WO2011088631A1 - 轻型单钮多功能电锤 - Google Patents

轻型单钮多功能电锤 Download PDF

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Publication number
WO2011088631A1
WO2011088631A1 PCT/CN2010/070975 CN2010070975W WO2011088631A1 WO 2011088631 A1 WO2011088631 A1 WO 2011088631A1 CN 2010070975 W CN2010070975 W CN 2010070975W WO 2011088631 A1 WO2011088631 A1 WO 2011088631A1
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WO
WIPO (PCT)
Prior art keywords
hammer
paddle
clutch
gear
knob
Prior art date
Application number
PCT/CN2010/070975
Other languages
English (en)
French (fr)
Inventor
王文江
Original Assignee
浙江海王电器有限公司
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 浙江海王电器有限公司 filed Critical 浙江海王电器有限公司
Priority to US13/502,400 priority Critical patent/US9227312B2/en
Priority to EP10843673.4A priority patent/EP2527096B1/en
Publication of WO2011088631A1 publication Critical patent/WO2011088631A1/zh

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Classifications

    • 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
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/061—Swash-plate actuated impulse-driving mechanisms
    • 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
    • B25D2216/0015—Tools having a percussion-only 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
    • B25D2216/0023—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
    • 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
    • B25D2216/0046—Preventing rotation
    • 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
    • B25D2216/0084—Mode-changing mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/255—Switches

Definitions

  • the invention relates to a power tool, in particular to a multifunctional electric hammer.
  • the electric hammer is popular among the users because of its four functions of single hammer, single drill, hammer drill and single hammer angle adjustment, but the single drill speed Too slow has always been a difficult point for electric hammers.
  • the function conversion of the electric hammer can be controlled by a single button, the structure is complicated, the manufacturing cost is high, and the service life is short, which is troublesome to implement; in the case of single drilling, the rotation speed is too slow due to the constant gear ratio, and the operation is performed. It is inconvenient to use.
  • the present invention provides a lightweight single-button multi-function electric hammer with simple and reasonable structure, flexible and convenient conversion, low cost and safe and reliable use.
  • a light single button multi-function electric hammer comprises a body, a motor, a rotating sleeve assembly, a cylinder assembly, a fork assembly and a knob, wherein the motor, the rotating sleeve assembly, the cylinder assembly and the fork assembly are located in the body, the knob and The paddle assembly is linked, the light single button multi-function hammer further includes a large gear and a transmission mechanism, the large gear includes a large end tooth and a small end tooth, and the big end tooth is a large end multi-gear, The small tooth end has a small end and a small gear; the torque clutch transmission mechanism comprises a pinion gear, a gear clutch, an intermediate shaft, a hammer gear clutch, a pendulum rod bearing and a first stage wheel, and the pinion gear and the intermediate shaft are a dynamic fit, small The gear meshes with the large end tooth of the large gear and cooperates with the internal tooth of the gear clutch.
  • the gear clutch meshes with the small end tooth of the large gear and cooperates with the pinion shaft of the intermediate shaft, and the gear clutch and the hammer clutch cooperate with the pinion of the intermediate shaft, and the pendulum
  • the rod bearing is movably coupled with the intermediate shaft and connected to the cylinder assembly through the swing rod, and the hammer clutch and the swing rod bearing are provided with matched concave and convex grooves, and the first stage wheel and the intermediate shaft are tightly matched; the knob is connected to the operating mechanism, and the operation is performed.
  • the mechanism is coupled to the large gear end of the large gear, the gear clutch and the hammer clutch.
  • the operating mechanism includes a stop piece spring, a stop piece, a drill paddle, a paddle holder, an inner knob, a hammer paddle, a tension spring, a paddle spring and a guide post, a stop piece spring, a stop piece
  • the drill paddle, the paddle holder, the hammer paddle, the tension spring, and the paddle spring are sequentially disposed on the guide post, and the stopper piece is provided with a stop tooth piece matched with the large end tooth of the large gear and the inner knob
  • One side is positioned, the other side of the drill paddle is fastened on the paddle holder, a tension spring is arranged between the drill paddle and the paddle holder, and the other side of the paddle holder is fastened on the hammer paddle
  • the paddle spring is disposed between the paddle holder and the hammer paddle, and the paddle of the drill paddle is correspondingly disposed on both sides of the gear clutch, and the gear clutch is clamped, and the hammer gear fork on the hammer paddle is correspondingly disposed
  • one side of the knob is provided with an elliptical dial which is offset from the knob core, and the elliptical dial block is arranged between the paddle holder and the hammer clutch fastening region, and the elliptical dial block is further provided.
  • One quarter of the circular bumps, the other side is provided with semi-circular bumps, and the outer edge of the semi-circular bumps is placed on the positioning plate of the stopper piece.
  • the needle clutch is radially positioned between the torque clutch and the rotating sleeve, and the large gear is movably matched with the rotating sleeve assembly, and the torque clutch and the large gear are provided with matching concave and convex grooves.
  • the knob passes through the cooperation of various states of the elliptical dial block, the quarter-circular bump and the semi-circular bump and the stop piece, the paddle holder and the hammer paddle, and the paddle holder is driven.
  • the drill plucking piece enables the drill plucking to drive the clutch of the gear clutch and the pinion, and mesh with the small end tooth of the large gear, and the hammer plucking wheel drives the clutch of the hammer gear and the pendulum bearing to make the electric hammer realize the single Drill 1, single drill 2, single hammer, hammer drill and single hammer angle adjustment five functions of smooth conversion; through the torque spring, large gear and torque clutch concave and convex groove, in the hammer drill and single drill 1, single drill 2 load overload After the automatic clutch, to achieve overload protection; has a simple structure, flexible and convenient conversion, low cost, safe and reliable use.
  • the invention has the advantages of simple and reasonable structure, flexible and convenient conversion, low cost and safe and reliable use.
  • Figure 1 is a schematic view of the structure of the present invention.
  • Fig. 2 is a schematic view showing the structure of the hammer drill of the present invention.
  • Fig. 3 is a schematic view showing the cooperation of the knob and the operating mechanism during hammer drilling of the present invention.
  • FIG. 4 is a schematic view showing the cooperation of the large gear, the pinion gear and the tooth piece according to the present invention.
  • Fig. 5 is a schematic view showing the structure of a single drill 1 of the present invention.
  • FIG. 6 is a schematic view showing the cooperation of the knob and the operating mechanism when the single drill 1 is used in the present invention.
  • Figure 7 is a schematic view showing the structure of the single drill 2 of the present invention.
  • FIG. 8 is a schematic view showing the cooperation of the knob and the operating mechanism when the single drill 2 is used in the present invention.
  • Figure 9 is a schematic view showing the structure of a single hammer of the present invention.
  • Figure 10 is a schematic view showing the cooperation of the knob and the operating mechanism of the single hammer of the present invention.
  • Figure 11 is a schematic view showing the structure of the single hammer angle adjustment of the present invention.
  • FIG. 12 is a schematic view showing the cooperation of the knob and the operating mechanism when the single hammer angle is adjusted according to the present invention.
  • Figure 13 is a schematic view showing the structure of a large gear of the present invention.
  • Figure 14 is a schematic view showing the structure of a gear clutch of the present invention.
  • Figure 15 is a schematic view showing the structure of the hammer clutch of the present invention.
  • Figure 16 is a schematic view showing the structure of a pendulum bearing of the present invention.
  • 17 is a schematic view showing the structure of a knob of the present invention.
  • a lightweight single-button multi-function electric hammer includes a body, a motor, a rotating sleeve assembly 1, a cylinder assembly 6, a torsion spring 2, a large gear (the large gear is composed of two parts, and the part is a large end Gear, referred to as big end tooth 3; part is small end less gear, referred to as small end tooth 4, torque clutch 2, transmission mechanism and knob 26, the speed of the transmission mechanism includes pinion 7, gear clutch 8, intermediate shaft 10, hammer
  • the shifting clutch 9, the pendulum rod bearing 11 and the first stage wheel 12, the pinion 7 and the intermediate shaft 10 are a dynamic fit, the pinion 7 meshes with the large gear big end teeth 3 and cooperates with the internal teeth of the gear clutch 8, the gear clutch 8 and
  • the large gear small end teeth 4 mesh and cooperate with the pinion shaft of the intermediate shaft 10, the gear clutch 8 and the hammer clutch 9 are movably engaged with the pinion shaft of the intermediate shaft 10, and the pendulum rod bearing 11 is movably engaged with the intermediate shaft 10 and
  • the operating mechanism includes a stop piece spring 13, a stop piece 14, a drill paddle paddle 17, a paddle holder 20, a hammer paddle 23, a tension spring 12, a paddle spring 21 and a guide post 25, and a stop piece
  • the spring 13, the stopper piece 14, the drill paddle paddle 17, the paddle holder 20, the hammer paddle 23, the tension spring 12 and the paddle spring 21 are sequentially disposed on the guide post 25, and the stopper piece 14 is provided with a heel
  • the large toothed end tooth 3 matches the stop tooth piece and is positioned on the side of the knob 26, and the other side of the drill paddle paddle 17 is fastened on the paddle holder 20, between the drill paddle paddle 17 and the paddle holder 20
  • a tension spring 21 is provided, and the other side of the paddle holder 20 is fastened to the hammer paddle 22, and the paddle spring 24 is disposed between the paddle holder 20 and the hammer paddle 22, and the drill paddle paddle 17 is
  • the picks are correspondingly disposed on both sides of the gear clutch 8, and the gear clutch 8 is clamped
  • the knob 26 is provided with an elliptical dial 27 deviating from the knob center, and the elliptical dial is disposed between the paddle 20 and the hammer clutch 9 fastening region, and the elliptical dial 27 is further provided with four points.
  • One of the circular bumps 28 is provided with a semi-circular bump 29 on the other side, and the outer edge of the semi-circular bump is placed on the positioning plate of the stopper piece 14.
  • the needle clutch is radially positioned between the torque clutch and the rotating sleeve, and the large gear is movably matched with the rotating sleeve assembly.
  • the torque clutch and the large gear are provided with matching concave and convex grooves, the torque clutch and the large gear are slipped, and the large gear is made.
  • the rotation force cannot be transmitted to the rotating sleeve assembly, and the drill stops rotating, thereby achieving the effect of overload protection. When the load is relieved, the hammer returns to normal operation.
  • the structure of the hammer drill function of the present invention is as shown in FIG. 2 and FIG. 3, and the knob elliptical dial 27 and the quarter circular lug 28 are sandwiched between the paddle holder 19 and the hammer paddle 22 at this time.
  • the circular outer dome of the semicircular projection 29 is on the positioning plate 16 of the stopper piece 14, and the tooth piece 15 of the stopper piece 14 is separated from the large gear end tooth 3, and the pinion gear 7 and the large gear are large.
  • the gear clutch 8 is under the action of the drill shifting fork 18 of the drill shifting paddle 17, one end of the gear clutch 8 meshes with the shaft shaft of the intermediate shaft 10, one end is meshed with the pinion gear 7;
  • the hammer gear clutch 9 is dialed at the hammer gear Under the action of the hammer shifting fork 23 of the blade 20, the internal teeth of the hammer clutch 9 mesh with the intermediate shaft 10, and the hammer clutch 9 is connected to the swing link bearing 11 via the concave-convex grooves 31 and the concave-convex grooves 32 which are matched with each other.
  • the motor output shaft drives the first stage wheel 12 to rotate
  • the first stage wheel 12 drives the intermediate shaft 10 to rotate
  • the intermediate shaft 10 drives the rotating sleeve assembly 1 through the gear clutch 8, the pinion gear 7, the large gear big end tooth 3 and the torque clutch 5
  • the intermediate shaft 10 simultaneously drives the swing rod bearing 11 through the hammer clutch 9.
  • the swing rod bearing 11 drives the cylinder assembly 6 to reciprocate, and pushes the air hammer in the cylinder assembly 6 to hit the hammer to complete the impact energy. Transfer, thus achieving the hammer drill function of the electric hammer.
  • the structure of the single hammer angle adjustment function of the present invention shown in FIG. 5 is as shown in the figure.
  • the knob 26 is adjusted to the single hammer angle adjustment position in the stop state, as shown in FIG. 6, the positioning plate 16 of the stopper piece 14 is shown in FIG.
  • the radius of rotation of the knob 26 is constant, the position of the stopper piece 14 remains unchanged, and the tooth piece 15 of the stopper piece 14 is still separated from the large end tooth 3 of the large gear.
  • the pinion gear 7, the large gear big end tooth 3, the torque clutch 5 and the rotating sleeve assembly 1 are in a neutral transmission state, and the rotating sleeve assembly 1 is rotated.
  • the angle of the drill bit can be adjusted lightly to realize the single hammer angle adjustment function of the electric hammer.
  • Figure 7 shows the structure of the single hammer function of the present invention as shown in the figure.
  • the knob is in the single hammer position, as shown in Fig. 8, the positioning plate 16 of the stopper piece 14 and the semicircular projection of the knob 26 are shown.
  • the first stage wheel 12 drives the intermediate shaft 10 to rotate, and since the gear clutch 8 is completely separated from the pinion gear 7, it is small
  • the wheel 7 does not transmit the rotational force, the large gear end tooth 3, the torque clutch 5 and the rotating sleeve assembly 1 do not rotate, and the function of the drill is not realized;
  • the intermediate shaft 10 simultaneously drives the swing rod bearing 11 through the hammer clutch 9 and the swing rod bearing 11
  • the cylinder assembly 6 is driven to reciprocate, and the air hammer in the cylinder assembly 6 is pushed against the hammer to complete the transmission of impact energy, thereby realizing the single hammer function of the electric hammer; the teeth of the stop piece and the large end teeth of the large gear can be locked to be locked
  • the rotating sleeve does not rotate, Make sure the drill angle does not change when hammering.
  • FIG. 10 shows when the knob is turned to the single drill 2 function position.
  • the structure is as shown in FIG. 10.
  • the positioning plate 16 of the stopper piece 14 is in contact with the semicircular surface of the semicircular projection 29 of the knob 26, and the rotation radius of the knob 26 is the largest, the position of the stopper piece 14 and the hammer drill function.
  • the position is the same, the tooth piece 15 of the stopper piece 14 is in a separated state from the large gear big end tooth 3, the pinion gear 7 and the gear clutch 8 are in a separated state, the pinion gear 7 and the large gear big end tooth 3 are in a separated state, and the knob 26 is
  • the radius of rotation of the contact surface of the elliptical dial 27 and the paddle 19 changes, and the radius of rotation of the knob 26 is the largest.
  • the elliptical dial 27 deviating from the knob core drives the paddle holder 19 to the right, and the gear clutch 8 and the drill paddle paddle 17 are moved to the right by the paddle holder 19, while the paddle holder 19 and the drill paddle are The tension spring 21 between the 17 is pulled, the external teeth of the gear clutch 8 are meshed with the small gear small end teeth 4, the gear clutch 8 and the pinion gear 7 are in a separated state, and the quarter circular lug 28 and the hammer gear are dialed.
  • Figure 11 shows when the knob is turned to the single drill 1 function position.
  • the structure is as shown in FIG. 12, and the positioning plate 16 of the stopper piece 14 is in contact with the semicircular surface of the semicircular projection 29 of the knob 26, and the rotation radius of the knob 26 is the largest, the position of the stopper piece 14 and the hammer drill function.
  • the outer teeth of the gear clutch 8 mesh with the large end teeth 3 of the large gear, and the rotation of the contact surface of the quarter circular lug 28 and the hammer paddle 22 remains stationary, and the position of the hammer paddle 22 and the single
  • the hammer clutch 9 is connected to the concave-convex groove 31 and the concave-convex groove 32 which are matched with each other by the hammer shifting fork 23 of the hammer shifting piece 22; when working, the output shaft of the machine is electrically driven.
  • the stage wheel 12 rotates, the first stage wheel 12 drives the intermediate shaft 10 to rotate, and the intermediate shaft 10 passes the gear clutch 8 and the pinion 7
  • the large gear end tooth 3 and the torque clutch 5 drive the rotating sleeve assembly 1 to rotate, and the transmission of the rotating force is completed; the hammer clutch 9 and the swing rod bearing 11 are in a separated state, so the swing rod bearing 11 does not drive the cylinder assembly 6 to reciprocate.
  • the air hammer in the cylinder assembly 6 does not realize the impact hammer, and is not a function of the hammer, thereby realizing the function of the single drill 1.

Description

轻型单钮多功能电锤
技术领域
本发明涉及一种电动工具，特别是一种多功能电锤。
背景技术
随着电动工具行业的发展，对其功能的要求越来越高，电锤由于具有单锤、单钻、锤钻、单锤角度调整四种功能而备受广大用户的喜爱，但单钻速度太慢一直是电锤的难点。目前，电锤的功能转换虽然能够采用单钮控制，但结构复杂、制造成本高、使用寿命短，实现起来比较麻烦；在单钻时，由于齿数比不变的情况下转速太慢，给操作着带来使用不便。
发明内容
为了克服现有电锤存在的结构复杂、制造成本高、使用寿命短的不足，本发明提供一种结构简单合理、转换灵活方便、成本低、使用安全可靠的轻型单钮多功能电锤。
本发明解决其技术问题所采用的技术方案：
一种轻型单钮多功能电锤，包括机体、电机、转动套组件、气缸组件、拨叉组件和旋钮，所述电机、转动套组件、气缸组件、拨叉组件位于机体内，所述旋钮与所述拨片组件联动，所述轻型单钮多功能电锤还包括大齿轮和传动机构，所述大齿轮包括大端齿和小端齿，所述大端齿呈大端多齿轮， 所述小齿端呈小端少齿轮；所述的扭矩离合器传动机构包括小齿轮、齿轮离合器、中间轴、锤档离合器、摆杆轴承和一级轮，小齿轮和中间轴是动配合，小齿轮与大齿轮大端齿啮合并与齿轮离合器的内齿配合，齿轮离合器与大齿轮小端齿啮合并与中间轴齿轴配合，齿轮离合器及锤档离合器与中间轴的齿轴动配合，摆杆轴承与中间轴动配合并通过摆杆与气缸组件连接，锤档离合器与摆杆轴承上设有匹配的凹凸槽，一级轮与中间轴紧配合；所述旋钮连接操作机构，所述操作机构与所述大齿轮大齿端、齿轮离合器和锤档离合器联动。
所述的操作机构包括止动片弹簧、止动片、钻档拨片、拨片托、内旋钮、锤档拨片、拉簧、拨片弹簧和导柱，止动片弹簧、止动片、钻档拨片、拨片托、锤档拨片、拉簧、拨片弹簧依次设置在导柱上，止动片上设有跟与大齿轮大端齿匹配的止动齿片以及与内旋钮一侧定位，钻档拨片的另一侧扣接在拨片托上，钻档拨片与拨片托之间设有一个拉簧，拨片托的另一侧扣接在锤档拨片上，拨片弹簧设置在拨片托与锤档拨片之间，钻档拨片的拨片对应设置在齿轮离合器的两边，夹住齿轮离合器，锤档拨片上的锤档拨叉对应设置在锤档离合器的拨槽上。
为了使功能转换准确到位，所述的旋钮一面设有偏离旋钮心的椭圆形拨块，椭圆形拨块设置在拨片托与锤档离合器扣接区域之间，椭圆形拨块上又设有四分之一圆形凸块，另一面设有半圆形凸块，半圆形凸块的外缘顶在止动片的定位板上。
为了防止负荷过载运行，所述的扭矩离合器与转动套之间采用滚针径向定位，大齿轮与转动套组件动配合，扭矩离合器与大齿轮上设有相互配合的凹凸槽。
采用上述结构后，旋钮通过椭圆形拨块、四分之一圆形凸块及半圆形凸块与止动片、拨片托、锤档拨片的各种状态的配合，拨片托带动钻档拨片，使钻档拨片带动齿轮离合器与小齿轮的离合，与大齿轮小端齿的啮合，锤档拨片带动锤档离合器与摆杆轴承的离合，即可使电锤实现单钻1、单钻2、单锤、锤钻及单锤角度调整五种功能的平稳转换；通过扭矩弹簧、大齿轮与扭矩离合器凹凸槽配合，在锤钻与单钻1、单钻2负荷过载后自动离合，从而实现过载保护；具有结构简单，转换灵活方便、成本低、使用安全可靠等特点。
本发明的有益效果为：结构简单合理、转换灵活方便、成本低、使用安全可靠。
附图说明
图1为本发明结构的示意图。
图2为本发明锤钻时的结构示意图。
图3为本发明锤钻时的旋钮与操作机构配合示意图。
图4为本发明大齿轮与小齿轮及齿片配合示意图。
图5为本发明单钻1时的结构示意图。
图6为本发明单钻1时的旋钮与操作机构配合示意图。
图7为本发明单钻2时的结构示意图。
图8为本发明单钻2时的旋钮与操作机构配合示意图。
图9为本发明单锤时的结构示意图。
图10为本发明单锤时的旋钮与操作机构配合示意图。
图11为本发明单锤角度调整时的结构示意图。
图12为本发明单锤角度调整时的旋钮与操作机构配合示意图。
图13为本发明大齿轮结构示意图。
图14为本发明齿轮离合器结构示意图。
图15为本发明锤档离合器结构示意图。
图16为本发明摆杆轴承结构示意图。
图17为本发明旋钮结构示意图。
具体实施方式
下面结合附图对本发明做进一步详细的描述
参照图1至图17，一种轻型单钮多功能电锤，包括机体、电机、转动套组件1、气缸组件6、扭矩弹簧2、大齿轮（大齿轮由两部分组成，一部分为大端多齿轮，简称大端齿3；一部分为小端少齿轮，简称小端齿4、扭矩离合器2、传动机构和旋钮26，所速的传动机构包括小齿轮7、齿轮离合器8、中间轴10、锤档离合器9、摆杆轴承11和一级轮12，小齿轮7和中间轴10是动配合，小齿轮7与大齿轮大端齿3啮合并与齿轮离合器8的内齿配合，齿轮离合器8与大齿轮小端齿4啮合并与中间轴10齿轴配合，齿轮离合器8及锤档离合器9与中间轴10的齿轴动配合，摆杆轴承11与中间轴10动配合并通过摆杆与气缸组件2连接，锤档离合器9与摆杆轴承11上设有匹配的凹凸槽，一级轮12与中间轴10紧配合；所述旋钮26连接操作机构，所述操作机构与所述大齿轮大齿端3、齿轮离合器8和锤档离合器9联动。
所述的操作机构包括止动片弹簧13、止动片14、钻档拨片17、拨片托20、锤档拨片23、拉簧12、拨片弹簧21和导柱25，止动片弹簧13、止动片14、钻档拨片17、拨片托20、锤档拨片23、拉簧12和拨片弹簧21依次设置在导柱25上，止动片14上设有跟与大齿轮大端齿3匹配的止动齿片以及与旋钮26一侧定位，钻档拨片17的另一侧扣接在拨片托20上，钻档拨片17与拨片托20之间设有一个拉簧21，拨片托20的另一侧扣接在锤档拨片22上，拨片弹簧24设置在拨片托20与锤档拨片22之间，钻档拨片17的拨片对应设置在齿轮离合器8的两边，夹住齿轮离合器8，锤档拨片22上的锤档拨叉对应设置在锤档离合器9的拨槽上。
所述的旋钮26一面设有偏离旋钮心的椭圆形拨块27，椭圆形拨块设置在拨片托20与锤档离合器9扣接区域之间，椭圆形拨块27上又设有四分之一圆形凸块28，另一面设有半圆形凸块29，半圆形凸块的外缘顶在止动片14的定位板上。
所述的扭矩离合器与转动套之间采用滚针径向定位，大齿轮与转动套组件动配合，扭矩离合器与大齿轮上设有相互配合的凹凸槽，扭矩离合器与大齿轮打滑，使大齿轮不能不能将旋转力传递到转动套组件，钻头停止转动，从而达到过载保护的效果，当负载减轻后，电锤又回复正常工作。
下面结合附图进一步减速本发明实现五种功能的工作原理。
本发明锤钻功能时的结构如图2、图3所示，此时的旋钮椭圆形拨块27和四分之一圆形凸块28夹在拨片托19与锤档拨片22之间，半圆形凸块29的圆面外圆顶在止动片14的定位板16上，止动片14的齿片15与大齿轮大端齿3处于分离状态，小齿轮7与大齿轮大端齿3啮合，齿轮离合器8在钻档拨片17的钻档拨叉18作用下，齿轮离合器8一端与中间轴10轴齿啮合，一端与小齿轮7啮合；锤档离合器9在锤档拨片20的锤档拨叉23作用下，锤档离合器9的内齿与中间轴10齿啮合，锤档离合器9通过互相匹配的凹凸槽31、凹凸槽32与摆杆轴承11连接。工作时，电机输出轴带动一级轮12转动，一级轮12带动中间轴10转动，中间轴10通过齿轮离合器8、小齿轮7、大齿轮大端齿3及扭矩离合器5带动转动套组件1旋转，完成旋转力的传递；中间轴10同时通过锤档离合器9带动摆杆轴承11，摆杆轴承11带动气缸组件6往复运动，推动气缸组件6里的气锤撞击冲锤，完成冲击能量的传递，从而实现电锤的锤钻功能。
图5所示本发明单锤角度调整功能时的结构如图所示，在停机状态下，将旋钮26调到单锤角度调整位置时，如图6所示，止动片14的定位板16与旋钮26的半圆形凸块29的半圆面接触，旋钮26的旋转半径不变，止动片14位置保持不变，止动片14的齿片15与大齿轮大端齿3仍然处于分离状态，四分之一圆形凸块28与锤档拨片22的接触面的旋转半径不变，锤档拨片22保持不动，锤档离合器9通过互相匹配的凹凸槽31、凹凸槽32与摆杆轴承11连接；椭圆形拨块27与拨片托19的旋转半径变化，偏离旋转心的椭圆形拨块27带动拨片托19向右移，钻档拨片17及齿轮离合器8在拨片托19的带动下向右移并脱离与小齿轮7的啮合，小齿轮7、大齿轮大端齿3、扭矩离合器5及转动套组件1处于空档传动状态，旋转转动套组件1就能轻型调节钻头的角度，从而实现电锤的单锤角度调节功能。
图7所示本发明单锤功能时的结构如图所示，此时的旋钮处于单锤位置时，如图8所示，止动片14的定位板16与旋钮26的半圆形凸块29半圆截面接触，旋钮26的旋转半径最小，止动片14在止动片弹簧13的弹力作用下向右移，止动片14的齿片15与大齿轮大端齿3啮合，四分之一圆形凸块28与锤档拨片22的接触面的旋转半径不变，锤档拨片22保持不动，锤档离合器9通过互相匹配的凹凸槽31、凹凸槽32与摆杆轴承11连接；椭圆形拨块27与拨片托19的旋转半径变化，偏离旋转心的椭圆形拨块27带动拨片托19向右移，钻档拨片17及齿轮离合器8在拨片托19的带动下向右移并脱离与小齿轮7的啮合，小齿轮7、大齿轮大端齿3、扭矩离合器5及转动套组件1处于空档传动状态，工作时，机输出轴电动一级轮12转动，一级轮12带动中间轴10转动，由于齿轮离合器8与小齿轮7完全分离，因此小齿轮7不传递转动力，大齿轮大端齿3、扭矩离合器5及转动套组件1不旋转，不实现钻的功能；中间轴10同时通过锤档离合器9带动摆杆轴承11，摆杆轴承11带动气缸组件6往复运动，推动气缸组件6里的气锤撞击冲锤，完成冲击能量的传递，从而实现电锤的单锤功能；止动片的齿片与大齿轮大端齿啮合可以锁定使转动套不旋转， 确保锤击时钻头角度不改变。
图9所示当旋钮转到单钻2功能位置时， 其结构如图10所示，止动片14的定位板16与旋钮26的半圆形凸块29的半圆面接触，旋钮26的旋转半径最大，止动片14的位置和锤钻功能时的位置相同，止动片14的齿片15与大齿轮大端齿3处于分离状态，小齿轮7与齿轮离合器8处于分离状态，小齿轮7与大齿轮大端齿3处于分离状态，旋钮26的椭圆形拨块27与拨片托19的接触面旋转半径发生变化，旋钮26的旋转半径最大， 偏离旋钮心的椭圆形拨块27带动拨片托19向右移，齿轮离合器8及钻档拨片17在拨片托19的带动下向右移，同时靠拨片托19与钻档拨片17之间的拉簧21拉住，是齿轮离合器8的外齿与大齿轮小端齿4啮合，齿轮离合器8与小齿轮7处于分离状态，四分之一圆形凸块28与锤档拨片22的接触面的旋转发生变化，锤档拨片22向左移，锤档离合器9在锤档拨片22的锤档拨叉23带动下脱离摆杆轴承互相匹配的凹凸槽31、凹凸槽32连接；工作时，机输出轴电动一级轮12转动，一级轮12带动中间轴10转动，中间轴10通过齿轮离合器8、大齿轮小端齿4及扭矩离合器5带动转动套组件1旋转，完成旋转力的传递；锤档离合器9与摆杆轴承11处于分离状态，因此摆杆轴承11不带动气缸组件6往复运动，气缸组件里的气锤不实现撞击冲锤，不是锤的功能，从而实现单钻2的功能。
图11所示当旋钮转到单钻1功能位置时， 其结构如图12所示，止动片14的定位板16与旋钮26的半圆形凸块29的半圆面接触，旋钮26的旋转半径最大，止动片14的位置和锤钻功能时的位置相同，止动片14的齿片15与大齿轮大端齿3处于分离状态，小齿轮7与大齿轮小端齿4处于分离状态，旋钮26的椭圆形拨块27与拨片托19的接触面旋转半径发生变化，旋钮26的旋转半径变小，拨片托19的位置与锤钻功能时的位置相同，同时靠拨片托19与钻档拨片17之间的拉簧21拉住，是齿轮离合器8的外齿与大齿轮大端齿3啮合，四分之一圆形凸块28与锤档拨片22的接触面的旋转保持不动，锤档拨片22的位置与单钻2功能时的位置相同，锤档离合器9在锤档拨片22的锤档拨叉23带动下脱离摆杆轴承互相匹配的凹凸槽31、凹凸槽32连接；工作时，机输出轴电动一级轮12转动，一级轮12带动中间轴10转动，中间轴10通过齿轮离合器8、小齿轮7、大齿轮大端齿3及扭矩离合器5带动转动套组件1旋转，完成旋转力的传递；锤档离合器9与摆杆轴承11处于分离状态，因此摆杆轴承11不带动气缸组件6往复运动，气缸组件6里的气锤不实现撞击冲锤，不是锤的功能，从而实现单钻1的功能。

Claims (3)

  1. 一种轻型单钮多功能电锤，包括机体、电机、转动套组件、气缸组件、拨叉组件和旋钮；所述电机、转动套组件、气缸组件、拨叉组件位于机体内，所述旋钮与所述拨片组件联动，其特征在于：所述轻型单钮多功能电锤还包括大齿轮和传动机构，所述大齿轮包括大端齿和小端齿，所述大端齿呈大端多齿轮， 所述小齿端呈小端少齿轮；所述的扭矩离合器传动机构包括小齿轮、齿轮离合器、中间轴、锤档离合器、摆杆轴承和一级轮，小齿轮和中间轴是动配合，小齿轮与大齿轮大端齿啮合并与齿轮离合器的内齿配合，齿轮离合器与大齿轮小端齿啮合并与中间轴齿轴配合，齿轮离合器及锤档离合器与中间轴的齿轴动配合，摆杆轴承与中间轴动配合并通过摆杆与气缸组件连接，锤档离合器与摆杆轴承上设有匹配的凹凸槽，一级轮与中间轴紧配合；所述旋钮连接操作机构，所述操作机构与所述大齿轮大齿端、齿轮离合器和锤档离合器联动。
  2. 根据权利要求1所述的轻型单钮多功能电锤，其特征在于：所述的操作机构包括止动片弹簧、止动片、钻档拨片、拨片托、内旋钮、锤档拨片、拉簧、拨片弹簧和导柱，止动片弹簧、止动片、钻档拨片、拨片托、锤档拨片、拉簧、拨片弹簧依次设置在导柱上，止动片上设有跟与大齿轮大端齿匹配的止动齿片以及与内旋钮一侧定位，钻档拨片的另一侧扣接在拨片托上，钻档拨片与拨片托之间设有一个拉簧，拨片托的另一侧扣接在锤档拨片上，拨片弹簧设置在拨片托与锤档拨片之间，钻档拨片的拨片对应设置在齿轮离合器的两边，夹住齿轮离合器，锤档拨片上的锤档拨叉对应设置在锤档离合器的拨槽上。
  3. 根据权利要求2所述的轻型单钮多功能电锤，其特征在于：所述的旋钮一面设有偏离旋钮心的椭圆形拨块，椭圆形拨块设置在拨片托与锤档离合器扣接区域之间，椭圆形拨块上又设有四分之一圆形凸块，另一面设有半圆形凸块，半圆形凸块的外缘顶在止动片的定位板上。
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EP2527096B1 (en) 2018-12-19
CN101758486A (zh) 2010-06-30

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