WO2012010093A1 - Power tool - Google Patents

Abstract

A power tool (1), comprising: a casing (3); a motor (21) located inside the casing (3) and having an output shaft providing a rotation output; a planetary gear reduction system comprising a sun gear (45), a planet gear engaged with the output gear of the sun gear (45), an inner gear ring encircling the planet gear and having in an axial direction a first position where the inner gear ring is engaged with both the sun gear and the planet gear and a second position where the inner gear ring is engaged with the planet gear but away from the sun gear. The invention further comprises a moving end gear (77) with which the inner gear ring is engaged at the second position so as to allow the two to circumferentially lock with each other; and an optional rotation stopper which locks the circumferential rotating motion of the moving end gear (77). In the power tool, the arrangement and adjustment of the inner gear ring is simplified by the presence of a moving end gear that cooperates with the inner gear ring.

Description

 Description

 Power tools

 The present invention relates to a power tool, and more particularly to a power tool having an internal ring gear for speed switching.

Background technique

 Among the existing gun-drilling power tools, electric drills, electric screwdrivers, impact drills, impact wrenches, and the like are usually included.

 The electric screwdriver is used to tighten the screws onto the workpiece. It typically includes an overload clutch structure that is comprised of a clutch actuating member and a follower member that is integral with the reduction gear and that is rotatably secured 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. During operation, the torque of the motor is transmitted to the screwdriver through the planetary gear reduction mechanism, causing it to rotate, and the screwdriver head and the screw head groove are engaged, so that the screw is quickly tightened. As the screw is tightened, the resistance torque received on the active member increases rapidly, and an axial thrust is generated through the end teeth. When the resistance torque exceeds the preset value of the trip, the axial thrust forces the follower to further compress forward. The spring is separated from the active member. When the active member loses the support of the driven member, it is rotationally driven, so that the planetary gear reduction mechanism has no output, and the active member has a tendency to rotate with the motor output shaft, and then under the restoring force of the working spring. Engage again, so that the screw is no longer subjected to torque and the motor is still rotating. With this structure, the tightened screw achieves the specified tensile force without being pulled, and the motor does not overload, block, damage or burn.

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 output shaft, the static cam is fixed on the casing, and a spring is arranged between the moving and static cams to separate the two. When impact drilling is performed, the drill bit is vertically pressed onto the surface of the workpiece, and an appropriate pressure is applied in the axial direction, so that the dynamic and static cams mesh with each other against the spring force of the spring, and the motor is started, and the torque of the motor is transmitted to the static and static gears. Output shaft. During the rotation process, the output shaft generates an axial backward thrust to the static cam fixed relative to the casing, so that the impact drill moves backward. When the moving cam turns to the meshing gear, the impact drill moves back one tooth height. distance. At the moment of disengagement, due to the continuous applied axial force, the static cam quickly impacts the cam with the impact drill, thereby generating a strong impact force on the surface of the workpiece. As a result of this cycle, a continuous movement of the rotation plus the impact is produced. The brittle material breaks under repeated strong impact, as the drill rotates, The debris is discharged from the drill bit groove, and holes are made in the masonry and concrete members.

 Impact wrenches are primarily used to tighten bolts. The utility model has an active impact block, a passive impact block, etc., and the active impact block is rotationally driven by the output shaft of the gear reduction mechanism, and the passive impact block can be rotationally driven by meshing with the active impact block, and the passive impact block is arranged on the working shaft and is rotationally driven. a working shaft, wherein 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 Intermittent impact on the working shaft in the direction of rotation

 The electric drill is used to drill holes on the workpiece. During the operation, the drill shaft continuously rotates. Usually, users need to perform different types of operations, such as screwing, screwing, drilling, etc., when performing work. Currently, many drill-type power tools can also adjust the output speed to suit different operating conditions.

 Drilling power tools also typically have a planetary gear reduction system that reduces the high speed of tens of thousands of revolutions that the motor directly outputs to a lower speed suitable for drilling operations. Planetary gear reduction systems typically include a planet carrier, a planetary gear, a sun gear, an internal ring gear, etc., which combine to reduce the speed of the motor multiple times. Among the drill-type power tools, the planetary gears with 3 stages of deceleration are more common, because when the 3-stage reduction system is set, the reduction ratio of each stage of deceleration can be lower, and due to the large number of components and space, the function is switched, and the speed is switched. Other functions leave more design space, which is easier for manufacturing design.

 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. As a result, drilling power tools have begun to be integrated, and there are already multi-drive drills with screwdriver, drilling, high and low speed switching functions on the market.

U.S. Patent No. 6,142,242 (hereinafter referred to as the '242 patent) discloses a power tool that can optionally implement an electric drill, an electric screwdriver, and a hammer drill. The power tool has a function switching element, and by rotating the element to different circumferential positions, the functions of an electric drill, an electric screwdriver, and a hammer drill can be realized accordingly. Wherein, in the mechanism for realizing the electric screwdriver and other function switching, the casing is provided with an axially extending limiting block which can resist the clutch follower and the clutch driving member cannot be rotationally driven, and the function switching element is provided with A bump that can be axially mated with the restriction block. When the electric drill or the impact drill function is realized, the lug in the function switching element cooperates with the restriction block to make the restriction block abut against the clutch follower; when the electric screwdriver function is realized, the bump in the function switching element is disengaged from the restriction block Thus, the clutch actuating member can be rotationally driven to achieve the clutch function. U.S. Patent No. 6,457,535 B1 (hereinafter referred to as the '535 patent) discloses a similar clutch switching structure, which is selected by rotationally operating a function switching element outside the casing to axially move the clutch function limiting element inside the casing. Achieve electric screwdriver function. Currently, many drill-type power tools can also adjust the output speed to suit different operating conditions. High speed and low speed adjustments are achieved by rotating the speed control knob provided on the casing as shown in U.S. Patent No. 7,044,882 B2 (hereinafter referred to as patent '882 patent). The multi-function power tool shown in U.S. Patent No. 7,124,839 B2 (hereinafter referred to as patent '839 patent) further discloses speed adjustment and function switching through a common button. Among them, high and low speed adjustment is performed by moving the button along the axial direction of the casing when the electric drill function is realized, and switching between the functions can be realized by rotating the common button on the circumferential surface of the casing at a high speed. However, in the '839 patent, although the adjustment of the speed and the switching of the functions are realized by a common button, the adjustment direction of the button during the speed adjustment and the adjustment direction of the button when the function is switched are different, which causes inconvenience to the operation.

 There are still many shortcomings in the current multi-function drill.

 For example, the switching of the screwdriver function and the switching of the high and low speed functions all involve the change of the state of the internal gear. When switching between high and low speeds, the internal movement of the internal gear is often required to change the meshing relationship between the internal gear and the sun gear. When switching the screwdriver function, it is often necessary to lock or allow the rotation of the internal gums. The prior art requires two different internal spurs to perform the above two functional switching, respectively, and two internal spurs mean that it is difficult to further reduce the number of components, and the function switching mechanism is difficult to set. However, the current speed switching and the screwdriver function switching of the drill-type power tools are independent of each other, and the structure is complicated and the space is large.

 For another example, the switching structure of the impact wrench is currently complicated, which results in insufficient rotation transmission under the drilling function.

 For example, the power tools are moving toward miniaturization and multi-functionality. However, the planetary gear reduction system with three stages of deceleration takes up more space and affects the size of the whole machine. However, if the planetary gear system with two stages is decelerated, the deceleration of each stage is relatively low, and the rotational speed of the components is correspondingly accelerated, which leads to a decrease in life and instability of the whole machine, and functional design such as function conversion becomes difficult.

Summary of the invention

 It is an object of the present invention to provide a power tool having a simplified, easily adjustable function conversion system.

To achieve the above object, the technical solution of the present invention is: A power tool comprising: a housing; a motor, located in the housing, having an output shaft that provides a rotary output; a planetary gear reduction system, the speed planetary gear reduction system including the sun a wheel, a planet gear meshing with an output gear of the sun gear, surrounding an inner tooth of the planet gear, the inner tooth has a first position and a second position in an axial direction, wherein the first position is a tooth Simultaneously engaging the sun gear and the planet gear, and in the second position, the gingival meshes the planet gear, Disengaging the sun gear, the power tool further includes a movable end tooth, the inner ring gear meshing with the movable end tooth when being in the second position to lock each other in the circumferential direction; and optionally locking the movable end tooth The rotation of the circumferential rotation motion.

 Further, including an end tooth adjacent to the movable end tooth, an axially movable static end tooth, and an elastic member that presses the static end tooth toward the movable end tooth, the end face of the static end tooth and the movable end tooth abutting Each has a matching end tooth.

 Further, a torsion cover is provided, the screw is coupled to the screw cover in the torsion cover, the elastic member is a torsion spring connected to the screw cover, and the torsion cover can adjust the axial movement of the screw cover to adjust the The amount of compression of the torsion spring.

 Further, the function switching button is provided, and the function switching button drives the rotation of the rotation preventing member to be selectively located in the first position and the second position, wherein the rotation of the rotation end tooth is locked in the first position Movement, in the second position the rotation member allows a circumferential rotational movement of the movable end teeth.

 Further, one end surface of the movable end tooth is provided with a plurality of circumferentially distributed key grooves, and the rotation preventing member is axially movable to be selectively located at the first position and the second position. The key groove is engaged at the end of the first position rotation preventing member, and the end of the rotation member at the second position is disengaged from the key groove.

 Further, a switching ring is disposed on which a screwdriver switching slot is disposed, and the rotation preventing member is provided with a pin located in the screwdriver switching slot, and the function switching button drives the switching ring to rotate to drive the The pin moves axially, causing the rotation member to move axially between the first position and the second position.

 Further, the function switching button drives the inner ring gear to move axially to be selectively located at the first position and the second position.

 Further, in the second position of the ring gear, the movable end teeth and the inner ring gear are engaged by a spline structure.

 Compared with the prior art, the power tool of the present invention simplifies the setting and adjustment of the ring gear by providing the movable end teeth that cooperate with the inner ring gear.

 Another object of the present invention is to provide a power tool having a combined speed and screwdriver switching mechanism.

To achieve the above object, the technical solution of the present invention is: a power tool comprising: a housing; a motor, located in the housing, having an output shaft that provides a rotary output; a planetary gear reduction system that outputs the rotation of the output shaft Rotary output after deceleration; power output system, including spindle driven by planetary gear reduction system; function switching mechanism, optional setting power tool in high speed drilling function, low speed drilling function, screwdriver function, said power tool Including speed and screwdriver switching components, The speed and screwdriver switching assembly comprises: an inner ring gear, wherein the inner ring gear can be axially moved by the function switching mechanism to adjust the output speed of the planetary gear reduction system; the movable end tooth is connected to the inner ring gear with a relatively rotational locking; The static end tooth presses the movable end tooth; the function switching mechanism is connected to the rotation stop member, and the rotation preventing member is moved between a position at which the movable end tooth is restricted to rotate and a position at which the movable end tooth is released.

 Further, under the high-speed drilling function, the inner ring gear is located at a first position in the axial direction, in which the ring gear simultaneously meshes the sun gear and the planetary gear, and the rotation preventing member is located away from a position of the movable end tooth; the low-speed drilling function, the inner ring gear is located at a second position in the axial direction, in which the ring gear engages the planetary gear to disengage from the sun gear; The inner ring gear is located at a second position in the axial direction, and the rotation preventing member is located at a position for restricting rotation of the movable end teeth.

 Further, the function switching mechanism includes a function switching button mounted on the housing and a switching ring disposed in the housing, wherein the switching ring is provided with a stepped speed switching slot and a stepped screwdriver switching slot. A speed switching member is mounted in the speed switching slot, and the speed switching member can slide in the speed switching slot to drive the inner ring gear to move axially; the rotation preventing member is installed in the screwdriver batch switching slot, and the rotation preventing member can be Sliding in the screwdriver change slot to move axially between the position that restricts the end tooth rotation and the position where the end tooth is disengaged

 Further, the inner ring gear and the movable end tooth are respectively provided with matching splines to be rotationally locked and connected to each other.

 Further, the movable end tooth is provided with a key groove, and the end of the rotation stop member can be embedded in the key groove to lock the rotational movement of the movable end tooth.

 Further, the opposite end faces of the movable end teeth and the static end teeth are respectively provided with matching teeth, and when the rotation preventing member is located at the position of the disengaged end teeth, the movement is performed when the torque on the main shaft reaches a predetermined value. The end teeth and the stationary end teeth rotate relative to each other.

 Further, the torsion cover is provided with an elastic member between the torsion cover and the static end tooth, and the torsion cover can adjust the compression amount of the elastic member.

Further, the power output system includes an impact mechanism including an active impact block that is rotationally driven by the main shaft, a passive impact block that is rotatably driven by the active impact block, and is connected to the passive impact block, and is driven by the passive impact block. a working shaft, wherein 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 The working axis is intermittently impacted in the direction of rotation, and the function switching mechanism is also connected to the impact wrench switching mechanism, and the impact mechanism can be selected or locked, and the optional power tool is in the impact wrench function. Further, the impact switching mechanism includes a clutch member, and the clutch member is driven by the function switching mechanism to selectively establish or cut a rigid rotation transmission connection from the main shaft to the active impact block, and the clutch member is rotationally locked. The main shaft, the clutch member and the active impact block are relatively axially movable, each of which is provided with an interlocking interlocking element that is coupled to each other in a selectively rotationally lockable manner.

 Further, the planetary gear reduction system includes a planetary frame fixedly coupled to the main shaft to output a rotational motion, and the clutch member is slidably mounted on the main shaft or the carrier by a sliding rail.

 Further, the switching ring is provided with a stepped impact wrench switching slot, and the switching slot is equipped with an impact wrench switching member, and the impact wrench switching member is connected with the clutch member, and can be moved in the impact wrench switching slot to drive The clutch member moves axially.

 Compared with the prior art, the power tool of the present invention has a combined speed and a screwdriver switching mechanism, which reduces the number of components and saves internal space.

 Another object of the present invention is to provide a power tool having a two-stage planetary gear reduction system that can be long-lived and stable in operation.

 To achieve the above object, the present invention provides a power tool comprising: a housing; a motor, a motor output shaft having an output rotary motion, a motor output shaft end being a gear; a planetary gear reduction system, the speed planetary gear reduction system including along a two-stage speed reduction mechanism in which the motor output shafts are arranged in the axial direction, the first stage speed reduction mechanism is disposed on a side close to the motor in the axial direction, and the second stage speed reduction mechanism is disposed on a side close to the main shaft in the axial direction; The first stage speed reduction mechanism comprises: a first planet carrier; a plurality of first stage planetary gears, wherein the first stage planetary gears are arranged along the circumferential direction of the first planet carrier and mesh with the motor output shaft; the first inner ring gear surrounds the first a first-stage planetary gear, the inner tooth meshes with the first-stage planetary gear; the sun gear rotates along the first planet carrier, and has a sun gear output shaft; the second-stage speed reduction mechanism includes: a second-stage planetary carrier; a second-stage planetary gear Installed on the second stage planet carrier to engage with the sun gear output shaft; the second inner ring gear surrounds the second stage planetary gear, The inner tooth and the second stage planetary gear mesh with the main shaft; the chuck, the number of teeth of the first stage planetary gear is larger than the number of teeth of the gear of the motor output shaft.

 Further, the motor output shaft includes an axially disposed shaft seat and an output gear, the axle seat length being greater than the output gear length, and the first planet carrier correspondingly includes a base and a planet carrier portion, The base is set on the axle seat.

 Further, a support is disposed between the base and the shaft seat.

 Further, the first ring gear is fixedly disposed relative to the casing.

Further, the first ring gear is movable between a first position and a second position in the axial direction. In the first position, the first ring gear is circumferentially fixed and does not mesh with the first carrier. In the second place The first ring gear simultaneously engages the first stage planetary gear and the sun gear, and is movable in the circumferential direction. Further, the second ring gear is fixedly disposed relative to the casing.

 Further, the second ring gear is movable between a first position and a second position in the axial direction, and in the first position, the second ring gear simultaneously engages the second stage planetary gear and the sun gear, The circumference is movable; in the second position, the second ring gear is circumferentially fixed and does not mesh with the first carrier.

 Further, the ratio of the number of teeth of the first stage planetary gear to the output shaft gear of the motor is greater than 2.

 Compared with the prior art, the power tool of the present invention improves the stability of the planetary gear system by increasing the number of teeth of the first stage planetary gears and setting a larger gear rotation support.

 SUMMARY OF THE INVENTION An object of the present invention is to provide a power tool having a function switching button that can switch between an impact wrench function and other functions, as well as speed adjustment, thereby improving the ease of operation.

 To achieve the above object, the technical solution of the present invention is: a power tool comprising: a housing; a motor, located in the housing, having an output shaft that provides a rotary output; a planetary gear reduction system that outputs the rotation of the output shaft a deceleration-rotating output; a power output system that transmits a rotary output of the planetary gear reduction system to the working head; a function switching button that is at least partially housed in the housing, the function switching button moves to select an impact wrench function of the power tool, One of the high speed drill function, low speed drill function, and screwdriver function.

 Further, the function switching button has a first position, a second position, a third position and a fourth position which are sequentially arranged along the circumferential direction of the housing, and the function switching button can be sequentially moved from the first position to the fourth position. Or moving from the fourth position to the first position, the power tool is in the impact wrench when the function switch button is in the first position, the power switch is in the second position, the power tool is in the high speed drill function, and the function switch button is located at the first position. The three-position power tool is in the low-speed drilling function, and the function switching button is located in the fourth position, and the power tool is in the screwdriver function.

 Further, the function switching button is selectively located in the first position, the second position, the third position and the fourth position, and the power tool is in the impact wrench function when the function switching button is in the first position, and the function switching button is located at the first position The two-position power tool is in a high-speed drilling function, the function switching button is located in the third position, the power tool is in the low-speed drilling function, the function switching button is located in the fourth position, the power tool is in the screwdriver function, the first position and the second position The third position and the fourth position are located on the same circumferential line of the housing, and the projection to the horizontal plane is in a straight line.

Further, the speed planetary gear reduction system includes an inner ring gear, and the inner ring gear is at a first position for causing the planetary gear reduction system to output a high rotation speed and a second position for causing the planetary gear reduction system to output a low rotation speed. Movable therebetween; the power output system includes a clutch member movable between a first position limiting the function of the impact wrench and a second position allowing the impact wrench function; the function switching button connecting the rotation stop member The rotation stop is movable between a first position limiting the function of the screwdriver and a second position allowing the function of the screwdriver; the function switching button is further connected to the ring gear and the clutch to operatively select the power tool Impact wrench function, high speed drill function, low speed drill function and screwdriver function.

 Further, in the function of the impact wrench, the clutch member is in the second position; in the high-speed drilling function, the inner ring gear is in the first position, the clutch member is in the first position; and in the low speed drilling function, the inner portion The ring gear is in the second position, the clutch member is in the first position, the rotation preventing member is in the first position; in the screwdriver function, the inner ring gear is in the second position, the clutch member is in the first position, and the rotation preventing member is located in the first position Two locations.

 Further, in the function of the impact wrench, the inner ring gear is in the first position, the screwdriver function is in the first position; and in the high speed drilling function, the screwdriver is in the first position.

 Further, the planetary gear reduction system includes a sun gear and a planetary gear meshed with an output gear of the sun gear, wherein the inner ring gear simultaneously meshes the sun gear and the planetary gear with the ring gear in the first position The high rotational speed is output, and in the second position, the ring gear engages the planetary gear, and the sun gear is disengaged to output a low rotational speed.

 Further, the power output system includes a main shaft, an active impact block assembled on the main shaft by a V-shaped groove ball mechanism, and the clutch member is coupled to the main shaft, and is axially movable relative to the main shaft and is not rotatable relative to the main shaft. The active impact block is snapped at the first position to directly output the rotation of the main shaft to the active impact block, and the clutch member is disengaged from the active impact block at the second position.

 Further, further comprising a movable end tooth, the inner ring gear meshing with the movable end tooth when being in the second position to lock with each other in the circumferential direction, and the rotation preventing member selectively locks the circumferential rotational movement of the movable end tooth .

 Further, one end surface of the movable end tooth is provided with a plurality of circumferentially distributed key grooves, and the rotation preventing member engages the key groove at an end of the first position rotation preventing member, in the second position The end of the rotation stop is disengaged from the keyway.

DRAWINGS

 The invention will now be described in further detail with reference to the accompanying drawings.

 1 is a front view of a functional drill of a specific embodiment of the present invention

 2 is a top plan view of an evening functional drill in accordance with an embodiment of the present invention.

 Figure 3 is a cross-sectional view showing the front view of the evening functional drill according to a specific embodiment of the present invention.

Figure 4 is a cross-sectional view of the evening functional drill in a plan view of a specific embodiment of the present invention. Figure 5 is an exploded perspective view of a multi-function drill in accordance with an embodiment of the present invention.

Figure 6 is a perspective view of a gearbox of a multi-function drill in accordance with an embodiment of the present invention.

Figure 7 is a perspective view of a second ring gear of the multi-function drill of the embodiment of the present invention.

FIG. 8 is a perspective view of a multi-function drill with respect to an impact wrench switching portion mechanism according to an embodiment of the present invention. FIG. 9 is a perspective view of a mechanism for switching a portion of a multi-function drill with respect to a screwdriver according to an embodiment of the present invention. FIG. 10 is a schematic diagram of a switching ring of an impact wrench function of a function drill according to an embodiment of the present invention. Figure 11 is a top cross-sectional view showing the function of the impact wrench of the evening function drill of the embodiment of the present invention. Fig. 12 is a schematic view showing a switching ring of a high-speed drilling function of a function drill according to an embodiment of the present invention. Figure 13 is a top cross-sectional view of the high-speed drilling function of the evening functional drill according to the embodiment of the present invention. Figure 14 is a schematic view of the switching ring of the low-speed drilling function of the evening functional drill according to the embodiment of the present invention. Figure 15 is a top cross-sectional view showing the low-speed drilling function of the evening functional drill according to the embodiment of the present invention. Figure 16 is a schematic view of the switching ring of the screwdriver function of the evening functional drill according to the embodiment of the present invention. Figure 17 is a front cross-sectional view showing the screwdriver function of the evening function drill according to an embodiment of the present invention. Multi-function drill 255 Gasket 531 Spline

Housing 27 shaft seat 533 ring groove

Handle 29 output gear 61 spindle

Battery pack 31 Gearbox 63 Active impact block Chuck 33 Front case 631 Inner V-groove Axis 35 Rear case 633 ■ End tooth

Switch 37 middle cover 635 clutch groove

Torque cover 39 bearing 65 impact spring

Directional button 41 First planet carrier 611 Outer V-groove Function toggle button 411 Base 67 Roller

Switching spring 413 Planetary support shaft 69 Passive impact block Top column 43 First planetary gear 691 Working shaft

Switch window 45 sun gear 693 second end tooth

Motor 47 second planet carrier 695 housing slot

Inner output shaft 473 slide rail 70 bearing

Outer output shaft 49 second planet gear 71 screw cover

Bracket 51 first inner ring gear 711 stud

Bushing 53 second inner ring gear 73 torsion spring 75 static end teeth 81 switching ring 871 spring

 751 column 811 impact wrench switching slot 89 clutch

 753 end teeth 813 speed switching slot 891 ring groove

 77 moving end teeth 815 screwdriver change slot 893 slider

 771 keyway 83 Impact wrench switcher 895 Clutch

 773 end tooth 85 speed switch

 775 internal spline 87 screwdriver changer

Detailed ways

 1 to 17 show a specific embodiment of the power tool of the present invention, which is specifically a multi-function drill 1. Multi-function drill 1 has impact wrench function, high-speed drilling function, low-speed drilling function, screwdriver function, among which high-speed drilling function and low-speed drilling function can also be collectively referred to as drilling function.

 As shown in FIG. 1, the multifunctional drill 1 is similar to a pistol shape, and includes a substantially cylindrical casing 3, a handle 5 disposed at an angle to the casing 3, and a detachable battery pack 7 disposed at the bottom of the handle 5. . The housing 3 has a longitudinal axis 10.

 The front end of the housing 3 is provided with a collet 9 for holding the working head for respectively clamping different working heads (not shown) when the multifunctional drill 1 realizes different functions, such as when the impact wrench function is realized Hold the fastening head and hold the twist drill when implementing the high speed drilling function or the low speed drilling function. A torsion cover is provided on the outside of the collet 9. The torsion cover 13 is rotatable about the axis 10 to adjust the maximum output torque of the multi-function drill 1 in the screwdriver function. The upper end portion of the handle 5 is provided with a switch 11 for opening and closing the multi-function drill 1. A reversing button 15 is also provided at the intersection of the handle 5 and the housing 3. The multi-function drill 1 has two reversing buttons 15, one on each side of the housing.

 Referring to Figures 1 and 2, the top of the casing 3 is provided with a function switching button 17, and the function switching button 17 is disposed in the switching window 19 which is located at the top of the casing 3 and extends circumferentially. The switching window 19 is arranged in four circumferential positions from one end to the other in the circumferential direction. The function switch button 17 can be moved between the four preset positions, and the multi-function drill 1 is sequentially placed in the impact wrench function, the high-speed drill function, the low-speed drill function, and the screwdriver function. A mark is provided on the switching window 19 or at a corresponding position of the casing 3 to indicate the four preset positions and their corresponding functions.

 The internal structure of the multi-function drill 1 is described in detail below.

As shown in Fig. 3, one end of the housing 3 on which the collet 9 is located is the front end, and the other end is the rear end. The rear end of the casing 3 houses a power source, specifically a DC motor 21. The motor 21 has an output shaft to output a rotational motion. In the present embodiment, the output shaft includes an inner output shaft 23 and an outer output shaft 25. Internal loss The output shaft 23 is rotated by the motor 21, and the outer output shaft 25 is fitted to the inner output shaft 23 via an interference fit, and is rotatable by the inner output shaft 23. The outer output shaft 25 has a front and a rear that extend longitudinally. The outer output shaft 25 includes a shaft seat 27 and an output gear 29, the shaft seat 27 is located at the rear of the outer output shaft 25, and is fitted on the inner output shaft 23; the output gear 29 is located at the front of the outer output shaft 25 for passing the gear structure. The power rotation of the motor 21 is output to the deceleration system of the multi-function drill 1. The shaft seat 27 is longer in length and diameter than the output gear 29.

 The output shaft extends into the gear case 31. The housing of the gear case 31 includes a front case 33 and a rear case 35 which are fastened to form a receiving space, and house a planetary gear reduction system and a power output system.

 3, FIG. 4, FIG. 5, the planetary gear reduction system is a two-stage reduction system, specifically including a first planet carrier 41, a first planet gear 43, a sun gear 45, a second planet carrier 47, and a second planet gear 49. And two inner ring gears, respectively a first inner ring gear 51 and a second inner ring gear 53.

 The first planet carrier 41 includes a cylindrical base 411 and a plurality of circumferentially evenly spaced planet wheel fulcrums 413 disposed on the end faces of the base.

 The center of the base 411 is a through hole through which the base 411 is mounted and supported on the shaft seat 27 of the output shaft. A support system is further disposed between the base 411 and the axle seat 27, and specifically includes a stepped bracket 251 disposed outside the motor output shaft, and a bushing disposed between the bracket 251 and the inner wall of the through hole of the base 411. 253 and a spacer 255 disposed between the rear end of the base 411 and the bottom of the inner wall of the gear case. The support system is such that the first planet carrier 41 can rotate well relative to the axle block 27. It should be noted that in the present embodiment, most of the base 411 of the first planet carrier is supported on the axle seat 27, and the length of the axle seat 27 is long, that is, the supported component of the first planet carrier 41. The length of the effective support is long, which makes the first planet carrier 41 stable, long-time high-speed rotation without significant wear or failure.

 A planetary gear support shaft 413 projects from the front end of the base 411, and a first planetary gear 43 is mounted on each of the planetary gear support shafts 413. In the present embodiment, the number of the planetary gear support shaft 413 and the planetary gear 43 corresponds to three. The first planetary gear 43 meshes with the output gear 29, and is driven to rotate about the planetary gear support shaft 413. The first planet gear 43 simultaneously meshes with the internal teeth of the first ring gear 51. The first ring gear 51 is fixedly disposed with respect to the gear case 31.

The end of the planetary gear support shaft 413 projects to the front of the first planetary gear 43. The sun gear 45 includes a gear plate and a gear shaft. The gear plate and the gear shaft are provided with teeth on the circumferential surface. A plurality of holes are formed in the gear plate, and their positions and numbers correspond to the positions and numbers of the planetary gear supports 413 to mount the sun gear 45 to the end of the planetary gear support shaft 413. Surrounded by the gear shafts are arranged a plurality of second planet gears 49 that mesh with the gear shaft. The specific number of the second planetary gears 49 is five, which is the pair of the second planet carrier 47. The number of planet wheels should be on the fulcrum. The second planet carrier 47 is fixedly coupled to the power take-off system.

 A second ring gear 53 is provided on the outer side in the radial direction of the sun gear 45 and the second planet gear 49. Further, the end teeth of the sun gear 45 and the second planetary gear 49 can be engaged with the internal teeth of the second ring gear 53. The second ring gear 53 is axially movable back and forth with respect to the gear case 31, and has a front position and a rear position. In the front position, the second ring gear 53 and the second planet gear 49 mesh, and are disengaged from the sun gear 45; and in the front position, the second ring gear 53 cannot be rotated, i.e., fixed in the circumferential direction relative to the gear box. In the rear position, the second ring gear simultaneously engages the end teeth of the second planetary gear 49 and the gear ring of the sun gear 45; and the rear position of the second inner ring gear is rotatable about the axis 10, that is, the circumference is movable relative to the gear box .

 The deceleration process of the planetary gear reduction system is described in detail below.

 Referring to FIG. 3, FIG. 4, FIG. 5, FIG. 6, FIG. 9, the output shaft of the motor 21 rotates, and the first planetary gear 43 rotates around the planetary support shaft 413 while the first planetary gear 43 is along the first inner ring gear. The annular internal tooth of 51 crawls and revolves around the axis 10 revolutions. The revolution of the first planet gear 43 causes the first planet carrier 41 to rotate about the axis 10. The sun gear 45 is coupled to the first planet carrier 41 via three planet wheel fulcrums 413 and thus rotates with the first planet carrier 41. The above is the first stage deceleration process of the planetary gear reduction system. In this process, the high-speed rotation of the output shaft output is initially lowered by the first planetary gear 43 by the inverse ratio of the number of teeth of the output gear 29 of the output shaft and the number of teeth of the first planetary gear 43, in this embodiment. The gear ratio of the output gear 29 and the first planetary gear 43 is 7:18. In order to achieve a superior deceleration effect, the gear ratio should preferably be less than 1:2. Setting a smaller gear ratio reduces the rotational speed of the first planetary gear 43, further improving the stability of the deceleration system, and at the same time, providing a longer axle seat 27 not only improves the stability of the support, but also makes the first planetary gear 43 Provided in a relatively forward position in the gear case 31, the front position is larger than the bottom of the gear case, and the space in the radial direction is larger, which also makes the larger first planetary gear 43 larger, and thus more It is possible to obtain a smaller gear ratio in the end. During this process, the first planet gear 43 revolves around the axis 10, causing the first planet carrier 41 and the sun gear 45 to rotate a second time to reduce the rotational output speed to the power take-off system.

After the rotational motion is output to the sun gear 45, there are two deceleration situations depending on the two positions of the front and rear of the second ring gear 53. When the second ring gear 53 is in the front position, the second ring gear 53 is selectively not rotated and disengages from the sun gear, so that the gear shaft of the sun gear 45 drives the second planet gear 49 around the planet gear of the second planet carrier 47. The fulcrum rotates and crawls on the internal teeth of the second ring gear 53 to revolve around the axis 10, thereby driving the second planet carrier 47 to rotate about the axis 10, transmitting rotational motion to the power take-off system. This process forms the second stage of deceleration of the planetary gear reduction system. When the second ring gear 53 is in the rear position, the second ring gear 53 can rotate and simultaneously engage the gear disk of the sun gear 45 and the second planet gear 49. Therefore, the sun The rotation of the wheel 45 is transmitted to the second planetary gear 49 and the second carrier 47 through the second ring gear 53, and the second stage deceleration is canceled.

 In summary, the planetary gear reduction system of the present embodiment can output two different rotational speeds. However, it is possible to modify the planetary gear reduction system to provide more different speed outputs. For example, the first ring gear 51 is disposed to have a front position and a rear position similar to the second ring gear 53, so that it is possible to selectively engage the first planet gear 43 and the sun gear 45 at the same time, or only engage the first The planetary gears 43 are then combined with the front and rear positional relationship of the first inner ring gear 51 and the second inner ring gear 53, that is, at least three kinds of rotational speed outputs can be provided, and the specific arrangement and combination thereof are based on the above-described ideas by those skilled in the art. It is easy to design and will not be described here.

 The joint portion of the front case 33 and the rear case 35 is further provided with a middle cover 37 which divides the gear case 31 into front and rear portions, the rear portion mainly accommodates the planetary gear reduction system, and the front portion mainly accommodates the power output system. The inner cover 37 has an inner ring to which a bearing 39 is mounted, and a bearing 39 supports the second carrier 47.

 The power output system of this embodiment will be described in detail below.

 3, FIG. 4, FIG. 5, FIG. 7, FIG. 8, as previously described, the second planetary gear 47 is fixedly coupled to the power take-off system. Specifically, the second planet carrier 47 and the main shaft 61 are fixed by an interference fit. In connection, the main shaft 61 always follows the rotation of the second carrier 47.

 The power output system includes a set of active impact blocks 63 disposed on the main shaft 61, an impact spring 65 disposed between the active impact block 63 and the second planet carrier 47, and a roller ball at the junction of the active impact block 63 and the main shaft 61. a V-groove impact mechanism, wherein the impact mechanism includes an outer V-shaped groove 611 formed on the surface of the main shaft 61, and a rolling ball 67 which is rotatable in the outer V-shaped groove 611, in the present embodiment, a steel ball, and The inner ring of the active impact block 63 is for receiving the inner V-shaped groove 631 of the ball 67. A pair of first end teeth 633 are radially symmetrically protruded from the front end surface of the active impact block 63. A washer and a gasket are provided between the impact spring 65 and the active impact block 63. The front end of the active impact block 63 is further provided with a passive impact block 69. The passive impact block 69 is provided with a pair of second end teeth 693 in a radially symmetric projection on the rear end surface opposite to the active impact block 63. The power take-off system also includes a working shaft 691 that extends out of the front end of the gearbox 31 and is coupled to the passive impact block 69. The front end of the working shaft 691 is provided with a receiving groove 695, which can accommodate the corresponding working head when the different functions are realized, and is fastened by the clamp 9 clamp. The collet 9 is set on the front end of the working shaft 691.

 The multi-function drill 1 of the present invention also has a torque control system for setting the maximum output torque of the power take-off system that is adjustable during the screwdriver function. The torque control system is detailed below.

Referring to Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 9, the torque control system includes a torsion cover 13, a spiral cover 71, a torsion spring 73, a stationary end tooth 75, and a movable end tooth 77. The torsion cover 13 is provided at the rear of the chuck 9 and outside the front case 33 of the gear case 31. A screw cover 71 is coupled to the torsion cover 13 by a threaded engagement. The spiral cover 71 is rotatable by the torsion cover 13 and moves back and forth along the axial direction of the axis 10. The spiral cover 71 has an annular casing and a plurality of projections 71 1 extending axially extending uniformly on the casing. A torsion spring 73 is mounted on the projection 7 11 . The housing is axially movable by the cooperation of the groove and the block, and is non-rotatably fitted on the front case 33. The protrusion 711 and the torsion spring 73, correspondingly at least partially extend into the corresponding plurality of axes on the front case 33 Into the hole.

 The middle cover 37 is provided with through holes corresponding to the plurality of axial holes described above. The stationary end tooth 75 is located in the rear portion of the gear case 33, and has an annular casing. The front end of the casing is provided with a plurality of columns 75 1 corresponding to the through holes, and the column 75 1 passes through the through hole of the middle cover 37. The torsion spring 73 on the stud 7 11 is abutted. A plurality of end teeth 753 are provided at the rear end of the housing. Since the column 751 passes through the through hole of the middle cover 37, the static end tooth 75 can move axially within a certain range, but cannot rotate. A movable end tooth 77 is provided at the rear of the stationary end tooth 75. The movable end tooth 77 has an annular housing, and the front end surface of the housing is provided with end teeth 773 matching the end teeth 753 of the static end teeth 75, and the rear end of the housing is provided with a key groove 77 1. The inner ring of the housing The surface is provided with an internal spline 775. The moving end teeth are immovable on the strike, and are optionally rotatable and non-rotatable in the circumferential direction.

 Through the adjustment of the function switching system, the multi-function drill 1 of the embodiment has the functions of an impact wrench, a high-speed drilling function, a low-speed drilling function, and a screwdriver function. The function switching system of this embodiment will be described in detail below.

 Referring to FIG. 3, FIG. 4, FIG. 5, FIG. 6, the function switching system mainly comprises a function switching button 17, a switching ring 8.1, a switching spring 17, a top column 173, an impact wrench switching member 83, a speed switching member 85, a screwdriver The switching member 87 is a clutch member 89.

 The function switching button 17 includes a dial located in the switching window 19 and a semicircular housing extending into the housing 3. The switching ring 8 is disposed under the housing of the function switching button 17, and the switching ring 8 1 is placed behind The casing 35 is rotatably rotated relative to the rear casing 35 about the axis 10 by the function switching button 17. The switching ring 81 has a notch on the ring surface through which the switching spring 17 1 and the top post 173 are disposed between the function switching button 17 and the rear case 35. The rear case 35 is provided with four recesses distributed in the circumferential direction, and the four recesses correspond to the aforementioned four preset positions of the function switching button 17, and when the top post 173 stays in a recess, the function switching button 17 Stay in a corresponding function position. That is, the operator can move the function switching button 17 to move circumferentially, and the top ring 173 drives the switching ring 8 1 to rotate. When moving to the recess, the switching spring 17 1 presses the top post 173 into the iHJ trap and tends to stay at the The iHJ is trapped, the operator perceives the elastic motion and knows to enter a functional gear position. When the function needs to be changed, the operator overcomes the elastic force of the switching spring 171 to drive the top post 173 away from the recess to enter another required recess, and The corresponding rotation of the switching ring 81 is driven.

The switching ring 8 1 is provided with a pair of impact wrench switching slots 8 11 , a pair of speed switching slots 813 and a screw The wire batch switches the groove 815. The two impact wrench switching grooves 811 can be overlapped by 180 degrees in the circumferential direction; the two speed switching grooves 813 can be overlapped by 180 degrees in the circumferential direction.

 The impact wrench switching groove 811 has a zigzag-shaped stepped shape, and the two segments are parallel to each other, and are axially spaced apart from the straight groove and the connecting groove between the two straight grooves. The straight grooves at both ends are perpendicular to the axis 10. The impact wrench switching member 83 is formed in a strip shape and is axially movable without being rotatable. A pin is disposed at one end thereof, and the pin is located in the impact wrench switching groove 811. Through the matching structure of the pin and the groove, when the switching ring 81 rotates, the pin moves from the straight groove to the other straight groove in the impact wrench switching groove 811. The impact wrench switching member 83 is driven to move axially.

 The other end of the impact wrench switching member 83 is bent toward the radially inner side of the gear case 13 to form a hook which is hooked into the ring groove 891 on the clutch member 89. The clutch member 89 is fitted outside the second carrier 47, the casing is formed in a ring shape, and the ring groove 891 is located on the outer peripheral surface thereof. A slider 893 is provided on the inner peripheral surface of the clutch member 89, and a clutch block 895 is provided on the front end surface. The outer peripheral surface of the second carrier 47 is provided with a slide rail 473 matched with the slider 893, and thus the clutch member 89 thus always rotates following the second carrier 47, and is axially movable relative to the second carrier 47. A clutch groove 635 is provided on the rear end surface of the active impact block 63 to match the clutch block 895. With the foregoing structure, the clutch member 89 has a front position and a rear position in the axial direction. In the front position, the clutch block 895 catches the clutch groove 635, and in the rear position, the clutch block 895 is disengaged from the clutch groove 635. The clutch member 89 is moved by the function switching button 17 through the switching ring 81, and the impact wrench switching member 83 is moved between the front position and the rear position.

 Similarly, the speed switching groove 813 is a meandering stepped shape consisting of two segments parallel to each other, axially spaced apart from the straight groove and a connecting groove between the two straight grooves. The straight grooves at both ends are perpendicular to the axis 10. The speed switching member 85 is in the form of a strip and is axially movable without being rotatable. A pin is disposed on one end thereof, and the pin is located in the speed switching slot 813. When the switching ring 81 rotates, the pin moves from the straight slot to the other straight slot in the speed switching slot 813, and the speed is switched. The piece 85 moves axially.

 The other end of the speed switching member 85 is bent toward the radially inner side of the gear case 13 to form a hook, which is hooked into the ring groove 533 of the outer peripheral surface of the second ring gear 53. The front end face of the second ring gear 53 is further provided with a spline 531 which matches the inner spline 775 of the movable end tooth 77. As previously mentioned, the second ring gear 53 has a front position and a rear position, respectively corresponding to two speed outputs. With the above structure, the second clutch member 53 is moved by the function switching button 17 through the switching ring 81, and the speed switching member 85 is moved between the front position and the rear position.

The screwdriver changeover groove 815 has an irregular shape having a step, and has a wide portion and a narrow portion in the circumferential direction, and the front end of the narrow portion is axially rearward behind the front end of the wide portion. There is a transition between the wide portion and the narrow portion. The screwdriver changer 87 is strip-shaped and can be moved axially without rotation. One end has a screw batch switching slot 815 A pin 871 is further disposed between the end and the gear case. The spring 871 drives the screwdriver changer 87 to abut the front end of the screwdriver change slot 813. The other end of the screwdriver changer 87 is matched with the key groove 771 of the movable end tooth 77. Through the cooperation structure of the pin and the groove, when the switching ring 81 rotates, the pin moves in the wide portion of the screwdriver change groove 815 to the narrow portion or the wide portion that moves from the narrow portion, and drives the screwdriver switch 85 to move axially. The screwdriver changer 85 thus has a front position and a rear position in the axial direction. In the front position, the end of the screwdriver changer 85 engages the key groove 771 of the movable end tooth 77, and in the rear position, the end of the screwdriver changer 85 is disengaged. The key groove 771 of the end tooth 77. In this way, the rotational movement of the movable end tooth 77 can be selectively locked.

 The function switching process of the multifunctional drill 1 is detailed below.

 As mentioned above, the multi-function drill 1 can be switched forward or reverse between the impact wrench function, the high-speed drilling function, the low-speed drilling function, and the screwdriver function. The conversion of these functions is closely related to the front and rear positions of the second ring gear 53, the clutch member 89 and the screwdriver shifting member 87. Table 1 shows the four functional states and the second ring gear 53, the clutch member 89 and the screw in the foregoing four functional states. The correspondence of the respective positions of the batch switching members 87.

 Table I

 With the impact wrench function as the initial state, as shown in FIG. 10 and FIG. 11, the function switching button 17 is in the impact wrench position, the second ring gear 53 is in the rear position, the clutch member 89 is in the rear position, and the screwdriver switch 87 is in the front position. .

 As described above, when the second ring gear 53 is in the rear position, the sun gear 45 and the second row star wheel 49 are simultaneously engaged, and the planetary gear reduction system outputs a high rotation speed to the power output system. At this time, the splines 531 of the second ring gear 53 and the inner splines 775 of the movable end teeth 77 are disengaged from each other, and the second ring gear 5 can be rotated by the sun gear 45. At this time, the screwdriver changer 87 is in the front position, and the end thereof is engaged with the key groove 771 of the movable end tooth 77, and the movable end tooth 77 is prohibited from rotating. However, since the movable end tooth 77 does not function at this time, it is also possible to set the screwdriver cutting member 87 to be in the rear position in the functional state, and the function of the impact wrench is not affected.

 The clutch member 89 is in the rear position under the impact wrench function, i.e., the clutch block 895 of the clutch member 89 is disengaged from the clutch groove 635 of the active impact block 63.

When the impact wrench function is implemented, the rotational motion is output to the main shaft 61 via the second carrier 47, At the pressure of the impact spring 65, the active impact block 63 is driven by the ball 67 clamped in the inner V-shaped groove and the outer V-shaped groove 611, and follows the rotation of the main shaft 61, and the passive impact block 69 also rotates, passing through the working shaft 691 and the clamp. The head 9 drives the working head (not shown). Quickly tighten the nut (not shown).

 When the nut end face is in contact with the surface of the workpiece (not shown), the resistance torque rapidly increases. After reaching a certain value, the intermeshing active impact block 63 and the passive impact block 69 are both blocked, and the passive impact block 69 stops rotating, but the spindle 61 is at The motor output shaft is still driven to rotate, forcing the ball 67 to roll along the groove against the frictional force between the inner V-shaped groove and the outer V-shaped groove 611, thereby pushing the active impact block 63 to move rearward, so that the impact spring 65 is compression. Thereby, the active impact block 63 gradually moves away from the passive impact block 69 in the axial direction. When the axial movement distance of the active impact block 63 just exceeds the tooth height of the second end tooth 693 of the passive impact block 69, that is, the moment when the active impact block 63 and the passive impact block 69 are disengaged, the main shaft 61 drives the active impact block 63 to rotate. The first end tooth 633 is slid over the second end tooth 693 of the passive impact block 69. At the moment of sliding, the ball 67 is returned along the inner V-shaped groove and the outer V-shaped groove 611 due to the action of the impact spring 65. In the original position, the active impact block 63 is pushed forward, and at the same time, as the spindle 61 accelerates and rotates, the second end tooth 693 of the passive impact block 69 is struck, so that the passive impact block 69 continues to move in the rotational direction, thus reciprocating and reciprocating. The pieces are tightened under impact force 1⁄2.

 When the impact wrench function is implemented as described above, the active impact block 63 is required to intermittently vibrate the passive impact block 69, so that the working head (fastening head) can tighten the nut, but when the drilling function, that is, the high speed drilling function and the low speed drilling function, is realized, Only the working head (twist drill) is required to continue drilling, and the intermittent impact of the active impact block 31 is no longer required. The process of switching from the impact wrench function to the high-speed drilling function and the working state of the high-speed drilling function are detailed below.

 Referring to FIG. 10, FIG. 11 and FIG. 12, FIG. 13, when switching from the impact wrench function to the high-speed drilling function, the switching ring 81 rotates to drive the impact wrench to switch the slot 811 displacement, and the pin of the impact wrench switching member 83 is from a straight slot. Moving to the other straight groove, the impact wrench switching member 83 is axially moved, thereby driving the clutch member 89 to move from the rear position to the front position. After the switching is completed, the second ring gear 53 is in the rear position, the clutch member 89 is in the front position, and the screwdriver switch 87 is in the front position.

 Since the movable end teeth 77 are not functioning at this time, it is also possible to set the screwdriver changer 87 in the rear position in the functional state without affecting the realization of the high speed drilling function.

As described above, when the clutch member 89 is in the front position, the clutch member 895 engages the clutch groove 635 of the active impact block 63, and the transmission path of the rotary output becomes the second planetary gear 47 and/or the main shaft 63 to the clutch member. 89 to the active impact block 63, and then transmitted to the working shaft 691 via the passive impact block 69. Specifically, during the drilling process, since the resistance torque of the working shaft 691 is gradually increased, the active impact block 63 tends to Moving toward the motor 11. At this time, since the clutch member 89 restricts the backward movement of the active impact block 63 in the axial direction, the first end tooth 633 of the active impact block 63 always fits the second end tooth 693 of the passive impact block 69, and at the same time, the active impact The block 63, the passive impact block 69, and the working shaft 691 move together in the direction of rotation. Since the passive impact block 69 and the active impact block 63 are always unable to be disengaged, that is, an impact cannot be formed between the two, it is ensured that the working head continues to drill.

 In the above embodiment, it is particularly important that: when the high-speed drilling or low-speed drilling function is realized, the rotation outputted by the motor 21 is decelerated to reach the output end 22 of the deceleration system, and then transferred to the active impact block with the clutch member 89 as the intermediate member. 63, thereby establishing a fixed connection or a rigid connection of the output end of the reduction system to the active impact block 63 to transmit the rotation; since the output ends of the main shaft 61 and the reduction system are fixedly connected by an interference fit, it can be said that the connection is established. The fixed connection of the main shaft 61 and the active impact block 63. In the past, when the power tool was switched from the impact wrench function to the drilling function, the rotation of the groove and the ball system between the main shaft 61 and the active impact block 63 was still transmitted.

 It is easily conceivable by a person of ordinary skill in the art that the clutch member 89 can also be arranged directly on the outer peripheral surface of the main shaft 61 so as to be slidable along the axial direction of the main shaft 61. In this embodiment, the clutch member 89 is partially and relatively fixedly coupled in the rotational direction, and a portion is selectively engaged or disengaged with the active impact block 63 by a spline fit, thereby in the drilling mode (including high speed). The fixed connection of the main shaft 61 to the active impact block 63 is established under the drill function and the low speed drill function. The idea of this embodiment is the same as the preferred embodiment of the present invention described above, and the specific form thereof will not be described again.

 It is also conceivable that the clutch member 89 can also be fixedly connected to the active impact block 63 in a form different from the spline fit, or in a form different from the slide rail and the second planet carrier 47 or the spindle 61. Rotating a relatively fixed fit, for example, using a snap and hole fit, or a bump and groove fit to achieve an optional solid connection of the clutch member 89 and the active impact block 63, using a spline fit to implement the clutch member 89 and the second The cooperation of the carrier 47 or the main shaft 61, and the like.

 The following describes the specific ways of switching from the high-speed drilling function to the low-speed drilling function and the low-speed drilling function.

 Figure 12, Figure 13 and Figure 14, Figure 15. When the high-speed drilling function is switched to the low-speed drilling function, the switching ring 81 rotates to drive the speed switching groove 813 to move, and the pin of the speed switching member 85 is moved from one straight groove to the other straight groove, thereby driving the speed switching member 85 to move axially. The second ring gear 53 is further moved from the rear position to the front position. After the switching is completed, the second ring gear 53 is in the front position, the clutch member 89 is in the front position, and the screwdriver switch 87 is in the front position.

As described above, after the second ring gear 53 is moved from the rear position to the front position, the sun gear 45 is disengaged. The engagement is still engaged with the second planet gear 49. At the same time, the splines 531 of the second ring gear 53 and the inner splines 775 of the movable end teeth 77 are engaged, and at this time, the screwdriver changer 87 is located at the front position, and the end of the screwdriver changer 87 is engaged with the movable end teeth 775. The key groove 771 prevents the movable end tooth 775 from rotating, and thus the second ring gear 53 cannot be rotated.

 Through the above cooperation mode, the multi-function drill 1 is located under the low-speed drilling function, and the planetary gear reduction system outputs the lower rotation speed to the power output system via the two-stage deceleration as described above, the operation mode of the power output system and the high-speed drilling function. The time is the same and will not be repeated here.

 The following describes the specific action of switching from the low-speed drilling function to the screwdriver function and the screwdriver function.

 Figure 14, Figure 15, and Figure 16, Figure 17. When switching from the low speed drilling function to the screwdriver function, the switching ring 81 rotates to drive the displacement of the screwdriver switching slot 815, and the pin of the screwdriver switching member 87 is moved from the wide portion to the narrow portion, thereby driving the screwdriver switching member 87 to move axially. The rear position, the engagement of the disengagement and the movable end teeth 77. After the switching is completed, the second ring gear 53 is in the front position, the clutch member 89 is in the front position, and the screwdriver switch 87 is in the rear position.

 As previously mentioned, the spiral cover 71 passes through the stud 711, and the torsion spring 73 presses the post of the stationary end tooth 75.

753, wherein the stud 711, the torsion spring 73 and the post 753 - corresponding settings. The stationary end teeth 75 are thus elastically urged against the movable end teeth 77. Specifically, the end teeth 753 of the stationary end teeth 75 and the end teeth 773 of the movable end teeth 77 are press-fitted together, thereby preventing the movable end teeth 77 from rotating. At this time, since the screwdriver changer 87 is disengaged from the engagement of the movable end teeth 77, the stationary end teeth 75 are the only members that directly block the rotation of the movable end teeth 77.

 When the upper screw is operated, the operator drives the screw cover 71 to move back and forth to adjust the compression amount of the torsion spring 73, that is, adjust the elastic force applied to the movable end tooth 77 by the static end tooth 75 to set the screw. The maximum output torque of the multi-function drill 1 under the batch function. When the torque required to drive the working shaft 691 to continue to rotate is greater than the set maximum output torque, the second ring gear 53 drives the movable end teeth 77 to rotate against the elastic pressing force, and the repetitively pushing the static end teeth 75 moves axially forward, the end teeth The 773 and the end teeth 753 climb the hills. That is, the movable end tooth 77 can no longer prevent the second ring gear 53 from rotating, so that the output of the motor only drives the second ring gear 53 to rotate freely, and does not drive the second carrier 47 to rotate, and outputs the rotary motion to the power output system.

 The function switch button 17 can also adjust the multi-function drill 1 in the order of the screwdriver function, the low-speed drill function, the high-speed drill function, and the impact wrench. The implementation manner is similar to that described above, and only the order is reversed, and details are not described herein again.

Claims

Claim A power tool comprising: a housing; a motor, located in the housing, having an output shaft that provides a rotary output; a planetary gear reduction system, the speed planetary gear reduction system including a sun gear, meshing with an output gear of the sun gear a planet gear that surrounds an inner ring gear of the planet gear, the inner ring gear having a first position in an axial direction and a second position in which the ring gear simultaneously engages the sun gear and the planet a wheel in which the ring gear engages the planetary gear and disengages from the sun gear, wherein: the power tool further includes a movable end tooth, and the movable end is located at the second position The teeth are engaged to interlock with each other in the circumferential direction; and an optional rotation preventing member that locks the circumferential rotational movement of the movable end teeth.  2. The power tool according to claim 1, comprising: an elastic member that abuts the movable end tooth, an axially movable static end tooth, and a static end tooth toward a direction of the movable end tooth, The end faces on which the stationary end teeth and the moving end teeth abut are each provided with matching end teeth.  3. The power tool according to claim 1, further comprising: a torsion cover, the screw is coupled to the screw cover in the torsion cover, the elastic member is a torsion spring connected to the screw cover, the torsion cover The helical cover can be axially moved to adjust the amount of compression of the torsion spring.  4. The power tool according to claim 1, comprising: a function switching button, wherein the function switching button drives the rotation of the rotation member to be selectively located at the first position and the second position, A positional stop member locks the circumferential rotational movement of the movable end teeth, and in the second position, the rotation stop member permits circumferential rotational movement of the movable end teeth.  The power tool according to claim 4, wherein: one end surface of the movable end tooth is provided with a plurality of circumferentially distributed key grooves, and the rotation stop member is axially movable to be optionally located at the One position and two positions. The key groove is engaged at an end of the first position rotation preventing member, and the end of the rotation member at the second position is disengaged from the key groove.  The power tool according to claim 5, further comprising: a switching ring having a screwdriver switching slot, wherein the rotation preventing member is provided with a pin located in the screwdriver switching slot, The function switching button drives the switching ring to rotate to drive the pin to move axially, so that the rotation preventing member moves axially between the first position and the second position.  7. The power tool according to claim 4, wherein: the function switching button drives the inner ring gear to move axially to be selectively located in the first position and the second position, the inner ring gear In the second position, the movable end teeth and the inner ring gear are engaged by a spline structure. 8. A power tool, including: a planetary gear reduction system, wherein the output of the output shaft is decelerated and then rotated; the power output system includes a spindle that is driven to rotate by the planetary gear reduction system; The function switching mechanism, the optional setting power tool is in the high speed drilling function, the low speed drilling function, the screwdriver function, wherein the power tool further comprises a speed and screwdriver switching assembly, and the speed and screwdriver switching assembly comprises : an inner ring gear, the inner ring gear can be axially moved by the function switching mechanism to adjust the output speed of the planetary gear reduction system; the movable end tooth can be connected to the inner ring gear with a relatively rotational lock; the static end tooth is pressed The movable end gear is connected to the rotation preventing member, and the rotation preventing member is moved between a position at which the movable end tooth is rotated and a position at which the movable end tooth is released.  9. The power tool according to claim 8, wherein: the high-speed drilling function, the inner ring gear is located at a first position in the axial direction, and the ring gear simultaneously meshes the sun gear in the first position And the planetary gear, the rotation preventing member is located at a position of the disengaged end tooth; the low ring drilling function, the inner ring gear is located at a second position in the axial direction, and the ring gear engages the inner ring in the second position The planetary gear is disengaged from the sun gear; under the screwdriver function, the inner ring gear is located at a second position in the axial direction, and the rotation preventing member is located at a position for restricting rotation of the movable end tooth.  10. The power tool according to claim 8, wherein: the function switching mechanism comprises a function switching button mounted on the housing and a switching ring disposed in the housing, wherein the switching ring is provided with a stepped shape a speed switching slot and a stepped screwdriver switching slot, wherein the speed switching slot is provided with a speed switching member, wherein the speed switching member can slide in the speed switching slot and drive the axial movement of the ring gear; the screwdriver is switched in the slot The rotation preventing member is mounted, and the rotation preventing member is slidable in the screwdriver switching groove to axially move between a position at which the movable end tooth is rotated and a position at which the movable end tooth is released.  The power tool according to claim 8, wherein: the inner ring gear and the movable end tooth are respectively provided with matching splines to be rotationally locked and connected to each other.  12. The power tool according to claim 8, wherein: the movable end tooth is provided with a key groove, and the end of the rotation stop member can be embedded in the key groove to lock the rotational movement of the movable end tooth.  The power tool according to claim 8, wherein: the movable end teeth and the opposite end faces of the static end teeth are respectively provided with matching teeth, and the rotation preventing member is located at a position of the disengaged end teeth When the torque on the main shaft reaches a predetermined value, the movable end tooth and the static end tooth rotate relative to each other.  14. The power tool according to claim 8, wherein: the torsion cover is provided, and an elastic member is disposed between the torsion cover and the static end tooth, and the torsion cover adjusts the compression amount of the elastic member. 15. The power tool according to claim 8, wherein: the power output system includes an impact mechanism including an active impact block that is rotationally driven by the main shaft, and is rotatably driven by engagement with the active impact block. a passive impact block coupled to the passive impact block, the rotating impact shaft being driven by the passive impact block, wherein the active impact block is selectively disengageable 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 intermittently impacting the working shaft in the rotating direction, and the function switching mechanism is further connected with the impact wrench switching mechanism, and the operation or the locking switch can be selected to allow or lock the The impact mechanism, and optionally the optional power tool, is in the impact wrench function. 16. The power tool according to claim 15, wherein: the impact switching mechanism comprises a clutch member, and the clutch member is driven by the function switching mechanism to selectively establish or cut off from the main shaft to the active impact block. a rigid rotary transmission connection, the clutch member is rotationally locked to the connecting main shaft, the clutch member and the active impact block are relatively axially movable, and each of the plurality of interlocking members is provided with an interlocking member that is mutually compatible to be selectively rotationally locked. Connect to each other.  17. The power tool according to claim 16, wherein: the planetary gear reduction system includes a planet carrier that fixedly connects the main shaft to output a rotational motion, and the clutch member is slidably mounted by a slide rail fit On the main shaft or on the planet carrier.  The power tool according to claim 16, wherein: the switching ring is provided with a stepped impact wrench switching slot, and the switching slot is provided with an impact wrench switching member, and the impact wrench switching member is connected. The clutch member can be moved in the impact wrench switching slot to drive the clutch member to move axially.  19. A power tool, including: Housing a motor, located in the housing, having an output shaft that provides a rotational output; a planetary gear reduction system, the rotation output of the output shaft is decelerated and then rotated; the power output system transmits the rotation output of the planetary gear reduction system to the working head; The function switching button is at least partially housed in the housing, wherein the function switching button is moved to select an impact wrench function of the power tool, a high speed drilling function, a low speed drilling function, and a screwdriver function. The power tool according to claim 19, wherein the function switching button has a first position, a second position, a third position, and a fourth position which are sequentially arranged in a circumferential direction of the housing, and the function switching The button can be sequentially moved from the first position to the fourth position, or from the fourth position to the first position. When the function switching button is in the first position, the power tool is in the impact wrench function, and the function switching button is in the second position. The tool is in a high speed drilling function, the function switching button is located in the third position, the power tool is in the low speed drilling function, and the function switching button is in the fourth position, and the power tool is in the screwdriver function. 21. The power tool according to claim 19, wherein said function switching button is selectable In the first position, the second position, the third position and the fourth position, the power tool is in the impact wrench function when the function switching button is in the first position, the power switch is in the second position, the power tool is in the high speed drilling function, The function switching button is located at the third position, the power tool is in the low speed drilling function, the function switching button is located in the fourth position, the power tool is in the screwdriver function, and the first position, the second position, the third position and the fourth position are located in the housing On the same circumference line, its projection to the horizontal plane is a straight line.  22. The power tool according to claim 19, wherein The speed planetary gear reduction system includes an inner ring gear movable between a first position at which the planetary gear reduction system outputs a high rotational speed and a second position at which the planetary gear reduction system outputs a low rotational speed; The output system includes a clutch member movable between a first position that limits the function of the impact wrench and a second position that allows the impact wrench function; The function switching button is connected to the rotation preventing member, and the rotation preventing member is movable between a first position for restricting the function of the screwdriver and a second position for allowing the function of the screwdriver; The function switch button also connects the ring gear and the clutch member to operatively select the impact wrench function of the power tool, the high speed drill function, the low speed drill function and the screwdriver function.  The power tool according to claim 22, wherein, in the function of the impact wrench, the clutch member is in the second position; in the high-speed drilling function, the inner ring gear is in the first position, and the clutch member is located a first position; in the low speed drilling function, the inner ring gear is in the second position, the clutch member is in the first position, the rotation preventing member is in the first position; and in the screwdriver function, the inner ring gear is in the second position The clutch member is in the first position, and the rotation stop member is in the second position.  The power tool according to claim 23, wherein, in the function of the impact wrench, the inner ring gear is in the first position, the screwdriver function is in the first position; and in the high speed drilling function, the screwdriver Located in the first position.  25. The power tool according to claim 22, wherein the planetary gear reduction system includes a sun gear and a planet gear meshing with an output gear of the sun gear, the inner ring gear being internally toothed in the first position The ring simultaneously engages the sun gear and the planet gear to output a high rotational speed, in which the ring gear engages the planet gear and disengages the sun gear to output a low rotational speed. 26. The power tool according to claim 22, wherein the power output system comprises a main shaft, an active impact block mounted on the main shaft by a V-groove ball mechanism, the clutch member being coupled to the main shaft, relative to the main shaft The movable member is axially movable and not relatively rotatable, and the clutch member is engaged with the active impact block at the first position to directly output the rotation of the main shaft to the active impact block, and the clutch member is disengaged at the second position. The active impact block. 27. The power tool according to claim 25, further comprising a movable end tooth, wherein the inner ring gear meshes with the movable end tooth when being in the second position to lock with each other in the circumferential direction, the rotation stop Optional to lock the circumferential rotational movement of the moving end teeth.  The power tool according to claim 27, wherein one end surface of the movable end tooth is provided with a plurality of circumferentially distributed key grooves, and the rotation preventing member is in the first position of the rotation preventing member The end engages the keyway, and the end of the rotation member is disengaged from the key groove at the second position.  29. A variety of power tools, including:  Housing  a motor, a motor output shaft having an output rotary motion, and a motor output shaft end is a gear;  a planetary gear reduction system, the speed planetary gear reduction system includes a two-stage speed reduction mechanism arranged in the axial direction of the motor output shaft, the first stage speed reduction mechanism is arranged on one side of the axial direction close to the motor, and the second stage speed reduction mechanism is arranged In the axial direction close to the side of the main shaft;  The first stage speed reduction mechanism includes:  First planet carrier;  a plurality of first stage planetary gears, wherein the first stage planetary gears are arranged circumferentially along the first planet carrier to mesh with the motor output shaft;  a first ring gear surrounding the first stage planetary gear, the inner teeth of which mesh with the first stage planetary gear; the sun gear, which rotates following the first planet carrier, has a sun gear output shaft;  The second stage reduction mechanism includes:  Second stage planet carrier;  a second stage planetary gear mounted on the second stage planet carrier to mesh with the sun gear output shaft; a second inner ring gear surrounding the second stage planetary gear, the inner tooth and the second stage planetary gear meshing main shaft a chuck, characterized in that  The number of teeth of the first stage planetary gear is greater than the number of teeth of the gear of the motor output shaft.  30. The power tool according to claim 29, wherein: the motor output shaft includes an axially disposed shaft seat and an output gear, the axle seat length being greater than the output gear length, the first planet The frame correspondingly includes a base and a planet carrier portion, and the base is fitted to the axle seat.  The power tool according to claim 30, wherein: a support is provided between the base and the shaft base. 32. The workbench according to claim 29, wherein: the first ring gear is fixedly disposed relative to the casing. 33. The workbench according to claim 29, wherein: the first ring gear is movable between a first position and a second position in the axial direction, in the first position, the first inner The ring gear is circumferentially fixed and does not mesh with the first carrier; in the second position, the first ring gear simultaneously engages the first stage planetary gear and the sun gear, and is movable in the circumferential direction.  34. The workbench according to claim 29, wherein: the second ring gear is fixedly disposed relative to the casing.  35. The workbench according to claim 29, wherein: the second ring gear is movable between a first position and a second position in the axial direction, in the first position, the second inner The ring gear simultaneously engages the second stage planetary gear and the sun gear, and is movable in the circumferential direction; in the second position, the second ring gear is circumferentially fixed and does not mesh with the first carrier.  36. The workbench according to claim 29, wherein: the ratio of the number of teeth of the first stage planetary gear to the motor output shaft gear is greater than two.