotated inside the casing 30.
  • the outer peripheral surface of the gear case 23 is radially symmetrically provided with a pair of axially extending guide grooves 231, and a pair of push rods 134 are correspondingly accommodated in and sliding within the guide grooves 231.
  • the outer surface of the push rod 134 is convexly provided with an externally threaded block
  • An annular gasket 133 is disposed between the push rod 134 and the pressing spring 132.
  • the gasket 133 is received in the gear box 23 and partially extends into the guiding groove 231 in the radial direction, so that the push rod 134 is in the guiding groove.
  • the thrust is transmitted to the pressing spring 132 through the spacer 133, and the second ring gear 116 is further pressed by the pressing ring 131 to be relatively fixed to the casing 30. .
  • the mode adjusting member 25 has a circular cover shape, and an inner thread 251 is recessed on the inner surface of the rear portion thereof, and can be correspondingly matched with the outer thread block 1341 of the push rod 134.
  • the rotation adjustment mode adjusting member 25 can axially move the push rod 134, thereby compressing the pressing spring
  • the axial dimension of 132 is used to adjust the axial pressing force of the pressing ring 131 against the second ring gear 116.
  • the clutch mechanism is composed of a second ring gear 116 and a pressing mechanism, wherein the second ring gear 116 constitutes an active member of the clutch, and the pressing mechanism constitutes a follower of the clutch.
  • the second ring gear 116 has a tendency to rotate under the driving of the motor 21, but cannot be driven due to the restriction of the pressing ring 131.
  • the rotational torque of the motor output is also increased accordingly, whereby the axial convex teeth 1 161 of the second ring gear 116 are applied to the axial convexity of the pressing ring 131.
  • the torsion force on the tooth 1311 also increases; when the axial component of the torsion is greater than the elastic pressing force generated by the pressing spring 132, the pressing ring 131 is axially pushed forward to disengage from the second ring gear 116. Thereby the second ring gear 116 is rotationally driven.
  • the axial critical length of the compression spring 132 is equal to the axial minimum length to which it is fully compressed plus the tooth height of the second ring gear axial projection 1 161. That is, when the pressing spring 132 is compressed by the push rod 134 to be smaller than the axial critical length, the axial force component of the torsion force applied to the pressing ring 131 by the second ring gear 116 is larger than the pressing force of the pressing spring 132. However, when the pressing ring 131 is retracted until the pressing spring 132 is fully pressed, it is still not disengaged from the second ring gear 116, so that the second ring gear 16 can never be rotationally driven.
  • the impact mechanism is disposed in the gear box 23 and the middle cover 24, and includes an active impact block 141 sleeved on the output shaft 1 151 and disposed behind the active impact block.
  • the impact spring 144 an inner ball screw groove mechanism at the junction of the active impact block 141 and the output shaft 1 151, and a passive impact block 142 axially slidably sleeved on the working shaft 16.
  • the inner ball spiral groove mechanism includes an outer spiral groove 1461 formed on the surface of the output shaft 1 151, and a rolling ball 1462 which can be rolled in the outer spiral groove 1461, which is a steel ball in the embodiment, and is disposed on the active impact block 141.
  • the inner ring is for receiving the inner spiral groove 1412 of the ball.
  • a pair of straight tooth blocks 141 1 are axially forwardly convex on the front end surface of the active impact block 141.
  • the straight tooth block means that the meshing surface of the tooth block is substantially perpendicular to the end surface.
  • a spacer 143 is provided between the impact spring 144 and the second carrier 1 15 .
  • a plurality of key grooves 1421 are arranged on the inner circumference of the inner ring of the passive impact block 142, and a plurality of convex keys 161 formed on the working shaft 16 can be accommodated correspondingly. With this structure, the passive impact block 142 can be rotated together with the working shaft 16 while The passive impact block 142 is axially moveable relative to the working shaft 16.
  • the keyway and the male key can also be interchanged, that is, the keyway is disposed on the working shaft, and the male key is disposed on the passive impact block.
  • the passive impact block 142 is oriented on the rear end face of the active impact block 141 A pair of straight tooth blocks 1422 projecting rearwardly from the straight tooth block 141 1 of the active impact block are engaged in the rotational direction.
  • the passive impact block 142 is recessed in the radial direction on the outer circumference adjacent to the front end thereof to define a limiting groove 1423.
  • the impact mechanism further includes a pressing member 145.
  • the pressing member is a coil spring whose rear end abuts against the passive impact block 142 and whose front end abuts against the inner wall of the middle cover 24.
  • the pressing member 145 may also be composed of a leaf spring or other elastic member.
  • the power tool includes an impact switching member 147 for cooperating with the impact mechanism to switch the function of the impact wrench.
  • the impact switching member has an adjustment portion 1471 disposed in the axial direction and a radially extending limit portion 1472 substantially perpendicular to the adjustment portion.
  • the mode adjusting member 25 is provided with a truncated shoulder 252 near the internal thread 251, and a substantially circular adjusting groove 2521 is recessed in the axial direction at the rear end surface of the shoulder 252.
  • the adjustment groove 2521 is mostly a normal section 2522 composed of a constant-circular arc, and a small portion is a abrupt section 2523 composed of a concave arc having a gradually decreasing radius.
  • the adjusting portion 1471 of the impact switching member 147 slides in the adjusting groove 2521.
  • the limiting portion 1472 of the impact switching member is inserted into the limiting groove 1423 in the radial direction, thereby being able to limit
  • the passive impact block 142 moves axially relative to the working shaft 16.
  • the impact switching member 147 includes two, one of which cooperates with the mode adjusting member 25 and the other with a circular adjusting ring 257.
  • the adjusting ring 257 is received in the mode adjusting member 25 and is fastened to the mode adjusting member by the cooperation of the card slot 2572 and the block 253.
  • the adjusting ring 257 is provided with a second adjusting groove 2571 for accommodating the adjusting portion of the other impact switching member.
  • the second adjusting groove 2571 is disposed opposite to the adjusting groove 2521 of the mode adjusting member, and the configurations thereof are also substantially the same, except that The abrupt section of the second adjusting groove 2571 is arranged offset from the abrupt section of the adjusting groove 2521 of the mode adjusting member by 180 degrees.
  • the two impact switching members 147 are also arranged in a staggered 180 degree, and the limiting portions 1472 of the two are basically They are located in the same radial plane, and the adjustment portions 1471 of the two are inclined away from each other in the axial direction.
  • the vibrating mechanism is received within the middle cover 24 and the front housing 26, including an intermeshing first cam block 151 and a second cam that are sleeved on the working shaft 16.
  • Block 152 wherein the first cam block 151 has a plurality of convex keys 1513 protruding radially from the outer circumference of the first cam block 151, and can cooperate with a plurality of axially extending key grooves (not shown) provided on the inner circumferential wall of the middle cover 24, through the structure
  • the first cam block 151 is fixed relative to the casing in the rotational direction while being axially movable.
  • the second cam block 152 is engaged with the working shaft 16 by a flat fit, so that the second cam block 152 can be prevented from rotating relative to the working shaft 16. After the assembly is completed, the rear end of the second cam block 152 abuts against the working shaft 16. The radially formed shoulder portion, and the front end abuts against the inner wall of the front case 26 by the bearing, by which the second cam block 152 is also fixed in the rotational direction with respect to the working shaft 16.
  • the opposite end faces of the first cam block 151 and the second cam block 152 are circumferentially distributed with continuous dog-shaped teeth 151 1 and 1521 which are in mesh with each other, and a pitch g is formed between the crests of the two.
  • the shock mechanism has a rear push spring 153 whose front end abuts against the inner wall of the front case 26, and the rear end pushes the first cam block 151 axially away from the second cam block 152.
  • the vibrating mechanism further includes a forward push spring 154 that elastically abuts against the working shaft 16 and the output shaft 1 151 by the ball, so that the working shaft is always pushed forward when not in operation.
  • the rear end surface of the working shaft 16 forms a space d with the front end surface of the output shaft 1 151, so that the working shaft 16 is most affected by the reaction force of the workpiece (not shown) during operation. It is possible to retreat to the rear end face thereof and abut against the front end face of the output shaft, whereby the interval d is the maximum receding distance of the working shaft 16.
  • the power tool further includes a shock switching member 155 for engaging the shock mechanism to switch the impact drill function.
  • the vibration switching member 155 is also an annular cam block sleeved on the working shaft 16, which is received at the front of the middle cover 24 and located behind the first cam block 151, and is restrained by a spacer. Move to.
  • the opposite ends of the shock switching member 155 and the first cam block 151 are circumferentially distributed with a plurality of obliquely projecting mutually engageable male teeth 1551, 151 1 .
  • the vibration switching member 155 is further provided with an extending arm 1552 extending radially.
  • the middle cover 24 is correspondingly provided with a notch 241 for receiving the extending arm 1552, and the notch 241 is sized in the steering to allow the impact switching member 147 to There is a certain displacement in the direction of rotation.
  • the side wall of the middle cover 24 is provided with an arcuate groove 242 communicating with the side of the notch 241 in the direction of rotation.
  • An arcuate spring 156 is received in the arcuate groove 242 and the extension arm 1552 of the vibration switching member is pushed toward the gap.
  • the other side of 241 (as shown in Figures 5f, 6f, 7f). As shown in FIG.
  • the mode adjusting member 25 is convexly disposed on the inner wall near the front end edge thereof, and the radial projection 254 is substantially in the same radial plane as the vibration switching member 155. After the adjusting member 25 is rotated to a certain angle, the radial protrusion 254 can be abutted against the extending arm 1552 of the vibration switching member, and then the mode adjusting member 25 is further rotated, so that the arm 1552 can be extended against the elastic force of the curved spring 156. Rotate.
  • the mode adjusting member 25 can also be used as a torsion cover for adjusting the tripping torque value of the clutch mechanism when the electric screwdriver function is realized.
  • the push rod 134 can be urged to press the pressing spring 132 to adjust the amount of compression of the spring in the axial direction.
  • the mode adjusting member 25 is marked with a plurality of tick marks on the outer circumferential surface near the rear end edge to indicate different Trip torque values, which correspond to different axial dimensions of the compression spring. These marks may be directly specific moment values, or may be substitute values of specific button moment values, as in the present embodiment, they are represented by different gear positions, such as 1-20 gears.
  • the mode adjustment member needs to be rotated to align the corresponding gear mark with the confirmation mark on the casing, such as arrow 33 (shown in Figure 1). .
  • the pressing spring 132 is compressed by the push rod 134 to a specific axial length corresponding to the torque value, and the generated pressing force is transmitted to the pressing ring 131 to force the pressing ring 131 to press the second ring gear 1 16 .
  • the screwdriver head screws the screw into the workpiece.
  • the second ring gear can be rotationally driven out of engagement with the pressing ring, so that the torque of the motor cannot be output to the output shaft of the planetary reduction gear.
  • the second ring gear continuously engages and disengages the pressing ring during rotation, so that the screw is no longer subjected to torque and the motor is still rotating.
  • a plurality of bumps 255 are disposed on the inner circumference of the inner wall of the mode adjusting member 25.
  • the leaf spring 258 is disposed on the middle cover 24, and has a protrusion 2581 which can be embedded in any of the bumps 255.
  • the leaf spring protrusion 2581 slides into the corresponding groove 256, so that, on the one hand, the mode adjusting member can be made 25 - Fixed to this position to a certain extent.
  • the leaf spring projection 2581 slides into the groove 256 to instantaneously emit a "click" sound to provide operator confirmation.
  • the adjustment cover of the torque gear can also be provided separately from the mode adjustment member, but is relatively cumbersome to operate with respect to the present embodiment.
  • the power tool further includes a speed switching mechanism for adjusting the output shaft output speed, which includes a speed control slider 121 fixedly coupled together, a speed control sleeve 123, a speed regulating wire 122, a bearing housing 124, and a bearing. 125.
  • the speed control slider 121 is disposed on the casing 30 and is slidable in the axial direction.
  • the speed control sleeve 123 is sleeved on the outside of the connecting cover 22, and the protrusion 1231 at the top thereof is embedded in the speed adjusting slider 121 so as to move together with the speed regulating slider.
  • the bearing housing 124 is disposed in the connecting cover 22, and the speed regulating wire 122 connects the speed regulating bush 123 outside the connecting cover 22 and the bearing seat 124 in the connecting cover.
  • the bearing 125 is fixedly received in the bearing housing 124 by an interference fit, and is fixedly sleeved outside the first ring gear 1 13 by an interference fit, so that the first ring gear 1 13 is connected to the speed adjusting slider 121 at the connecting cover 22 axial sliding.
  • the power tool can first select the clutch mode to operate, in which the power tool implements the electric screwdriver function.
  • the adjusting portion 1471 of the impact switching member is located in the normal portion 2522 of the adjusting slot 2521, and the limiting portion 1472 is outside the limiting slot 1423 of the passive impact block 142, that is, the impact switching member.
  • the passive impact block There is no fit between the passive impact block and the passive impact block.
  • the passive impact block 142 will follow the active impact block 141 under the push of the pressing member 145.
  • the extension arm 1552 of the vibration switching member 155 is not engaged with the radial projection 254 of the mode adjusting member 25, and the first cam block 151 is under the action of the rear push spring 153.
  • the rear end convex teeth 1511 mesh with the front end convex teeth 1551 of the vibration switching member 155, and the front end convex teeth 1512 of the first cam block 151 and the rear end convex teeth 1521 of the second cam block 152 are separated by a large distance g. Engage.
  • the power tool has a total of twenty trip torque values for selection when implementing the electric screwdriver function.
  • the number of gear positions may be increased or decreased as needed (e.g., the type of workpiece material to which the job is applied).
  • the axial dimension of the pressing spring 132 corresponding to all of these gear positions is greater than the axial critical length, so that when the load torque of the working shaft 16 exceeds the set trip torque value, the second ring gear 116 of the planetary gear reduction mechanism The pressing ring 131 is pushed forward until the tooth heights of the two are disengaged, so that the second ring gear 116 is rotationally driven, and the working shaft 16 has no torque output.
  • the shifting torque can be adjusted from small to large by rotating the mode adjusting member 25 clockwise, and the angle at which the mode adjusting member 25 is rotated is the first rotation angle. In the first gear mode, the angle of the adjustment member is zero degree, and the angle of the mode adjustment member is A1 when the twentieth gear is turned, and the other gears are corresponding to the specific angle smaller than the angle A1.
  • Figures 5a, 5b show the low speed operation of the power tool in the clutch mode.
  • the outer teeth 1 131 of the first ring gear 1 13 mesh with the inner teeth 221 of the connecting cover 22 to fix the first ring gear and the casing, and the inner teeth of the first ring gear 1 13 are only the first Planetary wheel set 1 11 meshes, at this time, the motor
  • the output speed of 21 is reduced to a lower speed by the first and second stage deceleration systems.
  • Figures 5c, 5d show the high-speed operation of the power tool in the clutch mode. Wherein, the speed control slider 121 has been slid forward to the high speed position by the low speed position shown in Figs.
  • the first ring gear 1 13 is synchronously slid to a high speed position.
  • the outer teeth 1 131 of the first ring gear 1 13 are disengaged from the inner teeth 221 of the connecting cover 22 to be rotationally driven, and at the same time, the inner teeth of the first ring gear 113 and the first planetary gear set 1 1 1 1 and the external teeth 1 121 of the first carrier 1 12 are engaged.
  • the output speed of the motor is directly transmitted to the sun gear 1 122 of the first carrier 1 12 and then to the output shaft 1 151 through the second stage reduction system, that is, the output speed of the motor only passes through the second The stage deceleration is reduced to a higher speed.
  • the mode adjustment member is rotated clockwise to the second rotation angle A2.
  • the power tool can select the impact mode to work, and the power tool realizes the impact wrench function.
  • the axial dimension of the compression spring has been compressed to less than the axial critical length, so when the load torque of the working shaft exceeds the set trip torque value, the second ring gear 16 of the planetary gear reduction mechanism will Pushing the pressing ring 131 forward until the pressing spring 132 is fully pressed, but at this time, the second ring gear 116 and the protruding teeth 1161, 131 1 of the pressing ring 131 are still engaged with each other, so that the second ring gear 1 16 It is still restricted by the pressing ring 131 and cannot be rotationally driven, that is, in a limited rotation state.
  • the adjusting portion 1471 of the impact switching member 147 is located at the middle of the abrupt portion 2522 of the adjusting groove 2521 at the closest position to the axis of the working shaft 16, and the limiting portion 1472 has Inserted radially into the limiting groove 1423 of the passive impact block, that is, the passive impact block is restricted from moving in the axial direction.
  • Figures 6a, 6b show the state when the load torque to the working shaft is low
  • Figures 6c, 6d show the state when the load torque to the working shaft is high.
  • the intermeshing active impact block 141 and the passive impact block 142 are both blocked, and the passive impact block 141 stops rotating, but the output shaft 1
  • the 151 is still rotated by the driving of the motor 21, forcing the ball 1462 to roll along the groove against the frictional force between the inner and outer spiral grooves 1412 and 1461, thereby pushing the active impact block 141 to move toward the motor, so that the impact spring 144 is compression.
  • the active impact block 141 is gradually displaced away from the passive impact block 142 in the axial direction.
  • the output shaft 1 151 drives the active impact block 141 to rotate, so that the tooth block 141 1 slides over the tooth block 1422 of the passive impact block.
  • the ball 1462 is returned along the spiral groove.
  • the active impact block 141 In the original position, the active impact block 141 is pushed forward, and at the same time, as the output shaft 1 151 accelerates, the tooth block of the passive impact block 142 is impacted in the rotational direction, so that the passive impact block continues to move in the rotational direction. , tighten the bolts by continuous intermittent rotary shock.
  • the outer ball spiral groove impact structure can also be used to realize the function of the impact wrench. Since the working process and working principle are the same as the inner ball spiral groove impact structure of the present embodiment, the applicant I will not repeat them here. In the impact mode, the speed adjustment can also be adjusted, and the adjustment mode is the same as the clutch mode, and the applicant will not repeat them.
  • the mode adjustment member is rotated clockwise to the third rotation angle A3.
  • the power tool can select the drilling mode to work, and the power tool realizes the electric drill function in this mode.
  • the axial compression dimension of the compression spring is compressed to less than the axial critical length so that the second internal ring gear is in a restricted rotation state.
  • the radial projection 254 of the mode adjusting member 25 starts to contact the extension arm 1552 of the shock absorbing member after being rotated to the third rotation angle A3, but does not drive the vibration switching member 155 to rotate, so the first two The mode is the same and the vibration mechanism is in a limited vibration state. Referring to FIG. 7e, and referring to FIG.
  • the adjusting portion 1471 of the impact switching member 147 re-enters the normal portion 2522 of the adjusting slot 2525, and the limiting portion 1472 is exited from the passive impact block limiting slot 1423, that is, There is no fit between the impact switching member and the passive impact block. Therefore, when the resistance torque is gradually increased and the active impact block is retracted, the passive impact block 142 is axially retracted along with the active impact block 141 so that the two cannot be separated from each other to form an impact, and thus the impact mechanism is Limit the impact state. Therefore, in this mode, the output of the working shaft 16 is only a simple rotation output, and of course, the output can also be adjusted at high and low speeds.
  • the mode adjusting member is rotated clockwise to the fourth rotation angle A4.
  • the power tool can select the vibration mode to operate, and the power tool realizes the impact drilling function.
  • the axial dimension of the pressing spring is compressed to be less than the axial critical length, so that the second ring gear is in a restricted rotation state.
  • the adjusting portion 1471 of the impact switching member 147 is located in the normal portion 2522 of the adjusting groove 2521, and the limiting portion 1472 is in the passive impact block limit.
  • the front end convex teeth 1551 and the rear end convex teeth 151 1 of the first cam block 151 are in meshing motion to the tooth height, and the first cam block 151 is axially moved forward to the front end thereof.
  • the lug 1512 is spaced apart from the rear end tooth 1521 of the second cam block 152 by a short gap g.
  • g is smaller than the retreat distance d of the working shaft, such that the front end tooth 1512 and the second cam block of the first cam block 151 are retracted by the reaction force of the workpiece when the drill bit is pressed onto the workpiece.
  • the rear end teeth 1521 of the 152 will engage first so that the working shaft 16 cannot be further retracted.
  • the first cam block 151 does not always remain engaged with the second cam block 152, which will continue to rotate and disengage. Since the first cam block 151 is now fixed relative to the casing 30, the bit moves axially forward relative to the casing during the engagement of the second cam block 152 into the disengagement, and because of the machine The casing is always urged toward the workpiece by the operator, such that constant engagement and disengagement between the first cam block and the second cam block creates a vibration of the working shaft in the axial direction, thereby causing a sustained impact on the workpiece. In this mode, the output shaft output speed of the planetary gear reduction mechanism can also be adjusted at high and low speeds.
  • the power tool of the present invention is provided with a passive impact block independent of the working axis, and the impact switch member is used to restrict the passive impact block from moving or releasing the restriction together with the active impact block, thereby realizing the switching between the impact wrench function and the electric drill function; Based on the realization of the electric screwdriver and the switching mechanism, or / and the realization and switching mechanism of the impact drill, a three-function gun drill or a four-function gun drill is realized. With this arrangement, the structure is simpler and easier to manufacture.
  • the switching of the clutch mode of the power tool of the present invention does not require a separate setting of the switching member, and only needs to be adjusted by adjusting the mode adjusting member to control the axial dimension of the pressing spring, and the mode adjusting member can also realize the control of the tripping torque. .
  • the number of components is reduced, the complexity of the structure is simplified, the cost of manufacturing is reduced, and the reliability of the tool is also improved.
  • the structure, shape, and the like of the various mechanisms mentioned in the present embodiment are not limited to the above, and various simple and well-known replacements may be made, such as the casing may be integrally formed with the middle cover, the front case, etc.; for example, the clutch The follower, that is, the pressing ring, can be axially slotted, and a steel ball or a steel column is disposed therein to cooperate with the clutch actuating member, that is, the axial protruding tooth of the second ring gear.
  • the sequential implementation of the four functions is an electric screwdriver, an impact wrench, an electric drill, a hammer drill, but in the field.
  • the power tool can only realize three functions, such as a combination of an electric screwdriver, an impact wrench, and an electric drill.
  • the vibration mechanism and the vibration switching member are omitted, or the impact wrench, the electric drill, the impact drill.
  • the speed switching mechanism may be omitted accordingly if high and low speed switching is not required.
  • the motor is used as the power source, and of course, the engine can also be used for replacement. Since such a simple replacement can be easily implemented by a person skilled in the art, the applicant will not repeat them.
  • the axial critical length of the pressing spring of the pressing mechanism is equal to the axial minimum length thereof plus the tooth height of the second ring gear axial convex tooth, so that the impact mode, the drilling mode, and the vibration In the mode, the axial dimension of the pressing spring is adjusted by the mode adjusting member to be smaller than the axial critical length, so that the second ring gear cannot be rotationally driven because it cannot always disengage from the engagement of the pressing ring.
  • the axial critical length of the compression spring may also be greater than its axial minimum length plus the tooth height of the second ring gear axial projection in the impact mode.
  • the second ring gear and the pressing mechanism constitute a first clutch mechanism
  • the active impact block and the passive impact block of the impact mechanism constitute a second clutch mechanism
  • the tripping torque value of the first clutch mechanism is greater than the second The trip torque value of the clutch mechanism.
  • Different tripping torque values can be achieved by using springs with different spring constants.
  • the pressing spring can use a spring with a larger spring rate
  • the impact spring can use a spring with a smaller spring rate, that is, at the same pressing force.
  • the elastic deformation of the pressing spring is smaller than the elastic deformation of the impact spring.
  • the second clutch will trip first, that is, the active impact block and the passive The impact block is disengaged, and then the active impact block applies an intermittent rotational impact to the working shaft.
  • the second inner ring gear of the first clutch mechanism receives the same resistance torque as the active impact block, that is, is always smaller than the trip torque value of the second clutch mechanism, thereby making the first clutch mechanism impossible.
  • the trip occurs when the trigger is triggered, that is, the second ring gear can never be pushed away from the pressing ring and is rotationally driven.
  • the axial dimension of the pressing spring may be slightly larger than the axial minimum length thereof plus the axial tooth height of the second ring gear, when the rotation mode adjusting member is further rotated to adjust the power tool to the drilling mode or the vibration mode
  • the pressing spring is further compressed to less than the axial minimum length plus the axial tooth height of the second ring gear. Therefore, in the present embodiment, the axial critical length of the compression spring of the zone separation mode and the other three modes may be greater than the axial minimum The length plus the axial tooth height of the second ring gear.
  • the mode adjusting member 25 is replaced by a combination of the first mode adjusting member 70 and the second mode adjusting member 80.
  • the first mode adjusting member 70 is used to switch the drilling mode, the impact mode, the clutch mode, and the trip torque value in the clutch mode, but it cannot be used.
  • the switching of the vibration mode that is, the first mode adjusting member 70 and the vibration switching member 155 are not matched.
  • the first mode adjusting member 70 and the mode adjusting member 25 operate in the same manner, so the applicant will not repeat them.
  • the second mode adjusting member 80 is for switching between the impact drill and the non-impact drill function, and is disposed on the front case 90.
  • the front housing 90 is provided with a shorter length of the slot 92 in the circumferential direction, and a longer length of the guiding slot 91 extends in the circumferential direction of the front housing, and is at the top of the guiding slot.
  • the inner wall of the front case is recessed with a plurality of recesses 91 1 .
  • the extension arm 1552 of the vibration switching member 155 extends into the slot 92.
  • the second mode adjusting member 80 includes a slider 83 disposed in the guiding groove 91 of the front case.
  • the slider 83 Since the size of the slider 83 in the circumferential direction is shorter than that of the guiding groove 91, the slider 83 can be along the guiding groove 91. Move in the circumferential direction.
  • the slider 83 is provided with a plurality of bumps 831 which can be fitted in the recesses 91 1 to reliably position the slider 83 in the guide groove 91.
  • the upper surface of the slider 83 projects radially outwardly from the slot 92 and is provided with an operating block 81.
  • a pair of projections 82 are protruded radially inwardly from the lower surface of the slider 83.
  • a groove (not shown) formed between the pair of projections 82 is for receiving the extension arm 1552 of the vibration switching member 155.
  • the vibration mechanism In the position shown in FIG. 1 ib, the vibration mechanism is in a limited vibration state, that is, the power tool 200 is in a non-impact drill function, so that the adjustment of the first mode adjustment member 70 can be switched to the electric screwdriver function, the impact wrench function, or the electric drill. Function, and torque adjustment can be performed with the electric screwdriver function.
  • the first mode adjustment member can only effect switching between the impact wrench function and the drill function, or switching between the impact wrench function and the electric screwdriver function.
  • the side position is rotated clockwise to the other side of the slot 92.
  • the protrusion 82 of the second mode adjusting member 80 drives the extension arm 1552 of the vibration switching member 155 to move to the other side of the slot 92. , thereby causing the vibrating mechanism to switch to a vibrating state, thereby realizing the impact drill function.
  • the function of the impact wrench and the function of the electric drill or the electric screwdriver are switched by the first mode adjusting member, and the impact drilling function and the non-impact drilling work are realized by the second mode adjusting member. Switch between energy.
  • the switching of multiple functions is shared by the two mode adjusting members, thereby improving the reliability of the tool, and at the same time, the structure is relatively simple and convenient for manufacturing.

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  • Drilling And Boring (AREA)

Abstract

L'invention concerne un outil de puissance (100) qui comprend un boîtier (30), un arbre de travail (16), une ressource de puissance (21), un mécanisme de réduction d'engrenage planétaire (11) pourvu de couronnes dentées internes (113, 116), un mécanisme de pression pour presser et maintenir les couronnes dentées interne, un mécanisme de choc pour avoir une fonction de clé à choc, une unité de commutation de choc (147) pour sélectionner et limiter la fonction de clé à chocs, une unité de commutation de percussion (155) pour sélectionner et limiter la fonction de perçage à percussion, et une unité de réglage de mode (25) qui est montée sur le boîtier et est mise simultanément en coopération avec le mécanisme de pression, l'unité de commutation de choc et l'unité de commutation de percussion. Un mode d'embrayage, un mode de choc, un mode de perçage et un mode de percussion sont sélectionnés par réglage de l'unité de réglage de mode et une fonction de tournevis électrique, une fonction de clé à choc, une fonction de perçage électrique et une fonction de perçage à percussion sont obtenues en conséquence. Cet arrangement réduit le nombre d'éléments, simplifie la complexité de la structure, réduit le coût de production et améliore la fiabilité.
PCT/CN2008/071589 2007-07-12 2008-07-09 Outil de puissance WO2009006845A1 (fr)

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CN200710024059.4 2007-07-12
CN2007100240594A CN101342693B (zh) 2007-07-12 2007-07-12 动力工具

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WO2009006845A1 true WO2009006845A1 (fr) 2009-01-15

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CN116833956A (zh) * 2023-06-30 2023-10-03 炬岱企业有限公司 压胶枪结构
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CN110561359A (zh) * 2018-06-06 2019-12-13 苏州宝时得电动工具有限公司 手持式动力工具以及夹头组件
CN109397202A (zh) * 2018-11-30 2019-03-01 张家港市创基机械设备制造有限公司 换头工具中的连接结构
CN109397202B (zh) * 2018-11-30 2023-10-20 张家港市创基机械设备制造有限公司 换头工具中的连接结构
CN111743563A (zh) * 2020-06-30 2020-10-09 北京永新医疗设备有限公司 用于核医学设备的探测器驱动装置和核医学设备
CN111743563B (zh) * 2020-06-30 2024-02-27 北京永新医疗设备有限公司 用于核医学设备的探测器驱动装置和核医学设备
US12325118B2 (en) 2020-12-21 2025-06-10 Techtronic Cordless Gp Rotary impact tool
CN116833956A (zh) * 2023-06-30 2023-10-03 炬岱企业有限公司 压胶枪结构
CN118682170A (zh) * 2024-08-23 2024-09-24 吉首长潭泵业有限公司 一种泵叶轮加工用打孔装置

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