WO2011029387A1 - 动力工具 - Google Patents

动力工具 Download PDF

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Publication number
WO2011029387A1
WO2011029387A1 PCT/CN2010/076711 CN2010076711W WO2011029387A1 WO 2011029387 A1 WO2011029387 A1 WO 2011029387A1 CN 2010076711 W CN2010076711 W CN 2010076711W WO 2011029387 A1 WO2011029387 A1 WO 2011029387A1
Authority
WO
WIPO (PCT)
Prior art keywords
impact block
power tool
active
clutch member
main shaft
Prior art date
Application number
PCT/CN2010/076711
Other languages
English (en)
French (fr)
Inventor
李成道
Original Assignee
苏州宝时得电动工具有限公司
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 苏州宝时得电动工具有限公司 filed Critical 苏州宝时得电动工具有限公司
Priority to US13/395,328 priority Critical patent/US20120241183A1/en
Priority to EP10814989.9A priority patent/EP2476519A4/en
Publication of WO2011029387A1 publication Critical patent/WO2011029387A1/zh

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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
    • B25B21/026—Impact clutches
    • 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
    • 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

Definitions

  • the present invention relates to a power tool, and more particularly to a multifunctional power tool capable of realizing an impact wrench function and an electric drill function or an electric screwdriver function or a hammer drill function.
  • an impact wrench is used to tighten the threaded fastener to the workpiece.
  • the structure generally includes a main shaft that is rotationally driven by a motor, an active impact block that is coupled to the main shaft through a spiral groove and a ball, and a working shaft that is disposed in front of the active impact block and that engages the active impact block through the end teeth.
  • An impact spring is also disposed behind the main impact block, which compresses the active impact block to maintain a positive fit of the active impact block with the working axis.
  • the rotary motion of the spindle is directly output to the screw through the active impact block and the passive impact block on the working shaft to screw the screw onto the workpiece.
  • the load on the working shaft gradually increases.
  • the rolling of the ball in the spiral groove causes the active impact block to move axially toward the motor with respect to the passive impact block on the working shaft, and at the same time Compress the spring behind it.
  • the active impact block and the end teeth of the passive impact block on the working shaft are disengaged, the active impact block moves axially forward and strikes the passive impact block on the working shaft in the direction of rotation to make the work work.
  • the shaft continues to tighten the threaded member in the direction of rotation. This cycle, through the continuous intermittent impact of the active impact block, ensures that the screw is finally tightened onto the workpiece.
  • the electric drill is used for drilling holes on the workpiece, but usually the user needs to screw the screw or the hole on the workpiece at the same time. Therefore, it is very troublesome for the user to continuously change the tool to operate.
  • a power tool that can simultaneously realize the functions of an impact wrench and an electric drill on the same tool.
  • This power tool often converts two functions through a function conversion knob.
  • the specific function conversion structure is implemented in a variety of ways. Among them, the more common way is to selectively limit the axial backward movement of the active impact block by a movable stop.
  • the active impact block can perform the impact wrench function as described above; when the stop limits the axial rearward movement of the active impact block At this time, the active impact block always fits with the working shaft without disengaging, and does not compress the spring behind it to achieve an energy storage impact to achieve the electric drill function.
  • the Chinese patent application CN 2 005 1 009 9 1 06 discloses a power tool having a radially movable stop at the rear end of the active impact block, which is limited when it comes into contact with the rear end of the active impact block.
  • the impact wrench function is when its radial upward movement does not contact the rear end of the active impact block.
  • the rotation transmission depends on the slip between the main shaft and the active impact block.
  • the groove ball structure transmits, the ball and the main shaft and the active impact block are all actively coupled, and the stop member that limits the axial backward movement of the active impact block is subjected to a large force of the active impact block, and the active impact block is opposite to the stop member. Rotation makes the stopper easy to wear, so the stability of such rotation transmission is low.
  • the present invention provides a power tool having a function switching mechanism for effecting a transition between an impact wrench function and a drill function or a screwdriver or hammer drill function, the rotation of which is stabilized by the rotary function of the power drill.
  • a power tool includes: a casing, a motor disposed in the casing, a motor output rotation motion, and a deceleration system that decelerates the rotation of the motor output, the deceleration system has an output end to output a rotation after deceleration, and a spindle connected to the output end
  • a working shaft for mating with the corresponding working head during operation the main shaft is provided with an active impact block, which is axially movable relative to the main shaft, and the working shaft is provided with a passive impact block, which rotates together with the working shaft a first end tooth is disposed on the active impact block, and a second end tooth is disposed on the passive impact block, and the active impact block rotationally drives the passive impact block through cooperation of the first end tooth and the second end tooth of the passive impact block;
  • the power tool further includes a clutch member moveable between the first position and the second position to selectively securely connect the active impact block with at least one of the output end and the main shaft.
  • the portion of the clutch member facing the active impact block is provided with a spline, the portion of the active impact block facing the clutch member has a matching spline, and the clutch member is in the second position, the clutch The splines of the piece and the splines of the active impact block engage each other to form a fixed connection.
  • the clutch member is annularly sleeved on the output end, the inner peripheral surface of the clutch member is provided with a radially convex slider, and the output end is provided with a path for accommodating the slider to move therein. To the recessed chute.
  • the inner circumferential surface of the clutch member has an inner ring groove to accommodate an elastic cymbal, and the outer circumferential surface of the output end is spaced apart from the first annular groove and the second annular groove, the clutch member The elastic ⁇ is moved to make the elastic ⁇ selectively located in the first annular groove or the second annular groove, and the clutch member is correspondingly located at the first position or the second position.
  • the power tool further includes a function conversion button disposed on the casing 1, the function conversion button connecting the clutch member through a connecting member located in the casing and driving the clutch member in the first position and Move between the second positions.
  • the power tool further includes an impact spring elastically abutting on a side of the active impact block away from the passive impact block and a ball located at the joint of the active impact block and the main shaft, wherein the inner wall of the active impact block is The main shaft is provided with a V for accommodating the ball and allowing the ball to roll therein ,
  • the power tool further includes an impact mechanism that effects an impact wrench function by applying an intermittent impact to the passive impact block in the rotational direction by the active impact block.
  • the power tool can realize a drilling function or an electric screwdriver function or a hammer drill function.
  • the deceleration system is a planetary gear reduction system connected between the motor and the main shaft for reducing the output speed of the motor.
  • a power tool comprising: a motor housed in a casing for outputting a rotary motion; a deceleration system for outputting a rotation of the motor after being decelerated and outputting by an output; a spindle that is driven to rotate by the output; a working shaft, Provided in the casing, and extending forward for driving a working head to work on the workpiece; an active impact block disposed on the main shaft; a passive impact block disposed on the working shaft; wherein the active The impact block is engaged or disengaged from the passive impact block according to the load received by the working shaft, thereby applying an intermittent impact to the impact block in the rotational direction; further comprising a clutch member movable between the first position and the second position Selectively attaching the active impact block to at least one of the input end and the drive shaft; when the clutch member is in the first position, disengaging from the active impact block to allow the active impact block to form the impact to achieve an impact mode, When the clutch member is in the second position, fixedly connecting with the active impact
  • the invention has the beneficial effects that: the power tool adds a movable moving clutch between the two positions, and optionally fixes at least one of the output end and the main shaft and the active impact block. Connected together to achieve a stable and efficient transfer of rotation in the drilling mode or the impact drill mode or the screwdriver mode, achieving impact in the impact mode.
  • the above function conversion mechanism has a simple and stable structure, a low manufacturing cost, and is easy to operate and labor-saving.
  • Figure 1 is a front elevational view of a power tool of the present invention.
  • FIG 2 is an internal view of the power tool of the present invention.
  • Fig. 3 is a structural view showing the power tool of the present invention in a functional state of an impact wrench.
  • Fig. 4 is a structural view showing the power tool of the present invention in a drilling function state.
  • the power tool 100 includes a horizontally disposed casing 1, a handle 6 disposed at an angle to the casing 1, and a detachable battery pack 8 at the bottom of the handle 6.
  • the front end of the casing 1 is provided with a tool chuck 52 for respectively clamping different working heads (not shown) when the power tool realizes different functions, such as clamping the fastening head when implementing the impact wrench function, and realizing the drilling Hold the twist drill while entering the function.
  • a switch 9 is provided on the handle 6, and the operator can activate the power tool 100 by pressing the switch 9.
  • the function switch button 44 is also provided on the casing 1, and the operator can switch the function mode of the operation of the power tool 100 by dialing the function switch button 44.
  • Figure 1 discloses the working components of the power tool 100 disposed within the cabinet 1.
  • the working member includes a motor 11, and the front end of the motor 11 extends out of the motor shaft (not shown).
  • a deceleration system 13 is disposed in front of the motor 11.
  • the deceleration system 13 is a planetary gear reduction system.
  • the specific implementation is well known to those skilled in the art and will not be described in detail herein.
  • the motor shaft drives the planetary gear reduction system to operate, thereby transmitting the rotation of the motor output to the spindle 24 connected to the output end 22 of the planetary gear reduction system through a certain reduction ratio.
  • the output end 11 is the last stage of the planetary gear reduction system.
  • the main shaft 24 is embedded in the carrier by an interference fit to form a fixed connection with the output end 11. When the output end 11 rotates, the main shaft 24 follows the rotation.
  • the mechanism of the impact wrench is provided in front of the deceleration system 13 and includes a set of active impact blocks 31 disposed on the main shaft 24, an impact spring 32 disposed between the active impact block 31 and the output end 11, and an active a ball V-groove impact mechanism at the junction of the impact block 31 and the main shaft 24, wherein the impact mechanism includes an outer V-shaped groove 241 recessed in the surface of the main shaft 24, and a rolling ball 25 which can be rolled in the outer V-shaped groove 241,
  • the steel ball and the inner V-shaped groove 312 are provided in the active impact block 31 for receiving the ball 25.
  • a pair of first end teeth 311 are radially symmetrically protruded from the front end surface of the active impact block 31.
  • a pad and a spacer are provided between the impact spring 32 and the active impact block 31.
  • the front end of the active impact block 31 is further provided with a passive impact block 51.
  • the passive impact block 51 is convexly symmetrically disposed on the rear end surface opposite to the active impact block 31 with a pair of second end teeth 511.
  • the working component further includes a working shaft 5 extending from the front end of the casing 1 and a tool chuck 52 sleeved at the front end of the working shaft.
  • the passive impact block 51 is connected to the working shaft 5 and integrated.
  • the front end of the working shaft 51 is provided with a receiving groove 512, which can accommodate the corresponding working head when different functions are realized, and is clamped by the tool chuck 52.
  • the working component also includes a function adjustment mechanism disposed between the active impact block 31 and the main shaft 24 and the deceleration system 13.
  • the function adjustment mechanism includes a clutch member 41, a function switching button 44, and a connecting member 42.
  • the clutch member 41 has an annular shape and is disposed around the outer peripheral surface of the output end 11.
  • An outer ring groove 411 is disposed on the outer peripheral surface of the clutch member 41.
  • One end of the connecting member 42 is hooked in the outer ring groove 411, and the other end is connected to the function switch button 44 disposed on the casing 1 for the operator to operate.
  • the movement function switching button 44 drives the connecting member 42, which in turn drives the clutch member 41 to move back and forth in the axial direction of the output end 22.
  • the function conversion button 44 is directly connected to a pin shaft, and the pin shaft is connected to the clutch member 41 through the casing 1, and it is also feasible to drive the clutch member 41 to move back and forth.
  • the function switching button 44 is disposed through the casing 1, and includes an operating portion disposed on the casing 1 and an annular portion disposed in the body. The operating portion is rotatable about the longitudinal axis of the working shaft 5 and causes the annular portion to rotate.
  • the annular portion is provided with a track groove, and the track groove comprises two straight grooves which are parallel in a direction perpendicular to the longitudinal axis of the working shaft 5 and which are spaced apart in the longitudinal axis direction of the working shaft 5 and an oblique line connecting the two straight grooves mentioned above groove.
  • the other end of the aforementioned connecting member 42 is disposed in the track groove. Specifically, the other end of the connecting member 42 is located in one of the two straight grooves of the track groove.
  • a straight groove connects the other end of the connecting member 42 and moves relative thereto, at which time the connecting member 42 does not move axially; then the chute portion of the track groove moves to the other end of the connecting member 42.
  • the chute continues to move, causing the connecting member 42 to move axially until the chute moves to the other end away from the connector 42, and the other straight slot moves to the position of the other end of the connecting connector 42.
  • the function switching button 44 drives the connecting member 42 to move axially in the above manner.
  • the connection and control manner between the function switching button and the clutch member 41 are various, and are not limited thereto.
  • the function switching button 44 can be radially inserted through the outer circumferential surface outer ring groove 411 of the clutch member 41 to directly move the clutch member 41 in the axial direction.
  • a symmetrical portion of the inner peripheral surface of the clutch member 41 is radially protruded to form a pair of sliders 413.
  • the slider 413 is disconnected in the middle, and an inner ring groove 415 is recessed into the clutch member 41, and an elastic ring is disposed in the inner ring groove 415. 45.
  • the symmetrical portion of the outer peripheral surface of the output end 22 is recessed in the radial direction to form a pair of chutes 221, and at the output end end
  • An outer circumferential surface of the sliding groove 221 is provided with two annular grooves perpendicularly intersecting each other in the axial arrangement stroke, which are respectively opposite to the first annular groove 223 on one side of the reduction gear system and relatively close to the active impact block 31.
  • the clutch member 41 is axially moved back and forth in the chute 221 of the output end 11 by the slider, but cannot be rotated about the output end 22.
  • the elastic cymbal 45 body is disposed in the inner ring groove 415 of the clutch member 41, follows the clutch member 41 to move axially on the outer peripheral surface of the output end 22, and when the elastic cymbal 45 reaches the two annular groove positions of the output end 22, Entering the annular groove, positioned at two axial positions of the output end 22, when the elastic cymbal 45 is positioned at the first annular groove 223, the clutch member 41 is in the first position, and when the elastic cymbal 45 is positioned in the second annular groove 225, The clutch member 41 is in the second position.
  • Such an arrangement can assist the operator in determining that the clutch member has reached the predetermined position and securing the clutch member 41 to the position without arbitrarily sliding unless the operator manually moves it.
  • the front end of the clutch member 41 facing the active impact block 31 in the axial direction is provided as a spline 417, and the active impact block 31 is provided with a corresponding spline 317 facing the rear end of the clutch member 41 in the axial direction to fit the clutch member.
  • the splines 417 of 41 mesh with each other.
  • Figure 3 shows the operation of the power tool 100 when it implements the impact wrench function.
  • the function change button 44 is adjusted to the position where the elastic ⁇ 45 of the clutch member 41 is positioned at the position of the first annular groove 223 of the output end 11, the spline 417 of the clutch member 41 and the flower of the active impact block 31.
  • the keys 317 are disengaged from each other. Since the pressure of the impact spring 32 causes the first end tooth 311 of the active impact block 31 to mesh with the second end tooth 411 of the driven impact block 41, the passive impact block 41 is restricted from moving.
  • the main shaft 24 is rotationally driven by the motor shaft via the deceleration system 13, and the active impact block 31 is driven by the ball 25 clamped in the inner V-shaped groove 312 and the outer V-shaped groove 241 to follow the rotation, and the passive impact block 41 also follows.
  • Rotation, the working head 51 and the tool chuck 52 drive the working head (not shown) to quickly tighten the nut (not shown).
  • the resistance torque rapidly increases.
  • the intermeshing active impact block 31 and the passive impact block 41 are both blocked, and the passive impact block 41 stops rotating, but the main shaft 24 is at The motor output shaft is still driven to rotate, forcing the ball 25 to roll along the groove against the frictional force between the inner and outer V-shaped grooves 312, 241, thereby pushing the active impact block 31 to move toward the motor, so that the impact spring 32 is compression.
  • the active impact block 31 gradually moves away from the passive impact block 41 in the axial direction.
  • the main shaft 24 drives the main shaft.
  • the moving block 31 rotates, causing the first end tooth 311 to slide over the second end tooth 411 of the passive impact block 41.
  • the ball 25 is returned along the spiral groove 312, 241 due to the action of the impact spring 32.
  • the active impact block 31 In the original position, the active impact block 31 is pushed forward, and at the same time, as the spindle 24 accelerates and rotates, the second end tooth 411 of the passive impact block 41 is impacted, so that the passive impact block 41 continues to move in the rotational direction, so that the cycle reciprocates and the thread is made.
  • the parts are tightened under impact torque.
  • the active impact block 31 is required to intermittently impact the passive impact block 51, so that the working head (fastening head) can tighten the nut, but only the working head (twist drill) is required to achieve the drilling function. Drilling, without the need for intermittent impact of the active impact block 31.
  • the function changeover button 44 is adjusted to the position where the elastic ⁇ of the clutch member 41 is positioned at the second annular groove 225 of the output end 11, that is, the spline 417 of the clutch member 41 and the flower of the active impact block 31
  • the keys 317 are engaged with each other, the power tool 100 is in an operating state in which the drilling function is realized.
  • the active impact block 31 tends to move toward the motor 11 due to the gradually increasing resistance torque of the working shaft 5.
  • the clutch member 41 restricts the backward movement of the active impact block 31 in the axial direction, the first end tooth 311 of the active impact block 31 always fits the second end tooth 511 of the passive impact block 51, and at the same time, the active impact The block 31, the passive impact block 41, and the working shaft 51 move together in the rotational direction. Since the passive impact block 41 and the active impact block 31 are always unable to disengage, that is, no impact can be formed between the two, it is ensured that the working head continues to drill.
  • the clutch member 31 can also be arranged directly on the outer peripheral surface of the main shaft 24 and can be slidably disposed in the axial direction of the main shaft 24.
  • a portion of the clutch member 41 and the main shaft 24 are relatively fixedly coupled in the rotational direction, and a portion is selectively engaged or disengaged from the active impact block 31 by a spline fit, thereby drilling mode in the power tool 100.
  • the fixed connection of the main shaft 24 to the active impact block 41 is established.
  • the idea of this embodiment is the same as that of the preferred embodiment of the present invention described above. The specific form is not described again. What is important is the rotation of the motor 11 after deceleration by the deceleration system.
  • the output is transmitted to the active impact block 31 via a fixedly connected transmission.
  • the clutch member 41 can also be selected in a form different from the spline fit and the main
  • the movable block 31 is fixedly connected, and can also be used in a different form from the slider slide and the output end 1 1 or the main shaft
  • a clutch mechanism is added between the planetary gear reduction system of the power tool and the inner ball V-groove impact structure, and the electric screwdriver can be correspondingly realized.
  • Function, and the addition of the active and static end ercussion mechanism at the front end of the working shaft 5 can realize the function of the impact drill.
  • the above functions can be separately set and combined with the impact wrench function to form a dual-function power tool, or can be superimposed to form a three-function power tool or a four-function power tool. Since the above-mentioned added functional mechanisms are all prior art, no further description is provided. .

Description

动力工具 技术领域
本发明涉及一种动力工具， 尤其涉及一种能实现冲击扳手功能和电钻功能 或电动螺丝批功能或冲击钻功能的多功能动力工具。
背景技术
在现有的动力工具中， 冲击扳手是用于将螺紋紧固件拧紧到工件上。 其结 构上通常包括由马达旋转驱动的主轴， 与主轴通过螺旋槽和滚珠配合连接的主 动冲击块， 和位于主动冲击块前方与主动冲击块通过端齿配合的工作轴。 在主 动冲击块后方还设有冲击弹簧， 其压迫主动冲击块使主动冲击块持续保持与工 作轴的可靠配合。 工作过程中， 主轴的旋转运动通过主动冲击块和工作轴上的 被动冲击块直接输出到螺紋件以将螺紋件拧到工件上。 在拧紧过程中， 工作轴 上的负载逐渐增大， 当负载超过预定值时， 通过滚珠在螺旋槽内的滚动， 主动 冲击块相对于工作轴上的被动冲击块轴向朝向马达运动， 并同时压缩其后的弹 簧。 当主动冲击块和工作轴上的被动冲击块的端齿脱离配合瞬间， 在冲击弹簧 的作用下， 主动冲击块轴向向前运动并在旋转方向上打击工作轴上的被动冲击 块， 使工作轴在旋转方向上继续旋紧螺紋件。 如此循环往复， 通过主动冲击块 不断的间歇性打击， 确保螺紋件最终拧紧到工件上。 电钻是用于在工件上进行 钻孔， 但通常使用者在工作时会同时需要在工件上拧螺紋件或钻孔， 如此， 需 要使用者不断地更换工具来进行操作的话将非常麻烦。
为了克服上述的弊端， 人们发展出了可以在同一工具上同时实现冲击扳手 和电钻功能的动力工具。 这种动力工具往往通过一个功能转换旋钮转换两种功 能。 具体的功能转换结构实现方式多种多样。 其中较为普遍， 而且较为简单的 方式为通过一个可以移动的止挡件选择性的限制主动冲击块的轴向向后的运 动。 这样， 当止挡件不限制主动冲击块的轴向向后的运动时， 主动冲击块可以 像前面所描述的那样实现冲击扳手功能； 当止挡件限制主动冲击块的轴向向后 的运动时， 主动冲击块始终和工作轴保持配合不脱开， 并且不会压缩其后的弹 簧以实现蓄能冲击， 以实现电钻功能。 例如， 中国专利申请 CN 2 005 1 009 9 1 06 揭示了一种动力工具， 其在主动冲击块后端置有一可径向移动的止挡件， 当其 与主动冲击块后端接触时， 限制主动冲击块的轴向向后运动以实现电钻功能。 当其径向上移不与主动冲击块后端接触时为冲击扳手功能。 然而， 上述方式的 功能转换机构在切换到电钻功能时， 旋转传递依靠主轴和主动冲击块之间的滑 槽滚珠结构传递， 滚珠和主轴和主动冲击块均为活动配接， 限制主动冲击块的 轴向向后运动的止挡件会受到主动冲击块较大的力， 并且主动冲击块相对止挡 件转动， 使止挡件易磨损， 所以这种旋转传递的稳定性较低。
发明内容
本发明提供一种动力工具， 其具有功能转换机构来实现冲击扳手功能和电 钻功能或螺丝批或冲击钻功能之间的转换， 该动力工具的电钻功能的旋转传递 稳定。
为实现上述目的， 本发明的技术方案是：
一种动力工具， 包括： 机壳、 设置在机壳内的马达， 马达输出旋转运动、 将马达输出的旋转进行减速的减速系统， 减速系统具有输出端以输出减速后的 旋转、 连接输出端的主轴、 以及在工作时用于和相应工作头配接的工作轴， 主 轴上设有主动冲击块， 其可相对于主轴作轴向运动， 工作轴上设有被动冲击块， 其随工作轴一起转动， 主动冲击块上设有第一端齿， 被动冲击块上设有第二端 齿， 主动冲击块通过其第一端齿与被动冲击块的第二端齿的配合来旋转驱动被 动冲击块； 该动力工具还包括离合件， 其可在第一位置和第二位置间运动以可 选择地将主动冲击块与输出端和主轴中的至少一个固定连接。
作为对本发明的进一步改进，所述离合件面向主动冲击块的部分设有花键， 所述主动冲击块面向离合件的部分具有相配合的花键， 所述离合件处于第二位 置时， 离合件的花键和主动冲击块的花键相互啮合以形成固定连接。
作为对本发明的进一步改进， 离合件呈环状以套接在输出端上， 离合件内 周面设有径向凸起的滑块， 输出端上设有容纳所述滑块在其中移动的径向凹陷 的滑槽。
作为对本发明的进一步改进， 所述离合件的内周面内具有内环槽以容纳一 弹性圏， 所述输出端的外周面上间隔设置有第一环形槽和第二环形槽， 所述离 合件带动弹性圏移动以使弹性圏可选的位于第一环形槽或第二环形槽， 此时离 合件对应的位于第一位置或第二位置。
作为对本发明的进一步改进， 该动力工具进一步包括设置于机壳 1上的功 能转换钮， 所述功能转换钮通过位于机壳内的连接件连接所述离合件并带动离 合件在第一位置和第二位置间移动。
作为对本发明的进一步改进， 该动力工具进一步包括弹性抵靠在主动冲击 块的远离被动冲击块一侧的冲击弹簧和位于主动冲击块和主轴接合处的滚球， 其中主动冲击块的内壁上和主轴上设有收容该滚球并容许滚球在其内滚动的 V ,
形槽。
作为对本发明的进一步改进， 该动力工具还包括冲击机构， 其通过主动冲 击块在旋转方向上对被动冲击块施加间歇性的冲击来实现冲击扳手功能。
作为对本发明的进一步改进， 该动力工具可实现钻进功能或电动螺丝批功 能或冲击钻功能。
作为对本发明的进一步改进， 所述减速系统为连接在马达和主轴之间的用 于降低马达输出转速的行星齿轮减速系统。
本发明的另一种技术方案是
一种动力工具， 其包括： 马达， 收容在一机壳内以输出旋转运动； 减速系 统， 将马达的旋转经过减速后由一输出端输出； 主轴， 由所述输出端驱动旋转； 工作轴， 设在所述机壳内， 并向前延伸用来驱动一工作头在工件上工作； 主动 冲击块， 设在所述主轴上； 被动冲击块， 设在所述工作轴上； 其中所述主动冲 击块根据工作轴所受的负载与被动冲击块形成配合或脱离， 从而在旋转方向上 对冲击块施以间歇性的冲击； 还包括离合件， 其可在第一位置和第二位置间运 动以可选择地将主动冲击块与输入端和传动轴中的至少一个固定连接； 当离合 件位于第一位置时， 与主动冲击块脱离以允许主动冲击块形成所述冲击从而实 现一冲击模式， 当离合件位于第二位置时， 与主动冲击块固定连接， 以传递转 动到所述主动冲击块从而实现一钻进模式或冲击钻模式或螺丝批模式。
与现有技术相比， 本发明的有益效果是： 动力工具增设了在两个位置间可 选择的移动的离合件， 以可选的将输出端和主轴的至少其中之一和主动冲击块 固定连接在一起， 以在钻进模式或冲击钻模式或螺丝批模式稳定有效的实现旋 转传递， 在冲击模式时实现冲击。 上述功能转换机构结构简单稳定、 制造成本 较低， 且操作方便、 省力。
附图说明
下面结合附图和实施例对本发明作进一步说明。
图 1是本发明的动力工具的主视图。
图 2是本发明的动力工具的内部视图。
图 3是本发明的动力工具处于冲击扳手功能状态的结构图。
图 4是本发明的动力工具处于钻进功能状态的结构图。
1 00 动力工具 8 电池包 1 3 减速系统
1 机壳 9 开关 2 2 输出端
6 手柄 1 1 马达 2 2 1 滑槽 223 第一环形槽 25 滚球 5 工作轴
225 第二环形槽 312 内 V形槽 52 夹头
24 主轴 311 第一端齿 512 收容槽
31 主动冲击块 317 花键 41 离合件
32 冲击弹簧 51 被动冲击块 411 外环槽
241 外 V形槽 511 第二端齿 413 滑块
42 连接件 45 弹性圏 417 花键
44 功能转换钮 415 内环槽
具体 .实施方式
图 1到图 4所示的是本发明的动力工具 100的一具体实施方式， 在该实施 方式中， 动力工具 100具有冲击扳手功能和钻进功能。 如图 1所示， 该动力工 具 100 包括水平布置的机壳 1、 与机壳 1呈一定角度布置的手柄 6、 和位于手柄 6底部可拆卸的电池包 8。 机壳 1 前端设有工具夹头 52, 用于在该动力工具实 现不同功能时分别夹持不同的工作头（未图示）， 如在实现冲击扳手功能时夹持 紧固头， 在实现钻进功能时夹持麻花钻。 手柄 6 上设有开关 9, 操作者可通过 按压该开关 9来启动该动力工具 100。 机壳 1上还设有功能转换钮 44, 操作者 可通过拨动该功能转换钮 44来转换动力工具 100的工作的功能模式。
图 1揭示的是设置在机壳 1 内的动力工具 100的工作部件。 如图 2所示， 工作部件包括马达 11, 马达 11前端延伸出马达轴（图未示）。 一减速系统 13设 置在马达 11 的前方， 在本实施方式中， 该减速系统 13为行星齿轮减速系统， 其具体实现方式为业界一般水平的技术人员所周知的， 在此不进行详细描述。 马达 11运行时， 马达轴驱动行星齿轮减速系统运转， 从而将马达输出的旋转通 过一定的减速比传递到与行星齿轮减速系统的输出端 22 相连的主轴 24。 输出 端 11为行星齿轮减速系统的最末一级行星架， 主轴 24通过过盈配合嵌入到该 行星架中， 形成与输出端 11的固定连接， 当输出端 11旋转时， 主轴 24跟随旋 转。
减速系统 13的前方设有用于实现冲击扳手功能的机构，其包括一套设在主 轴 24上的主动冲击块 31、设于主动冲击块 31和输出端 11之间的冲击弹簧 32、 以及位于主动冲击块 31和主轴 24接合处的滚球 V形槽冲击机构， 其中该冲击 机构包括在主轴 24表面凹陷形成的外 V形槽 241, 可在外 V形槽 241 内滚动的 滚球 25, 在本实施方式中为钢球， 和设于主动冲击块 31 内圏用于收容滚球 25 的内 V形槽 312。主动冲击块 31 的前端面上径向对称凸设有一对第一端齿 311。 在冲击弹簧 32和主动冲击块 31之间设有垫圏和垫片。主动冲击块 31 的前端还 设有被动冲击块 51 , 被动冲击块 51与主动冲击块 31相对的后端面上径向对称 的凸出设置有一对第二端齿 511。工作部件还包括延伸出机壳 1前端的工作轴 5 和套设在工作轴前端的工具夹头 52。 被动冲击块 51 与工作轴 5相连并结合为 一体。工作轴 51前端设有收容槽 512,可在实现不同功能时收容相应的工作头， 并通过工具夹头 52夹紧固持。
工作部件还包括设于主动冲击块 31和主轴 24、 减速系统 13之间的功能调 节机构。 功能调节机构包括离合件 41、 功能转换钮 44、 和连接件 42。 其中离 合件 41呈环状， 环绕输出端 11的外周面设置。 离合件 41 的外周面上设置有一 圏外环槽 411, 连接件 42的一端勾在该外环槽 411 内， 另一端和设置在机壳 1 上功能转换钮 44连接， 以供操作者操作， 通过移动功能转换钮 44带动连接件 42, 进而带动离合件 41在输出端 22的轴向方向上来回移动。 本领域的一般水 平的技术人员所容易思及的， 釆用功能转换钮 44直接连接一个销轴， 通过销轴 穿过机壳 1连接到离合件 41 上， 带动离合件 41来回移动也是可行的。 连接具 体的， 功能转换钮 44贯穿设置于机壳 1上， 包括设于机壳 1 的操作部分和设于 机身内的环状部分。 操作部分可以绕工作轴 5 的纵向轴线旋转并带动环状部分 旋转。 环状部分上设有轨道槽， 轨道槽包括两个沿垂直于工作轴 5纵向轴线的 方向平行并且在工作轴 5纵向轴线方向上间隔设置的直槽和一个连接前述的两 个直槽的斜槽。 前述的连接件 42 的另一端设置于轨道槽中， 具体的， 连接件 42的另一端位于轨道槽的两个直槽的其中之一中。 当转换功能时， 操作者拨动 功能转换钮的操作部分， 环状部分跟随旋转， 轨道槽也跟随环状部分相对于连 接件 42 的另一端运动。 在轨道槽的运动过程中， 首先是一个直槽连接连接件 42 的另一端并相对其运动， 此时连接件 42 没有轴向移动； 然后轨道槽的斜槽 部分移动到连接件 42的另一端， 斜槽继续移动， 带动连接件 42轴向移动， 直 到斜槽移动到离开连接件 42的另一端， 另一个直槽移动到连接连接件 42的另 一端的位置。 功能转换钮 44通过上述的方式带动连接件 42轴向移动， 但如业 界一般水平的技术人员所容易想到的，功能转换钮和离合件 41之间的连接及控 制方式是多样的， 并不限于上述的方式， 如， 功能转换钮 44可以以销轴方式径 向穿设在离合件 41 的外周面外环槽 411 内， 直接带动离合件 41轴向移动。 离 合件 41的内周面的对称部位径向上凸起形成一对滑块 413,滑块 413中间断开， 向离合件 41 内凹陷形成一个内环槽 415, 内环槽 415 内安放有弹性圏 45。 对应 的， 输出端 22的外周面对称部位在径向上凹陷形成一对滑槽 221, 且在输出端 22的外周面上，滑槽 221的轴向布置行程内设置有两个与之垂直相交的环形槽， 分别为相对靠近减速齿轮系统一侧的第一环形槽 223和相对靠近主动冲击块 31 一侧的第二环形槽 225。 离合件 41通过滑块在输出端 11 的滑槽 221 内轴向来 回移动， 但不能绕输出端 22 转动。 弹性圏 45 主体布置于离合件 41 的内环槽 415 内， 跟随离合件 41在输出端 22的外周面上轴向移动， 并且， 在弹性圏 45 到达输出端 22的两个环形槽位置时， 进入环形槽， 定位在输出端 22的两个轴 向位置， 当弹性圏 45定位于第一环形槽 223时， 离合件 41处于第一位置， 当 弹性圏 45定位于第二环形槽 225时， 离合件 41处于第二位置。 这样的设置可 以帮助操作者确定离合件已经到达预定的位置，并将离合件 41 固定于该位置而 不会任意滑动， 除非操作者手动移动之。
离合件 41在轴向上面向主动冲击块 31 的前端设置成花键 417, 同时主动 冲击块 31在轴向上面向离合件 41 的后端设置有对应的花键 317, 以适于和离 合件 41 的花键 417相互啮合。 弹性圏 45定位于第一环形槽 223时， 离合件 41 和主动冲击块 31之间间隔有一段距离， 各自的花键部分处于脱离啮合的状态； 弹性圏定位于第二环形槽 225时， 离合件 41和主动冲击块 31贴合在一起， 各 自的花键部分相互啮合。
图 3所示为该动力工具 100实现冲击扳手功能时的工作情形。 在实现冲击 扳手功能时， 功能转换钮 44被调节到离合件 41 的弹性圏 45定位于输出端 11 的第一环形槽 223的位置时，离合件 41的花键 417和主动冲击块 31的花键 317 彼此脱离啮合。 由于冲击弹簧 32的压力使主动冲击块 31 的第一端齿 311与被 动冲击块 41 的第二端齿 411啮合， 从而限制被动冲击块 41无法运动。 动力工 具工作时， 主轴 24 由马达轴经由减速系统 13旋转驱动， 主动冲击块 31通过夹 于内 V形槽 312、 外 V形槽 241 的滚球 25 带动， 跟随转动， 被动冲击块 41也 随之转动， 通过工作轴 51和工具夹头 52带动工作头（未图示）迅速将螺母（未 图示） 拧紧。
当螺母端面和工件 （未图示） 面相接触后， 阻力矩迅速增加， 达到一定值 后， 相互啮合的主动冲击块 31和被动冲击块 41均受阻， 被动冲击块 41停止转 动， 但主轴 24在马达输出轴的驱动下仍转动， 迫使滚球 25克服其与内、 外 V 形槽 312、 241之间的摩擦力沿槽滚动， 从而推动主动冲击块 31 向马达方向运 动， 使冲击弹簧 32被压缩。 由此， 主动冲击块 31在轴向上逐渐远离被动冲击 块 41。 当主动冲击块 31轴向移动距离刚超过被动冲击块 41 的第二端齿 411 的 齿高后， 即主动冲击块 31和被动冲击块 41脱离啮合的瞬间， 主轴 24便带动主 动冲击块 31旋转， 使其第一端齿 311 滑过被动冲击块 41 的第二端齿 411, 在 滑过瞬间， 由于冲击弹簧 32的作用，滚球 25 又沿螺旋槽 312、 241 回到原位置， 主动冲击块 31被向前推，同时随着主轴 24加速转动而冲击被动冲击块 41 的第 二端齿 411, 使被动冲击块 41在旋转方向上继续运动， 如此循环往复， 使螺紋 件在冲击力矩下拧紧。
上述实现冲击扳手功能时， 需要主动冲击块 31 间歇旋转冲击被动冲击块 51, 从而使工作头 （紧固头） 能够拧紧螺母， 但在实现钻进功能时， 只需要工 作头 （麻花钻） 持续钻进， 而不再需要主动冲击块 31 的间歇性冲击。 参照图 4 所示，当功能转换钮 44被调节到离合件 41 的弹性圏定位于输出端 11的第二环 形槽 225的位置时， 即离合件 41 的花键 417和主动冲击块 31 的花键 317彼此 啮合时， 该动力工具 100处于实现钻进功能的工作状态。 在钻进过程中， 由于 工作轴 5受到的阻力矩逐渐增大， 主动冲击块 31则倾向于朝向马达 11运动。 此时， 由于离合件 41 限制了主动冲击块 31在轴向上的向后移动， 主动冲击块 31 的第一端齿 311始终贴合被动冲击块 51 的第二端齿 511, 同时， 主动冲击块 31、 被动冲击块 41、 工作轴 51在旋转方向上一起运动。 由于被动冲击块 41和 主动冲击块 31始终无法脱离， 即两者之间无法形成冲击， 所以可确保工作头持 续钻进。
上述实施方式中， 尤其重要的是： 在实现钻进功能时， 由马达输出的旋转 经过减速， 到达减速系统的输出端 22, 然后以离合件 41 为中间件传递到主动 冲击块 31, 以此建立了减速系统的输出端 11到主动冲击块 31 的固定连接以传 递旋转； 由于主轴 24和减速系统的输出端 11通过过盈配合固定连接在一起， 也可以说建立了主轴 24和主动冲击块 41 的固定连接。 而以往的动力工具 100 在由冲击扳手功能切换到钻进功能时， 都仍是依靠主轴 24和主动冲击块 41之 间的槽和滚珠系统的活动连接传递旋转。
业界一般水平的技术人员容易想到的，离合件 31也可以选择直接设置在主 轴 24的外周面上， 沿主轴 24的轴向方向可滑移的设置。 在这种实施方式中， 离合件 41一部分和主轴 24在旋转方向上相对固定的相连， 一部分通过花键配 合可选择的和主动冲击块 31啮合或脱离，以此在动力工具 100的钻进模式下建 立主轴 24到主动冲击块 41 的固定连接， 这种实施例的思路和前述的本发明的 优选实施例相同， 其具体形式不再赘述， 重要的是马达 11 的经过减速系统减速 后的旋转输出通过固定连接的传动形式传递到主动冲击块 31。
同样容易想到的，离合件 41还可以以不同于花键配合的形式可选择的和主 动冲击块 31 固定连接， 也可以釆用不同于滑块滑轨的形式和输出端 1 1或主轴
24在旋转上相对固定的配合， 例如， 釆用卡扣和孔配合， 或者凸块和凹槽配合 实现离合件 4 1和主动冲击块 31 的可选的固连接， 釆用花键配合实现离合件 4 1 和输出端 1 1或主轴 2 4的配合等。
在其他实施方式中， 当被动冲击块随主动冲击块一起运动时， 在动力工具 的行星齿轮减速系统和内滚珠 V 形槽冲击结构间增加离合器结构（clutch mechanism) , 可相应实现电动螺丝批的功能， 而在工作轴 5 的前端增加动、 静 端齿主动冲击块结构 ( ercussion mechanism ) 则可相应实现冲击钻的功能。 上 述各功能可单独设置并于冲击扳手功能组合形成双功能动力工具， 也可叠加设 置而形成三功能动力工具或四功能动力工具， 由于上述增加的功能机构均为现 有技术， 所以不再赘述。

Claims

权 利 要 求
1. 一种动力工具， 包括： 机壳（1)、 设置在机壳内的马达（Π) , 马达输 出旋转运动、 将马达输出的旋转速度进行减速的减速系统（13) , 减速系统具 有输出端（22、 连接输出端的主轴（24)、 以及在工作时用于和相应工作头配接 的工作轴（5) , 主轴上套接有主动冲击块（31) , 其可相对于主轴作轴向运动， 工作轴上设有被动冲击块（51) , 其随工作轴一起转动， 主动冲击块上设有第 一端齿（311) , 被动冲击块上设有第二端齿（511) , 主动冲击块通过其第一端 齿与被动冲击块的第二端齿的配合来旋转驱动被动冲击块；
其特征在于： 该动力工具还包括离合件（41) , 其可在第一位置和第二位 置间运动以可选择地将主动冲击块与输出端和主轴中的至少一个固定连接。
2.根据权利要求 1所述的动力工具，其特征在于：所述离合件可操作的在 第一位置和第二位置之间轴向运动以将主动冲击块与输出端和主轴中的至少 一个固定连接， 使主动冲击块与输出端和主轴中的至少一个一起旋转。
3.根据权利要求 1所述的动力工具，其特征在于：所述离合件面向主动冲 击块的部分设有花键（417)或端齿，所述主动冲击块面向离合件的部分具有相 配合的花键（317)或端齿， 所述离合件处于第二位置时， 离合和主动冲击块的 花键或端齿相互啮合以形成固定连接。
4.根据权利要求 1所述的动力工具，其特征在于：离合件呈环状以套接在 输出端上， 离合件内周面设有径向凸起的滑块（413) , 输出端上设有容纳所述 滑块在其中移动的径向凹陷的轴向延伸的滑槽（221)。
5.根据权利要求 1所述的动力工具，其特征在于：所述离合件的内周面内 具有内环槽（415)以容纳一弹性圏 （45)，所述输出端的外周面上间隔设置有第 一环形槽（223)和第二环形槽（225) , 所述离合件带动弹性圏移动以使弹性圏 可选的位于第一环形槽或第二环形槽， 以使离合件对应的位于第一位置或第 二位置。
6.根据权利要求 1所述的动力工具，其特征在于：包括设置于机壳 1上的 功能转换钮（44) , 所述功能转换钮通过位于机壳内的连接件（42)连接所述离 合件并带动离合件在第一位置和第二位置间移动。
7.根据权利要求 1所述的动力工具，其特征在于：包括弹性抵靠在主动冲 击块的远离被动冲击块一侧的冲击弹簧（32)和位于主动冲击块和主轴接合处 的滚球（25) , 其中主动冲击块的内壁上和主轴上分别设有收容该滚球并容许 滚球在其内滚动的内 V形槽（312)和外 V形槽（241)。
WO 2011/029387 ^ , Λ ^ ^ L , , , , n , . T ^ PCT/CN2010/076711^ ¾ 据栻利要求 1所述的动力工具，其特征在于： 包 ； 构， 其通 过主动冲击块在旋转方向上对被动冲击块施加间歇性的冲击来实现冲击扳手 功能。
9.根据权利要求 1所述的动力工具，其特征在于：该动力工具可实现钻进 功能或电动螺丝批功能或冲击钻功能。
1 0.根据权利要求 1所述的动力工具，其特征在于： 所述功能转换钮具有 机壳外的操作部分和机壳内的环状部分， 所述环状部分上设有轨道槽， 所述 连接件的一端设于所述轨道槽中， 所述的操作部分可操作并带动环状部分的 轨道槽运动， 以带动所述连接件轴向移动。
PCT/CN2010/076711 2009-09-10 2010-09-08 动力工具 WO2011029387A1 (zh)

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CN102019608A (zh) 2011-04-20

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