CN102335904B - Power tool - Google Patents

Abstract

The invention relates to a power tool, comprising: a casing; a motor, located in the casing, having an output shaft for providing rotation output; a planetary gear reduction system, which decelerates the rotation output of the output shaft and then rotates it; the power output system , to transmit the rotational output of the planetary gear reduction system to the working head; the switching window, located on the housing; the function switching button, at least partially contained in the switching window, the function switching button moves in the switching window to select Impact wrench function, high-speed drill function, low-speed drill function, screwdriver function for power tools. The function switching button of the present invention can realize speed adjustment by sliding on the casing, and can also realize the switching of the impact wrench function at the same time, which improves the simplicity of operation.

Description

power tool

technical field

The invention relates to a power tool, especially a power tool that can switch between multiple functions.

Background technique

Existing gun drill power tools generally include electric drills, electric screwdrivers, impact drills, impact wrenches, and the like.

Electric screwdrivers are used to tighten screws onto workpieces. It usually includes an overload clutch structure, which is composed of a clutch driving part and a driven part. The driving part is integrated with the reduction gear, while the driven part is rotatably fixed in the casing and can move axially relative to the casing. A working spring acts on the end face teeth of the driving part through the driven part, so that the driving part is fixed in the direction of rotation and the torque can be transmitted to make the screwdriver rotate. During operation, the torque of the motor is transmitted to the screwdriver through the planetary gear reduction mechanism to make it rotate, and the screwdriver head matches the screw head groove, so that the screw is quickly tightened. As the screw is tightened, the resistance torque on the active part increases rapidly, and an axial thrust is generated through the end teeth. When the resistance torque exceeds the preset value for tripping, the axial thrust forces the driven part to further compress the working spring When the driving part is separated from the driving part, when the driving part loses the support of the driven part, it is driven to rotate, so that the planetary gear reduction mechanism has no output, and the driving part still has a tendency to rotate with the output shaft of the motor, and then under the action of the restoring force of the working spring. Engagement, and so on again and again, the screw is no longer subjected to torque, and the motor is still rotating. With this structure, the tightened screw can reach the specified tensile force without being pulled apart, and the motor will not be overloaded, locked, damaged or burned.

The impact drill is mainly used to punch holes in workpieces of brittle materials. It has a vibrating mechanism consisting of a movable cam and a static cam with canine teeth on opposite end faces. The movable cam is installed in the middle part of the output shaft, and the static cam is fixed on the casing, and a spring is arranged between the movable and static cams to separate the two from each other. When performing percussion drilling, press the drill bit vertically onto the surface of the workpiece, and apply appropriate pressure in the axial direction, so as to overcome the elastic force of the spring to make the dynamic and static cams mesh with each other, start the motor, and the torque of the motor is transmitted to the machine through the dynamic and static gears. Output shaft. During the rotation of the output shaft, it will generate an axial backward thrust on the static cam relatively fixed to the casing, so that the impact drill will move backward. distance. At the moment of disengagement, due to the continuous external axial force, the static cam quickly impacts the movable cam with the percussion drill, thereby generating a strong impact force on the surface of the workpiece. Repeatedly in this way, a compound movement of continuous rotation and impact is produced. The brittle material is broken under repeated strong impact, and with the rotation of the drill bit, the debris is discharged from the groove of the drill bit, so that holes are drilled in masonry and concrete components.

Impact wrenches are mainly used for tightening bolts. It has an active impact block, a passive impact block, etc. The active impact block is driven by the output shaft of the gear reduction mechanism, and the passive impact block can be meshed with the active impact block to be rotated and driven. The passive impact block is set on the working shaft and driven by rotation. The working shaft, wherein the active impact block selectively disengages from the passive impact block when the load on the working shaft increases to a certain value, and then re-engages with the passive impact block under the rotation drive of the output shaft, thereby in 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, bolting, drilling, etc., when performing operations. In this way, it will be very troublesome for the user to prepare multiple different types of electric tools and to constantly replace them for operation.

U.S. Patent No. 6,142,242 (hereinafter referred to as the '242 patent) discloses a power tool that can optionally realize an electric drill, an electric screwdriver, and a percussion drill. The electric 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 an impact drill can be realized accordingly. Among them, in the mechanism for realizing electric screwdriver and other function switching, an axially extending restricting block is provided in the casing, which can resist the clutch follower so that the clutch driving part cannot be driven in rotation, and the function switching element is provided with A protrusion that can axially cooperate with the restriction block. When the function of electric drill or impact drill is realized, the bump in the function switching element cooperates with the restriction block so that the restriction block is against the clutch follower; when the function of an electric screwdriver is realized, the bump in the function switching element is disengaged from the restriction block , so that the clutch active member can be rotationally driven to realize the clutch function. U.S. Patent No. 6,457,535B1 (hereinafter referred to as the '535 patent) discloses a similar clutch switching structure, by rotating and operating the function switching element outside the casing to axially move the clutch function limiting element inside the casing, so as to selectively realize the electric Screwdriver function.

At present, many drilling power tools can also adjust the output speed to adapt to different working conditions. As shown in U.S. Patent No. 7,044,882B2 (hereinafter referred to as the patent '882 patent), the adjustment of high speed and low speed is realized by rotating the speed adjustment knob arranged on the casing. The multifunctional electric tool shown in US Patent No. 7,124,839B2 (hereinafter referred to as the '839 patent) further discloses that speed adjustment and function switching are realized by a common button. Among them, when the electric drill function is realized, the high and low speed adjustments are performed by moving the button along the axial direction of the casing, and at high speed, the switching between functions can be realized by rotating and adjusting the common button on the circumferential surface of the casing.

However, although the '839 patent realizes the adjustment of speed and the switching of functions by a common button, the adjustment direction of the button is different from the adjustment direction of the button when the speed is adjusted and the function is switched, which brings inconvenience to the operation.

Contents of the invention

The purpose of the present invention is to provide a power tool, which has a function switching button, which can switch between the impact wrench function and other functions, and can also adjust the speed, thereby improving the simplicity of operation.

In order to achieve the above object, the technical solution of the present invention is: a power tool, comprising: a casing; a motor, located in the casing, having an output shaft that provides rotation output; a planetary gear reduction system that outputs the rotation of the output shaft After deceleration, the rotation output is performed; 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 accommodated in the housing, and the function switching button moves to select the 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 arranged in sequence along the circumference of the housing, and the function switching button can move from the first position to the fourth position in sequence, Or move from the fourth position to the first position in sequence, the power tool is in the impact wrench function when the function switching button is in the first position, the power tool is in the high-speed drilling function when the function switching button is in the second position, and the power tool is in the high-speed drilling function when the function switching button is in the second position The three-position power tool is in the low-speed drilling function, and the function switch button is in the fourth position and the power tool is in the screwdriver function.

Further, the function switch button can be selectively located at the first position, the second position, the third position and the fourth position. When the function switch button is at the first position, the power tool is in the impact wrench function, and the function switch button is at the second position. The power tool in the second position is in the high-speed drilling function, the function switching button is in the third position, the power tool is in the low-speed drilling function, the function switching button is in the fourth position, the power tool is in the screwdriver function, the first position, the second position , the third position and the fourth position are located on the same circumferential line of the casing, and their projections to the horizontal plane form a straight line.

Further, the planetary gear reduction system includes an inner ring gear, and the inner ring gear is movable between a first position where the planetary gear reduction system outputs a high rotational speed and a second position where the planetary gear reduction system outputs a low rotational speed; The power output system includes a clutch, and the clutch is movable between a first position that limits the function of the impact wrench and a second position that allows the function of the impact wrench; the function switching button is connected to a stopper, and the stopper The part is movable between the first position which restricts the function of the screwdriver and the second position which allows the function of the screwdriver; the function switching button is also connected with the ring gear and the clutch part, so as to operatively select the impact wrench function of the power tool, High-speed drill function, low-speed drill function and screwdriver function.

Further, when it is in the function of impact wrench, the clutch is at the second position; when it is in the function of high-speed drill, the inner ring gear is in the first position, and the clutch is in the first position; when it is in the function of low-speed drill, the inner The ring gear is at the second position, the clutch is at the first position, and the anti-rotation part is at the first position; when the screwdriver function is in place, the inner ring gear is at the second position, the clutch is at the first position, and the anti-rotation part is at the first position Second position.

Further, when the function of the impact wrench is used, the inner ring gear is located at the first position, and the function of the screw driver is located at the first position; when the function of the high-speed drill is performed, the screw driver is located at 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, and the ring gear meshes with the sun gear and the planetary gear at the first position at the same time to Output high speed, in the second position the ring gear meshes with the planetary gear and disengages from the sun gear to output low speed.

Further, the power output system includes a main shaft, an active impact block assembled on the main shaft through a V-groove ball mechanism, the clutch part is connected to the main shaft, and can move axially with respect to the main shaft but cannot rotate relatively. The active impact block is clamped at the first position to directly output the rotation of the main shaft to the active impact block, and the clutch part is disengaged from the active impact block at the second position.

Further, it also includes movable end teeth, when the inner ring gear is in the second position, meshes with the movable end teeth to lock with each other in the circumferential direction, and the rotation stopper can optionally lock the circumferential rotational movement of the movable end teeth .

Further, one end surface of the movable end tooth is provided with a plurality of key grooves distributed in the circumferential direction, and the end of the anti-rotation member engages the key grooves at the first position, and engages with the key grooves at the second position. The end of the anti-rotation piece disengages from the keyway.

The invention provides a power tool, comprising: a casing; a motor with a motor output shaft for outputting rotational motion, and a gear at the end of the motor output shaft; a planetary gear reduction system, the planetary gear reduction system includes The two-stage deceleration mechanism arranged in sequence, the first-stage deceleration mechanism is arranged on one side close to the motor in the axial direction, and the second-stage deceleration mechanism is arranged on the side close to the main shaft in the axial direction; the first-stage deceleration mechanism includes: The first planetary carrier; a plurality of first-stage planetary gears, the first-stage planetary gears are evenly arranged along the circumference of the first planetary carrier, meshing with the motor output shaft; the first inner ring gear, surrounding the first-stage planetary gears , its internal teeth mesh with the first-stage planetary gear; the sun gear, which rotates with the first planetary carrier, has a sun gear output shaft; the second-stage reduction mechanism includes: the second-stage planetary carrier; the second-stage planetary gear, installed on the second-stage On the secondary planet carrier, it meshes with the output shaft of the sun gear; the second inner ring gear, surrounds the second stage planetary gear, and its internal teeth and the second stage planetary gear mesh with the main shaft; the collet, the first stage The number of teeth of the planetary gear is greater than the number of teeth of the gear of the motor output shaft.

Further, the motor output shaft includes a shaft seat and an output gear arranged in the axial direction, the length of the shaft seat is greater than the length of the output gear, and the first planet carrier includes a base and a planet wheel carrier part accordingly, so The base is sleeved on the shaft seat.

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

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

Further, the first ring gear is movable between a first position in the axial direction and a second position, and in the first position, the first ring gear is fixed in the circumferential direction and does not mesh with the first planet carrier ; In the second position, the first ring gear meshes with the first-stage planetary gear and the sun gear at the same time, and can move in the circumferential direction.

Further, the second ring gear is fixedly arranged relative to the casing.

Further, the second ring gear can move between a first position and a second position in the axial direction, and at the first position, the second ring gear meshes with the second-stage planetary gear and the sun gear simultaneously, It is movable in the circumferential direction; in the second position, the second ring gear is fixed in the circumferential direction and does not mesh with the first planet carrier.

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

The invention also provides a technical solution. A power tool, comprising: a casing; a motor, located in the casing, having an output shaft providing a rotation output; a planetary gear reduction system, which reduces the rotation output of the output shaft and then rotates it; a power output system, including a The planetary gear reduction system drives the rotating main shaft; the function switching mechanism can optionally set the power tool to be in the high-speed drilling function, low-speed drilling function, and screwdriver function. The power tool also includes a speed and screwdriver switching assembly. The speed and The screwdriver switching assembly includes: the inner ring gear, which can be driven by the function switching mechanism to move axially to adjust the output speed of the planetary gear reduction system; the movable end teeth, which can be relatively rotated and locked to connect to the inner ring gear; the static end The tooth presses the tooth at the moving end; the function switching mechanism is connected to the anti-rotation piece, and drives the anti-rotation piece to move between a position where the rotation of the tooth at the stop end is limited and a position where the tooth at the driving end is disengaged.

Further, under the function of high-speed drilling, the inner ring gear is located at the first position in the axial direction. In the first position, the inner ring gear meshes with the sun gear and the planetary gear at the same time. The position of the moving end teeth; under the low-speed drill function, the inner ring gear is located at the second position in the axial direction, and in the second position the inner ring gear meshes with the planetary gear and disengages from the sun gear; under the screwdriver function , the inner ring gear is located at the second position in the axial direction, and the anti-rotation member is located at a position to limit the rotation of the end teeth.

Further, the function switching mechanism includes a function switching button installed on the casing and a switching ring provided in the casing, and the switching ring is provided with a stepped speed switching groove and a stepped screwdriver switching groove, so A speed switching piece is installed in the speed switching groove, and the speed switching piece can slide in the speed switching groove and drive the inner ring gear to move axially; Sliding in the switch slot of the screwdriver to move axially between the position of restricting the rotation of the stop tooth and the position of disengaging the stop tooth.

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

Further, the movable end tooth is provided with a keyway, and the end of the anti-rotation member can be inserted into the keyway to lock the rotational movement of the movable end tooth.

Further, matching teeth are respectively provided on the opposite end surfaces of the movable end teeth and the stationary end teeth, and when the anti-rotation member is located at a position away from the movable end teeth, when the torque on the main shaft reaches a predetermined value, the movable end teeth The end teeth and the static end teeth rotate relative to each other.

Further, a torsion cover is included, an elastic member is provided between the torsion cover and the static end teeth, and the compression amount of the elastic member can be adjusted by the torsion cover.

Further, the power output system includes an impact mechanism, including an active impact block driven by the rotation of the main shaft, a passive impact block that can be engaged with the active impact block and driven to rotate, connected to the passive impact block, driven by the passive impact block to rotate The working shaft, wherein the active impact block selectively disengages from the passive impact block when the load on the working shaft increases to a certain value, and then re-engages with the passive impact block under the rotation drive of the output shaft, thereby in Intermittent impact is applied to the working shaft in the direction of rotation, and the function switching mechanism is also connected to the impact wrench switching mechanism, which can optionally allow or lock the impact mechanism, and then optionally set the power tool to be in the impact wrench function.

Further, the impact switching mechanism includes a clutch, the clutch is driven by the function switching mechanism to selectively establish or cut off the rigid rotation transmission connection from the main shaft to the active impact block, and the clutch rotates to lock the connection The main shaft, the clutch part and the active impact block are axially movable relative to each other, and are respectively provided with interlocking elements that are mutually matched to each other so as to be selectively rotationally locked and connected to each other.

The invention also provides a technical solution. A power tool comprising: a housing; a motor located in the housing and having an output shaft providing a rotational output; a planetary gear reduction system, the planetary gear reduction system including a sun gear, a planet gear meshing with an output gear of the sun gear , a ring gear surrounding the planet gears, the ring gear having a first position in the axial direction and a second position, in which the ring gear simultaneously engages the sun gear and the planet gears, In the second position, the inner ring gear meshes with the planetary gear and disengages from the sun gear. The power tool also includes movable end teeth, and when the inner ring gear is in the second position, it meshes with the movable end teeth to rotate upward interlocking; and an optional stop that locks the circumferential rotational movement of the movable end teeth.

Further, it includes an axially movable static end tooth that is adjacent to the movable end tooth, and an elastic member that presses the static end tooth toward the direction of the movable end tooth, and the end surface where the static end tooth and the movable end tooth abut against Each is provided with matching end teeth.

Further, it includes a torsion cover, which is threadedly fitted to the torsion cover in the torsion cover, the elastic member is a torsion spring connected to the torsion cover, and the torsion cover can adjust the axial movement of the torsion cover to adjust the Compression of the torsion spring.

Further, a function switching button is included, the function switching button drives the rotation stopper to move to be optionally located at the first position and the second position, and at the first position the rotation stopper locks the circumferential rotation of the movable end teeth Movement, in the second position the anti-rotation member allows the circumferential rotational movement of the movable end teeth.

Further, a plurality of key grooves distributed in the circumferential direction are provided on one end surface of the movable end tooth, and the rotation-stopping member can move axially to be optionally located at the first position and the second position. In the first position, the end of the anti-rotation member engages with the keyway, and in the second position, the end of the anti-rotation member disengages from the keyway.

Further, it includes a switching ring, on which a screwdriver switching groove is provided, and a pin located in the screwdriver switching groove is arranged on the said anti-rotation member, and the function switching button drives the switching ring to rotate to drive the The pin moves axially to move the anti-rotation member axially between the first position and the second position.

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

Further, at the second position of the inner ring gear, the movable end teeth are engaged with the inner ring gear through a spline structure.

The invention also provides a technical solution. A power tool, comprising: a housing; a motor located in the housing and having an output shaft that provides rotational output; a planetary gear reduction system that decelerates the rotational output of the output shaft for rotational output; a power output system comprising The planetary gear reduction system drives the rotating main shaft, the active impact block driven by the main shaft rotation; the passive impact block meshed with the active impact block, and the passive impact block can be selectively driven by the active impact block; connected to the passive impact block 1. The working shaft driven by the passive impact block, the active impact block can be selectively disengaged and disengaged from the passive impact block when the load on the working shaft increases to a certain value, so that the working shaft in the direction of rotation Intermittent impact is applied; the function switching mechanism can optionally set the power tool to be in one of the drilling function, impact wrench function, and screwdriver function. The power tool includes an impact switching mechanism, and the impact switching mechanism includes The clutch part is driven by the function switching mechanism to selectively establish or cut off the rigid rotation transmission connection from the main shaft to the active impact block.

Further, the connecting main shaft of the clutch part is rotationally locked, and the clutch part and the active impact block are relatively movable in the axial direction, and are respectively provided with interlocking elements that are mutually fitted so as to be selectively connected to each other in a rotationally locked manner. .

Further, the planetary gear reduction system includes a planetary carrier that is fixedly connected to the main shaft to output rotational motion, and the clutch is slidably mounted on the main shaft or the planetary carrier through cooperation with slide rails.

Further, the function switching mechanism includes a function switching button installed on the casing and a switching ring provided in the casing, the switching ring is provided with a stepped impact wrench switching groove, and an impact wrench is installed in the switching groove. The wrench switching part, the impact wrench switching part is connected to the clutch part, and can move in the impact wrench switching groove to drive the clutch part to move axially.

Further, the planetary gear reduction mechanism includes an inner ring gear, and the inner ring gear can move axially to switch the output speed of the planetary gear reduction mechanism. The switching ring is provided with a stepped speed switching groove, and the speed A speed switching member is installed in the switching groove, and the speed switching member is connected to the ring gear of the planetary gear reduction system, and can move in the speed switching groove to drive the ring gear to move axially.

Further, the planetary gear reduction mechanism includes an inner ring gear, and the function switching mechanism includes a stepped screwdriver switching groove on the switching ring, and a screwdriver switching part is installed in the screwdriver switching groove, and the screwdriver The switching member moves within the screwdriver switching slot to selectively lock or allow the ring gear to rotate.

Compared with the prior art, the function switching button of the present invention can realize speed adjustment by sliding on the casing, and can also realize switching of the impact wrench function at the same time, which improves the convenience of operation.

Description of drawings

The present invention will be further described below in conjunction with accompanying drawing.

Fig. 1 is the front view of the multifunctional drill of the specific embodiment of the present invention

Fig. 2 is a top view of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 3 is a cross-sectional view of the front view direction of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 4 is a cross-sectional view of the multifunctional drill according to the specific embodiment of the present invention in the top view direction.

Fig. 5 is an exploded schematic view of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 6 is a perspective view of the gear box of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 7 is a perspective view of the second inner ring gear of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 8 is a perspective view of the mechanism for switching the impact wrench of the multi-function drill according to the specific embodiment of the present invention.

Fig. 9 is a perspective view of the multi-functional drill and the switching part of the screwdriver according to the specific embodiment of the present invention.

Fig. 10 is a schematic diagram of the switching ring of the impact wrench function of the multi-functional drill according to the specific embodiment of the present invention.

Fig. 11 is a top sectional view of the impact wrench function of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 12 is a schematic diagram of the switching ring of the high-speed drilling function of the multi-functional drill according to the specific embodiment of the present invention.

Fig. 13 is a top sectional view of the high-speed drilling function of the multi-functional drill according to the specific embodiment of the present invention.

Fig. 14 is a schematic diagram of the switching ring of the low-speed drilling function of the multi-functional drill according to the specific embodiment of the present invention.

Fig. 15 is a top sectional view of the low-speed drilling function of the multi-functional drill according to the specific embodiment of the present invention.

Fig. 16 is a schematic diagram of the switching ring of the screwdriver function of the multifunctional drill according to the specific embodiment of the present invention.

Fig. 17 is a front sectional view of the screwdriver function of the multifunctional drill according to the specific embodiment of the present invention.

1 Multifunctional drill 39 Bearing 71 Spiral cover

3 shell 41 first planet carrier 711 stud

5 handle 43 first planetary wheel 73 torsion spring

7 battery pack 45 sun gear 75 static end teeth

9 chuck 47 second planet carrier 751 column

10 axis 473 slide rail 753 terminal teeth

11 switch 49 second planetary gear 77 driving end teeth

13 Torque cover 51 First inner ring gear 771 Keyway

15 Reversing button 53 Second internal ring gear 773 End teeth

17 Function switching button 531 Spline 775 Internal spline

171 Switching spring 533 Ring groove 81 Switching ring

173 Top column 61 Main shaft 811 Impact wrench switch slot

19 Switching window 63 Active impact block 813 Speed switching slot

21 Motor 633 First end tooth 815 Screwdriver switch slot

23 Inner output shaft 635 Clutch groove 83 Impact wrench switch

25 Outer output shaft 65 Impact spring 85 Speed switch

251 Bracket 611 Outer V-groove 87 Screwdriver switch

253 Shaft sleeve 67 Rolling ball 871 Spring

255 Gasket 69 Passive impact block 89 Clutch

31 Gearbox 691 Working shaft 891 Ring groove

33 Front shell 693 Second-end teeth 893 Slider

35 Rear shell 695 Storage tank 895 Clutch block

37 Middle cover 70 Bearing

Detailed ways

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

As shown in FIG. 1 , the multifunctional drill 1 is similar to a pistol shape, and includes a substantially cylindrical housing 3 , a handle 5 arranged at a certain angle to the housing 3 , and a detachable battery pack 7 arranged 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 clamping the working head, which is used to respectively clamp different working heads (not shown) when the multifunctional drill 1 realizes different functions, such as clamping when realizing the impact wrench function. Hold the fastening head, and clamp the twist drill when realizing the high-speed drilling function or the low-speed drilling function. A torque cover 13 is provided on the outside of the chuck 9, and the torque cover 13 can rotate around 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 turning on and off the multifunctional drill 1 . A reversing button 15 is also provided at the interface between the handle 5 and the housing 3 . The multifunctional drill 1 has two reversing buttons 15, which are respectively located on both sides of the housing.

1 and 2, the top of the housing 3 is provided with a function switching button 17, and the function switching button 17 is arranged in a switching window 19 located on the top of the housing 3 and extending in the circumferential direction. The switching window 19 has four preset positions sequentially arranged from one end to the other end along the circumferential direction. The function switching button 17 can move among the four preset positions, and the multi-function drill 1 can be placed in the impact wrench function, the high-speed drill function, the low-speed drill function, and the screwdriver function in sequence. Signs are provided on the switching window 19 or on corresponding positions of the housing 3 to indicate the four preset positions and their corresponding functions.

The internal structure of the multifunctional drill 1 is introduced in detail below.

As shown in FIG. 3 , the end where the collet 9 is located on the housing 3 is the front end, and the opposite end is the rear end. The rear end of the casing 3 accommodates a power source, specifically a DC motor 21 . The motor 21 has an output shaft to output rotational motion. In this specific embodiment, the output shafts include an inner output shaft 23 and an outer output shaft 25 . The inner output shaft 23 is driven to rotate by the motor 21 , and the outer output shaft 25 is sleeved on the inner output shaft 23 through an interference fit, and can be driven to rotate by the inner output shaft 23 . The outer output shaft 25 has front and rear portions extending lengthwise. The outer output shaft 25 includes a shaft seat and an output gear. The shaft seat is located at the rear of the outer output shaft 25 and is sleeved on the inner output shaft 23; The power rotation is output to the reduction system of the multifunctional drill 1. The length and diameter of the shaft seat are greater than that of the output gear.

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

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

The first planetary carrier 41 includes a cylindrical base and a plurality of planet wheel fulcrums arranged on the end surface of the base at uniform intervals in the circumferential direction.

The center of the base is a through hole through which the base is installed and supported on the shaft seat of the output shaft. There is also a support system between the base and the shaft seat, which specifically includes a step-shaped bracket 251 that is sleeved outside the motor output shaft, a shaft sleeve 253 that is arranged between the bracket 251 and the inner wall of the through hole of the base, and a set Spacer 255 between the rear end of the base and the bottom of the inner wall of the gearbox. The supporting system is such that the first planet carrier 41 can rotate well relative to the shaft seat. It should be noted that, in this embodiment, most of the base of the first planet carrier is supported on the axle seat, and the length of the axle seat is relatively long, that is, the length of the first planet carrier 41 is effectively supported by the supporting components. The longer length enables the first planetary carrier 41 to be stable and rotate at high speed for a long time without obvious wear or failure.

Planetary gear fulcrums protrude from the front end of the base, and a first planetary gear 43 is installed on each planetary gear fulcrum. In this specific embodiment, the number of planetary gear shafts and the number of planetary wheels 43 correspond to three. The first planetary gear 43 meshes with the output gear and is driven by it to rotate around the fulcrum of the planetary gear. The first planetary gear 43 meshes with the internal teeth of the first ring gear 51 at the same time. The first ring gear 51 is fixedly arranged relative to the gear case 31 .

The ends of the planetary gear fulcrums protrude to the front of the first planetary gear 43 . The sun gear 45 includes a gear plate and a gear shaft. Teeth are provided on the peripheral surfaces of the gear disc and the gear shaft. There are a plurality of holes on the gear plate, and its position and quantity correspond to those of the planetary gear fulcrum, so that the sun gear 45 is installed on the end of the planetary gear fulcrum. A plurality of second planetary gears 49 meshed with the gear shaft are arranged around the gear shaft. The specific number of the second planetary gears 49 is 5, which are set one by one on the corresponding number of planetary wheel fulcrums of the second planetary carrier 47 . The second planet carrier 47 is fixedly connected to the power output system.

The radially outer sides of the sun gear 45 and the second planetary gears 49 are provided with a second ring gear 53 . In addition, the end teeth of the sun gear 45 and the second planetary gear 49 can mesh with the inner teeth of the second ring gear 53 . The second ring gear 53 is axially movable back and forth relative to the gear case 31 , and has a front position and a rear position. In the front position, the second ring gear 53 meshes with the second planetary gear 49 and disengages from the sun gear 45; and in the front position, the second ring gear 53 cannot rotate, that is, it is circumferentially fixed relative to the gearbox. In the rear position, the second ring gear meshes with the end teeth of the second planetary gear 49 and the gear ring of the sun gear 45 at the same time; and in the rear position, the second ring gear can rotate around the axis 10, that is, it can move circumferentially relative to the gearbox .

The following describes the deceleration process of the planetary gear reduction system in detail.

Refer to 3, FIG. 4, FIG. 5, FIG. 6, and FIG. 9, the output shaft of the motor 21 rotates, driving the first planetary gear 43 to rotate around the planetary gear shaft, and the first planetary gear 43 rotates along the first ring gear 51 The ring-shaped internal teeth crawl and revolve around the axis 10. The revolution of the first planetary gear 43 drives the first planetary carrier 41 to rotate around the axis 10 . The sun gear 45 is connected to the first planet carrier 41 through three planet wheel fulcrums, and thus rotates together 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 output by the output shaft is initially reduced by the first planetary gear 43, and its reduction ratio is the inverse ratio of the number of teeth of the output gear 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 and the first planetary gear 43 is 7:18. In order to achieve a better 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, which further improves the stability of the reduction system. In the forward position of the gear box 31, compared with the bottom of the gear box, the forward position has a larger space in the radial direction, which also makes it possible to set a larger first planetary gear 43 and further set more gears. , it is finally possible to obtain a smaller gear ratio. During this process, the first planetary gear 43 revolves around the axis 10 , driving the first planetary carrier 41 and the sun gear 45 to rotate for the second time, reducing the rotational output speed to the power output system for the second time.

After the rotational motion is output to the sun gear 45 , there are two corresponding deceleration situations according to the front and rear positions of the second ring gear 53 . When the second ring gear 53 is in the front position, the second ring gear 53 optionally does not rotate and is disengaged 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 inner teeth of the second ring gear 53, revolves around the axis 10, and then drives the second planet carrier 47 to rotate around the axis 10, and transmits the rotational motion to the power output system. This process forms the second stage reduction of the planetary gear reduction system. When the second ring gear 53 is located at the rear position, the second ring gear 53 is rotatable while meshing with the gear plate of the sun gear 45 and the second planetary gears 49 . Therefore, the rotation of the sun gear 45 is transmitted to the second planetary gear 49 and the second planet carrier 47 through the second ring gear 53, and the second-stage deceleration is canceled.

To sum up, the planetary gear reduction system of this embodiment can output two different rotational speeds. However, it is possible to modify the planetary gear reduction system to provide more different rotational speed outputs. For example, the first ring gear 51 is set to have similar front and rear positions as the second ring gear 53, so that it can optionally engage the first planetary gear 43 and the sun gear 45 at the same time, or only engage the first The planetary gear 43, and then combine the front and rear positional relationship of the first ring gear 51 and the second ring gear 53, that is, at least 3 kinds of speed outputs can be provided, and its specific setting and combination methods are those skilled in the art based on the ideas described above The ones that are easy to design will not be described in detail here.

The junction of the front case 33 and the rear case 35 is also provided with a middle cover 37, the middle cover 37 divides the gearbox 31 into two parts, the rear part mainly accommodates the planetary gear reduction system, and the front part mainly houses the power output system. A bearing 39 is installed on the inner ring of the middle cover 37 , and the bearing 39 supports the second planet carrier 47 .

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

As shown in Fig. 3, Fig. 4, Fig. 5, Fig. 7 and Fig. 8, as mentioned above, the second planetary gear 47 is fixedly connected with the power output system, specifically, the second planetary carrier 47 and the main shaft 61 are fixed by interference fit connected, the main shaft 61 always follows the rotation of the second planetary carrier 47 .

The power output system includes a set of active impact block 63 arranged on the main shaft 61, an impact spring 65 arranged between the active impact block 63 and the second planet carrier 47, and a rolling ball located at the joint between the active impact block 63 and the main shaft 61 V-shaped groove impact mechanism, wherein the impact mechanism includes an outer V-shaped groove 611 formed in a depression on the surface of the main shaft 61, a rolling ball 67 that can roll in the outer V-shaped groove 611, which is a steel ball in this embodiment, and is located on the active The inner ring of the impact block 63 is used to accommodate the inner V-shaped groove of the rolling ball 67 . A pair of first end teeth 633 protrude radially and symmetrically from the front end surface of the active impact block 63 . Washers and spacers are provided between the impact spring 65 and the active impact block 63 . The front end of the active impact block 63 is also provided with a passive impact block 69 , and a pair of second end teeth 693 protrude radially symmetrically on the rear end surface of the passive impact block 69 opposite to the active impact block 63 . The power output system also includes a working shaft 691 extending from the front end of the gearbox 31 and connected to the passive impact block 69 . The front end of the working shaft 691 is provided with a receiving groove 695, which can accommodate corresponding working heads when different functions are realized, and is clamped and held by the collet 9. The collet 9 is sleeved on the front end of the working shaft 691 .

The multifunctional drill 1 of the present invention also has a torque control system, which is used to adjustably set the maximum output torque of the power output system when the screwdriver is functioning. The torque control system is described in detail below.

Referring to Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 9, the torque control system includes a torque cover 13, a spiral cover 71, a torsion spring 73, a static end tooth 75, and a movable end tooth 77.

The torque cover 13 is located at the rear of the chuck 9 and outside the front shell 33 of the gear case 31 . A spiral cover 71 is connected to the torque cover 13 through thread fit. The spiral cover 71 can be rotated by the torsion cover 13 and move forward and backward along the axis 10 . The spiral cover 71 has a ring-shaped shell and a plurality of protruding posts 711 extending axially are uniformly arranged on the shell, and torsion springs 73 are installed on the protruding posts 711 . The casing can be axially moved but not rotatably fitted on the front casing 33 through the cooperation of the groove and the block, and the studs 711 and the torsion springs 73 are one-to-one corresponding and at least partly extend into a plurality of axial shafts correspondingly arranged on the front casing 33. in the hole.

The middle cover 37 is provided with through holes corresponding to the aforementioned plurality of axial holes. The static end teeth 75 are located in the rear part of the gear box 33 and have an annular housing. The front end of the housing is provided with a plurality of columns 751 corresponding to the aforementioned through holes. The columns 751 pass through the through holes of the middle cover 37 and abut against The torsion spring 73 on the stud 711. The rear end of the housing is provided with a plurality of end teeth 753 . Since the column 751 passes through the through hole of the middle cover 37, the stationary end tooth 75 can move axially within a certain range, but cannot rotate. A movable end tooth 77 is arranged behind the static end tooth 75 . The movable end tooth 77 has an annular housing, the front end surface of the housing is provided with an end tooth 773 matched with the end tooth 753 of the static end tooth 75, the rear end of the housing is provided with a keyway 771, and the inner ring surface of the housing Internal splines 775 are provided. The movable end teeth are immovable in direction, and can be optionally rotatable and non-rotatable in the circumferential direction.

Through the adjustment of the function switching system, the multifunctional drill 1 of this embodiment can optionally have the function of an impact wrench, a high-speed drill, a low-speed drill, and a screwdriver. The function switching system of this embodiment will be described in detail below.

Referring to Fig. 3, Fig. 4, Fig. 5 and Fig. 6, the function switching system mainly includes a function switching button 17, a switching ring 81, a switching spring 171, a top post 173, an impact wrench switching part 83, a speed switching part 85, and a screwdriver switching part 87, clutch 89.

The function switching button 17 includes a toggle button located in the switching window 19 and a semi-circular casing extending into the casing 3. A switching ring 81 is arranged under the casing of the function switching button 17, and the switching ring 81 is sleeved on the rear casing 35. , and can be driven by the function switching button 17 to rotate around the axis 10 relative to the rear shell 35 . There is a notch on the ring surface of the switch ring 81 , and the switch spring 171 and the push post 173 pass through the notch and are arranged between the function switch button 17 and the rear shell 35 . The rear shell 35 is provided with four depressions distributed along the circumferential direction, and the four depressions correspond to the aforementioned four preset positions of the function switching button 17. When the top column 173 stays in a depression, the function switching button 17 Stay in a corresponding function gear. That is to say, the operator can move the function switch button 17 to move in the circumferential direction, and the switch ring 81 is driven to rotate by the push column 173. When it moves to the depression, the switching spring 171 presses the push column 173 into the depression and tends to stay in the depression. The operator senses the elastic action and knows that he has entered a functional gear. When the function needs to be changed, the operator overcomes the elastic force of the switch spring 171 to drive the top column 173 to leave the depression and enter another required depression, and drives the switch ring 81 Rotate accordingly.

The switching ring 81 is provided with a pair of impact wrench switching slots 811 , a pair of speed switching slots 813 and a screwdriver switching slot 815 . The two impact wrench switching slots 811 can be overlapped when they are translated 180 degrees along the circumferential direction; the two speed switching slots 813 can be overlapped when they are translated 180 degrees along the circumferential direction.

The impact wrench switching groove 811 is in a zigzag shape with steps, and consists of two straight grooves parallel to each other, spaced apart in the axial direction and a connecting groove between the two straight grooves. The two-ended straight groove is perpendicular to the axis 10 . The shell of the impact wrench switching part 83 is strip-shaped, which can move axially but not rotate. One end is provided with a pin, 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 one straight groove to another straight groove in the impact wrench switching groove 811. Drive the impact wrench switch 83 to move axially.

The other end of the impact wrench switching part 83 is bent radially inwardly of the gear case 13 to form a hook, and the hook extends into the ring groove 891 on the clutch part 89 . The clutch part 89 is sleeved outside the second planetary carrier 47, and the casing is annular, and the ring groove 891 is located on its outer peripheral surface. A sliding block 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 planetary carrier 47 is provided with a slide rail 473 matched with the sliding block 893 , so the clutch member 89 always follows the rotation of the second planetary carrier 47 and can move axially relative to the second planetary carrier 47 . A clutch groove 635 matched with the clutch block 895 is provided on the rear end surface of the active impact block 63 . Through 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 is caught in the clutch groove 635 , and in the rear position, the clutch block 895 is disengaged from the clutch groove 635 . The clutch part 89 is driven by the function switching button 17 through the switching ring 81 and the impact wrench switching part 83 to move between the front position and the rear position.

Similarly, the speed switching groove 813 is zigzag and has a stepped shape, consisting of two straight grooves parallel to each other, spaced apart in the axial direction, and a connecting groove between the two straight grooves. The two-ended straight groove is perpendicular to the axis 10 . The housing of the speed switching member 85 is strip-shaped and can move axially but not rotate. One end is provided with a pin, and the pin is located in the speed switching groove 813. Through the matching structure of the pin and the groove, when the switching ring 81 rotates, the pin moves from one straight groove to another straight groove in the speed switching groove 813, driving the speed switching. Member 85 moves axially.

The other end of the speed switching member 85 is bent radially inward of the gear case 13 to form a hook, and the hook extends into the ring groove 533 on the outer peripheral surface of the second ring gear 53 . A spline 531 is also provided on the front end surface of the second inner ring gear 53 , and the spline 531 is matched with the internal spline 775 of the movable end tooth 77 . As mentioned above, the second ring gear 53 has a front position and a rear position, corresponding to two speed outputs respectively. Cooperating with the above structure, the second clutch member 53 is driven by the function switching button 17 through the switching ring 81 and the speed switching member 85 to move between the front position and the rear position.

The screwdriver switching groove 815 is irregular in shape with steps, and has a wide portion and a narrow portion in the circumferential direction, and the front end of the narrow portion is behind the front end of the wide portion in the axial direction. There is a transition portion between the wide portion and the narrow portion. The screwdriver switching part 87 is bar-shaped and can move axially but not rotate. One end has a pin located in the screwdriver switching slot 815, and a spring 871 is provided between this end and the gear case, and the spring 871 drives the screwdriver switching member 87 to abut against the front end of the screwdriver switching slot 813 forward. The other end of the screwdriver switching part 87 is matched with the keyway 771 of the movable end tooth 77 . Through the matching structure of the pin and the groove, when the switching ring 81 rotates, the pin moves from the wide part to the narrow part or from the wide part in the screwdriver switching groove 815, driving the screwdriver switching part 87 to move axially. The screwdriver switching part 87 thus has an axially forward position and a rear position. In the forward position, the end of the screwdriver switching part 87 engages the keyway 771 of the movable end tooth 77, and in the rear position, the end of the screwdriver switching part 87 is disengaged. The keyway 771 of the end tooth 77 . In this way, the rotational movement of the stop toothing 77 can be blocked selectively.

The function switching process of the multi-function drill 1 is described in detail below.

As mentioned above, the multi-function drill 1 can switch between the impact wrench function, the high-speed drill function, the low-speed drill function, and the screwdriver function sequentially in forward or reverse directions. The conversion of these functions is closely related to the front and rear positions of the second ring gear 53, the clutch part 89 and the screwdriver switching part 87. Table 1 shows that in the aforementioned four functional states and the second ring gear 53, the clutch part 89 and the screws The corresponding relationship between the respective positions of the batch switching members 87.

Second ring gear 53 Clutch 89 Screwdriver switch 87 Impact Wrench Features post position post position former position High speed drilling function post position former position former position

Low speed drilling function former position former position former position screwdriver function former position former position post position

Table I

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

As mentioned above, when the second ring gear 53 is at the rear position, it meshes with the sun gear 45 and the second planetary gear 49 at the same time, and the planetary gear reduction system outputs a high speed to the power output system. And at this moment, the spline 531 of the second inner ring gear 53 and the inner spline 775 of the movable end tooth 77 are disengaged from each other, and the second inner ring gear 5 can be driven to rotate by the sun gear 45 . At this time, the screwdriver switching part 87 is in the front position, and its end snaps into the keyway 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 work at this time, it is also possible to set the screwdriver switch 87 in the rear position in this functional state, which will not affect the realization of the impact wrench function.

Under the impact wrench function, the clutch part 89 is in the rear position, that is, the clutch block 895 of the clutch part 89 disengages from the clutch groove 635 of the active impact block 63 .

When the impact wrench function is realized, the rotational motion is output to the main shaft 61 via the second planetary carrier 47. Due to the pressure of the impact spring 65, the active impact block 63 is driven by the rolling ball 67 clamped in the inner V-shaped groove and the outer V-shaped groove 611. As the main shaft 61 rotates, the passive impact block 69 also rotates accordingly, and the working head (not shown) is driven by the working shaft 691 and the collet 9 to quickly tighten the nut (not shown).

When the end surface of the nut is in contact with the surface of the workpiece (not shown), the resistance torque increases rapidly, and when it reaches a certain value, the active impact block 63 and the passive impact block 69 that engage with each other are blocked, and the passive impact block 69 stops rotating, but the main shaft 61 Driven by the output shaft of the motor, it still rotates, forcing the rolling ball 67 to overcome the friction between it and the inner V-shaped groove and the outer V-shaped groove 611 to roll along the groove, thereby pushing the active impact block 63 to move backward, so that the impact spring 65 is driven compression. Thus, 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 , so that the first end tooth 633 slides over the second end tooth 693 of the passive impact block 69. At the moment of sliding, due to the effect of the impact spring 65, the rolling ball 67 returns along the inner V-shaped groove and the outer V-shaped groove 611. In the original position, the active impact block 63 is pushed forward, and at the same time, as the main shaft 61 accelerates to rotate, it impacts the second end tooth 693 of the passive impact block 69, so that the passive impact block 69 continues to move in the direction of rotation, and so on. The parts are tightened under the impact torque.

When the impact wrench function is realized above, the active impact block 63 needs to rotate intermittently to impact the passive impact block 69, so that the working head (tightening head) can tighten the nut, but when the drilling function is realized, that is, the high-speed drilling function and the low-speed drilling function, Only the working head (twist drill) is required to drill continuously, 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 drill function and the working status of the high-speed drill function are described in detail below.

Referring to Fig. 10, Fig. 11 and Fig. 12, as shown in Fig. 13, when switching from the impact wrench function to the high-speed drill function, the rotation of the switching ring 81 drives the displacement of the impact wrench switching groove 811, and the pin of the impact wrench switching part 83 is moved from a straight groove Move to another straight groove, thereby driving the impact wrench switching part 83 to move axially, and then driving the clutch part 89 to move from the rear position to the front position. After the switch is completed, the second ring gear 53 is located at the rear position, the clutch 89 is located at the front position, and the screwdriver switch 87 is located at the front position.

Because the movable end tooth 77 is not active at this time, it is also possible to set the screwdriver switching part 87 to be in the rear position in this functional state, which will not affect the realization of the high-speed drill function.

As previously mentioned, after the clutch 89 is in the front position, its clutch block 895 engages the clutch groove 635 of the active impact block 63, and the transmission route of the rotation output becomes from the second planetary wheel 47 and/or the main shaft 63 to the clutch 89 to the active impact block 63, and then delivered to the working shaft 691 through the passive impact block 69. Specifically, during the drilling process, since the resistance torque received by the working shaft 691 gradually increases, the active impact block 63 tends to move toward the motor 21 . At this time, because the clutch 89 restricts the backward movement of the active impact block 63 in the axial direction, the first end teeth 633 of the active impact block 63 are always in contact with the second end teeth 693 of the passive impact block 69. 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 cannot break away from all the time, that is, no impact can be formed between the two, so the continuous drilling of the working head can be ensured.

In the above-mentioned embodiment, it is particularly important that when realizing the function of high-speed drilling or low-speed drilling, the rotation output by the motor 21 is decelerated, reaches the output end 22 of the deceleration system, and then is transmitted to the active impact block with the clutch 89 as an intermediate piece 63, thus establishing a fixed connection or a rigid connection from the output end of the deceleration system to the active impact block 63 to transmit the rotation; since the main shaft 61 and the output end of the deceleration system are fixedly connected together through interference fit, it can also be said that a The fixed connection of the main shaft 61 and the active impact block 63. In the past, when the power tool is switched from the impact wrench function to the drilling function, it still relies on the groove between the main shaft 61 and the active impact block 63 and the active connection of the ball system to transmit the rotation.

Those skilled in the industry can easily imagine that the clutch member 89 can also be arranged directly on the outer peripheral surface of the main shaft 61 and be slidable along the axial direction of the main shaft 61 . In this embodiment, a part of the clutch 89 is relatively fixedly connected to the main shaft 61 in the direction of rotation, and a part is selectively engaged or disengaged with the active impact block 63 through spline fit, so that it can be used in drilling modes (including high-speed drilling) function and low-speed drilling function) to establish the fixed connection of the main shaft 61 to the active impact block 63, the idea of this embodiment is the same as the aforementioned preferred embodiment of the present invention, and its specific form will not be repeated.

It is also conceivable that the clutch 89 can also be selectively fixedly connected with the active impact block 63 in a form different from the spline fit, and can also be in a form different from the slide rail of the slider and the second planet carrier 47 or the main shaft 61. Rotationally relatively fixed fit, for example, adopt buckle and hole fit, or bump and groove fit to realize the optional fixed connection of clutch part 89 and active impact block 63, adopt spline fit to realize clutch part 89 and the second The cooperation of the planetary carrier 47 or the main shaft 61, etc.

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

As shown in Figure 12, Figure 13 and Figure 14, Figure 15. When switching from the high-speed drilling function to the low-speed drilling function, the rotation of the switching ring 81 drives the displacement of the speed switching groove 813, and moves the pin of the speed switching member 85 from one straight groove to another straight groove, thus driving the speed switching member 85 to move axially. Then it drives the second inner ring gear 53 to move from the rear position to the front position. After the switch is completed, the second ring gear 53 is at the front position, the clutch 89 is at the front position, and the screwdriver switch 87 is at the front position.

As mentioned above, after the second ring gear 53 moves from the rear position to the front position, it disengages from the engagement with the sun gear 45 and still engages with the second planetary gear 49 . At the same time, the spline 531 of the second internal ring gear 53 is engaged with the internal spline 775 of the movable end tooth 77, and at this time, the screwdriver switch 87 is in the front position, and the end of the screwdriver switch 87 snaps into the movable end tooth 775. The key groove 771 prevents the movable end teeth 775 from rotating, thereby preventing the second inner ring gear 53 from rotating.

Through the above-mentioned cooperation method, the multi-function drill 1 is under the low-speed drilling function, and the planetary gear reduction system outputs the lower rotational speed to the power output system through the two-stage reduction as mentioned above, the operation mode of the power output system and the high-speed drilling function are consistent and will not be repeated here.

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

As shown in Figure 14, Figure 15 and Figure 16, Figure 17. When switching from the low-speed drill function to the screwdriver function, the rotation of the switching ring 81 drives the displacement of the screwdriver switching slot 815, and moves the pin of the screwdriver switching part 87 from the wide part to the narrow part, thus driving the screwdriver switching part 87 to move axially to The rear position disengages from the engagement with the movable end tooth 77. After the switch is completed, the second ring gear 53 is at the front position, the clutch 89 is at the front position, and the screwdriver switch 87 is at the rear position.

As mentioned above, the spiral cover 71 presses the post 753 of the stationary tooth 75 through the stud 711 and the torsion spring 73 , wherein the stud 711 , the torsion spring 73 and the stand 753 are arranged in a one-to-one correspondence. The stationary tooth 75 is thus elastically pressed against the movable tooth 77, specifically, the terminal tooth 753 of the stationary tooth 75 and the terminal tooth 773 of the movable tooth 77 are forced to engage together, thereby preventing the movable tooth 77 from rotating. At this time, because the screwdriver switch 87 is disengaged and engaged with the movable end teeth 77, the static end teeth 75 are the only elements that directly prevent the movable end teeth 77 from rotating.

When carrying out the work of screwing, the operator drives the screw cover 71 to move back and forth through the torque cover 13 to adjust the compression amount of the torsion spring 73, that is, to adjust the elastic force applied by the static end teeth 75 to the movable end teeth 77 to set the screwdriver. The maximum output torque of multi-function drill 1 under 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 internal ring gear 53 drives the driving end teeth 77 to rotate against the elastic pressure force, and repeatedly pushes the stationary end teeth 75 to move axially forward, and the end teeth 773 and the end tooth 753 move uphill relative to each other. That is, the movable end teeth 77 can no longer prevent the second ring gear 53 from rotating, so the output of the motor only drives the second ring gear 53 to rotate freely, but cannot drive the second planetary carrier 47 to rotate, and output the rotary motion to the power output system.

The function switching button 17 can also adjust the multi-function drill 1 in the order of screwdriver function, low-speed drill function, high-speed drill function and impact wrench.

Claims (9)

1. a power tool, comprising:

Housing;

Motor, is arranged in housing, has the output shaft that rotation output is provided;

Planetary gear reduction system, rotation output after the rotation output of described output shaft is slowed down;

Power output system, is delivered to working head by the rotation output of planetary gear reduction system;

Function switching button, is contained in housing at least partly, it is characterized in that, described function switching button moves to select the impact wrench function, high speed drill function, low speed of power tool to bore one of them of function, screwdriver function,

Described planetary gear reduction system comprises ring gear, and described ring gear makes planetary gear reduction system export high-revolving primary importance and that planetary gear reduction system is exported between the slow-revving second place is removable;

Described power output system comprises clutch part, and described clutch part is removable between the primary importance of restriction impact wrench function and the second place of permission impact wrench function;

Described function switching button connects spline part, and described spline part is removable between the primary importance of restriction screwdriver function and the second place of permission screwdriver function;

Described function switching button also connects ring gear and clutch part, with impact wrench function, high speed drill function, the low speed of exercisable selection power tool, bores function and screwdriver function.

2. power tool according to claim 1, it is characterized in that, described function switching button has the primary importance being circumferentially arranged in order along housing, the second place, the 3rd position and the 4th position, described function switching button can move to the 4th position successively from primary importance, or move to successively primary importance from the 4th position, when function switching button is positioned at primary importance, power tool is in impact wrench function, described function switching button is positioned at second place power tool in high speed drill function, described function switching button is positioned at the 3rd position power tool and bores function in low speed, described function switching button is positioned at the 4th position power tool in screwdriver function.

3. power tool according to claim 1, it is characterized in that, the selectable primary importance that is positioned at of described function switching button, the second place, the 3rd position and the 4th position, when function switching button is positioned at primary importance, power tool is in impact wrench function, described function switching button is positioned at second place power tool in high speed drill function, described function switching button is positioned at the 3rd position power tool and bores function in low speed, described function switching button is positioned at the 4th position power tool in screwdriver function, described primary importance, the second place, the 3rd position and the 4th position are positioned on the same circumference of housing, it is to the straight line that projects into of horizontal plane.

4. power tool according to claim 1, is characterized in that, when impact wrench function, described clutch part is positioned at the second place; When high speed drill function, described ring gear is positioned at primary importance, and clutch part is positioned at primary importance; When low speed bores function, described ring gear is positioned at the second place, and clutch part is positioned at primary importance, and spline part is positioned at primary importance; When screwdriver function, described ring gear is positioned at the second place, and clutch part is positioned at primary importance, and spline part is positioned at the second place.

5. power tool according to claim 4, is characterized in that, when impact wrench function, described ring gear is positioned at primary importance, and described spline part is positioned at primary importance; When high speed drill function, described spline part is positioned at primary importance.

6. power tool according to claim 1, it is characterized in that, described planetary gear reduction system comprises sun gear and is engaged in the planetary gear of the gear shaft of sun gear, described ring gear engages described sun gear and described planetary gear to export high rotating speed at described primary importance ring gear simultaneously, at second place ring gear, engage described planetary gear, depart from described sun gear with the output slow-speed of revolution.

7. power tool according to claim 1, it is characterized in that, described power output system comprises main shaft, by V-shaped groove spin mechanism, be assemblied in the active impact block on main shaft, described clutch part connects main shaft, with respect to main shaft, can move axially and can not relatively rotate, described clutch part is at active impact block described in described primary importance clamping directly to export the rotation of main shaft to initiatively impact block, and described clutch part departs from described active impact block in the described second place.

8. power tool according to claim 6, is characterized in that, also comprises moved end tooth, engages upwards mutually lock in week when described ring gear is positioned at the second place with described moved end tooth, and described spline part optionally locks the motion that rotates in a circumferential direction of moved end tooth.

9. power tool according to claim 8, it is characterized in that, an end face of described moved end tooth is provided with multiple keyways of circumferential distribution, and described spline part engages described keyway at the end of described primary importance spline part, at the end of described second place spline part, departs from described keyway.

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