CN219188726U

CN219188726U - Impact electric drill

Info

Publication number: CN219188726U
Application number: CN202222230674.3U
Authority: CN
Inventors: 张建芳
Original assignee: Jiangsu Dartek Technology Co Ltd
Current assignee: Jiangsu Dartek Technology Co Ltd
Priority date: 2022-08-24
Filing date: 2022-08-24
Publication date: 2023-06-16
Anticipated expiration: 2032-08-24

Abstract

The present application relates to an impact electric drill; the technical proposal comprises: a gear case housing; an output shaft at least partially disposed within the gearbox housing; a reduction mechanism at least partially disposed in the gearbox housing and transmitting power to the output shaft; the torsion mechanism comprises a torsion cup, a spring seat, a torsion spring and a clutch assembly, wherein the torsion cup is rotationally connected to the gear box shell, the spring seat is in threaded connection with the torsion cup, the torsion spring is compressed when the torsion cup rotates, and the clutch assembly is abutted by the torsion spring; the impact mechanism comprises a first cam capable of axially sliding in the gear box shell, a second cam arranged on the output shaft and an elastic piece; a yielding gap is formed in the gear box shell, and is positioned at one side of the first cam far away from the second cam when the first cam is separated from the second cam; the first cam is connected in the yielding clearance in a sliding way through an elastic piece. Therefore, the problem of hard extrusion of the second cam and the first cam in the impact mechanism is solved, and the service life of the impact electric drill is prolonged.

Description

Impact electric drill

Technical Field

The application relates to the technical field of tools, in particular to an impact electric drill.

Background

With the development of the technique of impact electric drills, impact drills have appeared which are used to drill holes in a workpiece, typically with an impact mechanism, so that the drill bit has an impact effect.

In the related art, chinese patent publication No. CN101143440A discloses an impact electric drill, which specifically comprises a gear box shell; a motor; an output shaft which is rotated by driving the motor, protrudes in an axial direction so as to be capable of fine movement in a forward-backward direction, and has a tool bit insertion hole at a front end thereof; a vibration mechanism provided in the gear case and configured to impart vibration in an axial direction to the output shaft at a position where the output shaft retreats; a pressing member provided in the output shaft so as to be movable in a radial direction thereof; and a chuck sleeve provided at a front end of the output shaft so as to be movable forward and backward in an axial direction by a predetermined stroke, and loaded at a sliding position in either a forward or backward direction by a loading device, wherein the pressing member is pressed toward an axial center side of the output shaft at the sliding position, a tool bit inserted into the insertion hole is fixed in a lockable manner, a loading direction of the loading device to the chuck sleeve is set to a rear direction, and the chuck sleeve is brought into contact with the gear case side by a sliding caused by the loading to the rear direction, whereby the output shaft can be loaded at the forward position by the loading device.

However, when the front end of the output shaft generates smaller resistance, in the current impact mechanism, the impact teeth between the two cams still generate hard extrusion to cause rotary friction, and at the moment, the engagement position of the two cams generates a large amount of heat to cause abrasion of the impact teeth on the cams, so that the service life of the impact electric drill is reduced.

Disclosure of Invention

Accordingly, it is necessary to provide an impact electric drill against the problem of shortening the service life of the impact electric drill.

In order to solve the technical problems, the application is realized as follows:

in one embodiment, there is provided an impact electric drill comprising:

a gear case housing;

an output shaft at least partially disposed within the gearbox housing;

a reduction mechanism at least partially disposed in the gearbox housing and transmitting power to the output shaft;

the torsion mechanism comprises a torsion cup, a spring seat, a torsion spring and a clutch assembly, wherein the torsion cup is rotationally connected to the gear box shell, the spring seat is in threaded connection with the torsion cup, the torsion spring is compressed when the torsion cup rotates, and the clutch assembly is abutted by the torsion spring;

the impact mechanism comprises a first cam capable of sliding axially in the gear box shell, a second cam arranged on the output shaft and an elastic piece, wherein a first punching tooth is arranged on one surface of the first cam, a second punching tooth is arranged on one surface of the second cam, and the first punching tooth and the second punching tooth are oppositely arranged; a yielding gap is formed in the gear box shell, and is positioned at one side of the first cam far away from the second cam when the first cam is separated from the second cam; the first cam is connected in the yielding clearance in a sliding way through an elastic piece.

Optionally, a non-rotatable supporting frame is arranged inside the gear box shell, the elastic piece is configured in the supporting frame, the first cam axially slides in the supporting frame, and the supporting frame is provided with a through hole for the output shaft to pass through.

Optionally, the supporting frame lateral wall is provided with spacing lug, gear box shell inner wall is equipped with the anti-rotation recess that supplies spacing lug to insert.

Optionally, one, two or more elastic pieces are provided, and a supporting hole for inserting the elastic piece is formed in the surface of the gear box shell or the supporting frame facing the first cam; and/or the surface of the gear box shell or the supporting frame facing the first cam is provided with a supporting rod penetrating through the elastic piece, and an avoidance part for inserting the supporting rod is arranged around the first cam.

Optionally, a limiting piece is arranged on the supporting frame or the gear box shell, and after the first cam is assembled into the supporting frame or the gear box shell, one side of the first cam facing the second cam is contacted with or abutted against the limiting piece.

Optionally, still be equipped with gearshift in the gear box shell, gearshift includes setting up the retainer plate on the output shaft and setting up the butt piece on carriage or gear box shell, the lateral wall of retainer plate is provided with the locating piece, when the retainer plate rotates on the output shaft, the locating piece can offset with the butt piece in order to restrict the removal of output shaft in length direction.

Optionally, the output shaft is provided with an abutting piece and an elastic resetting piece abutting against the abutting piece, and the elastic resetting piece is compressed when the output shaft receives axial resistance.

Optionally, the movable distance of the abutment is greater than or equal to the maximum distance that the second cam is movable in the direction of the first cam.

Optionally, a positioning piece is arranged on the output shaft, and a limiting part which can be propped against the positioning piece to limit the position of the propping piece is arranged in the gearbox shell; when the positioning piece is propped against the limiting plate, the difference value between the movable distance of the propping piece and the movable maximum distance of the first cam is larger than or equal to the tooth height of the second punching tooth or the first punching tooth.

Optionally, the clutch assembly includes butt ball, butt round pin and gasket, the reduction gears includes an annular gear, one side of annular gear towards torsion cup is provided with the lug, butt ball butt is in the ring gear one side surface towards torsion cup, butt round pin one end and butt ball, the other end and gasket are in the butt, one side that the butt round pin was kept away from to the gasket is in the butt with torsion spring.

In the embodiment of the application, the first punching teeth on the first cam in the impact mechanism can push the first cam to move and compress the elastic piece along with the rotation of the output shaft when being meshed with the second punching teeth on the second cam, and the impact fixing plate can provide impact for the first cam when the first cam is disengaged from the second cam, so that impact output of the output shaft is realized. The elastic piece provides a buffer for the movement of the first cam, so that hard extrusion between the second cam and the first cam is not caused, and the problems of abrasion, heating and service life reduction caused by hard extrusion of the first cam and the second cam are relieved.

Drawings

Fig. 1 is a schematic view showing the overall structure of an impact electric drill according to an embodiment of the present application;

fig. 2 is a schematic view of an exploded structure of an impact drill according to an embodiment of the present application;

FIG. 3 is an enlarged schematic view of the structure at A in FIG. 1;

FIG. 4 is a schematic view of a supporting frame according to an embodiment of the present disclosure;

FIG. 5 is a schematic view of a structure of a rotation stopping groove and a limiting bump according to an embodiment of the present disclosure;

fig. 6 is a schematic view showing the overall structure of an impact electric drill according to another embodiment of the present application;

FIG. 7 is an enlarged schematic view of the structure at B in FIG. 6;

fig. 8 is a schematic view showing the overall structure of an impact drill according to another embodiment of the present utility model at another angle.

Description of the drawings: 1. a gear case housing; 11. a rotation stopping groove; 12. a limit baffle; 2. an output shaft; 21. a positioning ring; 211. a positioning block; 22. an abutment; 23. an elastic reset piece; 24. a positioning piece; 3. a speed reducing mechanism; 31. an inner gear ring; 311. a bump; 4. an impact mechanism; 41. a first cam; 411. a first tooth punching; 42. a second cam; 421. a second tooth punching; 43. an elastic member; 5. a support frame; 50. a limit bump; 51. a bearing chamber; 52. a boss; 521. a support hole; 53. a limit groove; 531. a limiting piece; 54. an abutment block; 6. a torsion mechanism; 61. a torque cup; 62. a spring seat; 63. a torsion spring; 64. a clutch assembly; 641. abutting the ball; 632. an abutment pin; 643. a gasket.

Detailed Description

In order to make the above objects, features and advantages of the present application more comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is, however, susceptible of embodiment in many other forms than those described herein and similar modifications can be made by those skilled in the art without departing from the spirit of the application, and therefore the application is not to be limited to the specific embodiments disclosed below.

In the description of the present application, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," etc. indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be configured and operated in a particular orientation, and therefore should not be construed as limiting the present application.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless explicitly defined otherwise.

In this application, unless specifically stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

In this application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

It will be understood that when an element is referred to as being "fixed" or "disposed" on another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are used herein for illustrative purposes only and are not meant to be the only embodiment.

Referring to fig. 1, fig. 1 shows the overall structure of an impact electric drill according to an embodiment of the present application, which includes a motor, a housing, a gear case housing 1, an output shaft 2, a reduction mechanism 3, and an impact mechanism 4. The gear case housing 1 may be configured to be integrally formed with the housing of the impact electric drill, or may be configured to be assembled with the housing of the impact electric drill in a discrete structure. The output shaft 2 is disposed at one end of the gear case housing 1 and partially disposed in the gear case housing 1, and the reduction mechanism 3 may include a planetary gear set for use in an impact electric drill, and the reduction mechanism 3 in the present embodiment may include a three-stage reduction planetary gear mechanism, although a two-stage reduction planetary gear mechanism may be employed as long as power transmission and reduction can be achieved. The reduction mechanism 3 is partially arranged in the gear box shell 1, and power output by the motor is reduced by the reduction mechanism 3 and then transmitted to the output shaft 2. The two ends of the output shaft 2 are supported by bearings, and the inner rings of the bearings can be in clearance fit with the output shaft 2 so that the output shaft 2 can move along the axial direction.

Referring to fig. 2, fig. 2 shows an explosion structure of the impact electric drill in an embodiment of the present application, the impact mechanism 4 includes a first cam 41, a second cam 42, and an elastic member 43, the first cam 41 is formed with a first punching tooth 411 on one face, the second cam 42 is formed with a second punching tooth 421 on one face, the first cam 41 is fixed on the output shaft 2, and the first cam 41 is disposed in the gear housing 1 and is capable of sliding in the axial direction of the output shaft 2 and is incapable of rotating circumferentially with respect to the axial center of the output shaft 2. After the first cam 41 is assembled, the first punching teeth 411 on the first cam 41 are disposed opposite to the second punching teeth 421 on the second cam 42.

Referring to fig. 2 and 3, fig. 3 shows a structure of the first cam and the second cam in an embodiment of the present application, in an initial state, the first cam 41 is separated from the second cam 42, and a gap is reserved between the first punch tooth 411 and the second punch tooth 421, so that the first punch tooth 411 and the second punch tooth 421 cannot be meshed; at this time, a yielding gap is formed on the side of the gear case housing 1, which is far away from the second cam 42, of the first cam 41, and the first cam 41 can slide in the yielding gap through the elastic member 43 as a yielding space for moving the first cam 41.

When the output shaft 2 is axially moved by the axial load, the second cam 42 moves toward the first cam 41, and at this time, the second punch tooth 421 is engaged with the first punch tooth 411, and when the second punch tooth 421 rotates with the output shaft 2, the first cam 41 pushes the first cam 41 to compress the elastic member 43 under the engagement of the first punch tooth 411 and the second punch tooth 421. When the first punching tooth 411 and the second punching tooth 421 are disengaged, the first cam 41 is reset under the elastic force of the elastic member 43, and impacts the second cam 42, so that the axial movement of the first punching tooth 411 is realized, and continuous vibration is given to the output shaft 2. The elastic member 43 may be a spring, a wave washer, or a rubber block, as long as it is compressed by the first cam 41 and provides a restoring elastic force to the first cam 41.

In addition, when the output shaft 2 moves until the first cam 41 abuts against the gear case housing 1 or the bearing, at this time, the first cam 41 cannot be retracted, and in this operating state, the first cam 41 can be continuously engaged with and disengaged from the second cam 42, so that continuous vibration can be provided to the output shaft 2. At this time, only the first cam 41 is in a state of not being retreated, and the first punching teeth 411 on the first cam 41 and/or the second punching teeth 421 on the second cam 42 may be gradually worn. It will be appreciated, of course, that whether the first cam 41 is in the retracted state or not is determined by the distance of movement of the output shaft 2, i.e. freely selectable by the operator in dependence on the operating conditions.

Referring to fig. 4 and 5, fig. 4 shows the structure of the supporting frame 5 in an embodiment of the present application, and fig. 5 shows the structure of the stopping groove 11 and the limiting bump 50 in an embodiment of the present application, in a specific implementation manner, the supporting frame 5 is slidably connected in the gear case housing 1, the limiting bump 50 is formed on the outer side wall of the supporting frame 5, the stopping groove 11 is formed in the gear case housing 1, and the limiting bump 50 and the stopping groove 11 cooperate to realize that the supporting frame 5 is slidably connected in the gear case housing 1 in a non-rotatable manner. The supporting frame 5 is provided with a through hole for the output shaft 2 to penetrate through so as to facilitate the installation of the output shaft 2. The supporting frame 5 can be arranged separately from the gear case shell 1 and fixed through assembly, or can be fixed in a mode of insert-molding the supporting frame 5 in the gear case shell 1; of course, the support frame 5 and the gear case 1 may be integrally formed, and when the support frame 5 and the gear case 1 are integrally formed, the rotation of the support frame 5 is stopped without the cooperation of the stop projection 50 and the rotation stopping groove 11.

The support frame 5 may be internally bulged toward the center to form a bearing chamber 51 for facilitating mounting of a bearing in clearance fit with the output shaft 2. Of course, the bearing may be mounted in the gear case housing 1 as long as the output shaft 2 can be supported. In addition, the supporting frame 5 may further be formed with a boss 52 protruding toward the center, and the boss 52 may be higher than the end surface of the bearing, or may be lower than or equal to the end surface of the bearing, and may be disposed as required. The boss 52 may have a support hole 521 formed thereon, and the elastic member 43 is disposed in the support hole 521 such that the elastic member 43 is stably compressed.

It can be understood that the supporting rod may be disposed on the boss 52 for fixing the elastic member 43, the elastic member 43 is sleeved on the supporting rod, and an avoidance portion is formed around the first cam 41 for inserting the supporting rod, and the height of the supporting rod is equal to the depth of the avoidance portion, so that the first cam 41 can abut against the bearing outer ring or the boss 52. Of course, a combination of the supporting hole 521 and the supporting rod may be adopted, which will not be described herein, as long as the elastic member 43 can be stably fixed, so that the elastic member 43 is stably compressed. The number of the elastic members 43 may be one, two or even more, and the avoiding portion and/or the supporting rod may be one, two or even more corresponding to the elastic members 43.

Referring to fig. 2 and 3, in order to enable the first cam 41 to be separated from the second cam 42 when needed, a limiting groove 53 is correspondingly formed in a side of the support frame 5 away from the reduction mechanism 3, and a limiting piece 531 is embedded in the limiting groove 53. When the first cam 41 is fitted into the support frame 5, the shoulder portion of the first cam 41 facing the side of the second cam 42 is in contact with or abuts against the stopper 531 at this time. The limiting member 531 may be a snap spring, and is clamped in the limiting groove 53 after the first cam 41 is installed in the supporting frame 5. Of course, a block that slides in the limit groove 53 may be used, so that the block is retracted into the limit groove 53 when the first cam 41 is mounted, and then extends out of the limit groove 53 after the first cam 41 is mounted, thereby limiting the first cam 41. Further, when the first cam 41 is mounted in the supporting frame 5, the elastic member 43 is compressed, and the elastic member 43 is pre-pressed during the back striking of the first cam 41, so that the applied force is large, and therefore, in this embodiment, it is preferable to limit the first cam 41 in this way.

Of course, it is contemplated that the support frame 5 may be integrally formed with the gear case housing 1 or insert-molded, and therefore, the limiting groove 53 and the limiting piece 531 may be disposed in the gear case housing 1, as long as the position of the first cam 41 can be limited so that the first cam 41 is separated from the second cam 42 when the output shaft 2 is not axially moved.

Referring to fig. 1 and 2, in addition, in order to expand the functions of the impact electric drill, so that the impact electric drill can have both functions of electric drill and impact, a gear shifting mechanism is further configured in the gear case shell 1, and the gear shifting mechanism comprises a positioning ring 21 and an abutting block 54, and the positioning ring 21 is sleeved on the output shaft 2 in a clearance fit manner. The output shaft 2 is also tightly provided with a supporting bearing, the edge of the positioning ring 21 is abutted against the supporting bearing, the outer side wall of the positioning ring 21 is provided with a positioning block 211, and the abutting block 54 can be formed at the end part of the supporting frame 5. When the positioning ring 21 rotates circumferentially relative to the axis of the output shaft 2, the positioning block 211 can abut against the abutting block 54, so that the movement of the output shaft 2 along the axial direction is limited, and at the moment, the output shaft 2 can only realize the function of an electric drill; when the positioning block 211 is offset from the abutment block 54, the output shaft 2 can move in the axial direction, and therefore the output shaft 2 can perform the function of impact.

In another embodiment, the abutment block 54 may be formed inside the gear case housing 1, so long as the positioning block 211 can abut against the abutment block 54 to restrict the axial movement of the output shaft 2 when the positioning ring 21 can be rotated circumferentially with respect to the axial center of the output shaft 2.

Optionally, considering that the output shaft 2 needs to be reset when being switched from the impact gear to the electric drill gear, correspondingly, an abutting piece 22 is formed on the output shaft 2, an elastic reset piece 23 is arranged between the abutting piece 22 and a bearing at one end of the output shaft 2 far away from the speed reducing mechanism 3, one end of the elastic reset piece 23 abuts against the abutting piece 22, and the other end abuts against an inner ring of the bearing; the elastic restoring member 23 may be a spring. When the output shaft 2 is positioned at the electric drill gear, the elastic reset piece 23 is in a natural state; after the output shaft 2 is shifted to the impact range, when the output shaft 2 receives an axial resistance force, the elastic restoring member 23 is compressed, and restores the output shaft 2 after the resistance force is removed.

In one embodiment, considering that a space is reserved between the second cam 42 and the first cam 41, this space is to separate the second cam 42 from the first cam 41 when the output shaft 2 is in the electric drill position; therefore, the movable distance of the abutment 22 is equal to or greater than the maximum distance that the second cam 42 moves toward the first cam 41 toward the second cam 42 in the axial direction of the output shaft 2. Considering the original length of the elastic restoring member 23 after compression, the deformation amount of the elastic restoring member 23 is equal to or greater than the maximum distance that the second cam 42 can move toward the first cam 41, so that the elastic restoring member 23 can still make the first cam 41 abut against the bearing or the gearbox housing 1 after the maximum compression.

Referring to fig. 6 and 7, fig. 6 shows the overall structure of an impact drill according to another embodiment of the present application; in another embodiment, the positioning member 24 is formed on the output shaft 2, and the positioning member 24 may be fixed to the output shaft 2 or may be integrally formed on the output shaft 2. Of course, the positioning member 24 may be fixed to the output shaft 2 by other structures, and may be fixed in position in the axial direction of the output shaft 2. The inside of the gear case shell 1 is provided with a limiting part, and the positioning piece 24 can prop against the limiting part in the axial movement process of the output shaft 2, so that the axial movement position of the output shaft 2 is limited. In order to save the internal structure of the gear box shell, a loose bearing inner ring which is close to one end of the speed reducing mechanism 3 on the output shaft can be used as a limiting part; of course, the inner ring of the bearing at the end of the output shaft away from the reduction mechanism 3 may be loosely fitted as a limiting portion, and the position of the positioning member 24 may be adjusted. Of course, it is understood that the limiting portion may have other structures at other positions inside the gearbox housing, and the position of the positioning member 24 may be adaptively adjusted, so long as the axial movement of the output shaft 2 can be limited.

When the positioning member 24 abuts against the limiting plate, the difference between the movable distance of the abutment member 22 and the maximum distance that the first cam 41 moves toward the first cam 41 in the axial direction of the output shaft 2 is greater than or equal to the tooth height of the first punch tooth 411 or the second punch tooth 421. Preferably, the first punch tooth 411 and the second punch tooth 421 may be the same, and at this time, when the first punch tooth 411 and the second punch tooth 421 are meshed, the second punch tooth 421 still has a tooth height of a receding space, so that the first punch tooth 411 does not abut against the bearing or the gear case shell 1 to cause hard extrusion of the first punch tooth 411 and the second punch tooth 421. If the first punching teeth 411 are different from the second punching teeth 421, the reserved distance is only required to be greater than or equal to the smaller tooth height of the second punching teeth 421 or the first punching teeth 411.

In addition, in view of the need to adjust the output torque of the impact drill, the impact drill further includes a torque mechanism 6, and referring to fig. 8, fig. 8 shows the overall structure of the impact drill in another embodiment of the present application. Wherein, torsion mechanism 6 includes torsion cup 61, spring holder 62, torsion spring 63 and clutch pack 64, and gearbox housing 1 keeps away from the one end tip of motor can be connected with limit baffle 12, and torsion cup 61 one end is abutted on limit baffle 12's surface. One side of the torsion cup 61, which is away from the limit baffle 12, is opened, and one end of the torsion cup 61, which is away from the limit baffle 12, is provided with threads on the inner wall and can be in threaded connection with the spring seat 62. The spring seat 62 may be sleeved on the gear case housing 1, and may move along the length direction of the gear case housing 1 as the torsion cup 61 rotates. One side of the spring seat 62, which is away from the limit baffle 12, abuts against the torsion spring 63, and the other end of the torsion spring 63 abuts against the clutch assembly 64, so that elastic force for limiting tripping is provided for the clutch assembly 64. Of course, it is understood that the spring seat 62 may be integrally formed with the gear case housing 1, and at this time, the torsion cup 61 is screwed with the spring seat 62 against the torsion spring 63, so that the torsion spring 63 is contracted.

The planetary gear set of the reduction mechanism 3 at least comprises an inner gear ring 31, and the inner gear ring 31 is positioned at one side of the limiting frame, which is away from the limiting baffle 12. The inner gear ring 31 is formed with a protrusion on a side surface facing the limit stop 12, and both sides of the protrusion may be inclined so that the side surface of the boss 52 forms an approximate triangle. The clutch assembly 64 includes an abutment ball 641, an abutment pin 632, and a washer 643, and the abutment ball 641 and the abutment pin 632 may be disposed inside the gear case housing 1. The abutting ball 641 may be disposed on one side surface of the ring gear 31 facing the limit stop 12, one end of the abutting pin 632 abuts against the abutting ball 641, the other end is disposed on the surface of the washer 643, and the other side surface of the washer 643 may abut against the torsion spring 63. The force of the torsion spring 63 when compressed is applied to the abutting pin 632 and the abutting ball 641 through the washer 643, thereby restricting the abutting force of the abutting ball 641 and the bump 311. At this time, the torsion cup 61 is abutted against the limit baffle 12, and when the torsion cup 61 is rotated, the torsion cup 61 is in threaded connection with the spring seat 62 to drive the spring seat 62 to move along the axial direction of the gear case housing 1, so that the torsion force required to be overcome by the abutment ball 641 passing the bump 311 is adjusted.

The working principle of the impact electric drill in the embodiment of the application is as follows:

when the impact electric drill is switched to the impact gear, the operator pushes the output shaft 2 against the position to be perforated, and at this time, the output shaft 2 is slightly retracted under the stress state, so that the second punching teeth 421 on the second cam 42 are engaged with the first punching teeth 411 on the first cam 41. At this time, the output shaft 2 will force the first cam 41 to retract and compress the elastic member 43 in the rotating process, when the second punching tooth 421 on the second cam 42 is disengaged from the first punching tooth 411 on the first cam 41, the first cam 41 resets under the elastic force of the elastic member 43 and impacts the second cam 42, so that the vibration can be continuously generated on the output shaft 2, and the problems of abrasion, heat generation and life reduction of the second punching tooth 421 and/or the first punching tooth 411 caused by hard extrusion between the first cam 41 and the second cam 42 are effectively alleviated.

The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.

The above examples only represent a few embodiments of the present application, which are described in more detail and are not to be construed as limiting the scope of the claims. It should be noted that it would be apparent to those skilled in the art that various modifications and improvements could be made without departing from the spirit of the present application, which would be within the scope of the present application. Accordingly, the scope of protection of the present application is to be determined by the claims appended hereto.

Claims

1. An impact electric drill, comprising:

a gear case housing;

an output shaft at least partially disposed within the gearbox housing;

2. An impact electric drill as claimed in claim 1, wherein a non-rotatable support frame is provided inside the gear housing, the resilient member being arranged in the support frame, the first cam being axially slidable in the support frame, the support frame being provided with a through hole through which the output shaft passes.

3. An impact electric drill according to claim 2, wherein the outer side wall of the support frame is provided with a limit projection, and the inner wall of the gear case housing is provided with a rotation-stopping groove into which the limit projection is inserted.

4. An impact electric drill according to claim 2, wherein the number of the elastic members is one, two or more, and the surface of the gear case housing or the supporting frame facing the first cam is provided with a supporting hole for inserting the elastic member; and/or the surface of the gear box shell or the supporting frame facing the first cam is provided with a supporting rod penetrating through the elastic piece, and an avoidance part for inserting the supporting rod is arranged around the first cam.

5. An impact electric drill according to claim 2, wherein the support frame or the gear housing is provided with a stopper, and after the first cam is fitted into the support frame or the gear housing, a side of the first cam facing the second cam is brought into contact with or against the stopper.

6. An impact electric drill according to claim 2, wherein a gear shifting mechanism is further provided in the gear case housing, the gear shifting mechanism including a positioning ring provided on the output shaft and an abutment block provided on the support frame or the gear case housing, the outer side wall of the positioning ring being provided with a positioning block capable of abutting against the abutment block to restrict movement of the output shaft in the longitudinal direction when the positioning ring rotates on the output shaft.

7. An impact electric drill according to claim 1, wherein the output shaft is provided with an abutment member and a resilient return member against the abutment member, the resilient return member being compressed when the output shaft is subjected to axial resistance.

8. An impact electric drill according to claim 7, wherein the movable distance of the abutment is equal to or greater than the maximum distance that the second cam is movable in the direction of the first cam.

9. The impact electric drill according to claim 7, wherein the output shaft is provided with a positioning member, and a limiting portion capable of abutting against the positioning member to limit the position of the abutting member is provided inside the gear case; when the positioning piece is propped against the limiting plate, the difference value between the movable distance of the propping piece and the movable maximum distance of the first cam is larger than or equal to the tooth height of the second punching tooth or the first punching tooth.

10. An impact electric drill as claimed in claim 1, wherein the clutch assembly comprises an abutment ball, an abutment pin and a spacer, the reduction mechanism comprises an annular gear, a projection is provided on a side of the annular gear facing the torsion cup, the abutment ball abuts against a surface of a side of the annular gear facing the torsion cup, one end of the abutment pin abuts against the abutment ball, the other end abuts against the spacer, and a side of the spacer away from the abutment pin abuts against the torsion spring.