CN201040318Y - Flexible wheel driving drill chuck - Google Patents

Abstract

The utility model discloses a flexible wheel drive formula drill chuck, include: the flexible wheel harmonic drive mechanism comprises a drill body, a plurality of clamping jaws, a drive screw nut, a control outer sleeve and a flexible wheel harmonic drive mechanism, wherein the clamping jaws are slidably arranged in an inclined hole of the drill body, and the flexible wheel harmonic drive mechanism is arranged between the drive screw nut and the control outer sleeve. The drill chuck has flexible gear harmonic driving mechanism, and can transmit the rotation torque applied to the outer sleeve of the drill chuck to the screw nut via the elastic deformation gear driving force increasing effect of the flexible gear harmonic law, so that the force of the screw nut driving the clamping jaw and the clamping force of the clamping jaw to the drilling tool are greatly increased compared with those of common drill chucks, the clamping function of the drill chuck to the drilling tool is greatly improved, and the drill chuck is ensured to reliably work under the working conditions of large load and vibration.

Description

Flexible spline driven drill chuck

technical field

The utility model relates to a drill chuck, in particular to a flexwheel driven drill chuck which can provide greater clamping force by utilizing the principle of a flexspline harmonic drive.

Background technique

Existing drill chucks are usually composed of a drill body, jaws, nuts, bearings and jackets. The drill body is connected to the transmission shaft of the power source, and the three jaws are respectively installed in three evenly distributed inclined holes on the drill body. Inside, there are threads on the jaws and form a thread transmission with the nut. When the outer shell connected with the nut is rotated, the jaws can move relative to the drill body along the inclined hole, thereby clamping or loosening the tool handle.

Due to the above structure, the thread between the jaw and the nut produces a large contact stress under the working load, which makes the relative sliding friction force very large, so the clamping tool produced by the thread transmission between the nut and the jaw The clamping force of the shank is not easy to be large enough, which makes the jaws unable to clamp the tool shank firmly under the conditions of heavy load and vibration, and there is a hidden danger of loosening.

In order to improve the clamping performance of the drill chuck and prevent the jaws from loosening during work, a known clamping structure adopts various booster mechanisms to provide greater clamping force.

US Patent No. 5,044,643 published on September 3, 1991 discloses a drill chuck with a cycloidal gear transmission mechanism. Referring to Fig. 39 and Fig. 40, the main sectional view and the sectional view along II-II position of this drill chuck are respectively shown. The drill chuck includes a drill body 41, which has a plurality of oblique holes equally divided along the circumference; a plurality of jaws 42, which are slidably arranged in the oblique holes of the drill body 1, and have threads at the rear end; a transmission screw nut 43 , rotatably sleeved on the outside of the drill body 41, and engaged with the threads of the jaws 42; the control jacket 45 is rotatably sleeved on the outside of the drill body 41, and its outer surface forms a gripping portion to drive the nut 43 provides rotational driving force. A tubular manipulation portion 51 is formed on the control jacket 45, and its outer circumference axis is eccentric “e” relative to the axis of the drill body 1 . It also includes an input/output ring 48 with an internal gear 55 at the rear end, an internal gear 53 at the middle, and an inner peripheral surface at the front end. The inner peripheral surface of the front end is supported on the outer surface of the tubular manipulation portion 51 by a rolling bearing 50 on the circumferential surface. The internal gears 55 and 53, which are eccentric relative to the axis of the drill body, mesh with the external gear 56 of the locking ring 49 with a small number of teeth and the external gear 54 of the transmission screw nut 43 respectively, and in the clamping operation, the pair of transmissions in the jaws 42 Under the axial thrust of the screw nut 43, the pin tightening ring 49 is relatively fixed to the drill body 1. When manipulating the outer casing 45, the input/output ring 48 eccentrically swings around the drill body 1 under the control of the eccentric outer peripheral surface of the tubular manipulating portion 51, so that the internal gears 55 and 53 and the external gears 56 and 54 constantly change the meshing tooth pairs , constitute a cycloidal gear arrangement (cycloidal gear arrangement), so that the input/output ring 48 and the screw nut 43 rotate at a very low speed relative to the control jacket 45, thereby providing increased torque and clamping force.

This kind of drill chuck can provide a large clamping force, but its input/output ring and locking ring and the meshing gear on the transmission nut are rigidly combined, and the tubular operating part of the control sleeve must be eccentrically configured and eccentrically arranged. The error will have an adverse effect on the meshing of the meshing pair and affect the steering effect.

The U.S. patent application US5261679 published on November 16, 1993 also discloses a drill chuck with a cycloidal gear transmission mechanism. The elastic drive sleeve between them, but the booster mechanism itself has not changed.

Utility model content

The purpose of the utility model is to provide a flexwheel-driven drill chuck capable of providing greater clamping force in view of the deficiencies in the prior art.

In order to solve the above technical problems, a flexwheel-driven drill chuck is provided, which includes a drill body with a plurality of oblique holes equally divided along the circumference; a plurality of jaws slidably arranged in the oblique holes of the drill body , the rear end of which has a screw thread; the transmission screw nut is rotatably sleeved on the outside of the drill body, and is threadedly engaged with the jaw; the control sleeve is rotatably sleeved on the outside of the drill body, and its The outer surface forms a gripping portion, which provides rotational driving force to the drive nut; it is characterized in that it also includes a flexspline harmonic drive mechanism, which is arranged between the drive nut and the control sleeve.

According to one aspect of the present invention, the flexspline harmonic transmission mechanism includes: a rigid spline fixed on the drill body and having rigid spline teeth distributed along the outer circumference; a flexspline connected to the nut , and have flexspline teeth distributed along the inner circumference; and a wave generator sleeve, connected to the control outer sleeve, and provided with a wave generator that drives the flexspline to deform and rotate, wherein, when the flexspline deforms, The flexible spline meshes with the rigid spline.

Wherein, the upper part of the flexible spline is fixedly sleeved on the outer surface of the nut.

Wherein, the flexible spline is provided with a long groove extending along the circumferential direction. The long slot is arranged between the part of the flexspline connected with the nut and the part in contact with the wave generator. Preferably, the long grooves include at least two groups of long grooves distributed in parallel along the circumferential direction, and the long grooves of adjacent groups are staggered from each other.

Wherein, the flexible spline further includes a driving groove, which is engaged with the wave generator of the wave generating sleeve. In the first driving stage of the wave generating sleeve, the wave generator is engaged in the driving groove of the flexspline, and in the second driving stage of the wave generating sleeve, the wave generator leaves the driving groove , rotate along the outer surface of the flexspline and apply pressure.

The wave generator is an inner protrusion formed on the inner surface of the wave generating sleeve, and the side surface of the wave generator in contact with the driving groove along the rotation direction forms a slope.

The wave generating sleeve further includes a positioning claw, and the flexible spline further includes a positioning groove, and when the drill chuck is in a clamped state, the positioning claw engages with the positioning groove. The positioning groove may be the driving groove.

Preferably, at least two groups of the wave generator, driving pawl and driving groove are included on the wave generating sleeve and the flexible spline. Each set of wave generators, driving pawls and driving slots on the wave generating sleeve and the flexible spline are staggered along the axial direction of the drill chuck.

The wave generating sleeve is set on the inner side of the control jacket, and a connecting key is arranged on it, and a connecting groove matching the connecting key is arranged on the control jacket.

The wave generating sleeve may be integrally formed with the control housing.

Preferably, the wave generator is a rolling element.

According to another aspect of the present invention, it also includes an intermediate sleeve, which is rotatably sleeved on the outside of the drill body and located behind the control sleeve, and the intermediate sleeve is synchronously connected with the flexible spline.

Wherein, the inner surface of the intermediate sleeve is provided with a driving groove, and the outer surface of the upper end of the flexible spline is provided with a key matching the driving groove.

A shaft coupling is arranged between the nut and the flexspline. The shaft coupling is provided with a first key and a second key, the first key fits with the key groove on the flexspline, and the second key fits with the key groove on the screw nut.

Wherein, it also includes a wire nut sleeve, which is sheathed on the outer surface of the wire nut.

According to another aspect of the present utility model, the flexspline harmonic transmission mechanism includes: a rigid sprocket, sleeved on the drill body, and has rigid spline teeth distributed along the outer circumference. In the first clamping stage, the rigid wheel rotates relative to the drill body in the circumferential direction, and in the second clamping stage of the drill chuck, the rigid wheel is fixed relative to the drill body in the circumferential direction; The nut is connected, and has flexspline teeth distributed along the inner circumference; and a wave generating sleeve, connected with the control jacket, and is provided with a wave generator for deforming and rotating the flexspline, wherein the The flexible gear teeth mesh with the rigid gear teeth.

Among them, it also includes a clutch flower sleeve, which is arranged between the rigid wheel and the wave generating sleeve, and is located at the lower end of the rigid wheel, and is synchronously connected with the rigid wheel, and can be rotated and fixed in the axial direction. slide between them and be releasably connected with the wave generating sleeve. The upper end of the clutch flower sleeve is provided with a transmission key, which is engaged with the transmission key at the lower end of the rigid wheel.

Wherein, it also includes a fixed flower sleeve, which is fixedly arranged on the drill body, and has a clutch tooth groove on it, and a clutch tooth engaged with the clutch tooth groove is provided at the lower end of the clutch flower sleeve.

The fixed flower sleeve includes a friction disc on which the clutch tooth groove is arranged, and the friction disc supports the front flange plane of the control sleeve.

Wherein, a return spring is also included, which is arranged between the inner surface of the front end flange of the control sleeve and the clutch sleeve to support the clutch sleeve. Preferably, the lower surface of the clutch sleeve is formed with an annular groove, and when the return spring is in a fully compressed state, the return spring is accommodated in the annular groove, and the lower surface is in contact with the control sleeve contact with the inner surface of the front flange.

A first positioning groove is formed on the upper surface of the clutch sleeve;

The lower end of the flexible spline is formed with connecting teeth;

Wherein, it also includes a pressure plate, which is arranged between the clutch flower sleeve and the flexspline, on which there are pressure claws matched with the first positioning groove of the clutch flower sleeve and connecting teeth with the flexspline Matching connecting teeth.

The clutch flower sleeve also includes an annular surface, which is located next to the first positioning groove. In the first clamping state of the drill chuck, the pressure claw of the pressure plate engages with the first positioning groove of the clutch flower sleeve. In a positioning groove, in the second clamping state of the drill chuck, the pressure jaw of the pressure plate leaves the first positioning groove, rotates along the annular surface of the clutch flower sleeve and applies pressure, so that the The clutch flower sleeve slides axially from a rotating position to a fixed position.

Wherein, the annular surface of the clutch hub includes a first annular surface and the second annular surface in turn, and the second annular surface is higher than the first annular surface, so that when the pressure claw of the pressure plate is in contact with the When in contact with the second annular surface, the clutch sleeve slides axially downwards and presses against the inner surface of the front end flange of the control sleeve.

Wherein, it also includes a return spring, which is arranged between the inner surface of the front flange of the control sleeve and the clutch sleeve, and the lower surface of the clutch sleeve is formed with an annular groove. When the return spring is fully compressed In a state, the return spring is accommodated in the annular groove.

The clutch sleeve also includes a limiting protrusion located beside the annular surface and higher than the annular surface.

The wave generating sleeve is set on the inner side of the control outer sleeve, and a coupling key and a driving claw are arranged on it, the coupling key is matched with the coupling groove provided on the control outer sleeve, and the driving claw is arranged on the control sleeve. The drive slot on the clutch sleeve fits.

Wherein, it also includes a nut sleeve, the fixed sleeve is arranged outside the nut, and the nut sleeve is keyed to the upper end of the flexspline.

According to another aspect of the present utility model, the clutch sleeve is provided with a drive groove, which is detachably connected with the drive claw provided on the wave generating sleeve. The clutch sleeve also includes a group of second positioning slots distributed along the circumference, located on one side of the drive slot, and selectively engaged with the drive claws of the wave generator sleeve.

The clutch flower sleeve also includes an annular surface, which is located next to the first positioning groove. In the first clamping state of the drill chuck, the pressure claw of the pressure plate engages with the first positioning groove of the clutch flower sleeve. In a positioning groove, in the second clamping state of the drill chuck, the pressure jaw of the pressure plate leaves the first positioning groove, rotates along the annular surface of the clutch flower sleeve and applies pressure, so that the The clutch flower sleeve slides axially from a rotating position to a fixed position.

The clutch flower sleeve is also provided with a limiting protrusion, which is located at the end of the annular surface opposite to the first positioning groove.

Described flexible spline (8 ") is made of nylon or polytetrafluoroethylene.

The drill chuck of the present utility model is provided with a flexwheel harmonic transmission mechanism between the transmission nut (3) and the control jacket (7), so that the rotational moment acting on the drill chuck jacket is transmitted through the flexwheel harmonic The force-increasing effect of the elastic deformation gear transmission of the wave law is transmitted to the screw nut, so that the force of the screw nut driving the jaws and the clamping force of the jaws on the drilling tool are much larger than ordinary drill chucks, which greatly improves the drill chuck. Clamping function for drilling tools.

In the drill chuck of the present utility model, the cooperation of the positioning claw on the wave generating sleeve and the driving groove on the flex spline, the clamping friction of the clutch sleeve and the fixed sleeve on the front flange of the jacket, and the driving of the wave generating sleeve are further adopted. The engagement of claws and the second positioning groove of the fixed sleeve forms an anti-loosening structure, which ensures that the drill chuck can work reliably under heavy load and vibration conditions.

Description of drawings

The above and other objectives and features of the present utility model will become more clear through the description of the preferred embodiments below in conjunction with the accompanying drawings. The same reference numerals are used for the same structural parts, and some parts are omitted in some figures for the sake of clarity. in:

Fig. 1 is a main sectional view of a drill chuck according to a first embodiment of the present invention;

Fig. 2 is a cross-sectional view of the drill chuck in Fig. 1 and Fig. 8 along the direction A-A (state before power-increasing clamping);

Fig. 3 is a cross-sectional view of the drill chuck in Fig. 1 and Fig. 8 along the direction A-A (status during clamping with increased force);

Fig. 4 is the main sectional view of the flexible spline in the first embodiment;

Fig. 5 is a cross-sectional view of the flexible spline in Fig. 4 along B-B direction;

Fig. 6 is a main sectional view of the wave generating sleeve in the first embodiment;

Fig. 7 is a top sectional view of the wave generating sleeve in Fig. 6 along E-E position;

Fig. 8 is a front sectional view of a drill chuck according to a second embodiment of the present invention;

Fig. 9 is a main sectional view of the middle sleeve in the second embodiment;

Figure 10 is a top view of the middle sleeve in Figure 9;

Fig. 11 is the main sectional view of the flexible spline in the second embodiment;

Fig. 12 is a top sectional view of the flexible spline in Fig. 11;

Fig. 13 is the bottom view of the split wire nut in the second embodiment;

Fig. 14 is the main sectional view of the split wire mother in Fig. 13;

Fig. 15 is a front sectional view of a shaft coupling in a second embodiment;

Figure 16 is a top view of the shaft coupling in Figure 15;

Figure 17 is a top view of the coat;

Fig. 18 is a main sectional view of the overcoat in Fig. 17;

Fig. 19 is a front partial sectional view of the drill chuck along the direction C-C in Fig. 20 according to the third and fourth embodiments of the present utility model;

Fig. 20 is a sectional view of the drill chuck in Fig. 19 along the D-D direction;

Fig. 21 is a main sectional view of the wave generating sleeve in the third embodiment;

Fig. 22 is a top view of the wave generating sleeve in Fig. 21;

Fig. 23 is a main sectional view of the flexible spline in the third embodiment;

Fig. 24 is a top view of the flexible spline of Fig. 23;

Fig. 25 is a front sectional view of the clutch flower sleeve in the third embodiment;

Fig. 26 is a top view of the clutch flower sleeve in Fig. 25;

Fig. 27 is a front sectional view of the pressure plate in the third embodiment;

Figure 28 is a top view of the platen in Figure 27;

Fig. 29 is the bottom view of the rigid wheel in the third embodiment;

Fig. 30 is the main sectional view of the rigid wheel in Fig. 29;

Fig. 31 is the front view of the thread female sleeve in the third embodiment;

Fig. 32 is the top view of the thread female sleeve in Fig. 31;

Fig. 33 is a front sectional view of the fixed faceplate in the third embodiment;

Figure 34 is a top view of the fixed faceplate in Figure 33;

Fig. 35 is a front sectional view of a clutch sleeve in a drill chuck according to a fourth embodiment of the present invention;

Figure 36 is a top view of the clutch flower sleeve in Figure 35;

Fig. 37 is a front sectional view of the wave generating sleeve in the fourth embodiment;

Fig. 38 is a top view of the wave generating sleeve in Fig. 37;

Fig. 39 is a main sectional view of a drill chuck in the prior art;

FIG. 40 is a cross-sectional view of the prior art drill chuck of FIG. 39. FIG.

Description of part number in the figure

1 - drill body;

2 - jaws;

3——Split wire mother, 32——Drive groove;

4——Bearing assembly;

5——Bearing washer;

6——back cover;

7——overcoat, 75——coupling groove, 76——end face;

8—flex spline, 81—flexible gear, 82, 83—drive slot, 85—groove, 8', 8”—flex spline, 86—groove, 87—key, 88—coupling tooth ;

9, 9’——wave generating sleeve, 91, 93——positioning claw, 92, 94——wave generator, 95——coupling key, 96——driving claw, 96’——elastic driving claw;

10, 10'——steel wheel, 101——steel gear teeth, 102——transmission key;

12 - front cover;

13——Positioning circlip;

15—middle sleeve, 157—drive groove;

16—coupling, 162—key, 166—key;

17'——Silk female sleeve;

18——clutch sleeve, 181——positioning slot, 182——turning key, 183——annular surface, 184——clutch tooth, 185——annular raised surface, 186——drive groove, 187——limit Protrusion, 188 ---locating groove;

19——pressure plate, 191——pressure jaw, 198——coupling teeth;

20——fixed sleeve, 201——friction disc, 204——clutch tooth groove;

21—elastic claw;

41——drill body; 42——jaw; 43——drive nut; 45——control jacket;

48—input/output ring; 49—lock ring; 50—rolling bearing; 51—tubular control part; 53—internal gear; 54—external gear; 55—internal gear; 56—outer gear.

Detailed ways

Below in conjunction with accompanying drawing, describe the specific embodiment of the utility model in detail. In the description, relative to the drill chuck itself, the direction where the tool shank is located is referred to as "front", and the direction where the drive shaft of the power source is located is referred to as "rear". When describing in conjunction with the accompanying drawings, "front" is generally also referred to as "bottom", and "rear" is generally also referred to as "rear". Except for otherwise special instructions or circumstances that obviously cannot be understood according to the instructions.

The utility model transmits the rotational moment acting on the jacket of the drill chuck to the screw nut through the boosting effect of the elastic deformation gear transmission of the flexwheel harmonic law, so that the force of the screw nut driving the clamping jaw and the impact of the clamping jaw on the drilling tool The clamping force of the drill chuck is much larger than that of the ordinary drill chuck, which greatly improves the clamping function of the drill chuck to the drilling tool.

first embodiment

Referring to Fig. 1-3, it shows the main sectional view and the top sectional view along the A-A direction of the drill chuck according to the first embodiment of the present utility model.

The drill chuck includes a drill body 1, a plurality of jaws 2, a screw nut 3, a rear cover 6, a jacket 7, a front cover 12, and the like.

The drill body 1 is located at the center of the drill chuck, its rear end is connected to the transmission shaft of the power source through a threaded hole or a tapered hole, and its front end forms an accommodating space for clamping the tool handle. The drill body 1 has a plurality of inclined holes evenly distributed around the central axis of the drill body.

A plurality of jaws 2 are respectively installed in a plurality of inclined holes of the drill body 1, the rear end of the jaws 2 has an incomplete external thread, and the front end has a clamping part, which can be approximately polygonal, for Grip tool handle.

The screw nut 3 may be a split screw nut, which is rotatably sleeved outside the drill body 1 and engaged with the external thread of the jaw 2 to drive the jaw 2 to advance and retreat along the inclined hole. The rear end of the screw nut 3 and the drill body 1 are supported by the thrust boss on the drill body 1 through the bearing assembly 4 . A bearing washer 5 is also arranged between the bearing assembly 4 and the thrust surface of the thrust boss.

The rear cover 6 is fixedly arranged on the rear end of the drill body 1, and the rear cover 6 can be connected with the drill body rear end by holes and fasteners, or by a key, or can be connected by a tight fit. The peripheral edge of the rear cover 6 extends forward to form a grip when operating the drill chuck.

An annular groove is formed on the outer surface of the front end of the drill body 1, in which an open retaining ring 13 is assembled. The front cover 12 is sleeved around the front end of the drill body and is supported by an opening retaining ring 13 .

The control jacket 7 is rotatably sleeved around the drill body 1 and is positioned in front of the rear cover 6. Its rear end is supported by the rear cover 6, and the middle part is supported by internal components arranged between it and the drill body 1. The front end is formed with a The radially inwardly extending flange is stopped by the front cover 12 to prevent forward movement. The outer surface of the control jacket 7 forms a gripping portion, which provides rotational driving force to the transmission nut 3 through an internal mechanism.

A flexspline harmonic drive mechanism is arranged between the transmission nut 3 and the control jacket 7 . The flexspline harmonic transmission mechanism includes a rigid spline 10, a flexspline 8 and a wave generating sleeve 9.

The rigid wheel 10 is fixedly sleeved on the outer surface of the drill body 1 and has rigid wheel teeth 101 distributed along the outer circumference. The rigid wheel 10 can be fixed on the drill body 1 by means of tight fit, key connection, etc., or it can be integrally formed on the drill body 1, for example, the corresponding rigid wheel teeth 101 are directly formed on the corresponding parts of the drill body 1, thereby forming the entire body. Describe rigid wheel 10.

Referring to FIG. 4 and FIG. 5 in conjunction, a main sectional view of the flexspline 8 and a top sectional view along BB are respectively shown. The flexible spline 8 is in the shape of a sleeve, and the upper end is fixedly sleeved on the outer surface of the nut 3 to drive the nut 3 to rotate. The lower end has flexspline teeth 81 distributed along the inner circumference to match the teeth of the rigid spline 10. 101 engagement. This flexible spline 8 plays the effect of silk female sleeve simultaneously. It can be seen from the figure that the flexible spline 8 is also provided with driving grooves 82 and 83 respectively.

Referring to FIG. 6 and FIG. 7 in conjunction, a main sectional view of the wave generator sleeve 9 and a top sectional view along E-E are respectively shown. The wave generating sleeve 9 is sleeved inside the control jacket 7 and is fixedly connected with the control jacket 7 . The inner surface of the front end of the control jacket 7 has a coupling groove 75 (see FIGS. 17 and 18 ), and the lower end of the wave generating sleeve 9 is formed with a coupling key 95 . When the outer sleeve 7 is rotated, the wave generating sleeve 9 rotates synchronously through the connection between the coupling groove 75 and the coupling key 95 . Of course, the wave generator sleeve 9 and the control jacket 7 can also be fixedly connected in other ways, such as tight fit. Optionally, the wave generator sleeve 9 and the control jacket 7 can also be integrally formed.

In addition, the wave generating sleeve 9 is also provided with wave generators 92 and 94 for cooperating with the drive slots 82 and 83 on the flexspline 8 to drive the flexspline 8 to rotate and deform. In the first driving stage of the wave generating sleeve 9, the wave generators 92, 94 are engaged in the driving grooves 82, 83 of the flex spline 8, and in the second driving stage of the wave generating sleeve 9, the wave generators 92, 94 leave the driving groove 82, 83, rotate along the outer surface of the flexible spline 8 and apply pressure. When the flexible spline 8 deforms, the gear teeth 81 mesh with the rigid gear teeth 101 .

It can be seen from FIG. 6 and FIG. 7 that in this embodiment, the wave generators 92 and 94 are radially inward protrusions. The inner protrusion as a wave generator can be formed on the inner surface of the wave generating sleeve 9 by shearing and punching. If the wave generator is formed by injection molding, the inner protrusion can also be integrally formed on the body of the wave generator sleeve. In this embodiment, both sides of the inner protrusion along the circumferential direction are sloped, but as an optional implementation, it is also possible to only make the inner protrusion contact with the driving grooves 82, 83 along the rotational direction. The sides form slopes.

The wave generating sleeve 9 also includes two positioning claws 91 , 93 , and the positioning claws 91 , 93 can engage with the drive slots 82 , 83 on the flex spline 8 when the drill chuck is in a clamped state. The function of the positioning claws 91 and 93 on the wave generating sleeve 9 is to keep the wave generating sleeve 9 and the flexible spline 8 relatively still after clamping, so as to avoid the reverse relative rotation under the condition of vibration and impact, which may cause the drilling tool to move from the clamping jaws. loose in the middle. In this embodiment, this function is realized by engaging the positioning claws 91, 93 with the drive grooves 82, 83. The drive grooves 82, 83 not only play a driving role, but also play a role of positioning and preventing loosening at the clamping position. In addition, additional positioning grooves or teeth can be provided on the flexible spline 8 to engage with the positioning claws 91, 93 to realize the positioning and anti-loosening effect.

In addition, as can be seen from FIGS. 4 and 5 , two groups of long slots 85 arranged in parallel extend along the circumferential direction on the flexible spline 8 . The long groove 85 is located between the part on the flexspline 8 connected with the nut 3 and the parts in contact with the wave generators 92 and 94 . The effect of long groove is to make the flexibility of flexspline 8 better, also can not have. The adjacent long grooves in the two groups of long grooves are staggered from each other, as shown in FIG. 4 .

In this embodiment, the wave generating sleeve 9 and the flexible spline 8 include at least two groups of wave generators 92 , 94 , driving claws 91 , 93 , and driving grooves 82 , 83 . These two groups of wave generators, driving and driving slots are staggered by 180 degrees along the circumferential direction, and also staggered by a distance D along the axial direction of the drill chuck. Due to the axial staggering, it is ensured that the wave generators and driving pawls in the same group can have a larger circumferential clamping angle relative to the driving grooves in this group, and will not cause engagement with the driving grooves in another group.

In order to reduce the contact friction between the wave generators 92, 94 and the flexible wheel 8 when the drill chuck is working, optionally, the wave generators 92, 94 can also be rolling bodies, such as balls or rollers, which are rotatably arranged on the wave On the body of the sleeve, it can roll on the outer surface of the flexible spline during work.

The working principle of this embodiment is described below.

When the outer sleeve 7 is rotated, the wave generating sleeve 9 rotates synchronously through the connection between the coupling groove 75 and the coupling key 95 . The wave generators 92, 94 on the wave generating sleeve 9 are respectively engaged with the driving grooves 82, 83 of the flexspline 8, and the flexspline 8 is fixedly connected with the nut 3, so turning the overcoat 7 makes the nut 3 rotate synchronously. When the outer casing 7 is rotated in the clamping direction, the screw nut 3 drives the three jaws 2 to move forward. At this time, the drill chuck is in the first clamping stage until the drilling tool is clamped.

Then, turning the overcoat 7 with force can make the clamping jaws 2 gradually increase the clamping force on the drilling tool. When a certain limit value is reached, the force of the wave generators 92, 94 forces the flexible spline to elastically deform, and the wave generators 92, 94 force the flexible spline to deform elastically. 94 overcomes the elastic deformation force and the frictional resistance of flexspline, deviates from drive groove 82,83, butts on the local outer surface of flexspline, presses flexspline and continues to deform into approximately ellipse, its tooth 81 and rigid spline (with The circumferential fixed connection of the drill body) gear teeth 101 enter into engagement, and at this time, enter the second clamping stage of the drill chuck. Continue to rotate the overcoat 7 to make the wave generators 92, 94 move on the surface of the flexspline, forcing the flexspline to deform continuously, and the gear teeth of its flexspline gear teeth 81 and the rigid gear teeth constantly change the meshing teeth pair until the rotation stops.

The tooth modulus of the flexible spline and the rigid spline are the same, but the number of teeth is different. If the number of teeth of the rigid spline is m, and the number of teeth of the flexible spline is n more than that of the rigid spline, then the number of flexible spline teeth is m+n, and the wave generators 92 and 94 are The process of wheel surface movement is the process of forcing the teeth of the flex spline to mesh with the teeth of the rigid spline. When the wave generators 92 and 94 rotate on the surface of the flexible spline relative to the rigid spline for a full circle, the m teeth of the flexible spline are meshed with the m teeth of the rigid spline, and the n extra teeth of the flexible spline are already relatively rigid. The wheel moves forward by the rotation angle β corresponding to n teeth. Therefore, when the wave generating sleeve rotates 360 degrees, the flexible spline turns over the angle β, and the transmission ratio between the wave generating sleeve 9 and the flexible spline 8 is i=360°/β=m/ n, if the tooth number of rigid gear is m=30, and the tooth number of flexible gear is m+n=33, then i=m/n=10.

It can be seen from the transmission ratio that this structure makes the rotation of the screw nut 3 much slower than that of the outer sleeve 7 and the wave generating sleeve 9 during the clamping process, ignoring the influence of the friction between the wave generator and the flex spline and the meshing gear teeth, It can be considered that the work done by the torque of the rotating overcoat 7 is approximately all transformed into the work done by the nuts to overcome the resistance torque. Let T be the moment acting on the jacket 7, and T1 be the moment received by the nut, then T×360≈T1β, T1/T≈360/β=m/n=i, thus explaining the moment T applied to the jacket 7 Transferred to the nut 3 becomes T1≈Ti, that is, it is approximately magnified by i times, so this clamping process has an obvious force-increasing effect. Compared with ordinary drill chucks, the same torque is applied to the jacket. The utility model The structure makes the clamping force of the jaws on the drilling tool approximately i times that of the common drill chuck.

The loosening process of the drill chuck in this embodiment is opposite to the above process.

second embodiment

The difference between the second embodiment and the first embodiment is that an intermediate sleeve 15 is added to the drill chuck, and the two stages of clamping can be performed by manipulating the intermediate sleeve and the outer sleeve respectively. For the sake of brevity, repeated descriptions are omitted.

8 is a front sectional view of a drill chuck according to a second embodiment of the present invention. It can be seen from the figure that in this embodiment, an intermediate sleeve 15 is added. 9 and 10 respectively show the main sectional view and top view of the intermediate sleeve. Referring to FIGS. 9 and 10 in conjunction, the middle sleeve 15 is rotatably sleeved on the outside of the drill body 1 and located between the rear cover 6 and the control housing 7 . The inner surface of the intermediate sleeve 15 is provided with a driving groove 157 .

Figure 11 and Figure 12 show the main sectional view and the top sectional view of flexspline 8'. As can be seen from the figure, the outer surface of the upper end of the flexible spline 8' is provided with a key 87 that cooperates with the driving groove 157, and a corresponding groove 86 is formed on the inner surface. The middle part of flexspline 8' forms drive slot 82, and the inner surface of the lower end forms flexspline teeth 81. Through the engagement of the key 87 and the driving groove 157, the intermediate sleeve 15 is connected with the flexible spline 8' synchronously.

Fig. 13 and Fig. 14 show the bottom view and the main sectional view of the split nut 3. A keyway 32 is formed on the lower end surface of the nut 3 .

Referring to Fig. 1 again, the outer surface of the nut 3 is also fixedly sleeved with a nut sleeve 17, and a shaft coupling 16 is also arranged between the nut 3 and the flexible spline 8'.

FIG. 15 is a front sectional view and a plan view of the shaft coupling 16 . As shown in the figure, the shaft coupling 16 is provided with a key 166 and a key 162, the key 166 cooperates with the keyway 86 on the aforementioned flexspline 8', and the key 162 cooperates with the keyway 32 on the aforementioned screw nut 3, whereby the wire The female 3 is connected synchronously with the flexible spline 8'.

Figures 17 and 18 show a top view and a front sectional view of the jacket, respectively. The flange formed by bending the lower end of the jacket 17 has a plurality of connecting grooves 75 for connecting with the connecting keys 95 of the wave generating sleeve 9 .

In this second embodiment, since the driving groove 157 of the intermediate sleeve 15 is connected with the key 87 of the flexspline 8', the groove 86 of the flexspline 8' is connected with the key 166 of the shaft coupling 16, and the key 162 of the shaft coupling 16 It is connected with the driving slot 32 of the split screw nut 3, so that the middle sleeve 15, the flexible spline 8' and the screw nut 3 rotate synchronously.

In the first stage of clamping, the hand rotates the middle sleeve 15 and the overcoat 7 at the same time, or only the middle sleeve 15 is rotated, so that the screw nut can be rotated to drive the jaws to move forward. In addition, because the coupling groove 75 of the control jacket 7 is connected with the coupling key 95 of the wave generating sleeve 9, and the wave generators 92, 94 of the wave generating sleeve 9 are engaged with the drive grooves 82, 83 of the flexible spline 8', therefore, manually Rotating the control overcoat 7 also can make the screw nut rotate, and drives the jaws to move forward.

In the second stage of clamping, only the outer sleeve 7 is rotated to drive the wave generating sleeve 9 to rotate, and the process is the same as that of the first embodiment.

Those skilled in the art will know that, where permitted, the different components of the synchronous coupling can be made into an integral part. For example, the shaft coupling 16 can be integrated with the nut sleeve 17, the flexspline 8' can be integrated with the middle sleeve 15, the shaft coupling 16 can be integrated with the flexspline 8', or the control outer sleeve 7 can be integrated with the wave generator sleeve 9. made into one, etc.

third embodiment

The third embodiment of the present utility model is introduced below, and repeated descriptions are omitted for the sake of brevity.

Referring to FIG. 19 and FIG. 20 , it shows a main sectional view and a top sectional view along the D-D direction of a drill chuck according to a third embodiment of the present invention. The flexspline harmonic transmission mechanism provided inside the drill chuck includes a rigid spline 10', a flexspline 8" and a wave generating sleeve 9, and also includes a clutch sleeve 18, a fixed sleeve 20, and a pressure plate 19.

The rigid wheel 10' is slidably sleeved on the drill body 1, and has rigid wheel teeth 101 distributed along the outer circumference. Referring to Fig. 29 and Fig. 30 in combination, it shows a bottom view and a main sectional view of the rigid wheel 10'. It can be seen that the outer surface of the rigid wheel 10' forms rigid wheel teeth 101, and the lower end forms four transmission keys 102 evenly distributed.

The clutch sleeve 18 is rotatably and slidably sleeved on the drill body 1, and is connected between the rigid wheel 10' and the wave generating sleeve 9' and between the rigid wheel 10' and the fixed sleeve 20.

Referring to FIG. 25 and FIG. 26 in conjunction, it shows a main sectional view and a top view of the clutch flower sleeve 18 . The upper end of the clutch sleeve 18 is provided with a transmission key 182, which is synchronously connected with the transmission key 102 at the lower end of the rigid wheel 10'; the lower part extends radially to form a roughly disc-shaped structure, and the periphery of the disc-shaped structure forms a radial notch-shaped driving groove 186, It engages with the drive pawl 96 (described below) on the wave generating sleeve 9 ′; the lower end extends downward to form a clutch tooth 184 engaged with the clutch tooth groove 204 (described below) of the fixed flower sleeve 20 . The clutch sleeve 18 can slide up and down in the axial direction. When sliding to the upper position, it will be disengaged from the clutch tooth groove 204 of the fixed sleeve 20 and can rotate. The tooth groove 204 is fixedly connected, and cannot rotate because the fixed flower sleeve 20 is fixedly arranged on the drill body 1 . In addition, the clutch sleeve 18 also includes a first positioning groove 181 .

The fixed sleeve 20 is fixedly arranged on the drill body 1 and has a clutch tooth groove 204 thereon. Referring to Fig. 33 and Fig. 34, the main sectional view and top view of the fixed flower sleeve 20 are shown respectively. The fixed sleeve 20 includes a radially extending friction disc 201 , on which a clutch tooth groove 204 is disposed, and the friction disc 201 supports the front plane of the control sleeve 7 .

Referring to Fig. 23 and Fig. 24, it shows the main sectional view and top view of the flexspline 8". The inner surface of the upper end of the flexspline 8" forms a plurality of evenly distributed key grooves 86, and the inner surface of the lower end forms evenly distributed flexspline teeth 81, and the lower end of the flexspline 8" It extends downwards to form a plurality of evenly distributed coupling teeth 88 .

The keyway 86 of the flexspline 8" is connected to the nut sleeve 17'. The nut sleeve 17' is fixedly set outside the nut (3). Figures 31 and 32 show the main sectional view and the nut sleeve 17'. From the top view, it can be seen that the lower end of the nut sleeve 17' forms a key 166 extending radially outwards to cooperate with the key groove 86 at the upper end of the flexspline (8') to form a key connection. The flexspline 8" passes through the nut sleeve 17' and connected to the silk mother 3.

Referring to Fig. 21 and Fig. 22, it shows the front view and the top view of the wave generating sleeve 9', wherein, the lower end of the wave generating sleeve 9' is provided with a connecting key 95, which is connected with the control jacket 7 (which has a corresponding keyway 75); And the driving pawl 96 has inclined surfaces formed on both sides, which are connected with the driving slot 186 on the clutch sleeve 18 . The inner surface of the middle part of the wave generating sleeve 9' forms a wave generator 92 through shearing and punching deformation inwardly, so as to deform and rotate the flexspline 8", so that the flexspline teeth 81 mesh with the rigid spline teeth 101.

Different from the first and second embodiments, in this embodiment, the flexspline 8" is not provided with a driving groove combined with the wave generator 92 of the wave generating sleeve 9, and the two wave generators 92 are always connected with the flexspline 8". contact pressure on the outer surface.

Referring to Fig. 1 again, a return spring 21 is also included between the inner surface of the front end flange of the control overcoat 7 and the clutch flower cover 18, for supporting the clutch flower cover 18 and making it reset upwards.

In order to accommodate the return spring 21 , an annular groove is formed on the lower surface of the clutch sleeve 18 . Back-moving spring 21 can all be accommodated in the annular groove under fully compressed state, does not prevent the lower surface of described clutch sleeve 18 from contacting with the inner surface of the front end flange of control overcoat 7 and applying pressure and providing friction (hereinafter A detailed description).

The downward sliding of clutch flower sleeve 18 is realized by pressure plate 19. The pressure plate 19 is arranged between the clutch flower sleeve 18 and the flexible spline 8”. FIG. 27 and FIG. 28 show the main sectional view and the top view of the pressure plate 19. Cooperate with the first positioning groove 181 on the top; and the connecting teeth 198 are used to cooperate with the connecting teeth 88 of the flexible spline 8".

Correspondingly, the side of the first positioning groove 181 on the clutch hub 18 includes annular surfaces 183 , 185 . In the first clamping state of the drill chuck, the pressure claw 191 of the pressure plate 19 is engaged in the first positioning groove 181 of the clutch sleeve 18, and in the second clamping state of the drill chuck, the pressure jaw 191 of the pressure plate 19 The pawl 191 leaves the first positioning groove 181, rotates along the annular surfaces 183, 185 of the clutch flower sleeve 18 and exerts pressure downward, so that the clutch flower sleeve 18 slides axially downward, from the rotating position to the fixed position.

Therefore, by virtue of the synchronous connection between the rigid wheel 10' and the clutch sleeve 18, it can be realized that in the first clamping stage of the drill chuck, the rigid wheel 10' rotates relative to the drill body 1 along the circumferential direction, and in the second clamping stage of the drill chuck In the tight stage, the rigid wheel 10' is fixed relative to the drill body 1 along the circumferential direction.

25 and 26, it can be seen that the annular surface of the clutch sleeve 18 includes a first annular surface 183 and a second annular surface 185, the second annular surface 185 is higher than the first annular surface 183, and is a raised annular surface. In this way, when the pressing claw 191 of the pressure plate 19 contacts the second annular surface 185, the clutch sleeve 18 slides axially downwards and presses on the inner surface of the front end flange of the control sleeve 7, so that the front end flange is pressed Clamped between the clutch flower sleeve 18 and the friction disc 201 of the fixed flower sleeve 20, the movement of the outer sleeve 7 along the circumferential direction is limited and controlled by the friction force, so as to realize the anti-loosening. The clutch flower sleeve 18 resets by the back-moving spring 21.

The clutch sleeve 18 also includes a limiting protrusion 187 located beside the annular surface and higher than the annular surface. Prevent the pressing claw 21 of the pressure plate 19 from falling into the first positioning groove 181 again when sliding along the second annular surface (protruding annular surface) during the clamping process, so that the frictional anti-loosening effect becomes invalid.

In this embodiment, the inclined surface of the driving groove 186 of the clutch flower sleeve 18 is arranged on the side along the clamping direction. The driving groove 186 may not be provided with inclined surfaces on both sides along the circumferential direction, and of course, inclined surfaces may also be provided on both sides.

The wave generator 92 of the wave generating sleeve 9' in this embodiment can also be a rolling body, such as a ball or a roller.

The working principle of the third embodiment is described below.

In the state where the jaws are not clamped to the drilling tool (the jaws are not subjected to resistance), when the outer cover 7 is rotated, it passes between the keyway 75 of the outer cover 7 and the key 95 of the wave generating sleeve 9', and between the key 95 of the wave generating sleeve 9'. Between the driving pawl 96 and the driving groove 186 of the clutch hub 18, between the positioning groove 181 of the clutch hub 18 and the pressure claw 191 of the pressure plate 19, between the transmission key 182 of the clutch hub 18 and the transmission key of the rigid wheel 10' 102, and the connection between the coupling tooth 198 of the pressure plate 19 and the coupling tooth 88 of the flexspline 8", the wave generating sleeve 9', the nut 3 and the nut sleeve 17', the clutch sleeve 18, and the pressure plate 19. The rigid wheel 10' and the flexible wheel 8" rotate synchronously with the outer cover 7. This is the first clamping stage of the drill chuck of the third embodiment.

When the jaw clamps the drilling tool and encounters resistance, the nut sleeve 17' and the flexible spline 8" also receive resistance. At this time, if the outer casing 7 continues to be rotated, the driving claw 96 of the wave generator sleeve 9' will move along the clutch sleeve. The inclined plane movement of the drive groove 186 of 18 disengages from the engagement with the groove 186, and presses the clutch flower sleeve 18 to overcome the elastic support force of the elastic member 21 to move axially forward, so that the clutch teeth 184 and the fixed flower sleeve 20 (with the drill Body fixed connection) clutch tooth groove 204 is connected, and the transmission key 182 of the clutch flower cover 18 is still connected with the transmission key 102 of the rigid wheel 10' at this moment, so the rigid wheel 10' and the clutch flower cover 18 are not connected with the fixed faceplate 20. The relative motion in the circumferential direction, that is, there is no relative rotation with the drill body 1; in this state, when the outer casing 7 is rotated again, only the wave generators 92 and 94 of the wave generating sleeve 9' will drive the flex spline 8" to decelerate Rotate and drive the pressure plate 19 to rotate relative to the rigid wheel 10' and the drill body 1. As the clutch flower cover 18 moves forward, the pressure pawl 191 of the pressure plate is released from the positioning groove 181 of the clutch flower cover, and the pressure claw 191 slides on the annular surface 183 with the relative rotation of the two parts, and presses the clutch flower cover 18 all the time. Be in the position that its clutch tooth 184 is connected with the clutch tooth groove 204, and this state has entered the power-increasing clamping state; along with continuing to rotate the outer cover, the clamping force of the jaws to the drilling tool is also constantly increased. The flexible spline 8" is driven by the wave generator 92, and the pressure claw 191 continues to slide on the annular surface 183. The pressure of the claw 191 on the raised surface 185 will cause the clutch sleeve 18 to apply a certain pressure to the end face (i.e. the front end flange) 76 of the outer cover 7, and the other side of the end face 76 is supported by the fixed sleeve friction disc 201, and at this time the rotation Overcoat 7, overcoat 7 will be subjected to the effect of the relatively large friction torque produced between the clutch sleeve 18 and friction disc 201 and its end face 76, and a relatively large torque must be applied to make the overcoat 7 rotate relative to the drill body 1, and the effect is to vibrate Under the impact state, it is not easy to produce reverse relative rotation between the outer cover 7 and the drill body 1, thereby maintaining the reliability of clamping the drilling tool. When the pressure claw 191 of the pressure plate 19 enters and slides to the end along the raised annular surface 185, it is limited The position protrusion 187 stops and limits. This is the second clamping stage of the drill chuck of the third embodiment.

Fourth embodiment

The drill chuck according to the fourth embodiment can also be referred to Fig. 19 and Fig. 20 , and its difference from the third embodiment is that the engagement of the elastic driving pawl 96' with the second positioning groove 188 is used to achieve the anti-loosening purpose.

Figures 35 and 36 show a front view and a top view of the clutch flower sleeve 18' in the fourth embodiment. The difference between this clutch flower cover 18' and the clutch flower cover 18 of the third embodiment shown in FIGS. The second positioning groove 188 is located on one side of the driving groove 186 along the clamping direction, and is selectively engaged with the driving claw 96' of the wave generating sleeve 9'.

Correspondingly, only the first annular surface 183 is located next to the first positioning groove 181 on the clutch flower sleeve 18'. In the first clamping state of the drill chuck, the pressure claw 191 of the pressure plate 19 is engaged in the first positioning groove 181 of the clutch flower sleeve 18 ′, and in the second clamping state of the drill chuck, the pressure plate 19 The pressing pawl 191 leaves the first positioning groove 181 , rotates along the annular surface 183 of the clutch flower sleeve 18 and exerts pressure, so that the clutch flower sleeve 18 slides axially from the rotating position to the fixed position. The clutch sleeve 18' is also provided with a limiting protrusion 187, which is located at the opposite end of the annular surface 183 to the first positioning groove 181.

Figure 37 and Figure 78 show the main sectional view and top view of the wave generator sleeve 9' in the drill chuck of the fourth embodiment. Wherein the shape of the driving pawl 96' is suitable for engaging with the second positioning groove 188.

In order to disengage the driving pawl 96' of the wave generating sleeve 9' from the driving groove 186 of the clutch flower sleeve 18', the driving groove 186 forms an inclined plane along one side of the clamping direction. In the same way, for the convenience of the pressure claw 191 of the pressure plate 19 to disengage from the first positioning groove 181 of the clutch flower sleeve 18', one side of the first positioning groove 181 along the clamping direction forms a slope.

Because in the second clamping stage of the drill chuck, the driving claw 96' of the wave generator sleeve 9' is constantly changing the second positioning groove 188 to be engaged during the clamping process, which ensures stable engagement after the clamping is completed. In a positioning groove 188, it can effectively prevent the drill chuck from loosening due to shock and vibration during operation.

In various embodiments of the present utility model, flexsplines 8, 8' and 8 " are all preferably made of flexible materials, such as nylon or polytetrafluoroethylene. Wave generators 92 and 94 can be made of The rolling element installed at the same position on the wave generating sleeve replaces it.

Although the preferred embodiment of the invention has been disclosed for descriptive purposes, those skilled in the art will understand that various modifications and variations of the invention are possible. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present utility model shall be included in the protection scope of the present utility model.

Claims (12)

1. A flex wheel driven drill chuck, comprising: Drill body (1), wherein has a plurality of oblique holes equally divided along the circumference; A plurality of jaws (2) are slidably arranged in the inclined hole of the drill body (1), and the rear end thereof has threads; A transmission nut (3), rotatably sleeved on the outside of the drill body (1), and threadedly engaged with the jaws; The control jacket (7) is rotatably sleeved on the outside of the drill body (1), and its outer surface forms a gripping portion to provide rotational driving force to the transmission nut (3); It is characterized in that it also includes a flexspline harmonic transmission mechanism, which is arranged between the transmission nut (3) and the control jacket (7). 2. The flexspline-driven drill chuck according to claim 1, wherein the flexspline harmonic transmission mechanism comprises: The steel wheel (10) is fixedly arranged on the drill body (1), and has steel wheel teeth (101) distributed along the circumference; Flexsplines (8, 8') are connected to the nut (3) and have flexspline teeth (81) distributed along the circumference; and The wave generating sleeve (9) is driven by the control sleeve (7), and the wave generator (92, 94) that drives the deformation and rotation of the flexible spline (8, 8') is arranged on it, Wherein, when the flexspline deforms, the flexspline teeth (81) mesh with the rigid spline teeth (101). 3. The flexspline-driven drill chuck according to claim 2, characterized in that, the upper part of the flexspline (8) is fixedly sleeved on the outer surface of the nut (3), and the flexspline (8) (8) also includes driving slots (82, 83) engaged with the wave generators (92, 94) of the wave generating sleeve (9). 4. The flexible spline driven drill chuck according to claim 3, characterized in that, the wave generators (92, 94) are inner protrusions formed on the inner surface of the wave generating sleeve (9), Its side faces in contact with the drive grooves (82, 83) in the direction of rotation form inclined surfaces. 5. The flexible spline driven drill chuck according to claim 2, characterized in that it also includes an intermediate sleeve (15), which is rotatably sleeved on the outside of the drill body (1) and located at the control The back of the jacket (7), the middle sleeve (15) is synchronously connected with the flexspline (8'), the inner surface of the middle sleeve (15) is provided with a driving groove (157), and the flexspline (8 ') The outer surface of the upper end is provided with a key (87) that cooperates with the drive groove (157). 6. The flexspline-driven drill chuck according to claim 1, wherein the flexspline harmonic transmission mechanism comprises: The rigid wheel (10') is sheathed on the drill body (1) and has rigid wheel teeth (101) distributed along the outer circumference. In the first clamping stage of the drill chuck, the rigid wheel Rotate relative to the drill body in the circumferential direction. In the second clamping stage of the drill chuck, the rigid wheel is fixed relative to the drill body in the circumferential direction; the flexible wheel (8"), and the nut ( 3) connected, and have flexible gear teeth (81) distributed along the inner circumference; and The wave generator sleeve (9') is connected with the control jacket (7), and is provided with a wave generator (92) that deforms and rotates the flexible spline (8"), Wherein, the flex gear teeth (81) mesh with the rigid gear teeth (101). 7. The flexible spline driven drill chuck according to claim 6, further comprising: The clutch flower sleeve (18, 18') is located at the lower end of the rigid wheel (10'), is synchronously connected with the rigid wheel (10'), and can slide between the rotating position and the fixed position in the axial direction, and It is detachably connected with the wave generating sleeve (9'), and the upper end of the clutch flower sleeve (18, 18') is provided with a transmission key (182), which is connected with the transmission key (182) at the lower end of the rigid wheel (10'). 102) join; The fixed flower sleeve (20), fixedly arranged on the drill body (1), has a clutch tooth groove (204) on it, and the lower end of the clutch flower sleeve (18, 18') is provided with the clutch tooth groove. (204) engaged clutch teeth (184); The fixed flower sleeve (20) includes a friction disc (201), the clutch tooth groove (204) is arranged on the friction disc (201), and the friction disc (201) supports the control sleeve (7 ) of the front end flange plane; also includes a return spring (21), which is arranged between the inner surface of the front end flange of the control jacket (7) and the clutch flower cover (18), and supports the clutch flower cover (18 , 18'); The lower surface of the clutch sleeve (18, 18') is formed with an annular groove, and when the return spring (21) is in a fully compressed state, the return spring (21) is accommodated in the annular groove, and The lower surface is in contact with the inner surface of the front flange of the control jacket (7). 8. The flexible spline driven drill chuck according to claim 7, characterized in that: A first positioning groove (181) is formed on the upper surface of the clutch flower sleeve (18, 18'); The lower end of the flexible spline (8") is formed with connecting teeth (88); It also includes a pressure plate (19), which is arranged between the clutch flower sleeve (18, 18') and the flexible spline (8"), on which there is a connection with the clutch flower sleeve (18, 18'). The first positioning groove (181) cooperates with the pressing claw (191) and the connecting tooth (198) that cooperates with the connecting tooth (88) of the flexspline (8"). 9. The flexible spline driven drill chuck according to claim 8, characterized in that, the clutch sleeve (18, 18') further includes an annular surface (183, 185), which is located in the first positioning groove (181), in the first clamping state of the drill chuck, the pressure claw (191) of the pressure plate (19) engages in the first positioning groove of the clutch hub (18, 18') (181), in the second clamping state of the drill chuck, the pressure claw (191) of the pressure plate (19) leaves the first positioning groove (181), and moves along the clutch sleeve ( 18, 18') the annular surface (183, 185) rotates and exerts pressure, so that the clutch flower cover (18, 18') slides from the rotating position to the fixed position in the axial direction; the clutch flower cover (18) The annular surface comprises in turn a first annular surface (183) and said second annular surface (185), said second annular surface (185) being higher than said first annular surface (183), so that when said pressure plate ( 19) when the pressure pawl (191) is in contact with the second annular surface (185), the clutch sleeve (18) slides axially downward and presses on the front end of the control sleeve (7) on the inner surface of the flange. 10. The flexible spline driven drill chuck according to claim 9, characterized in that, the clutch sleeve (18) further comprises a limit protrusion located beside the annular surface and higher than the annular surface (187). 11. The flexible spline driven drill chuck according to claim 8, characterized in that, the clutch sleeve (18, 18') is provided with a drive groove (186), which is connected to the wave generator sleeve (9' ) provided on the driving pawl (96') can be detachably connected; the clutch sleeve (18') also includes a group of second positioning grooves (188) distributed along the circumference, located in the driving groove (186) One side selectively engages with the driving pawl (96') of the wave generating sleeve (9'). 12. The flex spline driven drill chuck according to any one of claims 1 to 11, characterized in that, the wave generator (92) on the wave generating sleeve (9, 9') is a rolling element.

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